U.S. patent application number 10/105436 was filed with the patent office on 2002-08-08 for plate reduction press apparatus and methods.
This patent application is currently assigned to Ishikawajima-Harima Heavy Industries Co., Ltd.. Invention is credited to Dodo, Yasushi, Fujii, Yasuhiro, Ide, Kenichi, Ikemune, Shozo, Imai, Isao, Masuda, Sadakazu, Motoyashiki, Yoichi, Murata, Satoshi, Narushima, Shigeki, Obata, Toshihiko, Sato, Hisashi, Sato, Kazuyuki, Sekine, Hiroshi, Tazoe, Nobuhiro, Yamashina, Shuichi, Yokoyama, Takashi.
Application Number | 20020104356 10/105436 |
Document ID | / |
Family ID | 27585680 |
Filed Date | 2002-08-08 |
United States Patent
Application |
20020104356 |
Kind Code |
A1 |
Narushima, Shigeki ; et
al. |
August 8, 2002 |
Plate reduction press apparatus and methods
Abstract
A material 1 to be shaped is reduced and formed by bringing dies
with convex forming surfaces, when viewed from the side of the
transfer line of the material 1, close to the transfer line from
above and below the material 1, in synchronism with each other,
while giving the dies a swinging motion in such a manner that the
portions of the forming surfaces of the dies, in contact with the
material 1, are transferred from the upstream to the downstream
side in the direction of the transfer line.
Inventors: |
Narushima, Shigeki;
(Yokosuka-shi, JP) ; Ide, Kenichi; (Yokohama-shi,
JP) ; Dodo, Yasushi; (Kouza-gun, JP) ; Sato,
Kazuyuki; (Yokohama-shi, JP) ; Tazoe, Nobuhiro;
(Yokohama-shi, JP) ; Sato, Hisashi; (Yokohama-shi,
JP) ; Fujii, Yasuhiro; (Yokohama-shi, JP) ;
Imai, Isao; (Fujisawa-shi, JP) ; Obata,
Toshihiko; (Yokohama-shi, JP) ; Masuda, Sadakazu;
(Chiyoda-ku, JP) ; Yamashina, Shuichi;
(Chiyoda-ku, JP) ; Ikemune, Shozo; (Chiyoda-ku,
JP) ; Murata, Satoshi; (Chiyoda-ku, JP) ;
Yokoyama, Takashi; (Tokyo, JP) ; Sekine, Hiroshi;
(Chiyoda-ku, JP) ; Motoyashiki, Yoichi;
(Chiyoda-ku, JP) |
Correspondence
Address: |
GRIFFIN & SZIPL, PC
SUITE PH-1
2300 NINTH STREET, SOUTH
ARLINGTON
VA
22204
US
|
Assignee: |
Ishikawajima-Harima Heavy
Industries Co., Ltd.
2-1,Otemachi 2-chome
Chiyoda-ku
JP
100-0004
|
Family ID: |
27585680 |
Appl. No.: |
10/105436 |
Filed: |
March 26, 2002 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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10105436 |
Mar 26, 2002 |
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09912505 |
Jul 26, 2001 |
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09912505 |
Jul 26, 2001 |
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09308293 |
May 12, 1999 |
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6341516 |
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Current U.S.
Class: |
72/184 |
Current CPC
Class: |
B21J 7/18 20130101; B21B
39/12 20130101; B21J 1/04 20130101; B21B 1/42 20130101; B21B 39/14
20130101; B21B 13/18 20130101; B21B 2203/20 20130101; B21B 2203/10
20130101; B21B 1/024 20130101; B21B 39/04 20130101; B21B 39/006
20130101; B21B 15/0035 20130101; B21B 41/08 20130101 |
Class at
Publication: |
72/184 |
International
Class: |
B21B 001/00 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 16, 1997 |
JP |
8-250983 |
Oct 9, 1997 |
JP |
8-277490 |
Oct 14, 1997 |
JP |
8-280414 |
Oct 21, 1997 |
JP |
8-288638 |
Nov 26, 1997 |
JP |
8-324669 |
Dec 3, 1997 |
JP |
8-332569 |
Dec 9, 1997 |
JP |
8-338375 |
Dec 9, 1997 |
JP |
8-338376 |
Feb 17, 1998 |
JP |
9-34744 |
Feb 19, 1998 |
JP |
9-37012 |
Feb 19, 1998 |
JP |
9-37013 |
Feb 24, 1998 |
JP |
9-42326 |
Feb 24, 1998 |
JP |
9-42328 |
Jun 15, 1998 |
JP |
9-166546 |
Jun 16, 1998 |
JP |
9-167981 |
Jun 16, 1998 |
JP |
9-167985 |
Sep 11, 1998 |
JP |
PCT/JP98/04092 |
Claims
1. A plate reduction pressing method in which dies with convex
forming surfaces protruding towards a transfer line are brought
close to the transfer line from above and below the material to be
shaped, when viewed from the side of the transfer line, in
synchronism with the movement of the material to be shaped, in such
a manner that a portion of the forming surfaces of the material is
transferred from the upstream side to the downstream side of the
transfer line and the material to be shaped is reduced in the
direction of the plate thickness thereof.
2. A plate reduction press apparatus comprising die holders
opposite each other above and below a transfer line in which a
material to be shaped is transferred horizontally, dies mounted on
the said die holders and comprised of convex forming surfaces
protruding towards the said transfer line when viewed from the side
of the transfer line, upstream eccentric shafts arranged on the
side of each die holder on the opposite side from the transfer line
and extending in the lateral direction of the transfer line,
downstream eccentric shafts arranged on the side of each die holder
on the opposite side from the transfer line in alignment with the
said upstream eccentric shafts, on the downstream side of the
transfer line, and comprised of eccentric portions with a different
phase angle from the phase angle of the eccentric portions of the
upstream eccentric shafts, upstream rods whose tips are connected
to portions of the die holders, near the end of the die holders in
the upstream direction of the transfer line through bearings and
whose big ends are connected to the eccentric portions of the
upstream eccentric shafts through bearings, downstream rods whose
tips are connected to portions of the die holders, near the end of
the die holders in the downstream direction of the transfer line
through bearings and whose big ends are connected to the eccentric
portions of the downstream eccentric shafts through bearings, and
mechanisms for moving the dies backwards and forwards that
reciprocate the said die holders relative to the transfer line.
3. The plate reduction press apparatus specified in claim 2, in
which the mechanisms for moving the dies backwards and forwards are
comprised of arms one end of each of which is fixed to the die
holder, and guide members which are provided near the die holders
and guide the other end of each of the said arms.
4. The plate reduction press apparatus specified in claim 2, in
which the mechanisms for moving the dies backwards and forwards are
comprised of actuators one end of each of which is connected to one
of the die holders through a first bearing and the other end of
each thereof is connected to a predetermined fixing member through
a second bearing.
5. The plate reduction press apparatus specified in claim 2, in
which the mechanisms for moving the dies backwards and forwards are
comprised of eccentric shafts for backwards and forwards movements,
provided near the die holders, and rods for backward and forward
movements, one end of each of the said rods being connected to one
of the die holders through a first bearing and the other end
thereof being connected to one of the eccentric portions of the
eccentric shafts for backward and forward movements.
6. The plate reduction press apparatus specified in claim 2, in
which the mechanisms for moving the dies backwards and forwards are
comprised of levers one end of each of which is connected to one of
the die holders through a first bearing and the other end thereof
is connected to a predetermined fixing member through a second
bearing.
7. A plate reduction press apparatus comprising dies arranged
vertically opposite each other on opposite sides of a transfer line
in which a material to be shaped is transferred horizontally, and
moving towards and away from the transfer line in synchronism with
each other, a plurality of upstream table rollers arranged on the
upstream side of the dies on the transfer line in such a manner
that the lower surface of the material to be shaped, which is to be
inserted between the dies, can be supported substantially
horizontally, a plurality of downstream up and down table rollers
arranged on the downstream side of the dies on the transfer line in
such a manner that the downstream up and down table rollers can be
raised and lowered and can support the lower surface of the
material after being shaped and fed out of the dies, and a
plurality of downstream table rollers arranged on the downstream
side of the downstream up and down table rollers on the transfer
line in such a manner that the lower surface of the material after
being shaped and fed out of the dies can be supported substantially
horizontally at a height substantially the same as the height of
the said upstream up and down table rollers.
8. A plate reduction press apparatus comprising dies arranged
vertically opposite each other on opposite sides of a transfer line
in which a material to be shaped is transferred horizontally, and
moving towards and away from the transfer line in synchronism with
each other, a plurality of upstream up and down table rollers
arranged on the upstream side of the dies on the transfer line in
such a manner that the upstream up and down table rollers can be
raised and lowered, and can support the lower surface of the
material to be shaped, which is to be inserted between the dies,
and a plurality of downstream table rollers arranged on the
downstream side of the dies on the transfer line in such a manner
that the lower surface of the material being shaped and fed out of
the dies can be supported.
9. A plate reduction press apparatus comprising dies arranged
vertically opposite each other on opposite sides of a transfer line
in which a material to be shaped is transferred horizontally, and
moving towards and away from the transfer line in synchronism with
each other, a plurality of upstream up and down table rollers
arranged on the upstream side of the dies on the transfer line in
such a manner that the upstream up and down table rollers can be
raised and lowered, and the lower surface of the material to be
shaped, which is to be inserted between the dies, can be supported,
and a plurality of downstream up and down table rollers arranged on
the downstream side of the dies in such a manner that the lower
surface of the material being shaped and fed out of the dies can be
supported.
10. A method of operating the plate reduction press apparatus
specified in claim 7, in which when a long material to be shaped is
inserted between both dies, and reduced and formed in the direction
of the plate thickness, the vertical positions of the downstream up
and down table rollers near the dies are determined in such a
manner that the material after being shaped and fed out of the dies
is substantially horizontal, and the vertical positions of the
downstream up and down table rollers on the side farther from the
dies are determined in such a manner that the material being shaped
gradually descends towards the downstream table rollers.
11. A method of operating the plate reduction press apparatus
specified in claim 8, in which when a long material to be shaped is
inserted between both dies, and reduced and formed in the direction
of the plate thickness, the vertical positions of the upstream up
and down table rollers near the dies are determined in such a
manner that the material to be shaped, which is to be inserted
between the dies, is substantially horizontal.
12. A method of operating the plate reduction press apparatus
specified in claim 2, in which when a long material to be shaped is
inserted between both dies, and reduced and formed in the direction
of the plate thickness, the vertical positions of the upstream up
and down table rollers near the dies and the downstream up and down
table rollers from the dies are determined in such a manner that
the material to be shaped, which is to be inserted between the
dies, and the material after being shaped and fed out of the dies
are substantially horizontal.
13. The method of operating the plate reduction press apparatus
specified in claim 10, in which when a long material to be shaped
is not reduced or formed in the direction of the plate thickness by
the dies, the positions of the upper surfaces of the downstream up
and down table rollers are determined to be identical to the
positions of the upper surfaces of the downstream table
rollers.
14. A method of operating the plate reduction press apparatus
specified in claim 8, in which when a long material to be shaped is
not reduced or formed in the direction of the plate thickness by
the dies, the positions of the upper surfaces of the upstream up
and down table rollers are determined to be identical to the
positions of the upper surfaces of the downstream table
rollers.
15. A method of operating the plate reduction press apparatus
specified in claim 9, in which when a long material to be shaped is
not reduced or formed in the direction of the plate thickness by
the dies, the positions of the upper surfaces of the upstream up
and down table rollers and the downstream table rollers are
determined to be identical to each other.
16. A plate thickness reduction pressing method comprising a first
plate thickness reduction sub-method; in which a material to be
shaped is transferred from the upstream side of the transfer line
to the downstream side of the transfer line, upstream dies with
forming surfaces facing the said material to be shaped are moved
towards the material to be shaped while the upstream dies are being
moved in the downstream direction of the transfer line and the
upstream dies are moved away from the material being shaped while
the upstream dies are being moved in the upstream direction of the
transfer line, each in synchronism with the other die, the said
material to be shaped is reduced and shaped in the direction of the
plate thickness sequentially, and a second plate thickness
reduction sub-method; in which downstream dies with forming
surfaces facing the said material being shaped are moved towards
the material being shaped with a reverse phase angle to the phase
angle of the said upstream dies while the downstream dies are being
moved in the downstream direction of the transfer line from above
and below a portion of the material, whose thickness has been
reduced through the first plate thickness reduction sub-method and
the downstream dies are moved away from the material being shaped
while the downstream dies are being moved in the upstream direction
of the transfer line, in synchronism with each other; and the said
material after being shaped by the first plate reduction sub-method
is further reduced and shaped in the direction of the plate
thickness sequentially.
17. A plate reduction press apparatus comprising upstream sliders
arranged vertically opposite each other on opposite sides of a
transfer line in which a material to be shaped is transferred,
mechanisms for moving the upstream sliders that move the said
upstream sliders towards the transfer line and move the upstream
sliders away from the transfer line, upstream dies mounted on the
upstream sliders in such a manner that the upstream dies can move
along the transfer line, and are comprised of forming surfaces
facing the transfer line, mechanisms for moving the upstream dies
that move the said upstream dies backwards and forwards along the
transfer line, downstream sliders located on the downstream side of
the said upstream sliders on the transfer line, opposite each other
on opposite sides of the transfer line, mechanisms for moving the
downstream sliders that move the said downstream sliders towards
the transfer line and move the downstream sliders away from the
transfer line, downstream dies mounted on the downstream sliders in
such a manner that the downstream dies can move along the transfer
line, and are comprised of forming surfaces facing the transfer
line, and mechanisms for moving the downstream dies that move the
said downstream dies backwards and forwards along the transfer
line.
18. The plate reduction press apparatus specified in claim 17,
comprising mechanisms for moving the upstream sliders comprised of
upstream crank shafts arranged on the opposite side of the upstream
sliders to the transfer line, and upstream rods one end of each of
which is connected to an eccentric portion of one of the upstream
crank shafts through a first bearing and the other end of each of
which is connected to one of the upstream sliders through a second
bearing, and mechanisms for moving the downstream sliders comprised
of downstream crank shafts arranged on the opposite side of the
downstream sliders to the transfer line, and downstream rods one
end of each of which is connected to an eccentric portion of one of
the downstream crank shafts through a third bearing and the other
end of each of which is connected to one of the downstream sliders
through a fourth bearing.
19. The plate reduction press apparatus specified in claim 18,
comprising a synchronous drive mechanism that rotates the upstream
crank shafts and the downstream crank shafts in synchronism in the
same direction in such a manner that the phase angles of the
eccentric portions of both upstream and downstream crank shafts
maintain a difference of 180.degree..
20. The plate reduction press apparatus specified in claim 17 or
18, comprising upstream crank shafts and downstream crank shafts
that are supported through bearings in such a manner that both the
said crank shafts are substantially parallel to the direction
orthogonal to the transfer line.
21. A plate reduction press apparatus comprising a pair of dies
arranged opposite each other on opposite sides of the transfer line
of a material to be shaped and moved towards and away from each
other in synchronism with each other, upstream side guides arranged
in the close vicinity of the said dies on the upstream side in the
direction of the transfer line in such a manner that the upstream
side guides arc opposite each other in the lateral direction of the
material to be shaped on opposite sides of the transfer line, and
comprised of a first pair of side guide units that can be moved
towards and away from the transfer line, and downstream side guides
arranged in the close vicinity of the said dies on the downstream
side in the direction of the transfer line in such a manner that
the downstream side guides are opposite each other in the lateral
direction of the material being shaped on opposite sides of the
transfer line, and comprised of a second pair of side guide units
that can be moved towards and away from the transfer line.
22. A plate reduction press apparatus comprising a pair of dies
arranged opposite each other on opposite sides of the transfer line
of a material to be shaped and moved towards and away from each
other in synchronism with each other, upstream side guides arranged
in the close vicinity of the said dies on the upstream dies in the
direction of the transfer line in such a manner that the upstream
side guides are opposite each other in the lateral direction of the
material to be shaped on opposite sides of the transfer line, and
comprised of a first pair of side units that can be moved towards
and away from the transfer line, upstream vertical rollers
supported by the corresponding upstream side guides in such a
manner that the upstream vertical rollers can contact the lateral
edges of the material to be shaped, when the material passes
between the said upstream side guides, downstream side guides
arranged in the close vicinity of the said dies on the downstream
side in the direction of the transfer line in such a manner that
the downstream side guides are opposite each other in the lateral
direction of the material being shaped on opposite sides of the
transfer line, and comprised of a second pair of side guide units
that can be moved towards and away from the transfer line, and
downstream vertical rollers supported by the corresponding
downstream side guides in such a manner that the downstream
vertical rollers can contact the lateral edges of the material
being shaped, when the material passes between the said downstream
side guides.
23. A plate reduction press apparatus comprising upper and lower
drive shafts arranged opposite each other above and below a
material to be pressed, and driven to rotate, upper and lower press
frames one end of each of which engages with one of the said drive
shafts in a freely slidable manner, and the other ends of which are
connected together in a freely rotatable manner, a horizontal guide
device that supports the connection portions of the said press
frames in a manner such that they can slide in the horizontal
direction, and upper and lower dies mounted at the ends of the
upper and lower press frames, facing the material to be pressed, in
which the upper and lower drive shafts are comprised of a pair of
eccentric shafts that are located at both lateral ends with a phase
angle difference between each other, and the upper and lower dies
are opened and closed with a rolling movement by rotating the drive
shafts, and the material to be pressed is transferred while the
material is pressed with a rolling action.
24. The plate reduction press apparatus specified in claim 23, in
which a driving device rotates and drives the drive shafts, the
rotational speed of the said driving device is variable, and the
rotational speed is determined in such a manner that the speed of
the dies in the direction of the transfer line during pressing is
substantially equal to the speed of feeding the material to be
pressed.
25. The plate reduction press apparatus specified in claim 23,
comprising a looper device that provides a slack portion in the
material to be pressed on the downstream side and holds up the
material.
26. A plate reduction press apparatus comprising upper and lower
crank shafts arranged opposite each other above and below a
material to be pressed and driven to rotate, upper and lower press
frames one end of each of which engages with one of the said crank
shafts in a freely slidable manner, and the other ends of which are
connected in a freely rotatable manner, horizontal guide devices
that support the connecting portions of the said press frames in a
horizontally movable manner, and upper and lower dies mounted at
the ends of the upper and lower press frames, facing the material
to be pressed; in which the crank shafts rotate to open and close
the upper and lower dies, and press the material to be pressed,
while the material is being transferred.
27. The plate reduction press apparatus specified in claim 26,
comprising a driving device for rotating and driving the crank
shafts, in which the rotational speed of the said driving device is
variable and determined in such a manner that the speed of the dies
in the direction of the transfer line during pressing is
substantially equal to the feeding speed of the material to be
pressed.
28. The plate reduction press apparatus specified in claim 26,
further comprising a looper device that provides a slack portion in
the material to be pressed on the downstream side and holds up the
material.
29. The plate reduction press apparatus specified in claim 26,
further comprising height adjusting plates that are maintained
between the dies and the press frames and adjust the heights of the
dies.
30. A plate reduction pressing method in which the speed of feeding
a material to be pressed is made variable with respect to the
maximum speed of dies in the direction of transfer line.
31. The plate reduction pressing method specified in claim 30, in
which the speed of feeding the material to be pressed is made
variable in such a manner that at the beginning of pressing, the
speed is made higher than the said maximum speed and made lower at
an intermediate time in the pressing period.
32. A plate reduction press apparatus comprising upper and lower
eccentric drive shafts arranged opposite each other above and below
a material to be pressed and driven to rotate, upper and lower
synchronous eccentric shafts that rotate around the said eccentric
drive shafts, upper and lower press frames one end of each of which
engages with one of the said synchronous eccentric shafts in a
freely slidable manner, and the other ends of which are connected
together in a freely rotatable manner, and upper and lower dies
mounted at ends of the upper and lower press frames, facing the
material to be pressed, in which the upper and lower dies are
opened and closed by rotating the upper and lower eccentric drive
shafts, and when the material to be pressed is being pressed by the
dies, the synchronous eccentric shafts synchronize the speed of the
press frames in the direction of transfer line with the speed of
the material to be pressed in the direction of the transfer
line.
33. A plate reduction press apparatus comprising crank shafts
arranged above and below a material to be pressed, sliders which
engage with the said crank shafts in a freely slidable manner and
made to move in a circular path, dies mounted on the sliders facing
the said material to be pressed, and a driving device for driving
and rotating the said crank shafts, in which the said crank shafts
are comprised of eccentric shafts engaged with the said sliders,
and support shafts arranged at both ends of the eccentric shafts
with shaft center lines eccentric to the shaft center lines of the
eccentric shafts, and at least one of the support shafts is
provided with a counterweight offset with an eccentric center line
substantially at an angle of 180.degree., to the direction of the
eccentricity of the said eccentric shafts.
34. A plate reduction press apparatus comprising crank shafts
arranged above and below a material to be pressed, upper and lower
press frames one end of each of which engages with one of the crank
shafts in a freely slidable manner and made to move in a circular
path, and the other ends of which are connected together in a
freely rotatable manner, horizontal guide devices that hold the
connecting portions of the press frames in a manner such that they
can move in the horizontal direction, dies mounted at ends of the
said press frames facing the material to be pressed, and a driving
device for driving and rotating the said crank shafts, in which the
said crank shafts are comprised of eccentric shafts engaged with
the said ends of the press frames, and support shafts arranged on
both sides of the eccentric shafts with shaft center lines
eccentric to the shaft center lines of the eccentric shafts, and at
least one of the support shafts is provided with a counterweight
offset with an eccentric center line substantially at an angle of
180.degree., to the direction of eccentricity of the said eccentric
shafts.
35. The plate reduction press apparatus specified in claim 33 or
34, in which the said counterweight has a mass sufficient to store
rotating energy and can also function as a flywheel.
36. The plate reduction press apparatus specified in claim 33 or 34
in which the inertia force due to the eccentricity of the said
counterweight is determined so as to substantially cancel the
inertia force produced by the said sliders or one end of the said
press frames.
37. A plate reduction press apparatus comprising dies arranged
above and below a slab, sliders provided for each of the dies so
that the dies can be moved up, down, and backwards and forwards
with a swinging motion and a driving device for driving the
sliders, in which each of the said sliders is comprised of a main
unit with a circular hole with its center lines in the lateral
direction of the slab, and a crank with a first axis engaged with
the circular hole and a second shaft with a diameter smaller than
the diameter of the first shaft and a center line offset from the
center line of the first shaft, and the second shaft is rotated and
driven by the said driving device.
38. A plate reduction press apparatus comprising a die arranged
above or below a slab, a slider for moving the die up, down, and
backwards and forwards, a driving device for driving the slider,
and a slab supporting member arranged opposite the said die above
or below the slab, in which the said slider is comprised of a main
unit with a circular hole with a center line in the lateral
direction of the slab, a first shaft engaged with the circular
hole, and a crank comprised of a second shaft with a diameter
smaller than the diameter of the first shaft and a center line
offset from the center line of the first shaft, and the second
shaft is rotated and driven by the said driving device.
39. The plate reduction presses apparatus specified in claim 37 or
38, in which a plurality of circular holes and a plurality of
cranks arranged in the said sliders are arranged in a row in the
transfer direction of the slab, and constructed in such a manner
that each crank produces pressing force.
40. The plate reduction press apparatus specified in claim 37 or
38, in which a plurality of circular holes and a plurality of
cranks equipped in the said sliders are arranged in a row in the
transfer direction of the slab, and constructed in such a manner
that one crank bears the moment of the load and the other cranks
produce pressing force.
41. The plate reduction press apparatus specified in claim 37 or
38, in which the said slab is transferred by pinch rolls or tables,
and the slab is transferred in synchronism with the forward
velocity of the sliders when the slab is pressed by the
sliders.
42. The plate reduction press apparatus specified in claim 37 or
38, in which the distance L in which the slab is moved in a cycle
comprised of a reduction pressing time period and a time period
with a normal transfer speed is no greater than the length L1 of
the dies in the transfer direction of the slab.
43. A plate reduction press apparatus comprising a pair of dies
arranged opposite each other above and below a slab, and a device
that moves each of the dies backwards and forwards and in the
direction of the slab with a swinging motion, and eccentric shafts
rotating in the said circular holes, and each of the said eccentric
shafts is comprised of a first shaft rotating in a circular hole
with a center line A, and a second shaft driven to rotate around a
center line B offset from the said first shaft by a distance e.
44. A plate reduction pressing method using a pair of dies arranged
opposite each other above and below a slab, and a device that moves
each of the dies towards the slab with a swinging motion, in which
when the slab is pressed by the dies, the speed of feeding the slab
is synchronized with the speed of the dies, and during the period
when the slab is not being pressed and is not in contact with the
dies, the slab is fed at a constant speed corresponding to a
predetermined cycle speed.
45. A plate reduction press apparatus in which the direction in
which a material to be pressed moves after being pressed is defined
to be longitudinal, and N dies each of which has the same length in
the longitudinal direction are arranged and press the material with
an interval of NL between each die.
46. The plate reduction press apparatus specified in claim 45, in
which the lateral direction is defined to be the direction
orthogonal to the said longitudinal direction, and the longitudinal
length of the said dies is less than the length of the dies in the
lateral direction.
47. The plate reduction press apparatus specified in claim 45, in
which the said N dies press at the same time.
48. The plate reduction press apparatus specified in claim 45, in
which at least one of the said dies presses at a different time
from the time that the other dies press.
49. A plate reduction pressing method in which each of the N press
machines pressing a material to be pressed with a press length L in
the direction of the flow of the material to be pressed is defined
by a number K, the press machines are arranged such that K=1 on the
upstream side of the pressing line, and K increases sequentially to
K=N in the downstream direction when N press machines are arranged
in tandem, the material to be pressed is pressed sequentially from
K=N to K=1, then after the material to be pressed is fed by a
length NL, that is, by the total of the pressing lengths of each
press machine, sequential pressing from K=N to K=1 is repeated to
press the material.
50. A plate reduction pressing method in which each of the N press
machines pressing a material to be pressed with a press length L in
the direction of the flow of the material to be pressed is defined
by a number K, the press machines are arranged such that K=1 on the
upstream side of the pressing line, and K increases sequentially to
K=N in the downstream direction when N press machines are arranged
in a tandem configuration, each press machine reduces the material
by .DELTA.t, press machine K reduces the material by .DELTA.t from
the thickness after it has been pressed by press machine K-1, and
the material is pressed by repeatedly feeding the material by the
press length L after pressing the material in sequence from press
machine K=1 to press machines K=N.
51. A plate reduction press apparatus comprising speed adjusting
rolls arranged between a reduction press machine and a rolling mill
with a space provided in which the material to be pressed can be
deflected, metering instruments to measure the length passed are
arranged near the said speed adjusting rolls or in the vicinity
thereof, for measuring the length of the material to be pressed
which has passed, and a control apparatus for controlling the
operations of the said reduction press machine and adjusting both
speed adjusting rolls according to the measurement of the said
metering instrument for measuring the length passed.
52. The plate reduction press apparatus specified in claim 51, in
which the said control apparatus obtains the difference in the
measured lengths passed of both metering instruments for measuring
the length passed over a period of a multiple of pressing cycles of
the press machine, adjusts the number of pressing cycles of the
press machine or the transfer speeds of the speed adjusting rolls,
or a combination thereof, and controls the pressing operations in
such a manner that the difference in the lengths passed is brought
to 0.
53. The plate reduction press apparatus specified in claim 51, in
which a deflection metering instrument is provided to measure the
deflection of the material to be pressed, between the said speed
adjusting rolls, and the said control apparatus controls the
pressing operations according to the measurements thereof in such a
manner that the deflection remains within a predetermined
range.
54. The plate reduction press apparatus in which an apparatus for
conveying material being pressed that can be raised and lowered is
arranged between the said speed adjusting rolls, and when the
leading end or trailing end of the material to be pressed passes
the conveyor apparatus, the material to be pressed is conveyed
substantially at the same level as the transfer level of the speed
adjusting rolls.
55. A plate reduction pressing method, in the pressing method of a
crank type press machine that presses a material to be pressed
while it is being transferred using upper and lower dies, in which
during the pressing period, the dies are moved at the same speed as
the speed of the material to be pressed, and during the
non-pressing period, the speed of feeding the material to be
pressed is adjusted in such a manner that during one cycle, the
material to be pressed is moved by a predetermined distance L.
56. A plate reduction press apparatus comprising dies arranged
above and below a material to be pressed, crank devices for
pressing each of the dies, and transfer devices for transferring
the material to be pressed, in which the transfer devices move the
dies and the material to be pressed at the same speed when the
crank devices are pressing the material to be pressed by the dies,
and when the material to be pressed is not being pressed, the
transfer devices adjust the speed of feeding the material to be
pressed and move the material by a predetermined distance L in a
cycle of pressing operations, and the said distance L is not
greater than the length L0 which is the reduction length of the
dies in the direction of flow of the material to be pressed.
57. A plate reduction pressing method, in the pressing method of a
crank type press machine that presses a material to be pressed
while it is being transferred using dies from both sides in the
lateral direction of the transfer line, in which during the
pressing period, the dies are moved at the same speed as the speed
of the material to be pressed, and during the non-pressing period,
the speed of feeding the material to be pressed is adjusted in such
a manner that during one cycle, the material to be pressed is moved
by a predetermined distance L.
58. A plate reduction press apparatus comprising dies arranged on
both sides in the lateral direction of a material to be pressed,
crank devices that press each of the dies in the lateral direction,
and transfer devices that transfer the material to be pressed, in
which the transfer devices move the material to be pressed at the
same speed as the speed of the dies when the crank devices are
pressing the material to be pressed in the lateral direction with
the dies, and when the material to be pressed is not being pressed,
the speed of feeding the material to be pressed is adjusted, and
the material to be pressed is moved by a predetermined distance L
in one cycle of pressing operations, and the said distance L is not
greater than the length L0 which is the reduction length of the
dies in the direction of flow of the material to be pressed.
59. The plate reduction press apparatus specified in claim 56 or
58, further comprising a looper that forms a loop in the material
to be pressed and adjusts the length thereof, downstream of the
said transfer devices.
60. A plate reduction pressing method, in the pressing method of a
crank type press machine that presses a material to be pressed with
upper and lower dies and transfers the material with pinch rolls,
in which during the pressing period, the pinch rolls rotate in such
a manner that the peripheral speed of the pinch rolls is made equal
to a combination of the horizontal speed of the dies and the
elongation speed of the material to be pressed, added or
subtracted, and transfer the material to be pressed, and when the
press machine is not pressing, the speed of feeding the material to
be pressed is adjusted in such a manner that during one cycle, the
material to be pressed is moved by a predetermined distance L, and
the pressing force of the pinch rolls during the pressing period is
made smaller than the force thereof during the non-pressing
period.
61. A plate reduction press apparatus comprising dies arranged
above and below a material to be pressed, crank devices that press
each of the dies, and pinch rolls that transfer the material to be
pressed, in which when the crank devices are pressing the material
to be pressed through the dies, the pinch rolls rotate in such a
manner that the peripheral speed of the pinch rolls is made equal
to the combination of the horizontal speed of the dies and the
elongation speed of the material to be pressed, added or
subtracted, and transfer the material to be pressed, and when the
press machine is not pressing, the speed of feeding the material to
be pressed is adjusted in such a manner that during one cycle, the
material to be pressed is moved by a predetermined distance L and
the distance L is not greater than the reduction length L0 of the
dies in the direction of flow of the material to be pressed, and
the pressing force of the pinch rolls during the pressing period is
made smaller than the pressing force during the non-pressing
period.
62. The plate thickness press apparatus specified in claim 61, in
which the pressing force of the said pinch rolls is made smaller
for a predetermined time t before or after the press machine begins
to press.
63. The plate reduction press apparatus specified in claim 61, in
which the pressing force of the said pinch rolls during the
pressing period is made smaller when the pressing load becomes
greater than a predetermined load.
64. A plate reduction press apparatus comprising inlet transfer
devices that are arranged upstream of the press machine, and
transfer a material to be pressed, and can be raised and lowered,
and outlet transfer devices that are arranged downstream of the
press machine, and transfer the material being pressed, and can be
raised and lowered, in which the said inlet transfer devices are
adjusted to transfer height according to information about the
thickness of the material to be pressed, that has been input, in
such a manner that the center line of the thickness of the material
to be pressed agrees with the center line of the press machine, and
the said outlet transfer devices are adjusted to a transfer height
according to information about the thickness of the material being
pressed, in such a manner that the center line of the thickness of
the material agrees with the center line of the press machine.
65. A plate reduction press apparatus comprising inlet transfer
devices that are arranged upstream of a press machine for pressing
a material to be pressed between upper and lower dies, and transfer
the material to be pressed, and can be raised and lowered, and
outlet transfer devices that are arranged downstream of the said
press machine, and transfer the material being pressed, and can be
raised and lowered, in which when the material to be pressed is
passed through the press machine without being pressed, the upper
and lower dies are open, and the transfer heights of the said inlet
transfer devices and the said outlet transfer devices are
determined to be identical to each other and higher than the upper
surface of the lower die in the open position.
66. A plate reduction pressing method, in the transfer method of
the transfer devices that are arranged upstream and downstream of a
press machine and can adjust the transfer height of a material to
be pressed, where both transfer devices can transfer the material
to be pressed or being pressed while the transfer devices maintain
the height of the center line of the thickness of the material to
be pressed, in an unchanged manner during transfer.
67. A plate reduction pressing method, in the transfer method of
transfer devices that are arranged upstream and downstream of a
press machine and can adjust the transfer height of a material to
be pressed, in which when the material to be pressed is passed
through the press machine, the press dies are opened vertically in
such a manner that the material to be pressed does not contact the
dies, and both transfer devices transfer the material to be pressed
at the same height.
Description
[0001] This application is a division of U.S. patent application
Ser. No. 09/912,505, filed Jul. 26, 2001, which in turn is a
division of U.S. patent application Ser. No. 09/308,293, filed May
12, 1999, now U.S. Pat. No. 6,341,516, issued Jan. 29, 2002, the
entire disclosures of which are considered to be part of the
present disclosure and are specifically incorporated by reference
herein.
BACKGROUND OF THE INVENTION
[0002] 1. Technical Field of the Invention
[0003] The present invention relates to a plate thickness reduction
press apparatus that transfers and reduces a slab, and the methods
concerned with its use.
[0004] 2. Prior Art
[0005] 1. FIG. 1 shows an example of a roughing mill used for hot
rolling, and the roughing mill is provided with work rolls 2a, 2b
arranged vertically opposite each other on opposite sides of a
transfer line S that transfers a slab-like material 1 to be shaped,
substantially horizontally, and backup rolls 3a, 3b contacting the
work rolls 2a, 2b on the side opposite to the transfer line.
[0006] In the above-mentioned roughing mill, the work roll 2a above
the transfer line S is rotated counterclockwise, and the work roll
2b underneath the transfer line S is rotated clockwise, so that the
material 1 to be shaped is caught between both work rolls 2a, 2b,
and by pressing the upper backup roll 3a downwards, the material 1
to be shaped is moved from the upstream A side of the transfer line
to the downstream B side of the line, and the material 1 to be
shaped is pressed and formed in the direction of the thickness of
the slab. However, unless the nip angle .theta. of the material 1
to be shaped as it enters into the work rolls 2a, 2b is less than
about 17.degree., slipping will occur between the upper and lower
surfaces of the material 1 to be shaped and the outer surfaces of
both work rolls 2a, 2b, and the work rolls 2a, 2b will no longer be
able to grip and reduce the material 1 to be shaped.
[0007] More explicitly, when the diameter D of the work rolls 2a,
2b is 1,200 mm, the reduction .DELTA.t of a single rolling pass is
about 50 mm according to the above-mentioned nip angle .theta.
condition for the work rolls 2a, 2b, so when a material 1 to be
shaped with a thickness T0 of 250 mm is rolled, the thickness T1 of
the slab after being reduced and formed by a roughing mill becomes
about 200 mm.
[0008] According to the prior art, therefore, the material 1 to be
shaped is rolled in a reversing mill, in which the material is
moved backwards and forwards while gradually reducing the thickness
of the plate, and when the thickness of the material 1 to be shaped
is reduced to about 90 mm, the material 1 is sent to a finishing
mill.
[0009] Another system for reducing and forming the material 1 to be
shaped according to the prior art is shown in FIG. 2; dies 14a, 14b
with profiles like the plane shape of dies for a stentering press
machine are positioned opposite each other above and below a
transfer line S, and both dies 14a, 14b are made to approach each
other and separate from each other in the direction orthogonal to
the direction of movement of the material 1 using reciprocating
means such as hydraulic cylinders, in synchronism with the transfer
of the material 1, while reducing and forming the material 1 to be
shaped in the direction of the thickness of the plate.
[0010] The dies 14a, 14b are constructed with flat forming surfaces
19a, 19b gradually sloping from the upstream A side of the transfer
line towards the downstream B side of the line, and flat forming
surfaces 19c, 19d that continue from the aforementioned forming
surfaces 19a, 19b in a direction parallel to and on opposite sides
of the transfer line S.
[0011] The width of the dies 14a, 14b is set according to the plate
width (about 2,000 mm or more) of the material 1 to be shaped.
[0012] However, when the material 1 to be shaped is rolled with the
reversing method using the roughing mill shown in FIG. 1, space is
required at each of the upstream A and downstream B ends of the
transfer line S of the roughing mill, for pulling out the material
1 to be shaped as it comes out of the roughing mill, so the
equipment must be long and large.
[0013] When the material 1 to be shaped is reduced and formed in
the direction of its plate thickness using the dies 14a, 14b shown
in FIG. 2, the areas of the forming surfaces 19a, 19b, 19c and 19d
in contact with the material 1 to be shaped are much longer than
those of the dies of a stentering press machine, and the contact
areas increase as the dies 14a, 14b approach the transfer line S,
so that a large load must be applied to each of the dies 14a, 14b,
during reduction.
[0014] Furthermore, the power transmission members such as the
eccentric shafts and rods for moving the dies 14a, 14b, the
housing, etc. must be strong enough to withstand the above reducing
loads, so each of these members and the housing must be made large
in size.
[0015] Moreover, when the material 1 to be shaped is reduced and
formed in the direction of its plate thickness using the dies 14a,
14b, some of the material 1 is forced backwards towards the
upstream A side on the transfer line depending on the shape and the
stroke of the dies 14a, 14b, therefore, it becomes difficult to
transfer the material 1 to be shaped to the downstream B side of
the transfer line.
[0016] When the material 1 to be shaped is reduced and formed in
the direction of its plate thickness using the dies 14a, 14b shown
in FIG. 2, the height of the lower surface of the material 1 after
being reduced by the dies 14a, 14b is higher than the height of the
lower surface of the material 1 immediately before being reduced by
the dies, by an amount corresponding to the reduction in
thickness.
[0017] Consequently, the leading end of the material 1 to be shaped
tends to droop downwards, therefore the table rollers (not
illustrated) installed on the downstream B side of the transfer
line, to support the material 1 being shaped, may catch the leading
end of the material 1, possibly resulting in damage to both the
table rollers and the material 1 being shaped.
[0018] Recently, the flying-sizing press machine shown in FIG. 3
has been proposed.
[0019] This flying-sizing press machine is provided with a housing
4 erected on a transfer line S so as to allow movement of a
material 1 to be shaped, an upper shaft box 6a and a lower shaft
box 6b housed in window portions 5 of the housing 4 opposite each
other on opposite sides of the transfer line S, upper and lower
rotating shafts 7a, 7b extending substantially horizontally in the
direction orthogonal to the transfer line S and supported by the
upper shaft box 6a or the lower shaft box 6b by bearings (not
illustrated) on the non-eccentric portions, rods 9a, 9b located
above and below the transfer line S, respectively, connected to
eccentric portions of the rotating shafts 7a, 7b through bearings
8a, 8b at the end portions thereof, rod support boxes 11a, 11b
connected to intermediate portions of the upper and lower rods 9a,
9b by bearings 10a, 10b with spherical surfaces and housed in the
window portions 5 of the housing 4 and free to slide vertically,
die holders 13a, 13b connected to the top portions of the rods 9a,
9b through bearings 12a, 12b with spherical surfaces, dies 14a, 14b
mounted on the die holders 13a, 13b, and hydraulic cylinders 15a,
15b whose cylinder units are connected to intermediate locations
along the length of the rods 9a, 9b by means of bearings and the
tips of the piston rods are connected to the die holders 13a, 13b
through bearings.
[0020] The rotating shafts 7a, 7b are connected to the output shaft
(not illustrated) of a motor through a universal coupling and a
speed reduction gear, and when the motor is operated, the upper and
lower dies 14a, 14b approach towards and move away from the
transfer line S in synchronism with the transfer operation.
[0021] The dies 14a, 14b are provided with flat forming surfaces
16a, 16b gradually sloping from the upstream A side of the transfer
line towards the downstream B side of the transfer line so as to
approach the transfer line S, and other flat forming surfaces 17a,
17b continuing from the aforementioned forming surfaces 16a, 16b in
a direction parallel to the transfer line S.
[0022] The width of the dies 14a, 14b is determined by the plate
width (about 2,000 mm or more) of the material 1 to be shaped.
[0023] A position adjusting screw 18 is provided at the top of the
housing 4, to enable the upper shaft box 6a to be moved towards or
away from the transfer line S, and by rotating the position
adjusting screw 18 about its axis, the die 14a can be raised and
lowered through the rotating shaft 7a, rod 9a, and the die holder
13a.
[0024] When the material 1 to be shaped is reduced and formed in
the direction of the plate thickness using the flying-sizing press
machine shown in FIG. 3, the position adjusting screw 18 is rotated
appropriately to adjust the position of the upper shaft box 6a, so
that the spacing between the upper and lower dies 14a, 16b is
determined according to the plate thickness of the material 1 to be
shaped by reducing and forming in the direction of plate
thickness.
[0025] Next, the motor is operated to rotate the upper and lower
rotating shafts 7a, 7b, and the material 1 to be shaped is inserted
between the upper and lower dies 14a, 14b, and the material 1 is
reduced and formed by means of the upper and lower dies 14a, 14b
that move towards and away from each other and with respect to the
transfer line S while moving in the direction of the transfer line
S as determined by the displacement of the eccentric portions of
the rotating shafts 7a, 7b.
[0026] At this time, appropriate hydraulic pressure is applied to
the hydraulic chambers of the hydraulic cylinders 15a, 15b, and the
angles of the die holders 13a, 13b are changed so that the forming
surfaces 17a, 17b of the upper and lower dies 14a, 14b, on the
downstream B side of the transfer line, are always parallel to the
transfer line S.
[0027] However, the flying-sizing press machine shown in FIG. 3 has
much larger contact areas between the forming surfaces 16a, 16b,
17a and 17b of the dies 14a, 14b and the material 1 to be formed,
compared to the dies of a plate reduction press machine, and
because the above-mentioned contact areas increase as the dies 14a,
14b approach the transfer line S, a large load must be applied to
the dies 14a, 14b during reduction.
[0028] In addition, the die holders 13a, 13b, rods 9a, 9b, rotating
shafts 7a, 7b, shaft boxes 6a, 6b, housing 4, etc. must be strong
enough to withstand the reducing load applied to the dies 14a, 14b,
so that these members are made larger in size.
[0029] Also, the flying-sizing press machine shown in FIG. 3 may
suffer from the problem that the leading and trailing ends of the
material 1 being reduced and formed are locally bent to the left or
right, or with a camber so that when a long material 1 is being
formed it generally warps, unless the centers of the reducing
forces from the dies 14a, 14b on the material 1 to be shaped are in
close alignment when the material 1 is reduced and formed by the
upper and lower dies 14a, 14b.
[0030] 2. With a conventional rolling mill known in the prior art,
in which a material is rolled between two work rolls, there is a
reduction ratio limit of normally about 25% due to the nip angle
limitation. Therefore, it is not possible to reduce the thickness
of a material by a large ratio (for example, reducing a material
from about 250 mm thickness to 30 to 60 mm) in a single pass,
therefore three or four rolling mills are arranged in tandem in a
tandem rolling system, or the material to be rolled is rolled
backwards and forwards in a reverse rolling system. However, these
systems are accompanied with practical problems such as the need
for a long rolling line.
[0031] On the other hand the planetary mill, Sendzimir mill,
cluster mill, etc. have been proposed as means of pressing that
allow a large reduction in one pass. However, with these rolling
mills, small rolls press the material to be rolled at a high
rotational speed, resulting in a great impact, therefore the life
of the bearings, etc., is so short that these mills are not
suitable for mass production facilities.
[0032] On the other hand, various kinds of press apparatus modified
from the conventional stentering press machines have been proposed
(for example, Japanese patent No. 014139, 1990, unexamined Japanese
patent publication Nos. 222651, 1986, 175011, 1990, etc.).
[0033] An example of the "Flying-sizing press apparatus" according
to the unexamined Japanese patent publication No. 175011, 1990 is
shown in FIG. 4; rotating shafts 22 are arranged in the upper and
lower sides or the left and right sides of the transfer line Z of a
material to be shaped, and the bosses of rods 23 with a required
shape are connected to eccentric portions of the rotating shafts
22, and in addition, dies 24 arranged on opposite sides of the
transfer line of the material to be shaped are connected to the
tips of the rods 23; when the rotating shafts 22 are rotated, the
rods 23 coupled to the eccentric portions of the rotating shafts
cause the dies 24 to press both the upper and lower surfaces of the
material 1 to be shaped, thereby the thickness of the material to
be shaped is reduced.
[0034] However, the above-mentioned high-reduction means are
associated with problems such as (1) a material to be reduced
cannot be easily pressed by the flying-sizing apparatus in which
the material is reduced as it is being transferred, (2) the means
are complicated with many component parts, (3) many parts must
slide under heavy loads, (4) the means are not suitable for heavily
loaded frequent cycles of operation, etc.
[0035] With conventional high-reduction pressing means known in the
prior art, the position of the dies is controlled to adjust the
thickness of the material to be pressed by means of a screw, wedge,
hydraulic cylinder, etc., and, as a result, there are the practical
problems that the equipment is large, costly, complicated, and
vibrates considerably.
[0036] 3. Conventionally, a roughing-down mill is used to roll a
slab. The slab to be rolled is as short as 5 m to 12 m, and the
slab is rolled by a plurality of roughing-down mills or by
reversing mills in which the slab is fed forwards and backwards as
it is rolled. In addition, a reduction press machine is also used.
Recently, because a long slab manufactured by a continuous casting
system has been introduced, there is a demand for the continuous
transfer of the slab to a subsequent pressing system. When a
material is rough rolled using a roughing-down mill, the minimum
nip angle (about 17.degree.) must be satisfied, so the reduction
limit .DELTA.t per pass is about 50 mm. Because the slab is
continuous, reverse rolling is not applicable, so that to obtain
the desired thickness, a plurality of roughing-down mills must be
installed in series, or if a single rolling mill is to be employed,
the diameter of the work rolls should be very large.
[0037] Consequently, a reduction press machine is used. FIG. 5
shows an example of such a machine in which the dies are pressed by
sliders, to provide a flying-press machine that can press a moving
slab. Dies 32 provided above and below the slab 1 are mounted on
sliders 33, and the sliders 33 are moved up and down by the crank
mechanisms 34. The dies 32, sliders 33 and crank mechanisms 34 are
reciprocated in the direction of transferring the slab, by the
feeding crank mechanisms 35. The slab 1 is conveyed by pinch rolls
36 and transfer tables 37. When the slab is being reduced, the dies
32, sliders 33 and crank mechanisms 34 are moved in the direction
of transferring the slab by means of the feeding crank mechanisms
35, and the pinch rolls 36 transfer the slab 1 in synchronism with
this transfer speed. A start-stop system can also be used; the slab
1 is stopped when the system is working as a reduction press
machine and the slab is reduced, and after completing reduction,
the slab is transferred by a length equal to a pressing length, and
then pressing is repeated.
[0038] There are problems in the design and manufacturing cost of
the aforementioned roughing-down mill with large diameter rolls,
and the use of rolls with a large diameter results in a shorter
life for the rolls because of the low rolling speed and difficulty
in cooling the rolls. With the reduction press machine using
sliders and feeding crank mechanisms shown in FIG. 5, the cost of
the equipment is high because the mechanisms for reciprocating the
sliders, etc., in the direction of movement of a slab are
complicated and large in scale. In addition, the sliders vibrate
significantly in the vertical direction. With a reduction press
machine using a start-stop system, the slab must be accelerated and
decelerated repeatedly from standstill to transfer speed, and vice
versa. The slab is transferred using pinch rolls and transfer
tables, and these apparatus become large due to the high
acceleration and deceleration.
[0039] 4. When a material is reduced by a large amount, according
to the prior art, long dies were used to reduce the material while
it was fed through the dies by the length thereof during one or
several pressings. Defining the longitudinal and lateral directions
as the direction in which the pressed material is moved and the
direction perpendicular to the longitudinal direction,
respectively, the material to be pressed by a large amount in the
longitudinal direction is pressed by dies that are long in the
longitudinal direction using single pressing or by means of a
plurality of pressing operations while feeding the material to be
pressed in the longitudinal direction. FIG. 6 shows an example of
the above-mentioned reduction press machine, and FIG. 7 illustrates
its operation. The reduction press is equipped with dies 42 above
and below a material 1 to be pressed, hydraulic cylinders 43 for
pressing down the dies 42, and a frame 44 that supports the
hydraulic cylinders 43. A pressing operation is described using the
symbols L for the length of the dies 42, T for the original
thickness of the material 1 to be pressed, and t for the thickness
of the material after pressing. FIG. 7 (A) shows the state of the
dies 42 set to a location with thickness T on a portion of material
to be pressed next, adjacent to a portion with thickness t which
has been pressed. (B) shows the state in which the dies have
pressed down from the state (A). (C) is the state in which the dies
42 have been separated from the material 1 being pressed, that has
then been moved longitudinally by the pressing length L, and
completely prepared for the next pressing, which is the same state
as (A). Operations (A) to (C) are repeated until all the material
is reduced to the required thickness.
[0040] The longer the dies, the greater the force that is required
for reduction, so the reduction press machine must be large. With a
press machine, pressing is usually repeated at high speed. When an
apparatus with a large mass is reciprocated at a high speed, a
large power is required to accelerate and decelerate the apparatus,
therefore the ratio of the power required for acceleration and
deceleration to the power needed for reducing the material to be
pressed is so large that much power is spent on driving the
apparatus. When the material is reduced, the volume corresponding
to the thinned portion must be displaced longitudinally or
laterally because the volumes of the material before and after
reduction are substantially the same. If the dies are long, the
material is constrained so that it is displaced longitudinally
(this phenomenon is called material flow), so that pressing becomes
difficult especially when the reduction is large.
[0041] When a material to be rolled is reduced conventionally in a
horizontal mill, the gap between the rolls of the horizontal mill
is set so that the rolls are capable of gripping the material to be
rolled considering the thickness of the material after forming,
therefore the reduction in thickness allowed for a single pass is
limited so that when a large reduction in the thickness is
required, a plurality of horizontal mills have to be installed in
series, or the material must be moved backwards and forwards
through a horizontal mill while the thickness is gradually reduced,
according to the prior art. Another system was also proposed in the
unexamined Japanese patent publication No. 175011, 1990; eccentric
portions are provided in rotating shafts, the motion of the
eccentric portions is changed to an up/down movement using rods,
and a material to be pressed is reduced continuously by these
up/down movements.
[0042] The system with a plurality of horizontal mills arranged in
tandem (series) has the problems that the equipment is large and
the cost is high. The system of passing a material to be pressed
backwards and forwards through a horizontal mill has the problems
that the operations are complicated and a long rolling time is
required. The system disclosed in the unexamined Japanese patent
application No. 175011, 1990 has the difficulty that large
equipment must be used, because a fairly large rotating torque must
be applied to the rotating shafts to produce the required reducing
force as the movement of the eccentric portions of the rotating
shafts has to be changed to an up/down motion to produce the
necessary reducing force.
[0043] 5. Conventionally, a roughing-down mill is used to press a
slab. The slab to be pressed is as short as 5 to 12 m, and to
obtain the specified thickness, a plurality of roughing-down mills
are provided, or the slab is moved backwards and forwards as it is
pressed in the reversing rolling method. Other systems also used
practically include a flying press machine that transfers a slab
while it is being pressed, and a start-stop reduction press machine
which stops conveying the material as it is being pressed and
transfers the material during a time when it is not being
pressed.
[0044] Since long slabs are produced by continuous casting
equipment, there is a practical demand for a slab to be conveyed
continuously to a subsequent press apparatus. When a slab is rough
rolled in a roughing-down mill, there is a nip angle limitation
(about 17.degree.), so the reduction per rolling cannot be made so
large. Because the slab is continuous, it cannot be rolled by
reverse rolling, therefore to obtain the preferred thickness, a
plurality of roughing-down mills must be installed in series, or if
a single mill is involved, the diameter of the work rolls must be
made very large. There are difficulties, in terms of design and
cost, in manufacturing such a roughing-down mill with
large-diameter rolls, and large diameter rolls must be operated at
a low speed when rolling a slab, so the rolls cannot be easily
cooled, and the life of the rolls becomes shorter. Because a flying
press can provide a large reduction in thickness and is capable of
reducing a material while it is being conveyed, the press can
continuously transfer the material being pressed to a downstream
rolling mill. However, it has been difficult to adjust the speed of
the material to be pressed so that the flying press and the
downstream rolling mill can operate simultaneously to reduce and
roll the material. In addition, it has not been possible to arrange
a start-stop reduction press machine and a rolling mill in tandem
to reduce a slab continuously; with the start-stop reduction press,
the material being pressed is stopped during pressing, and is
transferred when it is not being pressed.
[0045] Another system in practical use is the flying system in
which the sliders that press down on a slab are moved up and down
in synchronism with the transfer speed of the slab.
[0046] In the start-stop system, the heavy slab is accelerated and
decelerated every cycle from standstill to the maximum speed Vmax,
and accordingly the capacity of the transfer facilities such as the
pinch rolls and transfer tables must be large. Because of the
discontinuous operation, it is difficult to carry out further
operations on a downstream press machine. The flying system
requires a large capacity apparatus to produce the swinging motion,
and to accelerate and decelerate the heavy sliders according to the
speed of the slab. Another problem with this system is that this
large capacity apparatus for producing the swinging motion causes
considerable vibrations in the press machine.
[0047] Still another problem with this system is that if the speed
of the slab deviates from that of the sliders, flaws may be
produced in the slab or the equipment may be damaged.
[0048] Recently, a high-reduction press machine that can reduce a
thick slab (material to be pressed) to nearly 1/3 of its original
thickness in a single reduction operation, has been developed. FIG.
8 shows an example of a reduction press machine used for hot
pressing. With this reduction press machine, dies 52a, 52b are
disposed opposite each other vertically on opposite sides of the
transfer line S, and are simultaneously moved towards and away from
a material 1 to be pressed that travels on the transfer line S by
the reciprocating apparatus 53a, 53b incorporating eccentric axes,
rods, and hydraulic cylinders, so that material of a thickness of,
for example, 250 mm can be reduced to 90 mm by a single reducing
operation.
[0049] However, the reduction of the aforementioned high-reduction
press machine can be as large as 160 mm, that is, the reduction on
one side is as large as 80 mm. According to the prior art, there is
a small difference of thickness before and after pressing, so the
transfer levels of the transfer devices of a press machine on the
inlet and outlet sides are substantially the same. With the
above-mentioned high-reduction press machine, however, there is the
problem that the material 1 to be pressed is bent if the transfer
levels are identical. Another problem of the machine is that the
transfer device is overloaded.
SUMMARY OF THE INVENTION
[0050] 1. The present invention has been accomplished under the
circumstances mentioned above, and the first object of the present
invention is to provide a plate reduction press apparatus and
methods that can efficiently reduce a material to be shaped in the
direction of the thickness of the plate, can securely transfer the
material to be shaped, can decrease the load imposed on the dies
during reduction, and can prevent bending of the material to be
shaped to the left or right as a result of the reducing and forming
operations.
[0051] To achieve the aforementioned first object of the present
invention, in the plate reduction pressing method of the present
invention, dies with convex forming surfaces protruding towards the
transfer line are moved towards the transfer line from above and
below the material to be shaped, when viewed from the side of the
transfer line, in synchronism with the movement of the material to
be shaped, in such a manner that a portion of the forming surfaces
of the material is moved from the upstream side to the downstream
side of the transfer line and the material to be shaped is reduced
in the direction of the plate thickness.
[0052] The plate thickness reduction press apparatus of another
embodiment of the present invention, is provided with die holders
arranged opposite each other above and below a transfer line in
which a material to be shaped is moved horizontally, dies mounted
on the above-mentioned die holders and comprised of convex forming
surfaces protruding towards the transfer line when viewed from the
side of the transfer line, upstream eccentric shafts arranged for
each die holder on the opposite side from the transfer line and
extending in the direction lateral to the transfer line, downstream
eccentric shafts arranged for each die holder on the opposite side
from the transfer line in alignment with the aforementioned
upstream eccentric shafts, in the downstream direction of the
transfer line, and comprised of eccentric portions with a different
phase angle from the phase angle of the eccentric portions of the
upstream eccentric shafts, upstream rods whose tips are connected
to portions of the die holders, close to the ends on the upstream
side of the transfer line through bearings and the other ends of
which are connected to the eccentric portions of the upstream
eccentric shafts through bearings, downstream rods whose tips are
connected to portions of the die holders, close to the ends on the
downstream side of the transfer line through bearings and the other
ends of which are connected to the eccentric portions of the
downstream eccentric shafts through bearings, and mechanisms for
moving the dies backwards and forwards that reciprocate the
above-mentioned die holders relative to the direction of the
transfer line.
[0053] According to the plate reduction press apparatus of another
embodiment of the present invention, the mechanisms for moving the
dies backwards and forwards in the plate press apparatus are
provided with arms one end of each of which is fixed to the die
holder, and guide members which are installed near the die holders
and guide the other end of each of the arms.
[0054] In the plate reduction press apparatus according to the
invention, the mechanisms for moving the dies backwards and
forwards are provided with actuators one end of each of which is
connected to one of the die holders through a first bearing and the
other end of each thereof is connected to a predetermined fixing
member through a second bearing.
[0055] The plate reduction press apparatus of another embodiment of
the present invention is composed of the mechanisms for moving the
dies backwards and forwards in the plate reduction press apparatus,
comprised of eccentric shafts for backwards and forwards movements,
provided near the die holders and rods for backwards and forwards
movements, one end of each of the aforementioned rods being
connected to one of the die holders through a first bearing and the
other end thereof being connected to one of the eccentric portions
of the eccentric shafts for backwards and forwards movements.
[0056] In the plate reduction press apparatus of a still further
embodiment of the invention, the mechanisms for moving the dies
backwards and forwards in the plate reduction press apparatus of
the present invention are composed of levers one end of each of
which is connected to one of the die holders through a first
bearing and the other end thereof is connected to a predetermined
fixing member through a second bearing.
[0057] According to the plate reduction pressing method of the
present invention, dies with convex forming surfaces protruding
towards the transfer line are moved towards the transfer line from
above and below the material to be shaped in synchronism with the
movement of the material to be shaped, and given a swinging motion
such that the portions of the forming surfaces in contact with the
material to be shaped move from the downstream side of the transfer
line to the upstream side thereof, thereby the areas of the
material being shaped, in contact with the forming surfaces, are
made small to reduce the pressing load on the dies.
[0058] In any of the plate reduction press apparatus according to
the present invention, the die holders on which the dies are
mounted are given a swinging motion by the upstream eccentric
shafts, downstream eccentric shafts, upstream rods and downstream
rods in such a manner that the portions of the forming surfaces of
the dies, in contact with the material to be shaped, are shifted
from the downstream side to the upstream side of the transfer line,
while moving the dies towards the transfer line, thereby the areas
of the forming surfaces in contact with the material to be shaped
are made small to reduce the load applied to the dies during
pressing.
[0059] Also, when the forming surfaces of the dies are in contact
with the material to be shaped, the mechanisms for moving the dies
backwards and forwards move the die holders towards the downstream
side of the transfer line, and convey the material being reduced
and formed without any material being displaced backwards, towards
the downstream side of the transfer line.
[0060] To achieve the above-mentioned first object of the present
invention, the plate reduction press apparatus according to one
embodiment of the invention is provided with dies arranged
vertically opposite each other on opposite sides of a transfer line
in which a material to be shaped is transferred horizontally, and
moving towards and away from the transfer line in synchronism with
each other, a plurality of upstream table rollers arranged on the
upstream side of the dies on the transfer line in such a manner
that the lower surface of the material to be shaped, which is to be
inserted between the dies, can be supported substantially
horizontally, a plurality of downstream up and down table rollers
arranged on the downstream side of the dies on the transfer line in
such a manner that the downstream up and down table rollers can be
raised and lowered and can support the lower surface of the
material being shaped and fed out of the dies, and a plurality of
downstream table rollers arranged on the downstream side of the
downstream up and down table rollers on the transfer line in such a
manner that the lower surface of the material being shaped and fed
out of the dies can be supported substantially horizontally at a
height substantially the same as the height of the aforementioned
upstream table rollers.
[0061] The plate reduction press apparatus according to a further
embodiment of the invention is provided with dies arranged
vertically opposite each other on opposite sides of a transfer line
in which a material to be shaped is transferred horizontally, and
moving towards and away from the transfer line in synchronism with
each other, a plurality of upstream up and down table rollers on
the upstream side of the dies on the transfer line in such a manner
that the upstream up and down table rollers can be raised and
lowered, and the lower surface of the material to be shaped, which
is to be inserted between the dies, can be supported, and a
plurality of downstream table rollers arranged on the downstream
side of the dies on the transfer line in such a manner that the
lower surface of the material being shaped and fed out of the dies
can be supported.
[0062] The plate reduction press apparatus according to yet another
embodiment of the present invention is comprised of dies arranged
vertically opposite each other on opposite sides of a transfer line
in which a material to be shaped is transferred horizontally, and
moving towards and away from the transfer line in synchronism with
each other, a plurality of upstream up and down table rollers on
the upstream side of the dies on the transfer line in such a manner
that the upstream up and down table rollers can be raised and
lowered, and the lower surface of the material to be shaped, which
is to be inserted between the dies, can be supported, and a
plurality of downstream up and down table rollers arranged on the
downstream side of the dies in such a manner that the lower surface
of the material being shaped and fed out of the dies can be
supported.
[0063] According to the method of operating the plate reduction
press apparatus according to one embodiment of the invention, when
a long material to be shaped is inserted, reduced and formed in the
direction of plate thickness between both dies, the vertical
positions of the downstream up and down table rollers near the dies
are determined in such a manner that the material being shaped and
fed out of the dies is substantially horizontal, and the vertical
positions of the downstream up and down table rollers on the side
farther from the dies are determined in such a manner that the
material being shaped gradually descends towards the downstream
table rollers.
[0064] In the method of operating the plate reduction press
apparatus according to one embodiment, when a long material to be
shaped is inserted, reduced and formed in the direction of the
plate thickness between both dies, the vertical positions of the
upstream up and down table rollers near the dies are determined in
such a manner that the material to be shaped, which is to be
inserted between the dies, is substantially horizontal.
[0065] According to a further embodiment of the present invention
for operating the plate reduction press apparatus, when a long
material to be shaped is inserted, reduced and formed in the
direction of the plate thickness between both dies, the vertical
positions of the upstream up and down table rollers near the dies
and the downstream up and down table rollers are determined in such
a manner that the material to be shaped, which is to be inserted
between the dies, and the material being shaped and fed out of the
dies are substantially horizontal.
[0066] In the method according to a further embodiment of the
present invention for operating the plate reduction press apparatus
of the invention, the positions of the upper surfaces of the
downstream up and down table rollers are determined to be identical
to the positions of the upper surfaces of the upstream table
rollers and the downstream table rollers, when no long material to
be shaped is inserted, or being reduced or formed in the direction
of the plate thickness between both dies.
[0067] When using the plate reduction press apparatus of the
present invention according to the method of another embodiment of
the invention, the positions of the upper surfaces of the upstream
up and down table rollers are determined to be identical to the
positions of the upper surfaces of the downstream table rollers,
when no long material to be shaped is inserted, or being reduced or
formed in the direction of the plate thickness between both
dies.
[0068] In the method for operating the plate reduction press
apparatus according to one embodiment of the present invention,
when no long material to be shaped is inserted, or being reduced or
formed in the direction of the plate thickness between both dies,
the positions of the upper surfaces of the upstream up and down
table rollers and the downstream table rollers are determined to be
identical to each other.
[0069] With the plate reduction press apparatus of one embodiment
of the present invention, the vertical positions of the downstream
up and down table rollers located on the transfer line downstream
of the dies are adjusted according to the amount of the reduction
in the direction of the plate thickness of the material being
shaped by the dies, and the lower surface of the material being
shaped and fed out from the dies is maintained in the most suitable
state.
[0070] In the plate reduction press apparatus of another embodiment
of the present invention, the vertical positions of the upstream up
and down table rollers located on the transfer line upstream of the
dies are adjusted according to the amount of the reduction in the
direction of the plate thickness of the material to be shaped, and
the lower surface of the material to be inserted between the dies
and shaped is maintained in the most suitable state.
[0071] In the plate reduction press apparatus according to one
embodiment of the present invention, the vertical positions of the
upstream up and down table rollers located on the transfer line
upstream of the dies and the downstream up and down table rollers
located on the transfer line downstream of the dies are adjusted
according to the amount of the reduction in the direction of the
plate thickness of the material being formed by the dies, and the
lower surface of the material being shaped and fed out from between
the dies is maintained in the most suitable state.
[0072] When using the plate reduction press apparatus of the
invention according to the method of one embodiment, the vertical
positions of the downstream up and down table rollers on the
portion of the transfer line near to the press machine are
determined in such a manner that the material being reduced, shaped
and fed out from between the dies is substantially horizontal, and
the vertical positions of the downstream up and down table rollers
farther down the transfer line are determined in such a manner that
the material being shaped and fed out of the aforementioned
downstream up and down table rollers gradually descends towards the
downstream table rollers, and the portion of the material being
reduced and shaped is moved smoothly.
[0073] According to the method of one embodiment of the present
invention for operating the plate reduction press apparatus of the
invention, the vertical positions of the upstream up and down table
rollers near the dies are determined in such a manner that a long
material to be shaped, which is to be inserted between the dies, is
substantially horizontal, when the long material to be shaped is
inserted, reduced and formed in the direction of the plate
thickness between both dies, the portion of the material to be
reduced and shaped is moved smoothly.
[0074] When the plate reduction press apparatus of the present
invention is operated according to the method of one embodiment of
the invention, the vertical positions of the upstream up and down
table rollers and the downstream up and down table rollers are
determined in such a manner that the material being reduced, shaped
and fed out from between the dies is substantially horizontal, and
the portion of the material to be reduced and shaped and the
portion of the material being reduced and shaped are moved
smoothly.
[0075] According to the method of the present invention for
operating the high-reduction press apparatus of the invention, the
vertical positions of the downstream up and down table rollers are
determined to correspond with the positions of the upstream table
rollers and the downstream table rollers, and material passed
between the dies without being reduced and shaped is moved
smoothly.
[0076] When the plate reduction press apparatus of the present
invention is operated by the method of a further embodiment, the
positions of the upper surfaces of the upstream up and down table
rollers are determined to be identical to the positions of the
upper surfaces of the downstream table rollers, and material passed
between the dies without being reduced and formed is moved
smoothly.
[0077] In the method of the present invention for operating the
high-reduction press apparatus according to one embodiment of the
invention, the vertical positions of the upstream up and down table
rollers and the downstream up and down table rollers are determined
to be the same as each other, and material passed between the dies
without being reduced and shaped is moved smoothly.
[0078] Furthermore, according to the plate reduction pressing
method according to one embodiment of the present invention for
achieving the aforementioned first object of the invention, a first
reduction in plate thickness is performed; in this sub-method the
material to be shaped is transferred from the upstream side of the
transfer line to the downstream side of the transfer line, upstream
dies with forming surfaces facing the above-mentioned material to
be shaped are moved towards the material to be shaped as the
upstream dies are moved in the downstream direction of the transfer
line and the upstream dies are moved away from the material to be
shaped as the upstream dies are moved in the upstream direction of
the transfer line, in synchronism with each other, and the
aforementioned material to be shaped is reduced and shaped in the
direction of the plate thickness sequentially, and then the second
reduction in plate thickness is carried out; in this sub-method,
downstream dies with forming surfaces facing the above-mentioned
material to be shaped are moved towards the material being shaped
in the opposite phase to the phase of the upstream dies while the
downstream dies are moved in the downstream direction of the
transfer line from above and below a portion of the material, whose
thickness has been reduced by the first plate thickness reduction
sub-method, and the downstream dies are moved away from the
material being shaped as the downstream dies are moved in the
upstream direction of the transfer line, in synchronism with each
other, and the material which has been shaped by the first plate
reduction is further reduced and shaped in the direction of the
plate thickness sequentially.
[0079] With the plate reduction press apparatus according to a
further embodiment of the present invention, upstream sliders are
arranged vertically opposite each other on opposite sides of a
transfer line; in which a material to be shaped is transferred,
mechanisms for moving the upstream sliders move the above-mentioned
upstream sliders towards the transfer line and move the upstream
sliders away from the transfer line, upstream dies are mounted on
the upstream sliders in such a manner that the upstream dies can
move along the direction of the transfer line, and are comprised of
forming surfaces facing the transfer line, mechanisms for moving
the upstream dies move the above-mentioned upstream dies in a
reciprocating manner in the direction of the transfer line,
downstream sliders are located on the transfer line downstream of
the upstream sliders, opposite each other on opposite sides of the
transfer line, mechanisms for moving the downstream sliders move
the downstream sliders towards the transfer line and move the
downstream sliders away from the transfer line, downstream dies are
mounted on the downstream sliders in such a manner that the
downstream dies can move along the direction of the transfer line,
and are comprised of forming surfaces facing the transfer line, and
mechanisms for moving the downstream dies move the downstream dies
in a reciprocating manner in the direction of the transfer
line.
[0080] The plate reduction press apparatus according to a further
embodiment of the present invention is provided with, in addition
to the components of the plate reduction press apparatus of the
invention, mechanisms for moving the upstream sliders comprised of
upstream crank shafts arranged on the opposite side of the upstream
sliders from the transfer line, and upstream rods one end of each
of which is connected to an eccentric portion of one of the
upstream crank shafts through a first bearing and the other end of
each of which is connected to one of the upstream sliders through a
second bearing, and mechanisms for moving the downstream slider
comprised of downstream crank shafts arranged on the opposite side
of the downstream sliders from the transfer line, and downstream
rods one end of each of which is connected to an eccentric portion
of one of the downstream crank shafts through a third bearing and
the other end of each of which is connected to one of the
downstream sliders through a fourth bearing.
[0081] Furthermore, the plate reduction press apparatus in one
embodiment of the present invention is provided with, in addition
to the component devices of the plate reduction press apparatus of
the invention as described above, a synchronous drive mechanism
that rotates the upstream crank shafts and the downstream crank
shafts in synchronism in the same direction in such a manner that
the eccentric portions of both of the upstream and downstream crank
shafts maintain a phase difference of 180.degree..
[0082] Moreover, the plate reduction press apparatus of a further
embodiment of the present invention is comprised of, in addition to
the component devices of the plate reduction press apparatus of the
invention, upstream crank shafts and downstream crank shafts
supported by bearings in such a manner that both the
above-mentioned crank shafts are substantially parallel to the
direction orthogonal to the transfer line.
[0083] In the plate reduction pressing method according to one
embodiment of the present invention, an unreduced and unformed
portion of the material to be shaped is reduced and formed in the
direction of its plate thickness by the upper and lower upstream
dies, in the first plate thickness reduction sub-method, and then
the portion of the material to be shaped, that has been reduced and
formed, is further reduced and formed in the direction of its plate
thickness by the upper and lower downstream dies, in the second
plate thickness reduction sub-method, thereby the material to be
shaped is reduced and shaped efficiently in the direction of its
plate thickness.
[0084] In addition, the first and second plate thickness reduction
sub-methods are operated alternately on an unreduced and unformed
portion and a partially reduced portion of the material to be
shaped, respectively, in order to reduce the loads applied to the
upstream and downstream dies during reduction.
[0085] In any of the plate reduction press apparatus of the present
invention, the mechanisms for moving the upstream sliders move the
upstream dies towards the transfer line together with the upstream
sliders, and an unreduced and unformed portion of the material to
be shaped is reduced in the direction of its plate thickness by the
upper and lower upstream dies, and then the mechanisms for moving
the downstream sliders move the downstream sliders and downstream
dies towards the transfer line, and the portion of the material to
be shaped, already reduced by the upstream dies, is further reduced
in the direction of its plate thickness by the upper and lower
downstream dies, thus the material to be shaped is reduced and
formed efficiently in the direction of its plate thickness.
[0086] In addition, the upstream and downstream dies are moved
towards and away from the transfer line, in the opposite phase to
each other, by means of the mechanisms for moving the upstream and
downstream sliders, respectively, so that the loads applied to the
upstream and downstream dies during reduction are made smaller.
[0087] According to the plate reduction press apparatus of one
embodiment of the present invention, as invented to achieve the
first object of the invention, a pair of dies are arranged opposite
each other on opposite sides of a transfer line of a material to be
shaped and moved toward and away from each other in synchronism
with each other, upstream side guides are arranged in the close
vicinity of the aforementioned dies in the upstream direction of
the transfer line in such a manner that the upstream side guides
are opposite each other in the lateral direction of the material to
be shaped on opposite sides of the transfer line, and comprised of
a first pair of side guide units that can move towards and away
from the transfer line, and downstream side guides arranged in the
close vicinity of the above-mentioned dies in the downstream
direction of the transfer line in such a manner that the downstream
side guides are opposite each other in the lateral direction of the
material being shaped on opposite sides of the transfer line, and
comprised of a second pair of side guide units that can move
towards and away from the transfer line.
[0088] The plate reduction press apparatus of the present invention
is provided with a pair of dies arranged opposite each other on
opposite sides of a transfer line of a material to be shaped and
moved towards and away from each other in synchronism with each
other, upstream side guides arranged in the close vicinity of the
aforementioned dies in the upstream direction of the transfer line
in such a manner that the upstream side guides are opposite each
other in the lateral direction of the material to be shaped on
opposite sides of the transfer line, and comprised of a first pair
of side units that can move towards and away from the transfer
line, upstream vertical rollers supported by the corresponding
upstream side guides in such a manner that the upstream vertical
rollers can contact the lateral edges of the material to be shaped,
when the material passes between the above-mentioned upstream side
guides, downstream side guides arranged in the close vicinity of
the aforementioned dies in the downstream direction of the transfer
line in such a manner that the down stream side guides are opposite
each other in the lateral direction of the material being shaped on
opposite sides of the transfer line, and comprised of a second pair
of side guide units that can move towards and away from the
transfer line, and downstream vertical rollers supported by the
corresponding downstream side guides in such a manner that the
downstream vertical rollers can contact the lateral edges of the
material being shaped, when the material passes between the
downstream side guides.
[0089] In any of the plate reduction press apparatus according to
one embodiment of the present invention, a material to be reduced
and shaped is moved from the upstream side to the downstream side
of the transfer line, guided into the upper and lower dies by the
left and right side guide units of the upstream side guides, the
material to be shaped, after being reduced and formed by the dies
and fed out on the downstream side of the transfer line, is
prevented from being deflected to the left or right, by the left
and right side guide units of the downstream side guides.
[0090] With the plate reduction press apparatus according to one
embodiment of the present invention, when the material to be shaped
is guided into the dies by the left and right side guide units of
the upstream side guides, the lateral edges of the material are
guided by the upstream vertical rollers to protect the lateral
edges of the material to be shaped from rubbing against the side
guide units, and the lateral edges of the material to be shaped are
restrained by the left and right side guide units of the downstream
side guides to prevent the material to be shaped from being
deflected to the left or right, and guided by the downstream
vertical rollers to protect the lateral edges of the material to be
shaped from rubbing against the side guide units.
[0091] 2. The second object of the present invention is to provide
a plate reduction press apparatus with (1) the capability of a
flying press apparatus that can reduce a material to be pressed
while it is being moved, (2) small number of component parts and a
simple configuration, (3) a reduced number of portions that slide
under load, (4) the capability for operating under a heavy load at
a high operating rate, and (5) a simply constructed means of
adjusting the positions of the dies and correcting the thickness of
a material to be pressed.
[0092] The plate reduction press apparatus according to one
embodiment of the present invention offers a plate reduction press
apparatus provided with upper and lower drive shafts arranged
opposite each other above and below a material to be pressed, and
made to rotate, upper and lower press frames one end of each of
which engages with one of the aforementioned drive shafts in a
freely slidable manner, and the other ends of which are connected
together in a freely rotatable manner, a horizontal guide device
that supports the above-mentioned press frames at the point of
connection in a manner that allows them to slide in the horizontal
direction, and upper and lower dies mounted at the ends of the
upper and lower press frames, opposite the material to be pressed,
in which the upper and lower drive shafts are constructed as a pair
of eccentric shafts that are located at both lateral ends and which
have a phase difference relative to each other, and the upper and
lower dies that are opened and closed with a rolling action by
rotating the drive shafts, and the material to be pressed is
transferred as the material is being pressed.
[0093] According to the configuration of the present invention as
described above, when the drive shafts are rotated, the upper and
lower dies move in a circular path, while rolling laterally at the
same time, and are opened and closed by the pair of eccentric
shafts of which the phase angles are shifted relative to each
other. Consequently, the material to be pressed can be conveyed
while being pressed, because the upper and lower dies move in the
direction of the line while they are closing. In addition, because
the upper and lower dies close with a rolling action, the load
during pressing can be reduced. The amount of reduction is
determined by the eccentricity of the eccentric shafts, so
high-reduction pressing is possible without being limited by a nip
angle, etc. Moreover, because the material to be pressed is
conveyed while being reduced, the apparatus operates as a flying
press.
[0094] In addition, only the eccentric shafts withstand loads
during pressing, and the horizontal guide device is acted on by
only a rather small load that only cancels the moments applied to
the press frames, and furthermore, the moments applied to the upper
and lower press frames cancel each other, so that the load imposed
on the horizontal guide device is further reduced. Therefore, the
construction can be simplified with a small number of component
parts, and with a small number of portions that slide under load
during pressing, and as a result, the apparatus can operate with
high loads at a high operating frequency.
[0095] According to the plate reduction press apparatus according
to a further embodiment of the present invention, a driving device
to rotate and drive the drive shafts is provided, and the
rotational speed of the driving device can be varied, and the
rotational speed is determined in such a manner that the speed of
moving the dies during reducing substantially matches the speed of
feeding the material to be pressed.
[0096] With this configuration, the speed of the dies in the line
direction can be made to be substantially equal to the speed of
feeding the material to be pressed (a slab), so the load on the
driving device that rotates and drives the drive shafts can be
reduced.
[0097] The plate reduction press apparatus according to a further
embodiment is provided with a looper device that creates a slack
portion in the material to be pressed on the downstream side and
holds up the material. In this configuration, the looper device can
absorb deviations between the speed of the dies in the line
direction and the speed of feeding the material to be pressed, so
that the line speed can be synchronized with a finish rolling mill
located further downstream.
[0098] The plate reduction press apparatus according to a further
embodiment of the present invention provides a plate reduction
press apparatus configured with upper and lower crank shafts
arranged opposite each other above and below a material to be
pressed and made to rotate, upper and lower press frames one end of
each of which engages with one of the aforementioned crank shafts
in a freely slidable manner, and the other ends of which are
connected together in a freely rotatable manner, horizontal guide
devices that support the above-mentioned press frames at the point
of connection in a manner that allows them to move horizontally,
and upper and lower dies mounted at the ends of the upper and lower
press frames, opposite the material to be pressed; in which the
crank shafts rotate to open and close the upper and lower dies, so
transferring the material while pressing the material to be
pressed, the material is transferred.
[0099] According to the above configuration based on the present
invention, the upper and lower dies move in a circular path when
the crank shafts rotate, and open and close. Consequently, as the
upper and lower dies move in the direction of the line while
closing, the material to be pressed can be conveyed while being
reduced. The amount of reduction is determined by the eccentricity
of the crank shafts, therefore high-reduction pressing is possible
without being limited by a nip angle, etc. Also, the apparatus
operates as a flying press because the material to be pressed is
transferred while being reduced.
[0100] In addition, only the crank shafts withstand loads during
pressing, and because the horizontal guide devices are acted on by
only relatively small loads that are sufficient to only cancel the
moments acting on the press frames, and also because the moments
applied to the upper and lower press frames cancel each other, the
loads on the horizontal guide devices become still smaller. As a
result, the construction of the apparatus is made simple with few
component parts, and with a small number of components that slide
under load during pressing, so that the apparatus can operate with
large loads at a high operating frequency.
[0101] With the plate reduction press apparatus according to yet
another embodiment of the present invention, a driving device for
rotating and driving the crank shafts is provided, and the
rotational speed of the driving device is variable and is
determined in such a manner that the speed of the dies in the line
direction during pressing substantially matches the speed of
feeding the material to be pressed.
[0102] With this configuration mentioned above, the speed of the
dies in the line direction can be made to be substantially the same
as the speed of feeding the material to be pressed (a slab), so the
load on the driving device that rotates and drives the crank shafts
can be reduced.
[0103] The plate reduction press apparatus according to another
embodiment is provided with a looper device that creates a slack
portion in the material to be pressed on the downstream side and
holds up the material. Using this configuration, the looper device
can absorb differences between the speed of the dies in the line
direction and the speed of feeding the material to be pressed, so
that the speed of the line can be synchronized with that of a
finish rolling mill located further downstream.
[0104] The plate reduction press apparatus according to another
embodiment is provided with up and down height adjusting plates
that are maintained between the dies and the press frames, and the
plates adjust the heights of the dies. By replacing these height
adjusting plates, the heights of the dies can be adjusted freely,
so compared to a conventional screw mechanism, etc., the
construction of the apparatus can be made tougher, simpler, and
more compact than a conventional one, consequently, the apparatus
vibrates less and fails less often than a conventional machine, so
the apparatus according to the present invention can be maintained
more easily whilst the cost is reduced.
[0105] According to a further embodiment of the present invention,
a hot slab pressing method is provided in which the feeding speed
of the material to be pressed is made variable, relative to the
maximum speed of the dies in the line direction. According to a
preferred embodiment of the present invention, the speed of feeding
the material to be pressed is varied in such a manner that at the
beginning of pressing, the speed is made greater than the
aforementioned maximum speed, and is made smaller at the
intermediate and final stages.
[0106] The plate reduction press apparatus according to another
embodiment of the present invention is comprised of upper and lower
eccentric drive shafts arranged opposite each other above and below
a material to be pressed and made to rotate, upper and lower
synchronous eccentric shafts that rotate around the axes of the
above-mentioned eccentric drive shafts, upper and lower press
frames one end of each of which engages with one of the synchronous
eccentric shafts in a freely slidable manner, and the other ends of
which are connected together in a freely rotatable manner, and
upper and lower dies mounted at the ends of the upper and lower
press frames, facing the material to be pressed; in which the upper
and lower dies are opened and closed by rotating the upper and
lower eccentric drive shafts, and when the material to be pressed
is pressed by the dies, the synchronous eccentric shafts
synchronize the speed of the press frames in the direction of the
transfer line with the speed of the material to be pressed in the
direction of the transfer line.
[0107] With the configuration mentioned above according to the
present invention, when the drive shafts are rotated, the upper and
lower eccentric shafts rotate around fixed axes, and due to the
rotation of the eccentric shafts, the upper and lower dies move in
circular paths while opening and closing. As a result, the upper
and lower dies can convey the material to be pressed in the
direction of the line while reducing the material, by synchronizing
the speed of the press frames in the direction of the line with the
speed of the material to be pressed by means of the synchronous
eccentric shafts during pressing with the dies. In this way, the
amount of the reduction is determined by the eccentricity of the
eccentric shafts without any nip angle restriction, etc., so
high-reduction pressing can be carried out.
[0108] In this apparatus, only the eccentric shafts (dual-eccentric
shafts) that rotate around the axes of the fixed shafts withstand
loads during pressing, and only rather small loads that merely
cancel the moments acting on the press frames are applied to the
connection portions, in addition, because the moments acting on the
upper and lower press frames cancel each other, the loads are
further reduced. Therefore, there are few component parts, the
construction is simple, there are only a small number of sliding
locations which are loaded during pressing, and the apparatus can
operate with high loads at a high operating frequency.
[0109] 3. The third object of the present invention is to offer a
plate reduction press apparatus and methods by means of which a
slab is transferred while the plate thickness is being reduced with
a high reduction ratio, and for which the construction of the
apparatus is rather simple and which can reduce the slab with
little vibration, and for which the required length of the
apparatus in the line direction can be reduced.
[0110] To achieve the aforementioned third object, one embodiment
of the present invention presents a plate reduction press apparatus
provided with crank shafts arranged above and below a material to
be pressed, sliders which engage with the above-mentioned crank
shafts in a freely slidable manner and are moved with an eccentric
motion, dies mounted on the sliders facing the material to be
pressed, and a driving device for driving and rotating the crank
shafts, in which the aforementioned crank shafts are composed of
eccentric shafts that engage with the sliders, and support shafts
arranged on both sides of the eccentric shafts with shaft center
lines offset from the shaft center lines of the eccentric shafts,
and at least one of the support shafts is comprised of a
counterweight with an eccentric center substantially in a direction
at 180.degree., to the direction of eccentricity of the eccentric
shafts.
[0111] The crank shafts engage directly with the sliders, and when
the crank shafts rotate, the eccentric shafts are rotated
eccentrically about the axes of the support shafts, so the sliders
move up and down and reduce the material to be pressed, while also
moving backwards and forwards in the direction of the flow of
material to be pressed. Thus, the sliders and the dies also move in
the direction of the flow of material to be pressed during
pressing, therefore the mechanisms for feeding the material during
pressing, shown in FIG. 8, are not required. Consequently, the
apparatus operates as a flying press and has a small number of
component parts and a simple construction. In addition, because the
counterweight provided on the support shafts is offset in a
direction substantially 180.degree. to the eccentricity of the
eccentric shafts, the accelerations and decelerations acting on the
sliders are canceled and the vibration of the apparatus is
reduced.
[0112] The plate reduction press apparatus according to another
embodiment of the present invention is comprised of upper and lower
press frames one end of each of which engages with one of the crank
shafts in a freely slidable manner and is rotated eccentrically,
and the other ends of which are connected together in a freely
rotatable manner, horizontal guide devices that restrain the press
frames at the point where they are connected together in a manner
such that they are free to move in the horizontal direction, dies
mounted at the ends of the above-mentioned press frames facing the
material to be pressed, and a driving device for driving and
rotating the aforementioned crank shafts, in which the crank shafts
are provided with eccentric shafts engaged with the above-mentioned
ends of the press frames, and support shafts arranged on both sides
of the eccentric shafts with shaft center lines eccentric to the
shaft center lines of the eccentric shafts, and at least one of the
support shafts is comprised of a counterweight with an eccentric
center substantially in a direction at 180.degree., to the
direction of eccentricity of the eccentric shafts.
[0113] In this configuration as mentioned above, the ends of the
press frames move in a circular path as the crank shafts rotate, so
the dies connected thereto move up and down and reduce the material
to be pressed, while also moving backwards and forwards in the
direction of the flow of the material to be pressed, consequently
by selecting the direction of rotation of the crank shafts, the
dies can be made to move in the direction of the flow of the
material to be pressed during pressing, that is, a flying press
operation can be achieved. The other ends of the upper and lower
press frames are connected together in a freely rotatable manner,
and are guided so that they can only move in the horizontal
direction, therefore the reaction moment imposed on one end during
pressing can be canceled by the one from the other end. The
apparatus according to this embodiment also does not require the
mechanisms for feeding the material during pressing, shown in FIG.
8. Consequently there are few components and the construction is
simple. In addition, the support shafts are provided with a
counterweight offset in a direction substantially at 180.degree. to
the direction of eccentricity of the eccentric shafts, so that
accelerations and decelerations produced at the two ends are
canceled out and the vibration of the apparatus can be reduced.
[0114] According to a further embodiment of the invention, the
aforementioned counterweight has a mass sufficient to store
rotational energy and also works as a flywheel.
[0115] As the counterweight rotates on a support shaft, it can
store rotational energy, and it functions as a flywheel by means of
a sufficient mass provided in the counterweight.
[0116] According to a still further embodiment of the invention,
the inertia force due to the eccentricity of the counterweight is
determined so as to substantially cancel out the inertia forces
from the sliders and the inertia forces of the ends of the press
frames.
[0117] Using the configuration described above, the vibration of
the reduction press apparatus can be greatly reduced.
[0118] According to a still further embodiment of the invention
which is aimed at achieving the third object mentioned above, the
apparatus is provided with dies arranged above and below a slab,
and equipped with sliders for each of the dies to give the dies an
up, down, backwards and forwards swinging motion and a driving
device for driving the sliders, in which each of the sliders is
composed of a main unit with a circular hole with its center line
in the lateral direction of the slab, and a crank with a first axis
that engages with the circular hole and a second shaft with a
diameter smaller than the diameter of the first shaft with its
center line offset from the axis of the first shaft, and the second
shaft is rotated and driven by the driving device.
[0119] When the second shaft rotates, the first shaft operates as a
crank about the center line of the second shaft, and the first
shaft engages with the circular hole and, moves the main unit up
and down, and backwards and forwards. Thereby, the sliders press
the dies, and can move the dies in a forward direction during
pressing, so that the slab is transferred forwards (in the
direction of the flow of the slab) while being reduced, therefore a
continuous pressing operation is enabled. The invention thus
provides a large amount of reduction because the dies press the
slab from both the upper and lower sides of the slab.
[0120] According to another embodiment of the invention, there are
dies arranged above or below a slab, sliders for giving the dies an
up and down and backwards and forwards swinging motion, a driving
device for driving the sliders, and slab supporting members
arranged opposite the dies above and below the slab, in which each
of the sliders is comprised of a main unit with a circular hole
with its axis in the lateral direction of the slab, a first shaft
engaged with the circular hole, and a crank composed of a second
shaft with a diameter smaller than the diameter of the first shaft
and with its center line offset from the axis of the first shaft,
and the second shaft is rotated and driven by the driving
device.
[0121] The apparatus according to this embodiment is provided with
dies either above or below the slab, and slab supporting members
are arranged opposite the dies above or below the slab, to support
the slab. Compared to the invention of the prior embodiment, the
amount of the reduction is smaller, and there is friction between
the slab and the support members when the slab being reduced moves
forwards, but the construction is simpler, and the cost can be
further reduced.
[0122] In the scope of the invention according to a still further
embodiment, the circular holes and the cranks provided in the
aforementioned sliders are arranged in pluralities in a row along
the direction of flow of the slab, and one crank accepts the force
due to the moment of the load, and the other cranks produce
pressing forces in this configuration.
[0123] By arranging pluralities of circular holes and cranks in a
row in the direction of flow of the slab (forwards), the dies can
be maintained parallel to each other. In addition, the pressing
loads can be distributed to several cranks, so the construction of
each crank can be made simpler.
[0124] In the invention according to yet another embodiment, the
circular holes and the cranks provided in the above-mentioned
sliders are arranged in pluralities in a row, and one crank accepts
the force due to the load moments, and the other cranks are
configured to produce pressing forces.
[0125] With this configuration, one crank bears the forces due to
the unbalanced moments of the loads, and the other cranks generate
only pressing forces, so the overall efficiency of a press machine
can be increased.
[0126] With the invention according to still a further embodiment,
the slab is conveyed by pinch rolls or tables, and when the sliders
press the slab, it is conveyed at the same speed as the speed of
the sliders in the forward direction.
[0127] When the sliders press the slab, the slab is transferred at
the same speed as the forward speed of the sliders, and at other
times, the slab is conveyed at an appropriate speed, for example, a
speed synchronized with that of a subsequent machine. In this way,
the slab can be reduced most suitably and conveyed
continuously.
[0128] In the invention according to another embodiment, the
distance L in which the slab moves in a cycle of the pressing
period plus the period with a normal transfer speed, is not longer
than the length L1 of the dies in the direction of flow of the
slab.
[0129] Because the distance L slab 1 moves per cycle is no longer
than the length L1 of the dies in the direction of flow of the
slab, the reduction length for the next cycle is slightly
superimposed on the length reduced in the previous cycle. Thus, the
reduction in thickness can be properly accomplished.
[0130] According to a further embodiment of the present invention,
aimed at achieving the third object mentioned above, the plate
reduction press apparatus is provided with a pair of dies arranged
opposite each other above and below a slab, and a swinging device
that gives each of the dies a swinging motion backwards and
forwards, towards the slab, and eccentric shafts rotating in the
above-mentioned circular holes, in which each of the aforementioned
eccentric shafts is comprised of a first shaft rotating in a
circular hole with center line A on the same axis as the circular
hole, and driving a second shaft with a center line B offset from
that of the first shaft by a difference e.
[0131] According to this configuration, the two eccentric shafts
rotating in a pair of circular holes in the sliders are located at
an inclined angle or perpendicular to the direction of feeding the
slab, therefore compared to the case in which the eccentric shafts
are installed parallel to the line direction, the required length
of the apparatus in the direction of the line can be reduced. In
particular, when the eccentric shafts are arranged at an inclined
angle, the pressing forces acting on the two eccentric shafts can
be shared equally, so that the length of the apparatus in the
direction of the line can be reduced at the same time as giving
equal loading to each eccentric shaft. When the eccentric shafts
are installed perpendicular to the direction of feed of the slab,
it is possible to load the inner eccentric shafts more than the
outer ones, and to make the outer eccentric shafts smaller.
[0132] Another embodiment of the present invention provides a plate
reduction pressing method using a pair of dies arranged opposite
each other above and below a slab, and a swinging device that moves
each of the dies towards the slab, in which the slab is
synchronized with the feeding speed of the dies when the slab is
being pressed by the dies, and during the non-pressing period when
the slab is separated from the dies, the slab is fed at a constant
speed corresponding to a predetermined cycle speed.
[0133] Using this method mentioned above, the slab can be conveyed
according to the upstream and downstream slab transfer speeds, so
the entire line can be operated continuously.
[0134] 4. The fourth object of the present invention is to provide
plate reduction press apparatus and methods that can press a slab
at a high speed with a large reduction, using a small pressing
force, small driving power, and a small configuration of the entire
press facilities.
[0135] To achieve the fourth object given above, the invention
discloses a plate reduction press apparatus in which the
longitudinal direction is defined as the direction in which a
material to be pressed moves after being pressed, and N dies each
of which has the same length in the longitudinal direction are
arranged with an interval of NL between each die, and press the
material.
[0136] Instead of using dies with a length of NL in the
longitudinal direction, N dies each with a length L are arranged in
tandem, and the interval between each of the dies is made to be NL.
After each of the dies has finished pressing a material to be
pressed, the material is moved longitudinally by a length NL. In
this way, the material to be pressed can be reduced continually in
lengths equal to the length NL. When a press machine is
reciprocated at a high speed, inertia forces are created, and the
magnitude of these forces depends on the GD2 of the component
members that are being reciprocated. The GD2 value of a
reciprocating body is greater than the sum of the GD2 values of
each segment if the body is divided into N segments. Accordingly,
the apparatus can be operated at a higher speed by dividing the
dies into segments, because the total inertia force is smaller. In
addition, the driving power is reduced when the dies are
divided.
[0137] With the invention according to another embodiment, the
lateral direction is defined as the direction orthogonal to the
aforementioned longitudinal direction, and the longitudinal length
of the dies is less than the length of the dies in the lateral
direction.
[0138] The volumes of a material to be pressed, before and after
pressing, are substantially equal to each other, therefore the
volume of a reduced portion is spread out both longitudinally and
laterally. However, if dies are long in the longitudinal direction,
the material cannot be displaced easily in the longitudinal
direction, so pressing with a large reduction becomes difficult,
however because the length of the dies in the longitudinal
direction is smaller than the length thereof in the lateral
direction, the material can also be displaced fairly easily in the
longitudinal direction, so that pressing with a large reduction can
be achieved, and also the driving power of the plate reduction
press apparatus is reduced.
[0139] In the invention according to a still further embodiment,
the N dies press a material to be pressed at the same time.
[0140] As N dies press simultaneously, the pressing time can be
made short and high-speed pressing can be achieved.
[0141] With the invention according another embodiment, at least
one of the dies presses at a different time from the time the other
dies press.
[0142] The power for driving a plurality of dies can be reduced by
separating the dies into several or a couple of groups and
differentiating the pressing times.
[0143] According to the plate reduction pressing method according
to one embodiment for achieving the aforementioned fourth object of
the present invention, the number of press machines pressing a
material to be pressed with a press length L in the direction of
the flow of the material to be pressed is defined as K, the press
machines are arranged with K=1 on the upstream side of the pressing
line, and with K increasing sequentially to K=N on the downstream
side when N press machines are arranged in tandem, the material to
be pressed is pressed in sequence from K=N to K=1, then after the
material to be pressed is fed by a length NL, that is, the total of
the pressing lengths of all the press machines, the pressing
sequence from K=N to K=1 is repeated. The pressing force of each
press machine is reduced by shortening the length L of the material
to be pressed by each press machine from K=1 to K=N, so that press
facilities are made smaller.
[0144] According to a still further embodiment of the invention,
the number of press machines pressing a material to be pressed with
a press length L in the direction of the flow of the material to be
pressed is defined as K, the press machines are arranged with K=1
on the upstream side of the pressing line, and with K increasing
sequentially to K=N on the downstream side when N press machines
are arranged in a tandem configuration, each press machine reduces
the material by .DELTA.t, press machine K reduces the material by
.DELTA.t from its thickness after being pressed by press machine
K-1, and the material is pressed by repeatedly feeding the material
by one press length L after pressing the material in sequence from
press machine K=1 to press machine K=N.
[0145] Each press machine, K=1 to K=N, presses the same portion of
a material to be pressed in turn, by an amount .DELTA.t each, that
is, by a total of N.DELTA.t, therefore a large amount of reduction
can be obtained in total, although each press machine only exerts a
small pressing force. Accordingly, the capacity of each press
machine can be small, and the pressing facilities are reduced in
size.
[0146] 5. The fifth object of the present invention is to provide a
plate reduction press apparatus and methods with which a reduction
operation by a reduction press machine and a rolling operation by a
downstream rolling mill can be carried out at the same time, the
capacities of the device for transferring the material to be
pressed and the device to provide a swinging motion during
reduction are small, the apparatus can be easily operated in series
with downstream equipment, and even if the moving speed of the dies
becomes different from the moving speed of the conveyor device
during a pressing operation, the equipment will not be damaged, the
material being pressed will not be bent, nor will the conveyor
device be overloaded.
[0147] To achieve the fifth object described above, the invention
is provided with speed adjusting rolls arranged between a reduction
press machine and a rolling mill with spaces provided to deflect
the material to be pressed, metering instruments arranged near the
aforementioned speed adjusting rolls or in the vicinity thereof, to
measure the length of the material to be pressed which has passed,
and a control apparatus for controlling the operations of the
above-mentioned reduction press machine and adjusting both speed
adjusting rolls according to the measurement of the length metering
instrument.
[0148] The control apparatus controls the operations of both the
speed adjusting rolls and the press machine so that the material to
be pressed is deflected between the press machine and the rolling
mill to absorb any speed difference between the press machine and
the rolling mill when the material is passing between them, length
metering instruments are provided at both ends of the deflection
between the press machine and the rolling mill to determine the
difference between lengths passed, and the difference between the
lengths passed is absorbed by the deflection and maintained in a
predetermined range. Thereby, the press machine can press the
material simultaneously with the operation of the rolling mill. The
press machine can be either a flying press machine or a start-stop
press machine, as far as simultaneous operation is concerned.
[0149] According to another embodiment of the invention, the
aforementioned control apparatus takes the difference in the
measured lengths of material which has passed the two length
metering instruments over a period of a multiple of pressing cycles
of the press machine, adjusts the number of pressing cycles of the
press machine or the transfer speed of the speed adjusting rolls,
or a combination thereof, and controls the pressing operations in
such a manner that the difference in the lengths passed is brought
to 0.
[0150] The difference in the lengths of material passed over a
period of a multiple of pressing cycles of the press machine is
absorbed by the deflection, while the control apparatus makes an
adjustment by increasing or decreasing the number of pressing
cycles per unit time of the press machine, or increases or
decreases the transfer speed of each speed adjusting roll, or a
combination of both, in order to bring the difference in the
lengths passed close to 0.
[0151] According to a further embodiment of the invention, a
deflection metering instrument is provided to measure the
deflection of the material to be pressed, between the
above-mentioned speed adjusting rolls, and the aforementioned
control apparatus controls the pressing operations according to
measurements thereof in such a manner that the deflections remain
within a predetermined range.
[0152] Using the configuration described above, the deflection is
kept within a predetermined range, so the press machine and the
rolling mill are protected from excessive forces that might
otherwise be applied if the deflection became too small, and also
the elongation of the material being pressed at a high temperature
due to an excessive deflection, can be prevented from
occurring.
[0153] The invention according to a further embodiment provides a
conveyor apparatus for the material being pressed that can be
raised and lowered and is arranged between the aforementioned speed
adjusting rolls, in which the material to be pressed is conveyed
substantially at the same level as the transfer level of the speed
adjusting rolls, when the leading end or trailing end of the
material to be pressed passes the conveyor apparatus.
[0154] At the section where the material to be pressed is given a
deflection, the conveyor apparatus is provided that can be raised
and lowered and is equipped with rolls for conveying the material
being pressed, in which the rolls are lowered when a deflection has
been formed, and when the leading end or trailing end of the
material to be pressed passes the conveyor apparatus, the level of
the conveyor rolls is made substantially the same as the transfer
level of the speed adjusting rolls. In this way, the leading end or
trailing end of the material to be pressed or being pressed can
pass smoothly across the section used for the deflection.
[0155] The invention according to a still further embodiment is
aimed at achieving the fifth object described above in the pressing
method of a crank type press machine that presses a material to be
transferred and pressed using upper and lower dies, in which the
dies are moved at the same speed as the speed of the material to bc
pressed during the pressing period, and the speed of feeding the
material to be pressed is adjusted during the period when there is
no pressing taking place in such a manner that during one cycle,
the material to be pressed is moved by a predetermined distance
L.
[0156] The material to be transferred and pressed is pressed by
dies from above and below the material, and during pressing, the
material is transferred at the same speed as that of the dies, and
when the material is not being pressed, the speed of the material
is adjusted to move the material by a distance L for each cycle, so
that the material to be pressed can be transferred at the same
speed during each cycle. In addition, the variations in the
transfer speed during a cycle are much less than those of a
start-stop apparatus, and the vibration of the equipment is much
less than that of a slider system.
[0157] The invention of another embodiment is provided with dies
arranged above and below a material to be pressed, crank devices
for pressing each of the dies, and transfer devices for
transferring the material to be pressed, in which the transfer
devices move the material to be pressed at the same speed as the
dies when the crank devices are pressing the material to be pressed
with the dies, and when the material to be pressed is not being
pressed, the transfer devices adjust the speed of feeding the
material to be pressed and move the material by a predetermined
distance L during one cycle of the pressing operation, and the
above-mentioned distance L is not greater than the length L0 which
is the reduction length of the dies in the direction of flow of the
material to be pressed.
[0158] The upper crank device presses the material to be pressed
when the die is near its lowest point of travel, and the lower
crank device presses the same when the die is in the vicinity of
the highest point of travel. As long as the dies are pressing the
material to be pressed, the transfer devices transfer the material
to be pressed and being pressed at the same speed as that of the
dies. The distance L in which the transfer devices move the
material to be pressed during one cycle of the crank devices is
less than the length L0 in which the dies press the material in the
direction of transfer, so the material to be pressed is pressed
sequentially by one length at a time. In this mode of operation,
variations in the transfer speed of the material to be pressed are
limited to a reasonable range, therefore large-capacity transfer
devices are not required. Furthermore, with this configuration it
is not necessary to give heavy sliders a swinging motion to match
the speed of the material to be pressed, therefore, no
high-capacity device is required for the swinging motion. In
addition, as the material to be pressed is transferred
substantially continuously, the apparatus can be integrated easily
with a downstream rolling mill.
[0159] According to a still further embodiment of the invention, in
the pressing method of a crank type press machine that presses a
material to be pressed and transferred using dies on both sides in
the lateral direction of the transfer line, during the pressing
period, the material to be pressed is moved at the same speed as
the speed of the dies, and during the period when it is not being
pressed, the speed of feeding the material to be pressed is
adjusted in such a manner that during one cycle the material to be
pressed is moved by a predetermined distance L.
[0160] The material to be pressed and transferred is pressed by the
dies from both sides in the lateral direction, and during pressing,
the material to be pressed is transferred at the same speed as that
of the dies, and when the press machine is not pressing, the speed
of the material to be pressed is adjusted to move the material by a
distance L per cycle, so that the material to be pressed can be
transferred at the same speed during each cycle. In addition, the
variations in the transfer speed during a cycle are much less than
those of a start-stop system, and the vibration is also much less
than that of a slider system.
[0161] The invention of one embodiment is configured with dies
arranged on both sides in the lateral direction of a material to be
pressed, crank devices that press each of the dies in the lateral
direction, and transfer devices that transfer the material to be
pressed, in which the transfer devices move the material to be
pressed at the same speed as the speed of the dies when the crank
devices are pressing the material to be pressed in the lateral
direction through the dies, and when the material to be pressed is
not being pressed, the speed of feeding the material to be pressed
is adjusted, and the material to be pressed is moved by a
predetermined distance L in one cycle of a pressing operation, and
the above-mentioned distance L is not greater than the length L0
which is the reduction length of the dies in the direction of flow
of the material to be pressed.
[0162] The invention of a further embodiment is a modification of
the invention of a prior embodiment using the apparatus of a prior
embodiment for lateral pressing; the crank devices on both sides in
the lateral direction of the material to be pressed, press the
material in the lateral direction, using the dies, when they are
near the point of travel closest to the material. While the dies
press the material to be pressed, the transfer devices transfer the
material at the same speed as that of the dies. Because the
distance La that the transfer devices move the material to be
pressed in one cycle of the crank devices is less than the pressing
length La0 of the dies in the direction of flow of the material,
the material to be pressed is pressed sequentially by a length La
during each cycle. These operations keep the variations in the
transfer speed of the material to be pressed in the limits of a
reasonable range, so that no large-capacity transfer devices are
required. In addition, because the configuration is such that heavy
sliders do not have to be given a swinging motion corresponding to
the speed of the material to be pressed, no large-capacity swinging
device is needed. Also, as the material to be pressed is
transferred essentially continuously, the material can be easily
passed on to a downstream rolling machine.
[0163] According to yet another embodiment of the invention, a
looper that forms a loop in the material to be pressed and adjusts
the length thereof is provided downstream of the transfer devices
specified above.
[0164] The transfer speed of the material to be pressed varies
during one cycle of the crank devices. Consequently, the looper is
provided to enable the material to be smoothly passed on to a
subsequent rolling mill etc.
[0165] To achieve the fifth object described above, the invention
of a further embodiment relates to the pressing method of a crank
type press machine that presses a material to be transferred with
pinch rolls and pressed with upper and lower dies; during the
pressing period, the pinch rolls rotate in such a manner that the
peripheral speed of the pinch rolls is made equal to the
combination of the horizontal speed of the dies and the elongation
speed of the material to be pressed, added or subtracted, and
transfer the material to be pressed, and when the press machine is
not pressing, the speed of feeding the material to be pressed is
adjusted in such a manner that during one cycle, the material to be
pressed is moved by a predetermined distance L, and the pressure of
the pinch rolls during the pressing period is made smaller than the
pressure thereof during the non-pressing period.
[0166] The material to be pressed and transferred is pressed by the
dies from above and below the material, and during the pressing
period, the pinch rolls are rotated at the peripheral speed equal
to the sum of the horizontal speed of the dies plus or minus the
elongation speed of the material to be pressed, and transfer the
material to be pressed, and when the apparatus is not pressing, the
speed of the pinch rolls is adjusted to give a moving distance of L
per cycle, so the material to be pressed can be transferred at an
equal speed during each cycle. In addition, because the pressure of
the pinch rolls is made smaller during pressing than during the
non-pressing period, even if there is a deviation between the sum
of the speeds and the transfer speed of the pinch rolls, flaws can
be prevented from being produced in the material to be pressed.
Furthermore, variations in the transfer speed during a cycle are
significantly smaller than those of a start-stop system, and the
vibration is much less than that of a slider system.
[0167] The plate reduction press apparatus of another embodiment is
provided with dies arranged above and below a material to be
pressed, crank devices that press each of the dies, and pinch rolls
that transfer the material to be pressed, in which the pinch rolls
rotate in such a manner that the peripheral speed of the pinch
rolls is made equal to a combination of the horizontal speed of the
dies plus or minus the elongation speed of the material to be
pressed, and transfer the material to be pressed when the crank
devices are pressing the material to be pressed through the dies,
and when the press machine is not pressing, the speed of feeding
the material to be pressed is adjusted in such a manner that during
one cycle, the material to be pressed is moved by a predetermined
distance L and the distance L is not greater than the reduction
length L0 of the dies in the direction of flow of the material to
be pressed, and the pressure of the pinch rolls is made smaller
during pressing with the dies than the pressure during the
non-pressing period.
[0168] The upper crank devices press the material to be pressed
using the dies, near the lowest point of travel, and the lower
crank devices press the material with the dies near to the
uppermost point of travel. While the dies are pressing the material
to be pressed, the pinch rolls rotate at the same peripheral speed
as the combined speed of the speed of the dies plus or minus the
elongation speed of the material to be pressed, so that the
material to be pressed is transferred. Because the distance L by
which the pinch rolls transfer the material to be pressed during
one cycle of the crank devices is less than the pressing length L0
of the dies in the direction of flow, the material to be pressed is
pressed sequentially in steps each of length L. In addition,
because the pressure of the pinch rolls is made smaller during
pressing than the pressure during the non-pressing period, the
material is protected from the occurrence of flaws even if there is
a deviation between the combination speed and the transfer speed of
the pinch rolls. Variations in the transfer speed of the material
to be pressed are kept within reasonable limits during these
operations, so no large-capacity transfer apparatus is required.
Also, the configuration does not require heavy sliders to be given
a swinging motion in synchronism with the speed of the material to
be pressed, therefore no large-capacity swinging apparatus is
needed. Because the material to be pressed is transferred
essentially continuously, the press apparatus can easily be used in
tandem with a downstream rolling mill.
[0169] According to the invention of another embodiment, the
pressure on the above-mentioned pinch rolls is made smaller for a
predetermined time t before or after the press machine begins to
press.
[0170] By reducing the pressure on the pinch rolls at a
predetermined time t before the press machine begins to press, the
pinching force of the pinching rolls on the material to be pressed
decreases, therefore the dies can grip the material to be pressed
more firmly. The time t is the time required for gripping. When the
pressure of the pinch rolls is made smaller at a predetermined time
t after the beginning of pressing, it is intended to make sure the
dies are capable of gripping the material to be pressed more
firmly.
[0171] In the invention of a further embodiment, the pressure of
the above-mentioned pinch rolls is made smaller when the pressing
load becomes more than a predetermined value.
[0172] The pinch rolls press the material to be pressed with a high
pressure until the pressing load of the press machine becomes more
than a predetermined value, to securely feed the material to be
pressed into the press machine, and thereafter the pressure is
reduced.
[0173] The invention of a still further embodiment, aimed at
achieving the fifth object mentioned above is comprised of inlet
transfer devices that are arranged on the upstream side of a press
machine, to transfer a material to be pressed, and can be raised
and lowered, and outlet transfer devices that are arranged on the
downstream side of the press machine, and transfer the material
being pressed, and can be raised and lowered, in which the
aforementioned inlet transfer devices are adjusted to give a height
of transfer according to information which has been input
concerning the thickness of the material to be pressed, in such a
manner that the center line of the thickness of the material to be
pressed is the same as the center line of the press machine, and
the above-mentioned outlet transfer devices are adjusted for a
height of transferring according to information about the thickness
of the material after being pressed, in such a manner that the
center line of the thickness of the material is the same as the
center line of the press machine.
[0174] With a press machine in which a material to be pressed is
transferred and pressed by dies from above and below the material,
the press is designed so that a line midway between the dies is at
a predetermined height, and the line passing through this height is
called the press center line. The thickness of a material to be
pressed has been measured during a process on the upstream side of
the transfer line, when the material is delivered to the press
machine. The height of transfer from the inlet transfer devices is
determined so that the center of the thickness of the material
coincides with the press center line. In addition, the thickness of
the material after being pressed by the press machine is known from
the design value of the press or by measurement, so the height of
transfer of the outlet transfer devices is determined so that the
center of the thickness of the material after being pressed matches
the press center line. Consequently, the material being pressed is
not bent after pressing, and also the outlet transfer devices will
not be damaged.
[0175] In another embodiment of the invention, inlet transfer
devices are provided that are arranged on the upstream side of a
press machine for pressing a material to be pressed between upper
and lower dies, that transfer the material to be pressed, and can
be raised and lowered, and outlet transfer devices that are
arranged on the downstream side of the aforementioned press
machine, transfer the material being pressed, and can be raised and
lowered, in which when the material to be pressed is passed through
the press machine without being pressed with the upper and lower
dies open, the transfer heights of the above-mentioned inlet
transfer devices and the aforementioned outlet transfer devices are
determined to be identical to each other and higher than the upper
surface of the opened lower die.
[0176] In practice, a material to be pressed must sometimes be
passed through a press machine without pressing, or a material
which has been pressed unsuccessfully must be transferred in the
reverse direction. In such cases, the upper and lower dies are
opened, the transfer heights of the inlet transfer devices and the
outlet transfer devices are made identical to each other and higher
than the upper surface of the opened lower die, then the material
to be pressed or which has been pressed can be passed either
forwards or backwards.
[0177] According to a still further embodiment of the invention,
the transfer method concerns the transfer devices that are arranged
on the upstream and downstream sides of a press machine and can
adjust the transfer height of a material to be pressed, in which
both transfer devices can transfer the material to be pressed or
after being pressed while the transfer devices maintain the height
of the center of the thickness of the material to be pressed,
unchanged during pressing.
[0178] The transfer devices arranged on the upstream and downstream
sides of the press machine do not cause bending or otherwise
adversely affect the material to be pressed and avoid unnecessary
loads being imposed on the transfer devices, by adjusting the
height of the center of the thickness of the material being pressed
so that the height of the center of the thickness of the material
is kept at the same level during transfer and pressing.
[0179] According to another embodiment of the invention, the
transfer method concerns the transfer devices that are arranged on
the upstream and downstream sides of a press machine and can adjust
the transfer height of a material to be pressed, in which when the
press dies are opened vertically in such a manner that the material
to be pressed does not contact the dies when the material to be
pressed is passed through the press machine, both transfer devices
transfer the material to be pressed at the same height.
[0180] In practice, a material to be pressed must sometimes be
passed through a press machine without pressing, or a material
which has been pressed unsuccessfully must be transferred in the
reverse direction. At this time, the press dies are opened upwards
and downwards so that they do not touch the material to be pressed,
and the material to be pressed is transferred with both transfer
devices maintained at the same height.
[0181] The other objects and advantages of the present invention
will be revealed as follows by referring to the attached
drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0182] FIG. 1 is a schematic view of an example of a rolling mill
used for hot rolling.
[0183] FIG. 2 is a schematic view showing an example of reduction
forming in the direction of plate thickness of a material to be
shaped using dies.
[0184] FIG. 3 is a conceptual view showing an example of a flying
sizing press apparatus.
[0185] FIG. 4 is a structural view of a conventional high-reduction
press machine.
[0186] FIG. 5 is a view showing a conventional flying reduction
press machine.
[0187] FIG. 6 is a view showing an example of the configuration of
a reduction press machine using conventional long dies.
[0188] FIGS. 7(A), 7(B), and 7(C) are views showing the operation
of the apparatus shown in FIG. 6.
[0189] FIG. 8 shows the method of reducing thickness used during
hot pressing.
[0190] FIG. 9 is a general view seen from the side of the transfer
line, of the first embodiment of the plate reduction press
apparatus according to the present invention.
[0191] FIG. 10 is a conceptual view showing the displacement of the
dies shown in FIG. 9 with respect to the transfer line, and the
swinging motion of the dies.
[0192] FIG. 11 is a conceptual view showing the displacement of the
dies shown in FIG. 9 with respect to the transfer line, and the
swinging motion of the dies.
[0193] FIG. 12 is a conceptual view showing the displacement of the
dies shown in FIG. 9 with respect to the transfer line, and
swinging motion of the dies.
[0194] FIG. 13 is a conceptual view showing the displacement of the
dies shown in FIG. 9 with respect to the transfer line, and the
swinging motion of the dies.
[0195] FIG. 14 is a general view seen from the side of the transfer
line, of the second embodiment of the plate reduction press
apparatus according to the present invention.
[0196] FIG. 15 is a general view seen from the side of the transfer
line, of the third embodiment of the plate reduction press
apparatus according to the present invention.
[0197] FIG. 16 is a general view seen from the side of the transfer
line, of the fourth embodiment of the plate reduction press
apparatus according to the present invention.
[0198] FIG. 17 is a side view showing the fifth embodiment of the
plate reduction press apparatus according to the present
invention.
[0199] FIG. 18 is a side view of the embodiment of FIG. 17 showing
the location of the up/down table rollers when the material to be
shaped is not being reduced or formed.
[0200] FIG. 19 is a side view showing the sixth embodiment of the
plate reduction press apparatus according to the present
invention.
[0201] FIG. 20 is a side view of the embodiment of FIG. 19 showing
the location of the up/down table rollers when the material to be
shaped is not being reduced or formed.
[0202] FIG. 21 is a conceptual view seen from the side of the
transfer line of the seventh embodiment of the plate reduction
press apparatus according to the present invention, when the
upstream dies are in the most separated position from the transfer
line and the downstream dies are in the closest position to the
transfer line.
[0203] FIG. 22 is a conceptual view seen from the side of the
transfer line of the seventh embodiment of the plate reduction
press apparatus according to the present invention, when the
upstream dies are moving towards the transfer line and the
downstream dies are moving away from the transfer line.
[0204] FIG. 23 is a conceptual view seen from the side of the
transfer line of the seventh embodiment of the plate reduction
press apparatus according to the present invention, when the
upstream dies are in the closest position to the transfer line and
the downstream dies are in the most separated position from the
transfer line.
[0205] FIG. 24 is a conceptual view seen from the side of the
transfer line of the seventh embodiment of the plate reduction
press apparatus according to the present invention, when the
upstream dies are moving away from the transfer line and the
downstream dies are moving towards the transfer line.
[0206] FIG. 25 is a conceptual view showing the mechanisms for
moving the sliders shown in FIGS. 21 through 24, in a sectional
view in the longitudinal direction of the transfer line.
[0207] FIG. 26 is a side view showing the eighth embodiment of the
plate reduction press apparatus according to the present
invention.
[0208] FIG. 27 is a plan view of the apparatus shown in FIG.
26.
[0209] FIG. 28 is a sectional view of the cylinder mounting portion
of the side guide shown in FIG. 26.
[0210] FIG. 29 is a sectional view of the vertical roller support
portion of the side guides shown in FIG. 26.
[0211] FIG. 30 shows the configuration of the press equipment
provided with the plate reduction press apparatus according to the
ninth embodiment of the invention.
[0212] FIG. 31 is a side view of the plate reduction press
apparatus shown in FIG. 30.
[0213] FIG. 32 is a sectional view along the line A-A in FIG.
31.
[0214] FIG. 33 is a schematic view showing the paths in which the
dies move.
[0215] FIG. 34 is a view showing the movement of the dies in the up
and down direction relative to the angular position .theta. of the
drive shafts.
[0216] FIG. 35 shows the configuration of a rolling facility
provided with the plate reduction press apparatus according to the
tenth embodiment of the present invention.
[0217] FIG. 36 is a side view of the plate reduction press
apparatus shown in FIG. 35.
[0218] FIG. 37 is a sectional view along the line A-A in FIG.
36.
[0219] FIGS. 38(A) and 38(B) are schematic views showing the paths
in which the dies move.
[0220] FIG. 39 is a diagram showing the plate reduction pressing
method according to the present invention.
[0221] FIG. 40 shows the configuration of a rolling facility
provided with the plate reduction press apparatus according to the
eleventh embodiment of the present invention.
[0222] FIG. 41 is a side view of the plate reduction press
apparatus shown in FIG. 40.
[0223] FIG. 42 is a sectional view along the line A-A in FIG.
41.
[0224] FIGS. 43(A) and 43(B) are schematic views showing the paths
in which the dies move.
[0225] FIG. 44 is a view showing the movement of the dies in the up
and down direction relative to the angular position .theta. of the
synchronous eccentric shafts.
[0226] FIG. 45 shows the configuration of the twelfth embodiment of
the present invention.
[0227] FIG. 46 is a sectional view along the line X-X in FIG.
45.
[0228] FIG. 47 shows one cycle of the operation of a slider.
[0229] FIG. 48 shows one cycle of the operation of a slider and the
material to be pressed.
[0230] FIG. 49 shows the configuration of the thirteenth embodiment
of the present invention.
[0231] FIG. 50 is a sectional view along the line Y-Y in FIG.
49.
[0232] FIGS. 51(A) and 51(B) are schematic views showing the paths
in which the dies move.
[0233] FIG. 52 is a view showing the configuration of the
fourteenth embodiment of the present invention.
[0234] FIG. 53 is a sectional view along the line X-X in FIG.
52.
[0235] FIG. 54 shows a practical construction of a slider.
[0236] FIG. 55 shows one cycle of the operation of a slider.
[0237] FIG. 56 shows the moving speed of a slab during one
cycle.
[0238] FIG. 57 shows one cycle of the operation of a slider and a
slab.
[0239] FIG. 58 shows the configuration of the fifteenth example of
the present invention.
[0240] FIG. 59 is a sectional view along the line X-X in FIG.
58.
[0241] FIG. 60 is a sectional view along the line Y-Y in FIG.
58.
[0242] FIG. 61 shows the construction of the sixteenth embodiment
of the present invention.
[0243] FIG. 62 is a sectional view along the line X-X in FIG.
61.
[0244] FIG. 63 shows the configuration of the seventeenth
embodiment of the present invention.
[0245] FIG. 64 shows the configuration of the eighteenth embodiment
of the present invention.
[0246] FIG. 65 shows one cycle of operation of a slider.
[0247] FIG. 66 shows the moving speed of a slab during one
cycle.
[0248] FIG. 67 shows the configuration of the nineteenth embodiment
of the present invention.
[0249] FIGS. 68(A), 68(B) and 68(C) show the operation of the
nineteenth embodiment, for the case in which each die presses at
the same time.
[0250] FIGS. 69(A), 68(B) and 69(C) show the operation of the
nineteenth embodiment, for the case in which each die presses in
sequence.
[0251] FIG. 70 shows the configuration of the twentieth embodiment
of the present invention.
[0252] FIGS. 71(A), 71(B) and 71(C) show the operation of the
twentieth embodiment, for the case in which all the dies press
simultaneously.
[0253] FIG. 72 is a side view showing the twenty-first embodiment
of the present invention.
[0254] FIGS. 73(A) and 73(B) are views describing the operation of
the twenty-first embodiment.
[0255] FIGS. 74(A) and 74(B) describe the operation of the
twenty-second embodiment, when the tip of the material to be
pressed has been moved to dies 1201 and dies 1202.
[0256] FIGS. 75(A) and 75(B) describe the operations of the
twenty-second embodiment, when the tip of the material to be
pressed has been moved to dies 1203 and dies 1204.
[0257] FIGS. 76(A), 76(B), 76(C) and 76(D) describe the operation
of the twenty-second embodiment, when the tip of the material to be
pressed has passed the dies 1204.
[0258] FIG. 77 shows the configuration of the twenty-third
embodiment of the present invention.
[0259] FIGS. 78(A) and 78(B) show the speed of the material to be
pressed in the twenty-third embodiment; (A) the transfer speed of
the material to be pressed at the outlet of the flying press
machine, and (B) the transfer speed at the inlet of the rolling
mill.
[0260] FIG. 79 shows the configuration of the twenty-fourth
embodiment of the present invention.
[0261] FIGS. 80(A) and 80(B) show the speed of the material to be
pressed in the twenty-fourth embodiment; (A) the transfer speed of
the material to be pressed at the outlet of the flying press
machine, (B) the transfer speed at the inlet of the rolling
mill.
[0262] FIGS. 81(A) and 81(B) show the configuration of the
twenty-fifth embodiment of the present invention.
[0263] FIG. 82 shows the crank angle .theta. and the pressing range
of the crank device.
[0264] FIG. 83 is a diagram developed from FIG. 82, with the crank
angle .theta. on the x-axis.
[0265] FIG. 84 shows the speed of the reciprocating motion of the
dies.
[0266] FIG. 85 shows the speed variations of the transfer
devices.
[0267] FIGS. 86(A), 86(B) and 86(C) are views showing the
configuration of the twenty-sixth embodiment of the present
invention.
[0268] FIG. 87 is a view showing the configuration of the
twenty-seventh embodiment of the present invention.
[0269] FIG. 88 is a view showing the configuration of the
twenty-eighth embodiment of the present invention.
[0270] FIGS. 89(A), 89(B) and 89(C) show one cycle of operation of
a press machine.
[0271] FIG. 90 shows the crank angle .theta. and the pressing range
of the crank devices.
[0272] FIGS. 91(A), 91(B), 91(C), 91(D) and 91(E) show the
operation of the twenty-eighth embodiment.
[0273] FIG. 92 shows the configuration of the twenty-ninth
embodiment of the present invention.
[0274] FIG. 93 shows the configuration of the thirtieth embodiment
of the present invention.
[0275] FIG. 94 shows the configuration of the thirty-first
embodiment of the present invention.
[0276] FIGS. 95(A), 95(B) and 95(C) show one cycle of operation of
the press machine.
[0277] FIG. 96 shows the configuration of the thirty-second
embodiment of the present invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0278] The embodiments of the present invention are described as
follows referring to the drawings.
[0279] (First Embodiment)
[0280] FIGS. 9 to 13 show the first embodiment of the plate
reduction press apparatus according to the present invention; this
apparatus is provided with a housing 101 erected in a predetermined
place on a transfer line S so that a plate-like material 1 to be
shaped can pass through the center portion, upstream eccentric
shafts 103a, 103b extending in the lateral direction of the
material 1 to be shaped and provided with eccentric portions 102a,
102b, downstream eccentric shafts 105a, 105b extending in the same
direction as the aforementioned upstream eccentric shafts 103a,
103b and provided with eccentric portions 104a, 104b, upstream rods
106a, 106b and downstream rods 107a, 107b extending up and down,
die holders 109a, 109b for mounting dies 108a, 108b, and mechanisms
121a, 121b for moving the dies backwards and forwards.
[0281] The upstream eccentric shafts 103a, 103b are arranged inside
the housing 101 such that the shafts are opposite each other above
and below the transfer line S, and the non-eccentric portions 110a,
110b at both ends of the shafts are supported by upstream shaft
boxes (not illustrated) mounted in the housing 101 through
bearings.
[0282] The downstream eccentric shafts 105a, 105b are arranged
inside the housing 101 in such a manner that the shafts are
opposite each other above and below the transfer line S on the
downstream B side of the transfer line downstream of the upstream
eccentric shafts 103a, 103b, and the non-eccentric portions 111a,
111b at both ends of the shafts are supported by downstream shaft
boxes (not illustrated) mounted in the housing 101 through
bearings.
[0283] The drive shaft (not illustrated) of a motor is connected to
one end of each of the upstream eccentric shafts 103a, 103b and the
downstream eccentric shafts 105a, 105b, through a universal
coupling and a gear box, so that each of the eccentric shafts 103a,
103b, 105a and 105b can rotate in synchronism together.
[0284] The gear box mentioned above is configured in such a manner
that when the motor is operated, both upper eccentric shafts 103a,
105a rotate counterclockwise so that the eccentric portion 104a of
the downstream eccentric shaft 105a rotates with a phase angle
90.degree. ahead of the phase angle of the eccentric portion 102a
of the upstream eccentric shaft 103a, and at the same time, both
lower eccentric shafts 103b, 105b beneath the transfer line S
rotate clockwise so that the eccentric portion 104b of the
downstream eccentric shaft 105b rotates with a phase angle
90.degree. ahead of the phase of the eccentric portion 102b of the
upstream eccentric shaft 103b, as shown in FIGS. 11 through 15; in
addition, the eccentric portions 102a, 104a and the eccentric
portions 102b, 104b are positioned symmetrically to each other on
opposite sides of the transfer line S.
[0285] The big ends of the upstream rods 106a, 106b are connected
to the eccentric portions 102a, 102b of the upstream eccentric
shafts 103a, 103b through bearings 112a, 112b.
[0286] The big ends of the downstream rods 107a, 107b are connected
to the eccentric portions 104a, 104b of the downstream eccentric
shafts 105a, 105b through bearings 113a, 113b.
[0287] The die holders 109a, 109b are installed inside the housing,
such that the holders are opposite each other on opposite sides of
the transfer line S.
[0288] Brackets 114a, 114b provided near the upstream A side of the
transfer line on the die holders 109a, 109b are connected to the
tips of the aforementioned upstream rods 106a, 106b by the pins
115a, 115b and bearings 116a, 116b extending substantially
horizontally in the lateral direction of the material 1 to be
shaped.
[0289] The tips of the above-mentioned downstream rods 107a, 107b
are connected to brackets 117a, 117b provided near the downstream B
side of the transfer line on the die holders 109a, 109b, by the
pins 118a, 118b and bearings 119a, 119b, that are parallel to the
pins 115a, 115b.
[0290] By means of these upstream rods 106a, 106b and downstream
rods 107a, 107b, and the displacements of the eccentric portions
102a, 102b associated with the rotation of the above-mentioned
upstream eccentric shafts 103a, 103b and the displacement of the
eccentric portions 104a, 104b associated with the downstream
eccentric shafts 105a, 105b, motion is transmitted to the die
holders 109a, 109b, so that the die holders 109a, 109b move towards
and away from the transfer line S with a swinging action.
[0291] The dies 109a, 109b mounted on each of the die holders 108a,
108b face the material 1 to be shaped, as it is being passed
through the transfer line S, and when viewed from the side of the
transfer line S, the dies are provided with forming surfaces 120a,
120b that are convex circular arcs projecting towards the transfer
line S.
[0292] Mechanisms 121a, 121b for moving the dies backwards and
forwards are composed of arms 122a, 122b one end of each of which
is fixed to the end of one of the die holders 109a, 109b, near the
downstream B side of the transfer line, and projecting in the
downstream B direction of the transfer line, guide members 124a,
124b fixed at locations near to the downstream B side of the
transfer line of the housing 101 and comprised of grooves 123a,
123b inclined at an angle to the transfer line so that the distance
from the transfer line increase in the downstream B direction, and
guide rings 126a, 126b connected to the tips of the arms 122a, 122b
through pins 125a, 125b in a rotatable manner, which engage with
the grooves 123a, 123b of the guide members 124a, 124b in a movable
manner.
[0293] The mechanisms 121a, 121b for moving the dies backwards and
forwards give the die holders 109a, 109b a reciprocating motion
relative to the transfer line S, so that the die holders 109a, 109b
move towards and away from the transfer line S with a swinging
motion, associated with the rotation of the upstream eccentric
shafts 103a, 103b and the downstream eccentric shafts 105a, 105b,
as described previously.
[0294] The operation of the plate reduction press apparatus shown
in FIGS. 10 through 13 is described as follows, with particular
emphasis on the upstream eccentric shaft 103a, downstream eccentric
shaft 105a, upstream rods 106a, downstream rods 107a, dies 108a,
and die holders 109a, on the upstream side of the transfer line
S.
[0295] When the angles of the eccentric portion 102a of the
upstream eccentric shaft 103a and the eccentric portion 104a of the
downstream eccentric shaft 105a are defined such that top dead
center is 0.degree. (360.degree.), and both eccentric portions
102a, 104a are rotated with the angle of rotation increasing in the
counterclockwise direction, and as shown in FIG. 10, the angle of
rotation of the eccentric portion 104a of about 45.degree. is
assumed to correspond to the angle of rotation of the eccentric
portion 102a of about 315.degree.; the die 108a is then in the
farthest position from the transfer line S, and the guide ring 126a
is located at the end of the guide member 124a, nearest to the
downstream side of the transfer line.
[0296] When both eccentric shafts 103a, 105a rotate
counterclockwise from the aforementioned state, the die 108a moves
towards the transfer line S.
[0297] At this time, because the phase angle of the eccentric
portion 104a is 90.degree. ahead of the phase angle of the
eccentric portion 102a, the end of the die 108a, near to the
downstream B side of the transfer line, moves towards the transfer
line S before the end near the upstream A side of the transfer
line, and at the same time, the guide ring 126a moves towards the
upstream A side of the transfer line, in the guide member 124a.
[0298] As shown in FIG. 11, when the angle of rotation of the
eccentric portion 102a becomes about 90.degree. and the angle of
rotation of the eccentric portion 104a is about 180.degree., the
guide ring 126a reaches the end of the guide member 124a, near the
upstream A side of the transfer line, and the portion of the
forming surface 120a of the die 108a, near to the downstream B side
of the transfer line, presses the material 1 to be shaped, as it
passes along the transfer line S.
[0299] When both eccentric shafts 103a, 105a rotate and the angle
of rotation of the eccentric portion 102a increases and the angle
of rotation of the eccentric portion 104a becomes greater than
180.degree., the guide ring 126a begins to move towards the
downstream B side of the transfer line, in the guide member 124a,
and the die 108a swings in such a manner that the portion of the
forming surface 120a of the die 108a, in contact with the material
1 to be shaped, moves towards the upstream A side of the transfer
line from the downstream B side thereof, thus the material 1 to be
shaped is subjected to a reducing and forming process.
[0300] After this, the die 108a moves towards the downstream B side
of the transfer line, and feeds the material 1 being reduced and
formed towards the downstream B side of the transfer line without
any material being forced backwards.
[0301] As shown in FIG. 12, after the angle of rotation of the
eccentric portion 102a becomes about 135.degree. and the angle of
rotation of the eccentric portion 104a is about 225.degree., the
portion of the forming surface 120a of the aforementioned die 108a,
near the upstream A side of the transfer line, reduces and forms
the material 1 to be shaped as the die 108a swings in the
downstream direction.
[0302] Furthermore, as shown in FIG. 13, when the angles of
rotation of the eccentric portions 102a, 104a become about
180.degree. and 270.degree., respectively, the die 108a moves away
from the transfer line S.
[0303] During these operations, the upstream eccentric shaft, 103b,
downstream eccentric shaft 105b, upstream rod 106b, downstream rod
107b, die 108b, and die holder 109b, below the transfer line S,
also operate in the same way as the ones above the transfer line S
as described above, thereby the material 1 to be shaped is reduced
and formed from above and below the material.
[0304] In the plate reduction press apparatus shown in FIGS. 9
through 13 as described above, the die holders 109a, 109b on which
the dies 108a, 108b are mounted are given a swinging motion by the
upstream eccentric shafts 103a, 103b, downstream eccentric shafts
105a, 105b, upstream rods 106a, 106b, and downstream rods 107a,
107b, in such a manner that the portions of the forming surfaces
120a, 120b, in contact with the material 1 to be shaped, of the
dies 108a, 108b are transferred from the downstream B side of the
transfer line towards the upstream A side thereof as the die
holders are brought close to the transfer line S, so that the areas
of the forming surfaces 120a, 120b in contact with the material 1
to be shaped are made smaller, so the pressing loads on the dies
108a, 108b can be reduced.
[0305] Consequently, the forces imposed on the power transmission
members such as the eccentric shafts 103a, 103b, 105a, and 105b and
the rods 106a, 106b, 107a, and 107b, are reduced, so that these
components can be made more compact than those known in the prior
art.
[0306] Moreover, because the die holders 109a, 109b are moved
towards the downstream B side of the transfer line by the
mechanisms 121a, 121b for moving the dies backwards and forwards
when the forming surfaces 120a, 120b of the dies 108a, 108b are in
contact with the material 1 to be shaped, the material is never
forced backwards, but the material 1 that is reduced and formed can
be fed forwards to the downstream B side of the transfer line.
[0307] (Second Embodiment)
[0308] FIG. 14 shows the second embodiment of the plate reduction
press apparatus according to the present invention; in the
following figures, the item numbers indicate the same components as
those shown in FIGS. 9 through 13.
[0309] This plate reduction press apparatus incorporates mechanisms
127a, 127b for moving the dies backwards and forwards in place of
the mechanisms 121a, 121b shown in FIGS. 9 through 13 for moving
the dies backwards and forwards.
[0310] The mechanisms 127a, 127b for moving the dies backwards and
forwards are composed of brackets 128a, 128b fixed to the end
portions of the die holders 109a, 109b, near to the downstream B
side of the transfer line, brackets 129a, 129b fixed to portions of
the housing 101, near to the downstream B side of the transfer
line, and hydraulic cylinders 134a, 134b, the tips of the piston
rods 130a, 130b of which are connected to the brackets 128a, 128b
through bearings by the pins 131a, 131b and the cylinders 132a,
132b of which are connected to the brackets 129a, 129b through
bearings by the pins 133a, 133b.
[0311] Also with this plate reduction press apparatus, hydraulic
pressure is applied to the hydraulic chambers on the head side of
the hydraulic cylinders 134a, 134b when the forming surfaces 120a,
120b of the dies 108a, 108b are not in contact with the material 1
to be shaped, thereby the die holders 109a, 109b together with the
dies 108a, 108b are moved towards the upstream A side of the
transfer line, and when the forming surfaces 120a, 120b of the dies
108a, 108b, are brought into contact with the material 1 to be
shaped, hydraulic pressure is applied to the hydraulic chambers on
the rod side of the hydraulic cylinders 134a, 134b, thus the die
holders 109a, 109b together with the dies 108a, 108b are moved
towards the downstream B side of the transfer line; in this way, as
for plate reduction press apparatus described previously by
referring to FIGS. 9 through 13, the material 1 being shaped can be
fed towards the downstream B side of the transfer line, without
forcing any material in the backward direction.
[0312] Also, other types of actuators such as screw jacks can be
applied instead of the hydraulic cylinders 134a, 134b.
[0313] (Third Embodiment)
[0314] FIG. 15 shows the third embodiment of the plate reduction
press apparatus according to the present invention, and in the
figure, item numbers refer to the same components as those shown in
FIGS. 9 through 13.
[0315] In this plate reduction press apparatus, mechanisms 135a,
135b for moving the dies backwards and forwards are used in place
of the mechanisms 121a, 121b for moving the dies backwards and
forwards, shown in FIGS. 9 through 13.
[0316] The mechanisms 135a, 135b for moving the dies backwards and
forwards are composed of brackets 128a, 128b fixed to the end
portions of the die holders 109a, 109b, on the downstream B side of
the transfer line, eccentric shafts 136a, 136b for the backwards
and forwards movements, provided at locations on the housing 101,
near the downstream B side of the transfer line, which can rotate,
and extending substantially horizontally in the lateral direction
of the material 1 to be shaped, and rods 139a, 139b for backwards
and forwards motion one end of each of which is connected to the
bracket 128a or 128b by the pin 137a or 137b, and the other ends of
which are connected to the eccentric portions 138a, 138b, of the
eccentric shafts 136a, 136b for backward and forward movements
through bearings.
[0317] Also with this plate reduction press apparatus, the
eccentric shafts 136a, 136b for backward and forward movements are
rotated, and the dies 108a, 108b are moved to the upstream A side
of the transfer line together with the die holders 109a, 109b,
while the forming surfaces 120a, 120b of the dies 108a, 108b are
not in contact with the material 1 to be shaped, and when the
forming surfaces 120a, 120b of the dies 108a, 108b come in contact
with the material 1 to be shaped, the eccentric shafts 136a, 136b
for backward and forward movements are rotated to move the dies
108a, 108b together with the die holders 109a, 109b in the
downstream B direction of the transfer line, thereby the material 1
after being reduced and formed can be fed out to the downstream B
side of the transfer line without any of the material being forced
backwards, in the same manner as with the plate reduction press
apparatus described previously by referring to FIGS. 9 through
13.
[0318] (Fourth Embodiment)
[0319] FIG. 16 shows the fourth embodiment of the plate reduction
press apparatus according to the present invention, and in the
figure, item numbers refer to the same components as those in FIGS.
9 through 13.
[0320] This plate reduction press apparatus incorporates mechanisms
140a, 140b for moving the dies backwards and forwards in place of
the mechanisms 121a, 121b for moving the dies backwards and
forwards shown in FIGS. 9 to 13.
[0321] The mechanisms 140a, 140b for moving the dies backwards and
forwards are composed of brackets 128a, 128b fixed to the end
portions of the die holders 109a, 109b, closest to the downstream B
side of the transfer line, brackets 141a, 141b whose bases are
fixed to predetermined locations on the housing 101 in such a
manner that the tips of the brackets are positioned on the side of
the die holders 109a, 109b on the opposite side to the transfer
line, and levers 144a, 144b one end of each of which is connected
to the bracket 128a or 128b by the pin 142a or 142b, and the other
ends of which are connected to:the brackets 141a, 141b through the
bearings-of pins 143a, 143b.
[0322] The mounting locations of brackets 128a, 128b, 141a, and
141b, the distances between connecting points of levers 144a, 144b,
and the locations of the bearings of levers 144a, 144b with respect
to the brackets 128a, 128b, 141a, and 141b are predetermined in
such a manner that as the eccentric shafts 103a, 103b, 105a, and
105b rotate, the die holders 109a, 109b with the dies 108a, 108b
mounted on them, move in substantially the same way as those of the
plate reduction press apparatus shown in FIGS. 9 to 13.
[0323] This plate reduction press apparatus shown in FIG. 16
according to the present invention can feed out the material 1
after being reduced and formed in the downstream B direction of the
transfer line without causing any of the material to be forced
backwards, in the same manner as the plate reduction press
apparatus described previously according to FIGS. 9 to 13.
[0324] As described above, the plate reduction press apparatus and
methods according to the present invention offer the following
advantages.
[0325] (1) The plate reduction pressing method of the present
invention can reduce the areas of the forming surfaces of the dies
that are in contact with a material to be shaped and the loads
applied to the dies during pressing, because the forming surfaces
of the dies are convex towards the transfer line, and the dies are
given a swinging motion in such a manner that the areas of the
forming surfaces, that are in contact with the material to be
shaped move from the ends in the downstream direction of the
transfer line to the ends in the upstream direction while the dies
are being moved towards the transfer line from above and below the
material to be shaped in synchronism with each other.
[0326] (2) In any of the plate reduction press apparatus of further
embodiments the present invention, the displacements of the
eccentric portions of the upstream and downstream eccentric shafts,
with different phase angles, are transmitted to the die holders
through the upstream and downstream rods and the dies are given a
swinging motion in such a manner that the portions of the convex
forming surfaces, that are in contact with the material to be
shaped, move from the ends in the downstream direction of the
transfer line to the upstream ends, so that the areas of the
forming surfaces of the dies that are in contact with the material
to be shaped, are made smaller, therefore the loads applied to the
dies during pressing can be reduced.
[0327] (3) In any of the plate reduction press apparatus specified
in claims 2 through 6 of the present invention, the loads applied
to the dies during pressing are reduced, so the required strengths
of the upstream and downstream eccentric shafts, upstream and
downstream rods, etc. become moderate, so that these components can
be made compact.
[0328] (4) With any of the plate reduction press apparatus of the
present invention, the loads applied to the dies during pressing
are reduced, the die holders are moved in the downstream direction
of the transfer line by the mechanisms for moving the dies
backwards and forwards when the forming surfaces of the dies are in
contact with the material to be shaped, so the material after being
reduced and formed is fed out in the downstream direction of the
transfer line without forcing any of the material in the backward
direction.
[0329] (Fifth embodiment)
[0330] FIGS. 17 and 18 show the fifth embodiment of the plate
reduction press apparatus according to the present invention.
[0331] Item number 207 represents the main unit of a press machine
that is comprised of a housing 208, upper shaft box 209, lower
shaft box 210, upper and lower rotating shafts 211a, 211b, upper
and lower rods 212a, 212b, upper and lower rod support boxes 213a,
213b, and upper and lower dies 214a, 214b.
[0332] The housing 208 is provided with a window 215 on both sides
in the lateral direction of the transfer line S on which a material
1 to be shaped is transferred horizontally, and extending in the
vertical direction thereof.
[0333] The upper shaft box 209 engages with the upper end portion
of the aforementioned window 215 in such a manner that it can slide
in the vertical direction, and the vertical position of the upper
shaft box is determined by an adjusting screw 216 which is mounted
in the upper part of the housing 208 and driven by a driving device
(not illustrated).
[0334] The lower shaft box 210 engages with the lower part of the
window 215 of the above-mentioned housing 208, in such a manner
that it is free to move in the vertical direction, and the vertical
position thereof is determined by an adjusting screw 216 which is
mounted in the lower part of the housing 208 and rotated by a
driving device (not illustrated).
[0335] Each of the upper and lower rotating shafts 211a, 211b is
provided with an eccentric portion 217 at an intermediate location
in the axial direction, and both ends thereof are supported by the
aforementioned upper and lower shaft boxes 209, 210, respectively,
and the other end of each shaft is connected to the driving device
(not illustrated) through a universal joint.
[0336] The big ends of each of the upper and lower rods 212a, 212b
are coupled to the eccentric portions 217 of each of the rotating
shafts 211a, 211b, through bearings 218, and the die holders 219a,
219b are connected to tips of the rods 212a, 212b, through ball
joints (not illustrated).
[0337] The piston rods of the hydraulic cylinders 220 that are
attached to the rods 212a, 212b through bearings are connected to
the die holders 219a, 219b, so that the angles of the dies 214a,
214b mounted on the die holders 219a, 219b can be adjusted by
actuating the above-mentioned hydraulic cylinders 220.
[0338] Each of the upper and lower rod support boxes 213a, 213b is
attached to an intermediate location on each of the rods 212a,
212b, through spherical bearings (not illustrated) located
substantially in the middle, and each of the rod support boxes
engages with the window 215 in a manner such that it can freely
slide up and down.
[0339] The upper and lower dies 214a, 214b are provided with
similar profiles to those of the dies 14a, 14b shown in FIG. 2, and
are mounted on the die holders 219a, 219b, respectively, opposite
each other on opposite sides of the transfer line S, in a freely
detachable manner, and when the rotating shafts 211a, 211b rotate,
the dies are driven by the rods 212a, 212b, and move towards and
away from the transfer line S in synchronism with each other.
[0340] Item number 221 represents an upstream table comprised of a
fixed frame 222 installed on the upstream A side of the transfer
line of the main press apparatus unit 207 and extending
substantially horizontally along the transfer line S, and a
plurality of upstream table rollers 223 that are provided in a
freely rotatable manner at predetermined intervals in the transfer
line direction so as to support the lower surface of a material to
be inserted between the dies 214a, 214b and shaped by the main
press apparatus unit 207, substantially horizontally.
[0341] Item number 224 indicates the first up/down table which is
composed of a first up/down frame 225 installed in the close
vicinity of the main press apparatus unit 207 on the downstream B
side of the transfer line, and extending substantially horizontally
along the transfer line S in a manner such that it can be moved up
and down, and a plurality of up/down table rollers 226 that are
provided in a freely rotatable manner on the first up/down frame
225 at predetermined intervals along the transfer line so that the
rollers can support the lower surface of the material 1 after being
formed, as the material is fed out from between the dies 214a, 214b
of the main press apparatus unit 207.
[0342] The aforementioned first up/down frame 225 is composed of a
plurality of guide members 228 erected at predetermined locations
on the floor surface 227 on the downstream side of the transfer
line S, and a main frame unit 229 equipped with leg portions that
engage with the guide members 228 in a manner such that they can
move up and down, in which the main frame unit 229 is connected to
the piston rods of the hydraulic cylinders 230 installed at
predetermined intervals in the longitudinal direction of the main
frame unit 229, and attached to the floor surface 227 through
bearings. When the hydraulic cylinders 230 are operated, the main
frame unit 229 is raised and lowered in a substantially horizontal
state, and the height of each up/down table roller 226 can be
adjusted relative to the transfer line S.
[0343] Item number 231 indicates a second up/down table comprised
of a second up/down frame 232 extending along the transfer line S
from the above-mentioned up/down table 224 in the downstream B
direction of the transfer line and free to move up and down, and a
plurality of up/down table rollers 232 provided on the second
up/down frame 232 at predetermined intervals in the direction of
the transfer line in a freely rotatable manner so that the rollers
can support the lower surface of the material 1 after being shaped
and fed out from the first up/down table 224.
[0344] The aforementioned second up/down frame 232 is composed of a
plurality of guide members 234 erected at predetermined locations
on the floor surface 227 beneath the transfer line S, leg portions
235 engaging with the guide members 234 in a manner so that they
can move up and down, and a main frame unit 236 supported on the
leg portions 235 through bearings; the main frame unit 236 is
connected to the piston rods of a plurality of hydraulic cylinders
237 arranged along the main frame unit 236 at predetermined
intervals and supported on the floor surface 227 by bearings.
[0345] Each of the aforementioned hydraulic cylinders 237 can be
operated individually, and by actuating each of the above-mentioned
hydraulic cylinders 237 individually, the second up/down frame 232
is raised and lowered in such a manner that the height of the
second up/down table 231 at the upstream end in the direction of
the transfer line S becomes identical to the height of the first
up/down table 224, and the height of the end in the downstream
direction of the transfer line S is slightly higher than the height
of the downstream table 238 to be detailed later.
[0346] In addition, the first and second up/down tables 224, 231
can also be lowered to a horizontal position substantially at the
same height as the upstream table 221 by the hydraulic cylinders
230, 237 provided for the first and second up/down tables 224,
231.
[0347] Item number 238 shows the downstream table configured with a
fixed frame 239 arranged adjacent to the second up/down table 231
on the downstream B side of the transfer line and extending
substantially horizontally along the transfer line S, and provided
with a plurality of downstream table rollers 240 installed at
predetermined intervals in the transfer line in a freely rotatable
manner so that the lower surface of the material 1 after being
shaped and fed out from the second up/down table 231 can be
supported substantially horizontally at a height essentially the
same as the height of the upstream table 221.
[0348] The operation of the plate reduction press apparatus shown
in FIGS. 17 and 18 is described as follows.
[0349] When a long material 1 to be shaped is to be reduced and
formed in the direction of its plate thickness by means of dies
214a, 214b, first a driving device (not illustrated) rotates the
up/down adjusting screws 216 of the main press apparatus 207,
thereby moving the upper and lower shaft boxes 209, 210 up or down
along the housing 208, and the dies 214a, 214b are moved towards or
away from the transfer line S by the rotating shafts 211a, 211b,
rods 212a, 212b and die holders 219a, 219b connected to each of the
shaft boxes 209 or 210, thus the gap between the die 214a and the
die 214b can be determined.
[0350] Referring to FIG. 17, the hydraulic cylinders 230 of the
first up/down table 224, arranged in the close vicinity of the main
press apparatus unit 207 on the downstream B side of the transfer
line, are actuated to raise or lower the first up/down frame 225,
thereby the height of the first up/down table 224 is set so that
the up/down table rollers 226 will come in contact with the lower
surface of the material 1 after being reduced, formed and fed out
from the dies 214a, 214b, and the material after being shaped will
be supported approximately horizontally.
[0351] In addition, by raising and lowering the second up/down
frame 232 by individually operating the hydraulic cylinders 237 of
the second up/down table 231, provided on the downstream B side of
the first up/down table 224 in the transfer line, the position of
the second up/down table 231 in the vertical direction is
determined such that the material 1 after being shaped will
gradually descend from the level of the first up/down table 224
towards the downstream table 238.
[0352] After that, the driving device (not illustrated) of the main
press apparatus unit 207 is operated to rotate the rotating shafts
211a, 211b, thereby the upper and lower dies 214a, 214b are
continuously moved towards and away from the transfer line S of the
material 1 to be shaped, and also the material 1 to be shaped is
placed on the upstream table 221 from the upstream A side of the
transfer line, and moved and inserted between the dies 214a, 214b,
and the angles of the dies 214a, 214b are changed appropriately by
the hydraulic cylinders 220a, 220b, both the upper and lower
surfaces of the material 1 to be shaped, are pressed by the dies
214a, 214b simultaneously while the material 1 to be shaped is
moving, and by repeating these operations, the thickness of the
material 1 being shaped is reduced as shown in FIG. 2, to a
predetermined dimension.
[0353] The material 1 after being shaped by the dies 214a, 214b of
the main press apparatus unit 207, moves on to the first up/down
table 224, is guided downwards by the second up/down table 231 and
smoothly transferred onto the downstream table 238, and is
transferred to the downstream B side of the transfer line.
[0354] The plate reduction press apparatus shown in FIGS. 17 and 18
is provided with a plurality of up/down table rollers 226 adjacent
to the main press apparatus 207 on the downstream B side of the
transfer line, that can be raised and lowered to match the lower
surface of the material 1 being reduced, formed and fed out of the
dies 214a, 214b, and a plurality of up/down table rollers 233 on
the downstream B side of the up/down table rollers 226, whose
heights can be set such that the material after being shaped
gradually descends from the height of the up/down table rollers 226
towards the downstream table rollers 240, thereby preventing the
leading end portion of the material 1 being reduced and shaped by
the dies 214a, 214b of the main press apparatus unit 207 from
drooping, and also preventing the leading end portion of the
material 1 being shaped from being caught by the downstream table
rollers 240 installed on the downstream B side of the transfer line
S. Consequently, both the downstream table rollers 240 and the
material 1 being shaped can be protected from being damaged,
thereby the material 1 to be shaped can be reduced and formed in
the direction of the plate thickness, and the material 1 being
shaped can also be transferred securely to the downstream B
side.
[0355] If a long material 1 to be shaped is to be passed without
being reduced and formed by the dies 214a, 214b in the direction of
the plate thickness, the first and second up/down tables 224, 231
are positioned as shown in FIG. 18.
[0356] First, a driving device (not illustrated) rotates the upper
and lower adjusting screws 216 of the main press apparatus unit
207, thereby moving the upper shaft box 209 and the lower shaft box
210 upwards and downwards, respectively, along the housing 208,
thereby separating the dies 214a, 214b from the transfer line S of
the material 1 to be shaped by the rotating shafts 211a, 211b, rods
212a, 212b and die holders 219a, 219b connected to each of the
shaft boxes 209, 210, and the driving device (not illustrated) of
the main press apparatus unit 207 is operated to rotate the
rotating shafts 211a, 211b so that each of the dies 214a, 214b is
moved to the farthest location from the transfer line S of the
material 1 to be shaped, and stopped there.
[0357] Also, the hydraulic cylinders 230 of the first up/down table
224 located in the close vicinity of the main press apparatus unit
207 on the downstream B side of the transfer line are operated, and
the first up/down frame 225 is lowered, and also the hydraulic
cylinders 237 of the second up/down table 231 are operated to lower
the second up/down frame 232, thereby the positions of the up/down
tables 224, 231 in the vertical direction are set at a height
equivalent to the height of the upstream and downstream tables 221,
238.
[0358] After that, the material 1 to be shaped is loaded on and
transferred by the upstream table 221 from the upstream A side of
the transfer line (A side shown in FIG. 18), passed through the
dies 214a, 214b of the main press apparatus unit 207, and sent out
to the first up/down table 224 on the downstream B side of the
transfer line of the main unit 207.
[0359] The material 1 to be shaped, after moving onto the first
up/down table 224, is further guided by the second up/down table
231 and transferred onto the downstream table 238, and conveyed
towards the downstream B side of the transfer line of the material
1 to be shaped.
[0360] In this way, with the plate reduction press apparatus shown
in FIGS. 17 and 18, the vertical positions of the first and second
up/down tables 224, 231 installed on the downstream B side of the
transfer line of the main press apparatus 207 in a manner such that
they can move up and down, can be set at the same level as those of
the upstream table 221 and the downstream table 238. Consequently,
even when the material 1 to be shaped is neither reduced nor formed
in the direction of its plate thickness, the material 1 to be
shaped can be conveyed securely to the downstream B side.
[0361] (Sixth Embodiment)
[0362] FIGS. 19 and 20 show the sixth embodiment of the plate
reduction press apparatus according to the present invention; item
numbers in the figures represent the same components as in FIGS. 17
and 18.
[0363] Item number 241 indicates an upstream table composed of a
fixed frame 242 provided on the upstream A side of the transfer
line of the main press apparatus 207, and extending substantially
horizontally along the transfer line S, and a plurality of upstream
table rollers 243 provided on the aforementioned fixed frame 242 at
predetermined intervals in the direction of the transfer line in a
freely rotatable manner, so that the lower surface of the material
1 can be inserted between and shaped by the dies 214a, 214b of the
main press apparatus unit 207.
[0364] Item number 244 shows a first up/down table that is composed
of a first up/down frame 245 installed on the downstream B side of
the upstream table 241 in the transfer line and extending along the
transfer line S in a manner such that it can move up and down, and
a plurality of up/down table rollers 246 installed at predetermined
intervals in the direction of the transfer line in a freely
rotatable manner so as to support the lower surface of the material
to be shaped and fed out from the above-mentioned upstream table
241.
[0365] The aforementioned first up/down frame 245 is supported on
the floor surface 27 by up/down mechanisms (not illustrated)
similar to the guide members 234 and the hydraulic cylinders 237
(see FIGS. 17 and 18) described before, and can be raised and
lowered with respect to the transfer line S.
[0366] Item number 247 is a second up/down table, installed between
the first up/down table 244 and the main press apparatus 207 and
extending substantially horizontally along the transfer line S in a
manner such that it can move up and down and which is provided with
a second up/down frame 248 and a plurality of up/down table rollers
249 installed on the second up/down frame 248 at predetermined
intervals in the direction of the transfer line in a freely
rotatable manner so as to support the lower surface of the material
to be shaped and fed out from the first up/down table 244.
[0367] The aforementioned second up/down frame 248 is supported on
the floor surface 227 by up/down mechanisms (not illustrated)
similar to the guide members 228 and the hydraulic cylinders 230
(see FIGS. 17 and 18) described before, and can be raised and
lowered with respect to the transfer line S.
[0368] In addition, the above-mentioned first and second up/down
tables 244, 247 can be raised to a position substantially at the
same height as the above mentioned upstream table 241 by the
up/down mechanisms provided for the tables, respectively.
[0369] Item number 250 indicates a downstream table installed on
the downstream B side of the main press apparatus unit 207 in the
transfer line, which is provided with a fixed frame 251, and
extending substantially horizontally along the transfer line S, a
plurality of downstream table rollers 252 installed on the fixed
frame 251 at predetermined intervals in the transfer line in a
freely rotatable manner, so that the lower surface of the material
1 after being shaped and fed out from between the dies 214a, 214b
can be supported substantially horizontally and essentially at the
same height as the above-mentioned upstream table 241.
[0370] The operation of the plate reduction press apparatus shown
in FIGS. 19 and 20 is described in the following paragraphs.
[0371] When a long material 1 to be shaped is reduced and formed in
the direction of its plate thickness using the dies 214a, 214b,
first the gap between the die 214a and the die 214b, in the main
press apparatus unit 207, is determined.
[0372] Then, as shown in FIG. 19, the up/down mechanisms (not
illustrated) adjust the heights of the first and second up/down
tables 244, 247 in such a manner that the up/down table rollers
246, 249 contact the lower surface of the material 1 to be shaped,
when fed out from the upstream table 241 towards the dies 214a,
214b, and the center lines of the material 1 before and after being
pressed, upstream and downstream of the main press apparatus 207,
are at the same height and the material 1 to be shaped and after
being shaped is maintained substantially horizontal.
[0373] Next, the upper and lower dies 214a, 214b are continuously
moved towards and away from each other in the main press apparatus
unit 207, and the material 1 to be shaped is placed on the upstream
table 221 and transferred from the upstream A side of the transfer
line, and inserted between the above-mentioned dies 214a, 214b,
thereby reducing the thickness of the material 1 being shaped as
shown in FIG. 2 to a predetermined dimension.
[0374] The material 1 after being shaped by the dies 214a, 214b of
the main press apparatus unit 207 is transferred smoothly onto the
downstream table 250, and conveyed to the downstream B side of the
transfer line of the material 1 being shaped.
[0375] As described above, the plate reduction press apparatus
shown in FIGS. 19 and 20 is provided with a plurality of up/down
table rollers 246, 249 on the upstream A side of the main press
apparatus unit 207 on the transfer line, that can be raised and
lowered according to the position of the lower surface of the
material 1 being reduced, formed and fed out from the dies 214a,
214b, therefore the leading end portion of the material 1 being
reduced and formed by the dies 214a, 214b of the main press
apparatus unit 207 can be prevented from drooping and also the
leading end portion of the material 1 being shaped can be prevented
from being caught by the downstream table rollers 252 installed on
the downstream B side of the transfer line S. Therefore, both the
downstream table rollers 252 and the material 1 being shaped can be
protected from damage, so that the material 1 being shaped can be
reduced and formed in the direction of the plate thickness
efficiently, and can be transferred securely to the downstream B
side.
[0376] When a long material 1 is to be passed without being reduced
or formed in the direction of the plate thickness with the dies
214a, 214b, the first up/down table 244 and the second up/down
table 247 are positioned as shown in FIG. 20.
[0377] First, the upper and lower dies 214a, 214b of the main press
apparatus unit 207 are moved away from the transfer line S of the
material 1 to be shaped, and each of the dies 214a, 214b is moved
to a position farthest from the transfer line S of the material 1,
and stopped there.
[0378] In addition, the up/down mechanisms (not illustrated) raise
the first and second up/down tables 244, 247, and each of the
up/down table rollers 247, 249 is adjusted to be at the same height
as the upstream table rollers 243 of the upstream table 241 and the
downstream table rollers 252 of the downstream table 250.
[0379] Thereafter, the material 1 to be shaped is loaded on the
upstream table 241 from the upstream A side of the transfer line (A
side shown in FIG. 20) and transferred, passing from the first and
second up/down tables 244, 247 between the dies 214a, 214b of the
main press apparatus unit 207, and is fed out onto the downstream
table 250 on the downstream B side of the transfer line of the main
press apparatus unit 207.
[0380] In the manner described above, with the plate reduction
press apparatus shown in FIGS. 19 and 20, the vertical positions of
the first up/down table 244 and the second up/down table 247,
installed on the upstream A side of the transfer line of the main
press apparatus unit 207, can be set to be at the same height as
the upstream table 241 and the downstream table 250, so that even
when the material 1 to be shaped is neither reduced nor formed in
the direction of the plate thickness, the material 1 to be shaped
can be securely transferred to the downstream B side.
[0381] However, the plate reduction press apparatus and the
operating methods according to the present invention are not
limited only to the embodiments described above, but, for example,
the up/down table rollers can be configured in a manner such that
they can be moved up and down individually, or the up/down table
rollers can be installed on both the upstream and downstream sides
of the transfer line of the main press apparatus unit, or
otherwise, various modifications can be made as long as the claims
of the present invention are satisfied, as a matter of course.
[0382] The following various advantages can be gained as described
above, according to the plate reduction press apparatus and the
operating methods of the present invention.
[0383] (1) The plate reduction press apparatus of the present
invention is provided with the movable up/down table rollers
downstream of the dies, to support the lower surface of the
material after being reduced and shaped by the dies in the
direction of the plate thickness, therefore drooping of the leading
end portion of the material being reduced and shaped by the dies
can be prevented, and the table rollers and the material being
shaped can be protected from damage that might otherwise occur due
to the drooping of the material.
[0384] (2) With the plate reduction press apparatus specified in
Claim 8 of the present invention, the movable up/down table rollers
are provided upstream of the dies, to support the lower surface of
the material to be inserted into and shaped by the dies, so
drooping of the leading end portion of the material being reduced
and shaped by the dies can be prevented, and the table rollers and
the material being shaped can be protected from damage that might
otherwise occur due to the drooping of the material.
[0385] (3) In the plate reduction press apparatus of a further
embodiment, the movable up/down table rollers are installed
upstream of the dies to support the lower surface of the material
to be inserted into and shaped by the dies, and the movable up/down
table rollers are provided downstream of the dies to support the
lower surface of the material reduced and shaped by the dies in the
direction of the plate thickness, so the drooping of the leading
end portion of the material being reduced and shaped by the dies
can be prevented, and the table rollers and the material being
shaped can be protected from damage that might otherwise occur due
to the drooping of the material.
[0386] (4) According to the method of operating the plate reduction
press apparatus, of the present invention, some of the movable
up/down table rollers that are provided to support the lower
surface of the material being reduced and shaped by the dies in the
direction of the plate thickness, are set in such a manner that the
material being shaped gradually descends towards the downstream
table rollers, so the leading end portion of the material being
reduced and shaped can be prevented from being caught by the
downstream table rollers, and therefore the material being shaped
can be securely transferred towards the downstream side.
[0387] (5) In a further embodiment of the method of operating the
plate reduction press apparatus of the present invention, the
up/down table rollers are set so that the material to be shaped,
which is to be inserted into the dies, is placed in a substantially
horizontal position before being reduced and formed, therefore the
leading end portion of the material being reduced and formed can be
prevented from being caught by the downstream table rollers, and
the material being shaped can be transferred securely in the
downstream direction.
[0388] (6) According to the method of operating the plate reduction
press apparatus of another embodiment of the present invention, the
up/down table rollers are set in such a manner that the material to
be shaped, is placed in a substantially horizontal position before
being inserted into, reduced and formed by the dies, and the
material after being reduced and formed by the dies in the
direction of plate thickness is also approximately horizontal,
consequently the material after being reduced and formed can be
protected from being caught by the downstream table rollers, and so
the material being shaped can be transferred securely in the
downstream direction.
[0389] (7) In any of the methods of operating the plate reduction
press apparatus discussed above according to the present invention,
the heights of the up/down table rollers can be set equal to those
of the upstream and downstream table rollers, so that a material
that is being neither reduced nor shaped by the dies can be
transferred securely in the downstream direction.
[0390] (Seventh Embodiment)
[0391] FIGS. 21 through 25 show an example of a plate reduction
press apparatus according to the present invention; this plate
reduction press apparatus is provided with a housing 319 erected at
a predetermined location on the transfer line S so that the
material 1 to be shaped can pass through the center portion of the
housing, a pair of upstream sliders 324a, 324b arranged above and
below the transfer line S opposite each other, a pair of downstream
sliders 325a, 325b located on the downstream B side of the upstream
sliders 324a, 324b in the transfer line, opposite each other above
and below the transfer line S, upstream dies 330a, 330b supported
by the upstream sliders 324a, 324b, downstream dies 333a, 333b
supported by the downstream sliders 325a, 325b, mechanisms 336a,
336b for moving the upstream sliders that move the upstream sliders
324a, 324b towards the transfer line S and move the sliders away
from the line S, the mechanisms 344a, 344b for moving the
downstream sliders that move the downstream sliders 325a, 325b
towards and away from the transfer line S, upstream hydraulic
cylinders 352a, 352b as the mechanisms for moving the upstream dies
that move the upstream dies 330a, 330b backwards and forwards along
the transfer line S, hydraulic cylinders 354a, 354b as the
mechanisms for moving the downstream dies that move the downstream
dies 333a, 333b backwards and forwards along the transfer line S,
and synchronous driving mechanisms 356a, 356b corresponding to both
the above-mentioned mechanisms 336a, 336b, 344a and 344b for moving
the sliders.
[0392] Inside a housing 319, upstream slider holders 320a, 320b are
installed opposite each other above and below a transfer line S
near the upstream A side of the transfer line, and constructed to
be concave in the direction away from the transfer line, and
downstream slider holders 321a, 321b are installed opposite each
other on opposite sides of the transfer line S near the downstream
B side of the transfer line, and constructed to be concave in the
direction away from the transfer line; the downstream slider
holders 321a, 321b are located closer to the transfer line S than
the upstream slider holders 320a, 320b.
[0393] On the outer surface of the housing 319, there are rod
insertion holes 322a, 322b communicating with the upstream slider
holders 320a, 320b from the top and bottom of the housing, near the
upstream A side of the transfer line, and rod insertion holes 323a,
323b communicating with the downstream slider holders 321a, 321b
from the top and bottom of the housing, near the downstream B side
of the transfer line, for each of the slider holders 320a, 320b,
321a, and 321b, at 2 locations each in a row in the lateral
direction of the material 1 to be shaped.
[0394] The upstream sliders 324a, 324b are housed in the upstream
slider holders 320a, 320b so that the sliders can slide in the
direction towards and away from the transfer line S, and the
downstream sliders 325a, 325b are housed in the downstream slider
holders 321a, 321b so that the sliders can slide in the direction
towards and away from the transfer line S.
[0395] On the surfaces facing the transfer line S of the upstream
sliders 324a, 324b and the downstream sliders 325a, 325b, die
holders 326a, 326b, 327a, and 327b are provided that can move
backwards and forwards substantially horizontally in the direction
of the transfer line S.
[0396] On the surfaces farthest from the transfer line, of the
upstream sliders 324a, 324b and the downstream sliders 325a, 325b,
brackets 328a, 328b, 329b, and 329b are constructed with 2 brackets
at each location, immediately opposite the rod insertion holes
322a, 322b, 323a, and 323b.
[0397] The upstream dies 330a, 330b are provided with flat forming
surfaces 331a, 331b that gradually approach the transfer line S
from the upstream A side to the downstream B side of the transfer
line, and flat forming surfaces 332a, 332b continuing from the
downstream B side of the above-mentioned forming surfaces 331a,
331b in the direction of the transfer line, facing the transfer
line S substantially horizontally, and the dies 330a, 330b are
mounted on the aforementioned die holders 326a, 326b.
[0398] The downstream dies 333a, 333b are provided with flat
forming surfaces 334a, 334b that gradually approach the transfer
line S from the upstream A side to the downstream B side of the
transfer line, and flat forming surfaces 335a, 335b continuing from
the downstream B side of the above-mentioned forming surfaces 334a,
334b substantially parallel to and facing the transfer line S, and
the dies 333a, 333b are mounted on the aforementioned die holders
327a, 327b.
[0399] The mechanisms 336a, 336b for moving the upstream sliders
are composed of shaft boxes 337a, 337b above and below the housing
319 and positioned on the sides away from above-mentioned upstream
slider holders 320a, 320b, crank shafts 339a, 339b extending
substantially horizontally in the direction orthogonal to the
transfer line S, whose non-eccentric portions 338a, 338b are
supported by the shaft boxes 337a, 337b through bearings, and rods
342a, 342b inserted through the above-mentioned rod insertion holes
322a, 322b, and the big ends of which are connected to the
eccentric portions 340a, 340b of the crank shafts 339a, 339b, and
the tips of which are connected to the brackets 328a, 328b of the
upstream sliders 324a, 324b by the pins 341a, 341b parallel to the
crank shafts 339a, 339b, through bearings.
[0400] The shaft box 337a located above the transfer line S is
supported by a support member 343a provided above the housing 319,
and the shaft box 337b located below the transfer line S is
supported by a support member 343b provided on the lower part of
the housing in a manner such that it can be moved up and down.
[0401] In addition, the location of the shaft box 337b with respect
to the transfer line S can be determined by moving it up or down
with a position adjusting screw (not illustrated).
[0402] In these mechanisms 336a, 336b, for moving the upstream
sliders, when the crank shafts 339a, 339b rotate, the displacements
of the eccentric portions 340a, 340b are transmitted to the
upstream sliders 324a, 324b through the rods 342a, 342b, and the
die holders 326a, 326b and the upstream dies 330a, 330b move
towards and away from the transfer line S together with the
above-mentioned upstream sliders 324a, 324b.
[0403] The mechanisms 344a, 344b for moving the downstream sliders
are composed of shaft boxes 345a, 345b arranged on the top and
bottom of the housing 319 on the sides farther from the transfer
line than the aforementioned downstream slider holders 321a, 321b,
crank shafts 347a, 347b extending substantially horizontally in the
direction orthogonal to the transfer line S, whose non-eccentric
portions 346a, 346b are supported by the shaft boxes 345a, 345b
through bearings, and rods 350a, 350b inserted through the
above-mentioned rod insertion holes 323a, 323b, the big ends of
which are connected to the eccentric portions 348a, 348b of the
crank shafts 347a, 347b through bearings, and the tips of which are
connected to the brackets 329a, 329b of the downstream sliders
325a, 325b through the bearings of pins 349a, 349b parallel to the
crank shafts 347a, 347b.
[0404] The shaft box 345a located above the transfer line S is
supported by and fixed to a support member 351a provided on top of
the housing 319, and the shaft box 345b located below the transfer
line S is supported by a support member 351b provided on bottom of
the housing 319 in a manner such that it can be moved up and
down.
[0405] Further, the location of the shaft box 345b with respect to
the transfer line S can be set by moving it up or down with a
position adjusting screw (not illustrated).
[0406] In the aforementioned mechanisms 344a, 344b for moving the
downstream sliders, the displacements of the eccentric portions
348a, 348b associated with the rotation of the crank shafts 347a,
347b are transmitted to the downstream sliders 325a, 325b through
the rods 350a, 350b, and the die holders 327a, 327b and the
downstream dies 333a, 333b move towards and away from the transfer
line S together with the above-mentioned downstream sliders 325a,
325b.
[0407] Upstream hydraulic cylinders 352a, 352b are installed on the
upstream A side of the upstream sliders 324a, 324b on the transfer
line so that the piston rods 353a, 353b point towards the
downstream B side of the transfer line and are located parallel to
the transfer line S, and the aforementioned piston rods 353a, 353b
are connected to the upstream dies 330a, 330b.
[0408] With these upstream hydraulic cylinders 352a, 352b, when
hydraulic pressure is applied to the hydraulic chambers on the head
side, the piston rods 353a, 353b are pushed out, and the die
holders 326a, 326b and the upstream dies 330a, 330b move towards
the downstream B side of the upstream sliders 324a, 324b on the
transfer line, and when hydraulic pressure is applied to the
hydraulic chambers on the rod side, the piston rods 353a, 353b are
retracted, and the die holders 326a, 326b and the upstream dies
330a, 330b move towards the upstream A side of the upstream sliders
324a, 324b on the transfer line.
[0409] The downstream hydraulic cylinders 354a, 354b are mounted
near the downstream B side of the downstream sliders 325a, 325b on
the transfer line so that the piston rods 355a, 355b point towards
the upstream A side of the transfer line and are located parallel
to the transfer line S, and the above-mentioned piston rods 355a,
355b are connected to the downstream dies 333a, 333b.
[0410] With these downstream hydraulic cylinders 354a, 354b, when
hydraulic pressure is applied to the hydraulic chambers on the rod
side, the piston rods 355a, 355b are retracted, and the die holders
327a, 327b and the upstream dies 333a, 333b move towards the
downstream B side of the downstream sliders 325a, 325b on the
transfer line, and when hydraulic pressure is applied to the
hydraulic chambers on the head side, the piston rods 355a, 355b are
pushed out, and the die holders 327a, 327b and the downstream dies
333a, 333b move towards the upstream A side of the downstream
sliders 325a, 325b on the transfer line.
[0411] Synchronous drive mechanisms 356a, 356b are provided with
input shafts 357a, 357b, upstream output shafts 358a, 358b,
downstream output shafts 359a, 359b, and a plurality of gears (not
illustrated) that transmit the rotation of the input shafts 357a,
357b to the output shafts 358a, 358b, 359a, and 359b, and when the
input shafts 357a, 357b rotate, the output shafts 358a, 358b, 359a,
and 359b rotate in the same direction at the same rotational
speed.
[0412] The upstream output shaft 358a of the synchronous drive
mechanism 356a is connected on one side through a universal
coupling (not illustrated) to, a non-eccentric portion 338a of the
crank shaft 339a that is a component of the mechanism 336a for
moving the upstream slider and the downstream output shaft 359a is
connected through a universal coupling (not illustrated), to a
non-eccentric portion 338b of the crank shaft 347a that is a
component of the mechanism 344a for moving the downstream
slider.
[0413] The crank shafts 339a, 347a are connected to the
aforementioned output shafts 358a, 359a in such a state that there
is a phase angle difference of 180.degree. between the eccentric
portion 340a of the crank shaft 339a and the eccentric portion 348a
of the crank shaft 347a.
[0414] The upstream output shaft 358b of the other synchronous
drive mechanism 356b, is connected via a universal coupling (not
illustrated) to a non-eccentric portion 338b of the crank shaft
339b, that is a component of the mechanism 336b for moving the
upstream slider, and the downstream output shaft 359b, is connected
through a universal coupling (not illustrated) to a non-eccentric
portion 338b of the crank shaft 347b that is a component of the
mechanism 344b for moving the downstream slider.
[0415] The crank shafts 339b, 347b are connected to the
aforementioned output shafts 358b, 359b in such a state that there
is a phase angle difference of 180.degree. between the eccentric
portion 340b of the crank shaft 339b and the eccentric portion 348b
of the crank shaft 347b.
[0416] The input shafts 357a, 357b of the synchronous drive
mechanisms 356a, 356b, are connected to the output shafts of motors
through universal couplings (not illustrated), and one motor
operates so that the crank shafts 339a, 347a rotate
counterclockwise in FIGS. 21 through 24, and the other motor
operates so that the crank shafts 339b, 347b rotate clockwise in
FIGS. 21 through 24.
[0417] The rotational speeds of the upper and lower motors are
controlled by a control device (not illustrated) synchronously in
such a manner that the speed of rotation corresponds to the speed
of the material 1 to be shaped, moving on the transfer line S, and
the phase angles of the upper crank shafts 339a, 347a and the lower
crank shafts 339b, 347b are symmetrical with respect to the
transfer line S.
[0418] When the material 1 to be shaped is reduced and formed by
the plate reduction press apparatus as shown in FIGS. 21 through
25, position adjusting screws (not illustrated) for the lower shaft
boxes 337b, 345b of the transfer line S are rotated appropriately,
thereby the space between the upper dies 330a, 330b and the space
between the downstream dies 333a, 333b are determined according to
the plate thickness of the material 1 to be reduced and formed.
[0419] Also, both of the motors (not illustrated) connected to the
synchronous drive mechanisms 356a, 356b are operated to rotate the
crank shafts 339a, 347a above the transfer line S counterclockwise
and the crank shafts 339b, 347b below the transfer line S
clockwise.
[0420] Thus, as the crank shafts 339a, 339b rotate the
displacements of the eccentric portions 340a, 340b, are transmitted
to the upstream sliders 324a, 324b through the rods 342a, 342b, and
the upstream dies 330a, 330b move towards and away from the
transfer line S together with the above-mentioned upstream sliders
324a, 324b, and as the crank shafts 347a, 347b rotate the
displacements of the eccentric portions 348a, 348b are transmitted
to the downstream sliders 325a, 325b through the rods 350a, 350b,
and the downstream dies 333a, 333b move towards and away from the
transfer line S in the reverse phase to the aforementioned upstream
dies 330a, 330b, together with the above-mentioned sliders 325a,
325b.
[0421] Moreover, when the upstream dies 330a, 330b move towards the
transfer line S, hydraulic pressure is applied to the fluid
chambers on the head side of the upstream hydraulic cylinders 352a,
352b, and the upstream dies 330a, 330b are moved to the downstream
B side of the transfer line (see FIGS. 22 and 23), and when the
upstream dies 330a, 330b move away from the transfer line S,
hydraulic pressure is applied to the fluid chambers on the rod side
of the upstream hydraulic cylinders 352a, 352b, so that the
upstream dies 330a, 330b are moved towards the upstream A side of
the transfer line (see FIGS. 24 and 21).
[0422] In the same way as above, when the downstream dies 333a,
333b move towards the transfer line S, hydraulic pressure is
applied to the hydraulic chambers on the rod side of the downstream
hydraulic cylinders 354a, 354b, and the downstream dies 333a, 333b
are moved towards the downstream B side of the transfer line (see
FIGS. 24 and 21), and when the downstream dies 333a, 333b move away
from the transfer line S, hydraulic pressure is applied to the
hydraulic chambers on the head side of the downstream hydraulic
cylinders 354a, 354b, so that the downstream dies 333a, 333b are
moved towards the upstream A side of the transfer line (see FIGS.
22 and 23).
[0423] Next, the end on the downstream B side of the transfer line
of the material 1, to be reduced and shaped in the direction of the
plate thickness, is inserted between the upstream dies 330a, 330b
from the upstream A side of the transfer line, and the
aforementioned material 1 to be shaped is moved towards the
downstream B side of the transfer line, then the first plate
reduction sub-method is carried out, in which the material 1 to be
shaped is reduced and formed in the direction of the plate
thickness, by means of the upper and lower upstream dies 330a, 330b
that move towards the transfer line S and move in the downstream B
direction of the transfer line.
[0424] At this time, the downstream dies 333a, 333b are moving away
from the transfer line S and moving in the upstream A direction of
the transfer line.
[0425] As the material 1 to be shaped moves towards the downstream
B side of the transfer line, the first plate reduction sub-method
as described above presses the portion of the end near the
downstream B side of the transfer line of the material 1 to be
shaped, then the end near the downstream B side of the transfer
line of the material 1 after being shaped by the first plate
thickness reduction sub-method, is inserted between the downstream
dies 333a, 333b, and the material 1 to be shaped is further reduced
and formed in the direction of the plate thickness by the upper and
lower downstream dies 333a, 333b that move towards the transfer
line S and also move in the downstream B direction of the transfer
line, and this is defined as a second plate reduction
sub-method.
[0426] At this time, because the upstream dies 330a, 330b are
moving away from the transfer line S and moving in the upstream A
direction of the transfer line, the rotational force transmitted
from the upper and lower motors to the synchronous drive mechanisms
356a, 356b can be utilized efficiently to reduce and form the
material 1 to be shaped by the downstream dies 333a, 333b.
[0427] In addition, the inertia forces of the crank shafts 339a,
339b and the rods 342a, 342b of the mechanisms 336a, 336b for
moving the upstream sliders, the upstream dies 330a, 330b, etc. are
transmitted to the downstream dies 333a, 333b through the
synchronous drive mechanisms 356a, 356b, the crank shafts 347a,
347b and the rods 350a, 350b of the mechanisms 344a, 344b, for
moving the downstream sliders etc., and assist the aforementioned
downstream dies 333a, 333b to reduce and form the material 1 to be
shaped.
[0428] When the second plate reduction sub-method is completed for
the portion of the end near the downstream B side of the transfer
line of the material 1 to be shaped, the upstream dies 330a, 330b
are in the farthest position from the transfer line S (see FIG.
21), and as the material 1 to be shaped moves in the downstream B
direction of the transfer line, an unreduced portion of the
material 1 to be shaped, which is following after the portion
already reduced by the first plate reduction sub-method, is
inserted between the upstream dies 330a, 330b, so that the material
1 to be shaped is reduced by the first plate reduction sub-method
as the upper and lower upstream dies 330a, 330b move towards the
transfer line S.
[0429] In addition, because the downstream dies 333a, 333b are
moving away from the transfer line S (see FIG. 22), the rotational
forces transmitted from the upper and lower motors to the
synchronous drive mechanisms 356a, 356b can be utilized efficiently
to reduce and form the material 1 to be shaped by the upstream dies
330a, 330b.
[0430] Furthermore, the inertia forces of the crank shafts 347a,
347b and the rods 350a, 350b of the mechanisms 344a, 344b for
moving the downstream sliders, the downstream dies 333a, 333b, etc.
are transmitted to the upstream dies 330a, 330b through the
synchronous drive mechanisms 356a, 356b, the crank shafts 339a,
339b and the rods 342a, 342b of the mechanisms 330a, 330b for
moving the upstream sliders, etc., and assist the above-mentioned
upstream dies 330a, 330b to press and form the material 1 to be
shaped.
[0431] When the first plate reduction sub-method is completed for
the portion of the material 1 to be shaped, as described above, the
downstream dies 333a, 333b are in the farthest position from the
transfer line S (see FIG. 23), and as the material 1 to be shaped
moves in the downstream B direction of the transfer line, the
portion of the material 1 to be shaped, that has been reduced by
the first plate reduction sub-method, and is in continuation with a
portion which has already been reduced by the second plate
reduction sub-method, is inserted between the downstream dies 333a,
333b, and as the upper and lower downstream dies 333a, 333b move
towards the transfer line S, the material 1 to be shaped is
processed by the second plate reduction sub-method, and as soon as
it is finished, the upstream dies 330a, 330b move away from the
transfer line S (see FIG. 24).
[0432] With the plate reduction press apparatus illustrated in
FIGS. 21 through 25, as described above, an unreduced portion of
the material to be shaped is subjected to the first plate reduction
sub-method in which the portion is reduced and formed in the
direction of the plate thickness by means of the upstream dies
330a, 330b, and then the portion that has been reduced and formed
of the material 1 to be shaped is further reduced and formed by the
downstream dies 333a, 333b in the direction of the plate thickness,
according to the second plate reduction sub-method, and so the
material 1 to be shaped can be efficiently reduced and formed in
the direction of the plate thickness.
[0433] Because the first and second plate reduction sub-methods are
operated alternately on an unreduced portion of the material 1 to
be shaped and a portion which has already been reduced by the first
sub-method, respectively, the loads applied to the upstream dies
330a, 330b and the downstream dies 333a, 333b during pressing can
be reduced, and therefore the rotational forces of the upper and
lower motors transmitted to the synchronous drive mechanisms 356a,
356b can be used efficiently.
[0434] Consequently, the strengths required for the mechanisms
336a, 336b, 344a, and 344b for moving the sliders composed of
various components and members such as the housing 319, sliders
324a, 324b, 325a, and 325b, die holders 326a, 326b, 327a, and 327b,
shaft boxes 337a, 337b, 345a, and 345b, crank shafts 339a, 339b,
347a, and 347b, and rods 342a, 342b, 350a, and 350b can be reduced,
so that these mechanisms, components and members can be made more
compact.
[0435] Moreover, when the upstream dies 330a, 330b and the
downstream dies 333a, 333b reduce and form the material 1 to be
shaped, the dies move towards the downstream B side of the transfer
line, so the movement of the material in a backward direction
towards the upstream A side of the transfer line, when the material
1 to be shaped is reduced and formed, can be avoided.
[0436] The plate reduction press apparatus and sub-methods
according to the present invention are not limited only to the
embodiments described above, but for example, the hydraulic
cylinders can be replaced by expanding actuators such as screw
jacks, for the die moving mechanisms; all the crank shafts can be
rotated by a single motor; each crank shaft can be rotated by an
individual motor; the number of rods that transmit the
displacements of the eccentric portions of the crank shafts to the
sliders can be changed; or any other modifications can be
incorporated unless they deviate from the claims of the present
invention.
[0437] As described above, the plate reduction press apparatus and
sub-methods of the present invention provide the following various
advantages.
[0438] (1) According to the plate reduction pressing sub-method of
the present invention, an unreduced portion of the material to be
shaped is reduced and formed by the first plate reduction
sub-method in which the upper and lower upstream dies reduce the
material in the direction of the plate thickness, and then the
portion of the material to be shaped, after being reduced and
formed by the first sub-method, is further reduced and formed by
the upper and lower downstream dies in the direction of the plate
thickness, by the second plate reduction sub-method, therefore the
material to be shaped can be reduced and formed efficiently in the
direction of the plate thickness.
[0439] (2) According to the plate reduction pressing methods of the
present invention, the first and second plate reduction sub-methods
are carried out alternately on an unreduced portion of the material
to be shaped and a portion of the material to be shaped, that has
been reduced by the first sub-method, consequently the loads to be
applied to the upstream and downstream dies during pressing can be
reduced.
[0440] (3) With any of the plate reduction press apparatus of the
present invention as discussed above, the mechanisms for moving the
upstream sliders move the upstream dies together with the upstream
sliders towards the transfer line, and an unreduced portion of the
material to be shaped is reduced by the upper and lower upstream
dies in the direction of the plate thickness, and then the
mechanism for moving the downstream sliders move the downstream
dies together with the downstream sliders towards the transfer
line, and the portion of the material to be shaped, already reduced
by the upstream dies, is further reduced by the upper and lower
downstream dies in the direction of the plate thickness, so that
the material to be shaped can be reduced and formed efficiently in
the direction of the plate thickness.
[0441] (4) In any of the plate reduction press apparatus of the
present invention discussed above, the upstream dies are moved
towards and away from the transfer line by the mechanisms for
moving the upstream sliders in the reverse phase to the phase that
the downstream dies are moved towards and away from the transfer
line by the mechanisms for moving the downstream sliders, therefore
the loads applied to the upstream and downstream dies during
pressing are reduced, so the strengths required for the various
components and members constituting the sliders on which the dies
are mounted and the mechanisms for moving the sliders, can be
reduced and they can be made more compact.
[0442] (Eighth Embodiment)
[0443] FIGS. 26 through 29 show an embodiment of the plate
reduction press apparatus according to the present invention, and
the item numbers in the figures identify components in the same way
as in FIG. 3.
[0444] Item number 417 indicates a flying sizing press apparatus,
which is configured in the same way as that shown in FIG. 3.
[0445] An upstream roller table 418 is arranged on the upstream A
side of dies 412a, 412b on the transfer line, and a downstream
roller table 419 is arranged on the downstream B side of the
transfer line.
[0446] The upstream roller table 418 is provided with a fixed frame
420 that is parallel to the material 1 to be shaped in the lateral
direction at a predetermined distance below the transfer line S and
extending substantially horizontal along the transfer line S, and a
plurality of table rollers 421 arranged on the fixed frame 420 at
predetermined intervals so that the rollers can support the lower
surface of the material 1 to be shaped, which is to be inserted
between the dies 412a, 412b, substantially horizontally, and that
are supported by the fixed frame 420 in a freely rotatable
manner.
[0447] The downstream roller table 419 is composed of a fixed frame
422 installed parallel to the material 1 to be shaped in the
lateral direction at a predetermined distance below the transfer
line S, and extending along the transfer line S substantially
horizontally, and a plurality of table rollers 423 arranged on the
aforementioned fixed frame 422 at predetermined intervals in a
freely rotatable manner, so that the rollers can support the lower
surface of the material 1 being shaped and fed out from the dies
412a, 412b of the flying sizing press apparatus 417.
[0448] On the upstream A side of the transfer line in the close
vicinity of the dies 412a, 412b of the flying sizing press
apparatus 417, a pair of upstream side guides 424 are installed,
that face the material 1 to be shaped in the lateral direction of
the transfer line S above the table rollers 421 of the upstream
roller table 418, and that are capable of being moved towards or
away from the transfer line S, and on the downstream B side of the
transfer line in the close vicinity of the above-mentioned dies
412a, 412b, a pair of downstream side guides 425 are installed,
that face the material 1 to be shaped in the lateral direction of
the transfer line S above the table rollers 423 of the downstream
roller table and that can be moved towards and away from the
transfer line S.
[0449] As shown in FIGS. 27 through 28 the upstream side guides 424
and the downstream side guides 425 are provided with a plurality of
guide frames 426 arranged on the floor further from the transfer
line than the fixed frames 420, 422 of the upstream and downstream
roller tables 418, 419, at predetermined intervals along the
transfer line S and extending horizontally in a direction
orthogonal to the transfer line S, a plurality of brackets 427
supported by the aforementioned guide frames 426 in a manner such
that they are free to move in the direction orthogonal to the
transfer line S, and a pair of main side guide units 428a, 428b
installed on and fixed to the tip portions of each of the brackets
427 and extending in the direction parallel to the transfer line
S.
[0450] The main side guide units 428a of the upstream side guides
424 are forced, as shown in FIG. 27, in such a manner that the ends
in the upstream A direction of the transfer line become gradually
wider towards the upstream side of the transfer line S, and the
main side guide units 428 of the downstream side guides 425 are
formed, as shown in FIG. 27, in such a manner that the ends in the
downstream B direction of the transfer line become gradually wider
towards the downstream side of the transfer line S.
[0451] Furthermore, the upstream and downstream side guides 424,
425 are provided with hydraulic cylinders 431 whose bases are
supported by the brackets 429 at the ends of the guide frames 426
farthest from the transfer line, and the tips of the rods of which
are connected to predetermined locations on the main side guide
units 428a, 428b through pins 430; by applying hydraulic pressure
to the hydraulic chambers on the head or rod side, the left and
right main side guide units 428a, 428b can be moved towards or away
from the transfer line S in synchronism with each other.
[0452] Moreover, the upstream side guides 424 are composed of a
plurality of upstream vertical rollers 432 supported by the left
and right main side guide units 428 at predetermined intervals
through bearings so that the vertical rollers 432 can contact the
lateral edges of the material 1 to be shaped, when the material
passes between the upstream side guides 424, and the downstream
side guides 425 are composed of a plurality of downstream vertical
rollers 433 supported by the left and right main side guide units
428b at predetermined intervals through bearings in such a manner
that the vertical rollers 433 can contact the lateral edges of the
material 1 to be shaped, when the material passes between the
aforementioned downstream side guides 425.
[0453] Item numbers 434 denote pinch rolls which are arranged on
the upstream A and downstream B sides of the transfer line in the
close vicinity of the flying sizing press apparatus 417.
[0454] The operation of the plate reduction press apparatus shown
in FIGS. 26 to 29 is described as follows.
[0455] When a long material 1 to be shaped is inserted between the
upper and lower dies 412a, 412b of the flying sizing press
apparatus 417 and the material 1 to be shaped is reduced and formed
in the direction of the plate thickness by the dies 412a, 412b,
appropriate hydraulic pressures are applied to the hydraulic
chambers on the rod and head sides of the hydraulic cylinders 431
of the upstream and downstream side guides 424, 425, to make the
upstream and downstream side guides 424, 425 move towards or away
from the transfer line S, thereby the gaps between the left and
right main side guide units 428a, 428b of the upstream and
downstream side guides 424, 425 are adjusted to predetermined
amounts (for example, about +10 mm) from the edges of the material
1 to be shaped.
[0456] In addition, by rotating the position adjusting screw 416
appropriately, the gap between the upper and lower dies 412a, 412b
is set according to the plate thickness of the material 1 to be
reduced and formed in the direction of the plate thickness.
[0457] Next, motors rotate the upper and lower rotating shafts
407a, 407b, and simultaneously the material 1 to be reduced and
shaped is supplied from the upstream side of the transfer line S
onto the upstream roller table 418.
[0458] When the material 1 to be shaped is moving from the upstream
side to the downstream side of the transfer line S on the upstream
roller table 418, the lateral edges of the material are guided by
the main side guide units 428a of the upstream side guides 424 and
the upstream vertical rollers 432 near the upstream side of the
flying sizing press apparatus 417 and made to move along the
transfer line S, in such a way that the lateral center line of the
material is guided into alignment with the lateral center line of
the upper and lower dies 412a, 412b of the flying sizing press
apparatus 417.
[0459] Thus, while the material 1 to be shaped is moving from the
upstream A side to the downstream B side of the transfer line S
along the line S, the material is reduced and formed in the
direction of the plate thickness by the upper and lower dies 412a,
412b that move towards and away from the transfer line S according
to the displacement of the eccentric portions of the rotating
shafts 407a, 407b.
[0460] During this time, the angles of the die holders 411a, 411b
are adjusted by applying hydraulic pressure to the hydraulic
chambers on the rod and head sides of the hydraulic cylinders 413a,
413b, in such a manner that the forming surfaces 415a, 415b of the
upper and lower dies 412a, 412b, near the downstream B side of the
transfer line, remain parallel to the transfer line S at all
times.
[0461] When the material 1 to be shaped is reduced and formed by
the dies 412a, 412b of the flying sizing press apparatus 417 and
transferred in the downstream direction of the transfer line S,
lateral deflections of the material are restrained by the main side
guide units 428b of the downstream side guides 425 and the
downstream vertical rollers 433, in the vicinity of the flying
sizing press apparatus 417 on the downstream side of the transfer
line, and the lateral edges of the material are thereby guided and
transferred along the transfer line S.
[0462] As described above, the plate reduction press apparatus
shown in FIGS. 26 to 29 is provided with the upstream side guides
424 equipped with a pair of main side guide units 428a which
support the upstream vertical rollers 432 through bearings, in the
close vicinity of the dies 412a, 412b on the upstream A side of the
transfer line, therefore the material 1 to be reduced and shaped in
the direction of the plate thickness by the upper and lower dies
412a, 412b can be moved along the transfer line S, and also can be
guided so as to align the lateral center line of the material with
the lateral center line of the upper and lower dies 412a, 412b of
the flying sizing press apparatus 417, and consequently, the
lateral edges of the material 1 to be shaped can be prevented from
being abraded by the main side guide units 428a.
[0463] In addition, downstream side guides 425 are provided,
equipped with a pair of main side guide units 328b that support the
downstream vertical rollers 433 through bearings, in the close
vicinity of the dies 412a, 412b on the downstream side of the
transfer line, therefore lateral deflections of the material 1
after being reduced by the upper and lower dies 412a, 412b in the
direction of plate thickness can be prevented, and the lateral
edges of the material 1 being shaped can be protected from being
abraded by the main side guide units 428b.
[0464] As described above, the plate reduction press apparatus
according to the present invention provides the following various
advantages.
[0465] (1) In any of the plate reduction press apparatus specified
in claims 21 or 22 of the present invention, a long material to be
shaped can be reduced and formed continuously in the direction of
the plate thickness because the material to be reduced and formed
is guided into the upper and lower dies by the upstream side guides
when the material is moving from the upstream to the downstream
sides of the transfer line, and after the material has been reduced
and formed by the dies and fed out to the downstream side of the
transfer line, lateral deflections of the material are prevented by
the downstream side guides.
[0466] (2) With the plate reduction press apparatus specified in
claim 22 of the present invention, the lateral edges of the
material to be shaped, when being introduced into the dies by the
upstream side guides, are guided by the upstream vertical rollers,
thereby protecting the lateral edges of the material from abrasion
with the main side guide units of the upstream side guides, and the
lateral edges of the material being shaped are prevented from being
deflected laterally by the downstream side guides, and are guided
by the downstream vertical rollers, in such a manner that abrasion
of the lateral edges of the material from the main side guide units
of the downstream side guides can be prevented.
[0467] (Ninth Embodiment)
[0468] FIG. 30 shows the configuration of a rolling mill operating
together with the plate reduction press apparatus according to the
present invention. In this figure, a looper device 506 is provided
downstream of the plate reduction press apparatus 510 of the
present invention, and a finishing rolling mill 505 is installed
further downstream. The looper device 506 holds up a material being
pressed in a slack loop, and the slack absorbs any differences in
the line speeds of the plate reduction press apparatus 510 and the
finish rolling mill 505.
[0469] FIG. 31 is a side view of the plate reduction press
apparatus shown in FIG. 30, and FIG. 32 is a sectional view along
the line A-A in FIG. 31. As shown in FIGS. 31 and 32, the plate
reduction press apparatus 510 according to the present invention is
provided with upper and lower drive shafts 512 arranged opposite
each other above and below a material 1 to be pressed and made to
rotate, upper and lower pressing frames 514 one end of each of
which (right end in FIG. 31) engages with one of the drive shafts
512 in a freely slidable manner, and the other ends 514b (left end
in the figure) of which are connected together in a freely
rotatable manner, a horizontal guide device 516 that supports the
connection portions 514c of the pressing frames 514 so that they
can move in the horizontal direction, and upper and lower dies 518
mounted at one end of the upper and lower pressing frames 514
opposite the material to be pressed. In FIG. 31, 511 indicates the
main frame of the unit.
[0470] The upper and lower drive shafts 512 are provided with
eccentric shafts 512a at both ends in the lateral direction, which
have different phase angles. In addition, spherical seats 515 are
provided at the places where the eccentric shafts 512a engage with
the press frames 514, and the press frames 514 can roll about the
axis X of the drive shafts as shown by the arrows A. The contacting
surfaces between the dies 518 and the material 1 to be pressed are
circular arcs and are convex towards the material to be pressed,
and can smoothly press the material when the press frames roll.
[0471] As shown in FIG. 32, there are driving devices 520 that
drive and rotate the drive shafts 512. These driving devices 520
are controlled by a speed controller 522, and the rotational speed
of the driving devices 520 can be freely controlled. In this
embodiment, height adjusting plates 524 are sandwiched between the
dies 518 and the press frames 514, and by changing the thickness of
the height adjusting plates 524, the heights of the dies 518 are
adjusted.
[0472] FIG. 33 schematically shows the paths in which the dies
move; (A) shows the general movement of the dies 518 and the press
frames 514, and (B) shows the movement of the dies 518 only. FIG.
34 shows the displacements of the dies 518 in the up and down
direction with respect to the angle of rotation .theta. of the
drive shafts. As shown in FIGS. 33 and 34, when each drive shaft
512 rotates, the corresponding eccentric shafts 512a rotate in
circles with a diameter equal to twice the eccentricity e of the
shaft, which cause the up and down press frames 514 to move in such
a manner that while the left end portion 514b is moving backwards
and forwards in the direction of the line, the right end portion
514a (in FIG. 31) moves up and down. Consequently, as shown in FIG.
33, each of the upper and lower dies 518 move in a circular path
with a diameter equal to twice the eccentricity e of the eccentric
shafts 512a, and at the same time, the dies open and close and also
roll in the lateral direction. Therefore, as the upper and lower
dies 518 move in the direction of the line while closing, the
material 1 to be pressed can be conveyed while it is being reduced.
In addition, because the upper and lower dies 518 close with a
rolling action, the loads during pressing can be reduced. The
amount of the reduction is determined by the eccentricity e of the
eccentric shafts 512a, therefore high-reduction pressing can be
carried out without being restricted by a nip angle etc. Also
because the material 1 to be pressed is transferred while being
reduced, a flying press operation can be achieved.
[0473] As shown in FIG. 33(B), the dies 518 are mounted at a small
angle to the press frames 514 when the dies are open (shown by the
solid lines in the figure) so that the parallel portions 518 become
parallel to each other during pressing (shown by the double dotted
chain lines in the figure). At this time, the area pressed during a
cycle is shown by the hatched area in the figure.
[0474] As shown in FIG. 34, the pair of eccentric shafts 512a
positioned at the two ends in the lateral direction are shifted in
phase relative to each other, and so the ranges in which the two
ends press the material 1 to be pressed are different from each
other, and because the upper and lower dies 518 close with a
rolling action, the loads during pressing can be reduced.
[0475] In addition, the speed controller 522 of the driving devices
520 determines the rotational speed of the drive shafts 512 so that
when the dies 518 press, the speed of the dies in the line
direction substantially match the feeding speed of the material 1
to be pressed. In this configuration, it is possible to match the
speed of the dies 518 in the line direction substantially with the
feeding speed of the material 1 to be pressed, therefore loads on
the driving devices 520 that drive and rotate the drive shafts 512
can be reduced.
[0476] In this way, the plate reduction press apparatus according
to the present invention provides various advantages such as (1)
flying press operation is enabled, in which a material to be
pressed is reduced while being transferred, (2) the number of
component parts is small, and the construction is simple, (3) a
small number of components need to slide under load during
pressing, (4) high-load and high-cycle operations are possible, (5)
the thickness of a material to be pressed can be corrected by
adjusting the position of the dies using a simple method, and so
forth.
[0477] (Tenth Embodiment)
[0478] FIG. 35 shows the configuration of a rolling facility used
together with the plate reduction press apparatus according to the
present invention. In this figure, a looper device 606 is installed
on the downstream side of the hot slab press apparatus 610
according to the present invention, and further downstream, a
finishing rolling mill 605 is provided. The looper device 606 holds
up a material being pressed in a slack loop, so that the slack
length of the material, smooths out any differences between the
line speeds of the hot slab press apparatus 610 and the finishing
rolling mill 605.
[0479] FIG. 36 is a side view of the hot slab press apparatus shown
in FIG. 35, and FIG. 37 is a sectional view along the line A-A in
FIG. 36. As shown in FIGS. 36 and 37, the hot slab press apparatus
610 according to the present invention is composed of upper and
lower crank shafts 612 arranged opposite each other above and below
the material 1 to be pressed and made to rotate, upper and lower
press frames 614 one end 614a (right end in the figure) of each of
which is engaged with one of the crank shafts 612 in a freely
slidable manner, and the other ends 614b (left end) are connected
together in a freely rotatable manner, a horizontal guide device
616 for supporting the connecting portion 614c of the press frames
614 so that they can move horizontally, and upper and lower dies
618 mounted at one end of each of the upper and lower press frames
614 facing the material 1 to be pressed. In this figure, 611 is the
main frame unit.
[0480] As shown in FIG. 37, driving devices 620 are provided to
drive and rotate the crank shafts 612, and the driving devices 620
are controlled by a speed controller 622, so that the rotational
speed of the driving devices 620 can be freely controlled.
[0481] With this embodiment, height adjusting plates 624 are placed
between the dies 618 and the press frames 614, and by changing the
thicknesses of the height adjusting plates 624, the heights of the
dies 618 are adjusted.
[0482] FIG. 38 schematically shows the paths in which the dies
move; (A) shows the general movement of the dies 618 and the press
frames 614, and (B) shows the movements of the dies 618 only. As
shown in FIG. 38, when the crank shafts 612 rotate, each of the
crank shafts 612 rotates in a circle with a diameter equal to twice
the eccentricity e of the shaft, and following this motion, the
upper and lower press frames 614 move in such a manner that while
the left end portion 614b moves backwards and forwards in the
direction of the line, the right end portions 614a (in FIG. 36)
move up and down. Therefore, as shown in this figure, each of the
upper and lower dies 618 moves in a circular path with a diameter
equal to twice the eccentricity e of one of the crank shafts 612,
and as the upper and lower dies 618 move in the line direction
while closing, the material 1 to be pressed can be transferred
while it is being pressed. The amount of the reduction depends on
the eccentricity e of the crank shafts 612, and a high-reduction
pressing operation can be achieved without being restricted by a
nip angle etc. In addition, a flying press system can be realized
because the material 1 to be pressed is conveyed while being
reduced.
[0483] As shown in FIG. 38 (B), the dies 618 are mounted on the
press frames 614 at a small angle thereto when the dies are open
(solid lines in the figure) so that the parallel portions 618a are
parallel to each other during pressing (double-dotted chain lines
in the figure). For this configuration the area pressed during a
cycle is shown by the hatched area in the figure.
[0484] In addition, the speed controller 622 of the drive devices
620 determines the rotational speed of the crank shafts 612 to make
the speed of the dies 618 in the line direction during pressing
substantially agree with the feeding speed of the material 1 to be
pressed. In this configuration, the speed of the dies 618 in the
direction of the line can be made to be substantially identical to
the feeding speed of the material 1 to be pressed, so variations in
the loads on the crank shafts, caused by a difference in speeds,
can be reduced.
[0485] FIG. 39 is a diagram showing how a hot slab is pressed
according to the present invention. In this figure, the abscissa
and the ordinate indicate the crank angle and the speed in the line
direction, respectively. According to the method of the present
invention, the speed for feeding a material to be pressed is
variable and made equal to the maximum speed of the dies in the
line direction. More preferably, the speed of feeding the material
to be pressed should be varied in such a manner that the speed is
greater than the above-mentioned maximum speed at the beginning of
pressing, and then be made smaller at an intermediate time during
pressing. Accordingly, the loads applied to the press crank shafts,
produced by variations in the inertia forces and speeds of the
material to be pressed, can be reduced.
[0486] As can be understood from the above description, the hot
slab press apparatus and pressing methods according to the present
invention present excellent practical advantages including (1) a
flying pressing system can be established to press a material while
it is being conveyed, (2) there are few component parts and the
construction is simple, (3) there are few parts which slide under
load during pressing, (4) the system can be operated at high loads
with fast operating cycles, (5) the position of the dies can be
adjusted using a simple method, and the thickness of the material
to be pressed can be corrected, and so on.
[0487] (Eleventh Embodiment)
[0488] FIG. 40 shows the configuration of a rolling facility used
together with the plate reduction press apparatus according to the
present invention. In this figure, a looper device 706 is installed
on the downstream side of the plate reduction press apparatus 710
according to the present invention, and further downstream, a
finishing rolling mill 706 is provided. The looper device 706 holds
up a material being pressed in a slack loop, so that the slack
portion of the material smooths out any differences in the line
speeds of the plate reduction press apparatus 710 and the finish
rolling mill 705.
[0489] FIG. 41 is a side view of the plate reduction press
apparatus shown in FIG. 40, and FIG. 42 is a sectional view along
the line A-A in FIG. 41. As shown in FIGS. 41 and 42, the plate
reduction press apparatus 710 according to the present invention is
provided with upper and lower eccentric drive shafts 715 arranged
opposite each other above and below a material 1 to be pressed and
driven and rotated by driving devices 720b, upper and lower
synchronous eccentric shafts 713 which are rotated by the eccentric
drive shafts 715, upper and lower press frames 714 one end 714a of
each of which is engaged with one of the synchronous eccentric
shafts 713 in a freely slidable manner, and the other ends 714b are
connected together in a freely rotatable manner, and upper and
lower dies 718 mounted opposite each other at one end of each of
the upper and lower press frames 714. In this figure, 711 indicates
the main frame unit.
[0490] Referring to FIG. 42, the upper and lower dies 718 are
opened and closed by rotating the upper and lower eccentric drive
shafts 715, and when the dies 718 are pressing, the speed of the
press frames 714 in the direction of the line is synchronized with
the speed at which the material to be pressed is being conveyed in
the line direction by means of the synchronous eccentric shafts
713, while pressing the material.
[0491] The outer peripheries of the synchronous eccentric shafts
713, are equipped with gear teeth, and the shafts are driven and
rotated by the driving devices 720a by the small gear wheels 712a
mounted on the drive shafts 712. As shown in FIG. 42, each shaft
can be connected to the driving devices 720a, 720b, through
universal joints etc., or, although not illustrated, each shaft may
also be driven by a differential device.
[0492] Also with this embodiment, height adjusting plates 724 are
positioned between the dies 718 and the press frames 714, so by
varying the thicknesses of the height adjusting plates 724, the
heights of the dies 718 can be adjusted.
[0493] FIG. 43 schematically shows the paths in which the dies
move; (A) shows the general movement of the dies 718 and the press
frames 714, and (B) shows the movements of the dies 718 only. FIG.
44 shows the displacements of the dies 718 in the up and down
direction with respect to the rotational angle .theta. of the
synchronous eccentric shafts. As shown in FIGS. 43 and 44, when the
drive shafts 712 are rotated, the upper and lower synchronous
eccentric shafts 713 rotate around the eccentric drive shafts 715,
therefore the synchronous eccentric shafts 715 move in a circle
with a diameter equal to twice the eccentricity e thereof, and the
outer peripheries thereof cause the upper and lower press frames
714 to move in such a manner that the left end 714b moves backwards
and forwards in the line direction, while the right end 714a (in
FIG. 41) move up and down. Consequently as shown in FIG. 43 (B),
each of the upper and lower dies 718 moves in a circular path with
a diameter equal to twice the eccentricity e of the synchronous
eccentric shafts 712a, while opening and closing.
[0494] Also as shown in FIG. 44, which shows the relation in speed
that results from combining the eccentricity E of the eccentric
drive shafts 715 and the eccentricity e of the synchronous
eccentric shafts 713, and a pseudo constant speed can be produced
over a range by varying the speed pattern. The amount of the
reduction at that time depends on the eccentricity e of the
synchronous eccentric shafts 713, so a high-reduction operation can
be carried out without being restricted by a nip angle etc.
Furthermore, because the material 1 to be pressed is conveyed by
the synchronous drive devices 716 while being reduced, a flying
pressing operation can be easily performed.
[0495] In addition, only the synchronous eccentric shafts 713
(double synchronous eccentric shafts) that are rotated by the
eccentric drive shafts 715 withstand loads during pressing, and the
connection portion 714c and the synchronous drive devices 716 have
to withstand only rather small loads that only cancel moments
acting on the press frames 714, and in addition, the moments
applied to the upper and lower press frames 714 cancel each other,
so the loads on the connection portion and the driving devices are
further reduced. As a result, there are few component parts, the
construction is simple, there are few portions that slide under
load during pressing, and the system can operate under high loads
at a high operating rate.
[0496] As shown in FIG. 43(B), the dies 718 are mounted on the
press frames 714 at a slight angle thereto when the dies are open
(solid lines in the figure) so that during pressing (double-dotted
chain lines in the figure), the parallel portions 718a are parallel
to each other. At this time, the area pressed during one cycle is
shown by the hatched area in the figure.
[0497] Obviously from the description above, the plate reduction
press apparatus according to the present invention provides
excellent advantages including (1) a material to be pressed can be
pressed by a flying press operation, in which the material is
reduced while it is being transferred, (2) there are few component
parts and the construction is simple, (3) a small number of parts
slide under load during pressing, and (4) the system can be
operated at high loads at a high operating rate.
[0498] (Twelfth Embodiment)
[0499] FIG. 45 shows the configuration of the plate reduction press
apparatus according to the twelfth embodiment of the invention, and
FIG. 46 is a sectional view along the line X-X in FIG. 45. Upper
and lower dies 802 are provided above and below a material 1 to be
pressed. Cooling water is supplied to the inside of the dies 802,
to cool the dies. Otherwise, cooling water can also be sprayed from
outside. The dies 802 are mounted on sliders 803 through die
holders 804, in a detachable manner. Two crank shafts 805 engage in
a freely slidable manner with the sliders 803 in the lateral
direction of the material 1 to be pressed, arranged in a row in the
direction (forward direction) of flow of the material. The crank
shafts 805 are composed of eccentric shafts 805b engaging with the
sliders 803, and support shafts 805a connected to both ends of the
eccentric shafts 805b in the axial direction thereof, and one of
the ends of the support shafts 805a is connected to a driving
device not illustrated which drives and rotates the crank 805. The
support shafts 805a and the eccentric shafts 805b are connected so
that the center line thereof are offset from each other, thus the
eccentric shafts 805b are rotated eccentrically around the support
shafts 805a.
[0500] Counterweights 806 are attached at each end of the support
shafts 805a of the eccentric shafts 805b. The counterweights 806
are mounted with the centers of gravity thereof offset from the
center lines of the support shafts 805a, and the angle of the
offset is 180.degree. from the direction of the eccentricity of the
eccentric shafts 805b with respect to the support shafts 805a. The
inertia forces (unbalanced forces) due to the eccentricity of the
counterweights 806 substantially cancel the inertia forces due to
the sliders 803, dies 802 and die holders 804, so that the
vibration of the apparatus can be reduced greatly.
[0501] The dies 802, sliders 803, die holders 804, crank shafts
805, and counterweights 806 are arranged symmetrically above and
below the material 1 to be pressed, and composed into one body by
the main frame unit 808. The eccentric shafts 805b are connected to
the sliders 803 in a freely rotatable manner through the bearings
807, and the support shafts 805a are supported through the bearings
807 provided on the main frame unit 808, in a freely rotatable
manner.
[0502] Next, the operation is described. FIG. 47 shows one cycle of
operation of the sliders 803. FIG. 48 illustrates the movements of
the sliders 803 and the material 1 to be pressed, during one
operating cycle. In FIG. 47, in a cycle time increase in the
sequence t1-t2-t3-t4-t1, and the material is pressed during the
period ta-tb which includes t2. In FIG. 48, t1-t4 corresponds to
t1-t4 in FIG. 47. At t1, the sliders 803 are raised to an
intermediate position, and are located at the farthest position in
the backward direction. At t2, the state during pressing is shown,
and the sliders are located at an intermediate position in the
backward and forward direction. At t3, the sliders are partly
raised, and at the farther position in the forward direction.
Hence, the sliders 803 move forwards during the period t1-t2-t3 as
shown by the arrows, and move at the maximum speed at t2 during
pressing. Consequently, the material 1 to be pressed is transferred
by the pinch rolls 809 when the sliders 803 are pressing, according
to the speed of the sliders, thereby the material can be conveyed
continuously at a speed most suitable for pressing, even during a
pressing period. Because the counterweights 806 move with phase
angles offset by 180.degree. from those of the sliders 803, the
vibration caused by the sliders 803 is reduced. In addition, the
counterweights also function as flywheels that contribute to a
reduction of the power required from the driving devices.
[0503] (Thirteenth Embodiment)
[0504] The thirteenth embodiment is described next. FIG. 49 shows
the configuration of the plate reduction press apparatus according
to this embodiment, and FIG. 50 is a sectional view along the line
Y-Y in FIG. 49, showing only the half on one side of the lateral
center line of the material 1 to be pressed, because the entire
construction is symmetrical about the center line. As shown in
FIGS. 49 and 50, this embodiment of the plate reduction press
apparatus according to the present invention is composed of upper
and lower crank shafts 815 arranged opposite each other above and
below the material 1 to be pressed and driven and rotated, upper
and lower press frames 813 one end 813a (right end in the figure)
of each of which is engaged with one of the crank shafts in a
freely rotatable manner, and the other ends 813b (left ends) are
connected together in a freely rotatable manner, horizontal guide
devices 819 that guide the connecting portions 813c of the press
frames 813 so that they can move horizontally, upper and lower dies
812 mounted at one end 813a of each of the upper and lower press
frames 813, facing the material 1 to be pressed, counterweights 816
installed on the crank shafts 815, and a main frame unit 818 that
supports the crank shafts 815. The dies 812 are mounted on the ends
813a through the height adjusting plates 814.
[0505] The horizontal guide device 819 is either a hydraulic
cylinder, crank mechanism or a servo motor, that moves the
connection portions 813c to which the upper and lower press frames
813 are connected, in the direction of transfer of the material to
be pressed when the crank shafts 815 rotate.
[0506] The crank shafts 815 are shown in FIG. 50, and are comprised
of eccentric shafts 815b that engage with the ends 813a of the
press frames 813, and support shafts 815a attached to both ends of
the eccentric shafts 815b with their axial center lines offset from
each other. The support shafts 815a are supported by the main frame
unit 818 through bearings 817, and the eccentric shafts 815b are
connected to the ends 813a through the bearings 817. On the support
shafts 815a outside the main frame unit 818, counterweights 816 are
mounted the centers of gravity of which are offset from the axial
center lines of the support shafts 815a, and the angle of the
offset is 180.degree. from the direction of the eccentricity of the
eccentric shafts 815b relative to the support shafts 815a. A
driving device 820 is provided at the end of a support shaft 815a
equipped with a counterweight 816, and is controlled by a control
device 822.
[0507] The operation of the present embodiment is described next.
FIG. 51 schematically shows the path in which the dies 812 move;
(A) shows the general movements of the dies 812 and the press
frames 813, and (B) shows the movements of the dies 812 only. When
the crank shafts 815 rotate, the upper and lower eccentric shafts
815b are rotated by the support shafts 815a, and the eccentric
shaft 815b rotates in a circle with a diameter equal to twice the
eccentricity e thereof, and the outer periphery thereof causes the
upper and lower press frames 813 to move in such a manner that the
other ends 813b reciprocate in the direction of the flow of the
material to be pressed, while the ends 813a move up and down.
Consequently, as shown in FIG. 51(B), the upper and lower dies 812
move up and down as they travel in a circular path with a diameter
equal to twice the eccentricity e of the eccentric shafts 815b.
[0508] As shown in FIG. 49, the horizontal guide device 819 allows
the connecting portion 813c of the press frames 813 to move in the
direction of flow of the material to be pressed when the dies 812
are pressing, thus the upper and lower dies 812 can move in the
direction of the flow of the material to be pressed while the dies
are pressing the material. At this time, the amount of the
reduction depends on the eccentricity e of the eccentric shafts
815b, therefore high-reduction pressing can be carried out without
being limited by a nip angle etc. Because the horizontal guide
device 819 allows the material 1 to be pressed to be transferred
while being pressed, flying press operations can be easily carried
out. In addition, as the counterweights 816 move with an angular
offset of 180.degree. from the motion of the ends 813a, they cancel
the vibrations due the ends 813a, which reduces the vibration as a
whole. In addition, the counterweights can also function as a
flywheel which contributes to reducing the power required from the
driving devices.
[0509] As can be easily understood from the description above, the
present invention can provide a flying reduction press system in
which a material to be pressed is reduced while it is being
conveyed, by directly rotating the ends of sliders or press frames
by eccentrics on crank shafts. Furthermore, as counterweights are
provided on the crank shafts, the vibration of the system can be
reduced, and because the counterweights function as flywheels, the
power required from the driving devices can be reduced. Moreover,
because the dies can be moved in the direction of flow of the
material to be pressed during the pressing period, thanks to the
eccentric motion of the crank shafts, no mechanisms are required to
move the dies in the direction of flow of the material to be
pressed during pressing, so the construction of the apparatus
becomes simple.
[0510] (Fourteenth Embodiment)
[0511] FIG. 52 is a sectional view showing a configuration of the
plate reduction press apparatus of the fourteenth embodiment
according to the present invention, and FIG. 53 is a sectional view
along the line X-X in FIG. 52. Dies 902 are arranged above and
below a slab 1. Cooling water is supplied to the dies 902 to cool
the interior of the dies 902. Otherwise, cooling water may also be
sprayed on the outside. The dies 902 are mounted on sliders 903
through the die holders 904, in a detachable manner. The sliders
903 are composed of main units 905 and cranks 907; on each main
unit 905, two circular holes 906 are arranged in a row in the
direction of flow (forward direction) of the slab, in which the
shafts of the cranks 907 are directed in the lateral direction of
the slab. The cranks 907 shown in FIG. 53 are composed of a first
shaft 907a engaging with the circular hole 906 through a first
bearing 908a, and second shafts 907b attached to both ends of the
first shaft 907a, with a diameter smaller than the diameter of the
first shaft, and the center lines thereof are made eccentric to
each other, and one end of the second shaft 907b is connected to a
driving device that is not illustrated. The second shafts 907b, in
the upper or lower sliders 903, are supported by a common frame 909
through the second bearings 908b. Pinch rolls 912 are arranged on
the downstream side of the dies 902, and control the transfer speed
of the slab 1. Table rollers 913 are provided on the inlet or
outlet side of the pinch rolls 912, and transfer the material to be
pressed or being pressed. In FIG. 53, A and B indicate the axes of
the first and second shafts, respectively.
[0512] FIG. 54 is a view showing the construction of the sliders;
since FIGS. 52 and 53 illustrated the sliders in a slightly
schematic way, a practical example is shown in FIG. 54, showing the
upper half above the slab 1. The die 902 for pressing the slab 1 is
mounted on a main unit 905 by means of a die holder 904. The main
unit 905 is provided with a row of two circular holes 906 arranged
in the direction of transfer of the slab 1. A crank 907 is
comprised of a first shaft 907a and second shafts 907b attached to
both ends of the first shaft, with a diameter smaller than the
diameter of the first shaft; the first shaft 907a is connected
through a first bearing 908a, and the second shafts are supported
by the second bearings 908b. The circular hole 906 indicates the
inner surface of the first bearing 908a. A and B indicate the axial
center lines of the first and second shafts, respectively, and both
shafts rotate around the center line B.
[0513] Next, the operation of the fourteenth embodiment is
described. FIG. 55 shows one cycle of operation of the slider 903,
and FIG. 56 shows the speed of the slab during such a cycle. FIG.
57 shows the movements of the slider 903 and the slab 1 during a
cycle. In FIG. 55, during the cycle time changes in the sequence
t1-t2-t3-t4-t1, and the slab is pressed during the interval ta-tb
which includes t2. In FIG. 56, the transfer speed of the slab 1 is
controlled by pinch rolls 912. During pressing, the slab 1 is
conveyed in synchronism with the forward speed of the slider 903,
and at other times, the slab 1 is transferred at the normal
transfer speed. The normal transfer speed is adjusted such that the
distance L moved by the slab per cycle is not longer than the
pressing length L1 of the dies 902 shown in FIG. 52, and also the
speed must match the speed of a downstream apparatus. Using such a
moving distance L as described above, the length of the slab
pressed in the previous cycle is slightly superimposed by the
length pressed in the next cycle, so pressing is carried out
appropriately.
[0514] In FIG. 57, t1-t4 corresponds to t1_t4 in FIGS. 55 and 56.
At t1, the slider 903 is raised to an intermediate position, and is
located at the farthest position in the backward direction. At t2,
the state during pressing is shown, in which the slider is located
at an intermediate position in the backward and forward direction.
The slider is partly raised at t3, and located at the farthest
position in the forward direction. The slider is located at the
highest position at t4, but at an intermediate position in the
backward and forward direction. The slider 903 is driven forwards
during the period t1-t2-t3 as shown by the arrows, as described
above, and the speed thereof becomes a maximum near t2 during
pressing. Therefore, the slab 1 can be continuously transferred at
the most suitable speed for pressing even during the pressing
period, by conveying the slab 1 by means of the pinch rolls 912 in
synchronism with the speed of the slider 903.
[0515] (Fifteenth Embodiment)
[0516] The fifteenth embodiment is described next. With this
embodiment, balancers that absorb the unbalanced moments are
provided on the sliders. FIG. 58 is a side view of the fifteenth
embodiment, showing the upper half of the structure which is
symmetrical in the vertical direction; FIG. 59 is a sectional view
along the line X-X in FIG. 58, and FIG. 60 is a sectional view
along the line Y-Y shown in FIG. 58. As shown in FIG. 58, the
slider 903 is composed of a large crank 907 the unbalanced moment
of which due to the load, is absorbed by the balancer 914 using a
crank 917.
[0517] Referring to FIGS. 58 and 59, a die 902 is provided above a
slab 1, and the die 902 is mounted on a main unit 905 by means of a
die holder 904, in a detachable manner. In the crank 907, a first
shaft 907a is connected to two second shafts 907b at both ends of
the first shaft with the shaft center lines offset. The first shaft
907a is connected through first bearings 908a, and the second
shafts 907b are supported by the second bearings 908b provided on
the frame 909 shown in FIGS. 52 and 53. A and B indicate the center
lines of the first and second shafts, respectively. A gear coupling
916 is provided at the end of one of the second shafts 907b,
through which the second shaft 907b is rotated by a driving device
not illustrated.
[0518] The balancer 914 is provided with the crank 917 which is
comprised of a first shaft 917a and second shafts 917b attached to
both ends of the first shaft, with a diameter smaller than the
diameter of the first shaft 917a, and the axial center line "a" of
the first shaft is offset from the axial center line B of the
second shaft. The first shaft 907a is connected to the first
bearings 908a which are fixed to an outer ring 919. The second
shafts 907b are supported by the second bearings 908b which are
fixed to a support structure 915. The support structure 915 is
installed on the main unit 905 using bolts. At the end of the other
second bearing 907b, the gear coupling 916 is provided and driven
by a driving device that is not illustrated. "a" and "b" indicate
the axial center lines of the first shaft 917a and the second
shafts 917b, respectively.
[0519] Next, the operation of the fifteenth embodiment is
described. The operation of the slider 903 during the reduction of
a slab 1 is same as that of the first embodiment. However, because
a crank 907 is provided on each of the upper and lower sides, an
unbalanced moment is produced by the reaction force when the slab 1
is pressed. The balancer 914 functions to cancel this unbalanced
moment.
[0520] (Sixteenth Embodiment)
[0521] Next, the sixteenth embodiment is described. FIG. 61 is a
sectional view of the configuration of the plate reduction press
apparatus according to the sixteenth embodiment, and FIG. 62 is a
sectional view along the line X-X in FIG. 61. The same item numbers
as in FIGS. 52 and 53 are used to indicate the same components and
functions. With the present embodiment, a die 902 and a slider 903
are provided either above or below a slab, but on the side opposite
the die 902, a support member 910 is installed, and pressing is
carried out from one side. Reducing operations and backward and
forward movements of the slider are carried out in the same way as
in the fourteenth embodiment shown in FIG. 57, but the amount of
the reduction due to pressing is less. In addition, during the
backward and forward movements of the die when it presses a slab 1,
the transfer of the slab is resisted by a friction force produced
between the slab and the support member 910, so the driving device
of the slider 903 and the pinch rolls 912 are more heavily loaded.
However, the construction is simpler and the cost of manufacture is
reduced.
[0522] Obviously as described above, according to the present
invention, the die and the backwards and forwards moving slider are
provided, so that the slab can be transferred while being pressed
and a downstream rolling operation can be carried out continuously.
A plurality of cranks are also provided and can maintain the die
parallel to the transfer line. Alternatively one pressing crank and
a balancing crank can also be provided to maintain the die
parallel. The die can also be easily cooled internally or
externally, therefore the life of the die can be prolonged. It is
also possible to reduce a slab by more than 50 mm during one
pressing operation. Furthermore, the entire apparatus can be made
compact.
[0523] (Seventeenth Embodiment)
[0524] FIG. 63 shows the configuration of the seventeenth
embodiment according to the present invention. As shown in this
figure, the plate reduction press apparatus of the present
invention is provided with a pair of dies 1002 opposite each other
above and below a slab 1, and devices 1010 for swinging the dies
provided for each die 1002, that drive the dies backwards and
forwards with respect to the slab 1.
[0525] As shown in FIG. 63, the devices 1010 for swinging the dies
are composed of sliders 1012 each of which is provided with a pair
of circular holes 1012a positioned obliquely to the direction of
feed of the slab with an interval L between each hole, and
eccentric shafts 1014 rotating inside the circular holes 1012a.
[0526] Each of the eccentric shafts 1014 is comprised of a first
shaft 1014a that rotates in the circular hole 1012a around the
center line A of the circular hole, and a second shaft 1014b driven
and rotated around a center line B offset from the first center
line 1014a by the eccentricity e. The second shaft 1014b is
supported by bearings not illustrated, and is driven and rotated by
a driving device also not illustrated.
[0527] Cooling water is supplied to the dies 1002 to cool the dies
1002. Cooling water can also be sprayed from the outside of the
dies. The dies 1002 are mounted detachably on the sliders 1012
through the die holders 1011. Pinch rolls 1016 are installed
downstream of the dies 1002 and control the transfer speed of the
slab 1, table rollers 107 are provided at the inlet or outlet side
of the pinch rolls 1016 and transfer the material to be pressed. In
FIG. 63, A and B indicate the axial center lines of the first and
second shafts, respectively.
[0528] (Eighteenth Embodiment)
[0529] FIG. 64 shows the configuration of the eighteenth embodiment
according to the present invention. In this figure, a pair of
circular holes 1012a in the sliders 1012 are positioned
perpendicular to the transfer direction of a slab, and a pair of
eccentric shafts 1014 are also located perpendicular to the
direction of feed of the slab. The other details of the
configuration are the same as those in FIG. 63.
[0530] Next, the operation is described. FIG. 65 shows one cycle of
operation of the sliders 1012, and FIG. 66 shows the slab speed
during the cycle. In FIG. 65, time during the cycle changes in the
sequence t1-t2-t3-t4-t1, and the slab is pressed within the period
ta-tb which includes t2. In FIG. 66, the transfer speed of the slab
1 is controlled by the pinch rolls 1016. The speed is synchronized
with the speed at which the slab 1 is fed by the dies 1002 during
the pressing time (reducing time) in which the dies 1002 press the
slab 1, and during the period in which there is no pressing and the
slab 1 is not in contact with the dies 1002, the slab is conveyed
at a constant speed so that a specified cycle speed is achieved. In
other words, the slab 1 is transferred in synchronism with the
forward speed of the sliders 1012 during pressing, and otherwise a
normal conveying speed is used. The normal speed is selected such
that the distance in which the slab is moved per cycle is not
longer than the pressing length of the dies 1002, and so that the
speed is also suitable for a downstream system. The moving distance
selected as above results in the length being pressed in the
present cycle, being slightly superimposed on the length pressed in
the previous cycle so that the reduction is performed properly.
[0531] At t1 shown in FIGS. 65 and 66, the sliders 1012 are raised
to an intermediate position and are located in the farthest
position in the backward direction. At t2, the sliders are in the
pressing position and are located at an intermediate position in
the backward and forward direction. The sliders are partially
raised at t3, and located at the farthest position in the forward
direction. At t4, the sliders are located at the highest point, and
are in an intermediate position in the backward and forward
direction. The sliders 1012 are advanced as shown by the arrows
during the period t1-t2-t3, and the speed thereof becomes a maximum
near t2 during pressing. Consequently, by conveying the slab 1 with
the pinch rolls 1016 in synchronism with the speed of the sliders
1012 during pressing, the slab can be transferred continuously at
the most suitable speed for reducing, even during pressing.
[0532] According to the configurations of the present invention as
described above, the two eccentric shafts 1014 rotating in a pair
of circular holes 1012a in the sliders 1012 are positioned at an
inclined angle or perpendicular to the direction of feed of the
slab, so the required length of the apparatus in the direction of
the line can be reduced from the case where the eccentric shafts
are installed on the same level parallel to the direction of the
line. In particular, when the eccentric shafts on one side of the
transfer line are installed at different distances from the line,
the forces acting on the two eccentric shafts during pressing can
be made identical to each other, so that the length of the
apparatus in the direction of the line can be reduced while at the
same time achieving uniform loading of each eccentric shaft. When
the two eccentric shafts on one side of the slab feeding direction
are arranged vertically to the direction as shown in FIG. 64, the
load applied to the lower eccentric shaft can be made greater,
therefore the upper eccentric shaft can be made compact.
[0533] Obviously from the description above, the present invention
provides dies and sliders that press the dies and move them
backwards and forwards, with which a slab can be conveyed while
being pressed, hence a downstream rolling operation can be carried
out continuously. In addition, the necessary length of the press
apparatus in the direction of the line can be reduced, and while
transferring the slab, the plate thickness of the slab can be
reduced with a high reduction ratio.
[0534] (Nineteenth Embodiment)
[0535] FIG. 67 is a view showing the configuration of the plate
reduction press apparatus according to the nineteenth embodiment.
The press machine is provided with upper and lower dies 1102 above
and below a material to be pressed 1, hydraulic cylinders 1103 that
press the dies 1102, and frames 1104 supporting the hydraulic
cylinders 1103. Assuming the thickness of the material 1 to be
pressed is T, that is, T is reduced to a thickness t. The
longitudinal length of the dies 1102 is indicated by L which is
shorter than the width of the material 1 to be pressed. The
hydraulic cylinders 1103 are composed of rods 1103a connected to
the dies 1102, pistons 1103b pushing the rods 1103a, and cylinders
1103c that house the rods 1103a and the pistons 1103b. In addition,
a device for supplying a hydraulic fluid under pressure to the
hydraulic cylinders is also provided, although not illustrated. The
present embodiment relates to a case in which two pairs of the dies
1102 are provided above and below the material to be pressed, in
which the two pairs of the dies 1102 are arranged at intervals of
2L in the longitudinal direction.
[0536] The operation is described below.
[0537] FIG. 68 shows the configuration in which the two pairs of
dies 1102 are pressed simultaneously. (A) shows the state when
pressing begins in the present step of the process after the
material has been reduced in a previous step of the process. (B)
shows the state in which the material has been pressed from the
state shown in (A). In (C), the dies 1102 are ready to reduce the
material 1 to be pressed, after the dies 1102 have been separated
from each other from the state shown in (B), and the material was
moved a distance 2L in the longitudinal direction. In (C) the state
has returned to the state of (A). Thus by repeating steps (A)
through (C), the thickness T can be reduced to t. As two pairs of
dies 1102 press simultaneously, high-speed pressing can be
carried.
[0538] FIG. 69 shows the case in which the pressing operations of
the two pairs of dies 1102 are shifted in time. (A) shows the state
when pressing begins in the present step of the process after the
material has been reduced in a previous step of the process. (B-1)
shows the status when the material 1 to be pressed has been pressed
by the downstream dies 1102 from the state of (A). (B-2) shows the
condition after the material has been pressed by the upstream dies
from the state of (B-1). (C) is a sectional view of the material 1
to be pressed after the dies 1102 have been opened from the state
of (B-2) and the material has been moved a distance 2L
longitudinally, and the two pairs of dies 1102 are ready to press.
The state in (C) has returned to the state (A). Thus by repeating
the steps (A) through (C), the thickness T can be reduced to t. In
this way, the power required to press the dies 1102 becomes only
one half of the power required to drive all the dies during
pressing as shown in FIG. 68, accordingly the capacity of the
driving devices can also be halved together with a reduction in the
cost.
[0539] (Twentieth Embodiment)
[0540] The twentieth embodiment is described below. FIG. 70 shows
the configuration of the plate reduction press apparatus of the
twentieth embodiment, and FIG. 71 shows its operation. According to
the present embodiment, three pairs of dies 1102 are arranged in
the direction of movement of the material 1 to be pressed at
intervals of 3L where L is the length of a die 1102, and the other
details are the same as those of the previous embodiment shown in
FIG. 67. FIG. 71 shows the operations when the three pairs of dies
1102 press simultaneously. FIG. 71(A) shows the state when pressing
is just beginning in the present step of the process after the
material has been pressed in a previous step of the process. (B)
shows the condition of the material after it has been pressed from
the state shown in (A). (C) shows a view of the material 1 after it
has been pressed by the dies 1102 after the dies 1102 have been
separated from each other from the state shown in (B) and after the
material has been moved a distance 3L longitudinally. (C) has
returned to the state of (A). By repeating steps (A) through (C),
the thickness T can be reduced to t. Because three pairs of dies
1102 press simultaneously, high-speed pressing can be carried out.
When three pairs of dies 1102 press sequentially, the process shown
in (B) is divided into sub-processes, the upstream dies 1102 press
first, the middle dies 1102 press next, and then the downstream
dies 1102 press. Although this method requires a long pressing
time, the power to drive the dies can be as low as the power for a
single pair of dies, so the cost is reduced.
[0541] The above explanation of the embodiment is related to two
and three pairs of dies, however N pairs of dies can also be
introduced into a press machine.
[0542] It can easily be understood from the above description, that
because a plurality of short dies are arranged in tandem according
to the present invention, the masses of the dies and the driving
devices can be reduced to permit high-speed reduction and
large-reduction pressing can be carried out.
[0543] In addition, the material to be pressed can be conveyed
smoothly in the longitudinal direction, resulting in reducing the
power required for driving the dies. When a plurality of dies are
operated sequentially, the power required for driving the dies can
be greatly reduced.
[0544] (Twenty-first Embodiment)
[0545] FIG. 72 shows a configuration of the plate reduction press
apparatus according to the present embodiment. In FIG. 72, the
plate reduction press apparatus is provided with N press machines
1212 installed in a housing 1211. The following description assumes
N=4, which is not a necessary condition. The press machines 1212
are composed of pairs of upper and lower machines above and below a
material 1 to be pressed, and four pairs are arranged in tandem in
the direction of flow of the material 1 to be pressed. A press
machine 1212 is comprised of dies 1213 and pressing devices 1214
that press the dies. Although the pressing devices 1214 are shown
in an example in which hydraulic cylinders 1214 are used, other
devices may also be used. The dies 1213 are numbered 1201 through
1204 sequentially from the upstream end. The length of a pair of
dies 1213 in the direction of the flow of the material to be
pressed is shown as L, so the pressing length of the four pairs of
dies 1213 is 4L. Pinch rolls 1215 are installed at the inlet of the
housing 1211, and feed out the material 1 to be pressed as required
to suit the pressing operation of the press machines 1212. The
hydraulic cylinders 1214 and the pinch rolls 1215 are controlled by
a control device 1216.
[0546] Next, the operation of the twenty-first embodiment is
described. With this embodiment, the material 1 to be pressed is
reduced sequentially to a predetermined thickness by means of the
downstream reduction press machines 1212. FIG. 73 is a descriptive
diagram of the operation of the twenty-first embodiment. FIG. 73
and subsequent figures show only the upper half of the material 1
to be pressed, and also the upper half of the reduction press
machines 1212. FIG. 73 (A) shows the process in which a length 4L
of material, that is, 4 times the length L of a die, is reduced by
pressing the material using dies 1204 through 1201 in that order,
and (B) shows the conditions during pressing of the next length 4L.
As shown in (A), the material 1 to be pressed is conveyed by pinch
rolls 1215 under the dies 1204 through 1201, where each of dies
1204 to 1201 press one at a time and is retracted, and then the
next die presses, that is, one die completes its pressing in one
operation. Consequently, two or more reduction press machines 1212
never operate at the same time, so the pressing loads are small. At
that time, the corresponding upper and lower hydraulic cylinders
1214 operate simultaneously. After the die 1201 has finished
pressing, the material is fed by a length 4L by pinch rolls 1215 as
shown in (B), and pressing of the next length 4L begins.
[0547] (Twenty-second Embodiment)
[0548] The operation of the twenty-second embodiment is described
as follows. With this embodiment, every time a material 1 to be
pressed is conveyed by a length L, each of the dies 1201 to 1204
presses the material in that order. Each of dies 1201 through 1204
presses the material by an amount .DELTA.t from the thickness
already reduced by the preceding dies. After the pinch rolls 1215
feed the material through a distance L, each of dies 1201 to 1204
presses once in that order. FIG. 74(A) is a view showing that the
material 1 to be pressed after it has been conveyed only up to the
die 1201 only. At this time, the dies 1202 through 1204 operate
idly. (B) shows the state after the material 1 to be pressed has
been fed so that the end is under the die 1202. In "a," the
material is pressed by an amount .DELTA.t with the die 1201 and in
"b," the material is pressed by another amount .DELTA.t, that is,
the original thickness is reduced by 2.DELTA.t. As shown in c and
d, dies 1203 and 1204 press idly.
[0549] In FIG. 75(A), the material 1 to be pressed has been fed so
that the end is under the die 1203. In "a," the die 1201 presses
the material by an amount .DELTA.t. In "b," the die 1202 presses by
a further amount .DELTA.t to give a total of 2.DELTA.t. In "c," the
die 1203 reduces the material from the reduction of 2.DELTA.t to
3.DELTA.t. The die 1204 presses idly as shown in "d." FIG. 75 (B)
shows the condition in which the material 1 to be pressed has been
conveyed so that the end is under the die 1204. In "a," the die
1201 presses the material by an amount .DELTA.t. In "b," the die
1202 reduces the material from a reduction of .DELTA.t to
2.DELTA.t. In "c," the die 1203 presses to reduce from 2.DELTA.t to
3.DELTA.t. In "d", the die 1204 presses, from the reduction of
3.DELTA.t to 4.DELTA.t. At this time, the amount of reduction of
4.DELTA.t is the planned reduction.
[0550] FIG. 76 is a view in which the leading end of the material 1
to be pressed has been transferred beyond the die 1204 by a length
L. In "a," the die 1201 presses the material by an amount .DELTA.t.
In "b," the die 1202 presses the material from a reduction of
.DELTA.t to 2.DELTA.t. In "c," the die 1203 presses from a
reduction of 2.DELTA.t to 3.DELTA.t. In "d," the die 1204 reduces
the material from 3.DELTA.t to 4.DELTA.t. In this way, the planned
reduction of 4.DELTA.t is achieved. Because each reduction press
machine works sequentially, and only one machine is actuated at a
time, the loads applied to the entire reduction equipment are
small, and the equipment can be made small.
[0551] In the aforementioned embodiment, the material 1 to be
pressed has been assumed to move only in the forward direction, but
the amount of the reduction can be increased to twice as much by
feeding the material backwards and then pressing again.
[0552] As can easily be understood from the above description,
according to the present invention, the pressing length of each of
a plurality of reduction press machines is made short, and the
machines press the material sequentially, so that two or more
machines will not be working at the same time, therefore the loads
applied to the entire reduction press equipment are small and the
equipment becomes compact.
[0553] (Twenty-third Embodiment)
[0554] FIG. 77 shows the configuration of the plate reduction press
apparatus of the twenty-third embodiment. A flying press machine
1302 is installed in the upstream direction of the flow of a
material 1 to be pressed, and a rolling mill 1303 is installed in
the downstream direction of the flow. The flying press machine 1302
is provided with dies 1302a that press the material 1 to be
pressed, pressing cylinders 1302b that depress the dies 1302a, and
transfer cylinders 1302c that move the dies 1302a and the pressing
cylinders 1302b backwards and forwards in the direction of flow of
the material to be pressed. The rolling mill 1303 is either a
roughing-down mill and a finishing rolling mill, or a finishing
rolling mill. Press-side speed adjusting rolls 1304 are provided on
the downstream side of the flying press machine 1302, and
rolling-mill-side speed adjusting rolls 1305 are installed on the
upstream side of the rolling mill 1303, between the flying press
machine 1302 and the rolling mill 1303. For the speed adjusting
rolls 1304, 1305, pinch rolls, and measuring rolls, etc. are
provided, which adjust the speed of the material 1 to be
transferred and pressed and also measure the length of the material
passed. Transfer tables 1306 are installed between the flying press
machine 1302 and the press-side speed adjusting rolls 1304 and
between the rolling mill 1303 and the rolling-mill-side speed
adjusting rolls 1305.
[0555] Guide rolls 1307 are provided with a spacing m between each
other, between the press-side speed adjusting rolls 1304 and the
rolling-mill-side speed adjusting rolls 1305, and this space
between the two guide rolls 7 constitutes a section m in which the
material 1 to be pressed is deflected. In the deflection section m,
a pit has been formed in the foundations in which an up/down table
1308 with rollers for transferring the material 1 to be pressed is
installed and can be raised and lowered by means of up/down
cylinders 1309 provided under the table. In the deflection section
m, there is a low-position detector 1310a that detects the
occurrence of a large deflection and a high-position detector 1310b
that detects the occurrence of a small deflection. A control device
1311 controls the flying press machine 1302, the press-side speed
adjusting rolls 1304, the rolling-mill-side speed adjusting rolls
1305, and the up/down cylinders 1309 based on data for the lengths
passing the press-machine side speed adjusting rolls 1304 and the
rolling-mill-side speed adjusting rolls 1305 and deflection data
from the low-position detector 1310a and the high-position detector
1310b.
[0556] Next, the operations are described. First, the up/down table
1308 is positioned at the highest level, that is, the rolls of the
up/down table 1308 are on the same level as the level of the guide
rolls 1307, by means of the up/down cylinders 1309, and then the
flying press machine 1302 is operated to reduce the material 1 to
be pressed and feed the material to the rolling mill 1303. At the
rolling mill 1303, continuous rolling begins. When the material 1
to be pressed enters between the rolling-mill-side speed adjusting
rolls 1305, the up/down table 1308 is lowered to the lowest
position to enable the material to be deflected. At the same time,
the press-side speed adjusting rolls 1304 and the rolling-mill-side
speed adjusting rolls 1305 provide data for the lengths passed, and
the low position detector 1310a and the high position detector
1310b provide data about the deflection, and these data are input
to the control device which determines the difference between the
lengths passed, that is, the difference between two lengths passed
during one cycle or a plurality of cycles of the flying press
machine, and the control device adjusts the transfer speeds of the
material 1 to be pressed by the press-side speed adjusting rolls
1304 and the rolling-mill-side speed adjusting rolls 1305, and
increases or decreases the number of operating cycles in a
predetermined time period, and so forth. These three adjustments
are performed by selecting either one, two or three of them. In
addition, data from the low position detector 1310a and the high
position detector 1310b are monitored continuously, and the
deflection data is checked to see if the deflection remains within
a predetermined range, and if not, the speed adjusting rolls 1304,
1305 adjust the deflection to keep it in the range. When the
trailing end of the material 1 to be pressed approaches the
press-side speed adjusting rolls 1304, the up/down cylinders 1309
are operated in such a manner that the position of the rollers on
the up/down table 1308 match the guide rolls 1307.
[0557] FIG. 78(A) shows the variations in the speed of the material
to be pressed at the inlet of the press-side speed adjusting rolls,
and (B) shows the speed at the outlet of the rolling-mill-side
speed adjusting rolls 1305. The transfer speed of the material 1 to
be pressed, as it passes through the flying press machine 1302, is
adjusted by the press-side speed adjusting rolls 1304, and the
speed of the material 1 to be pressed, sent into the rolling mill
1303, is adjusted by the rolling-mill-side speed adjusting rolls
1305. In (A), the pressing period is determined by the transfer
cylinders so that an optimum transfer speed for pressing is
established, and the press-side speed adjusting rolls 1304 are
adjusted to establish this speed. After pressing, the transfer
speed is increased from the low speed used during pressing, and
then after the speed is decreased to the normal transfer speed and
maintained at that speed, the speed is reduced to the pressing
speed for the next cycle. The dies 1302a and the pressing cylinders
1302b are moved by the transfer cylinders 1302c in such a manner
that during a predetermined period from before pressing, during
pressing and after pressing, the dies and the cylinders move in the
direction of flow of the material 1 to be pressed and then return
to the upstream side. The press-side speed adjusting rolls 1304
adjust the transfer speed during the period other than the pressing
period (the period in which the dies 1302a are separated from the
material 1 to be pressed). The rolling-mill-side speed adjusting
rolls 1305 adjust the transfer speed of the material 1 to be
pressed so as to convey the material at as even a speed as possible
to the rolling mill 1303.
[0558] (Twenty-fourth Embodiment)
[0559] The twenty-fourth embodiment is described next. FIG. 79
shows the configuration of the plate reduction press apparatus
according to the twenty-fourth embodiment. Item numbers refer to
the same components as those in FIG. 77. The present embodiment is
different from the embodiment shown in FIG. 77, in that a
start-stop reduction press machine 1320 is used in place of the
flying press machine 1302 shown in FIG. 77, in which transfer of
the material 1 to be pressed is stopped during pressing, and the
other details of the configuration are same. Because the transfer
speed adjusting methods are considerably different for the two
embodiments, the method is described by referring to FIG. 80. FIG.
80(A) shows the transfer speed of the material 1 to be pressed as
it passes through the reduction press machine 1320. One cycle means
that of the reduction press machine 1320. The transfer speed during
the pressing period is 0. After completing the pressing of the
material, the transfer speed is increased abruptly to recover the
delay caused by pressing, and then it is decreased sharply down to
the normal speed. When the next cycle of pressing approaches, the
speed is adjusted to close to zero. At the rolling-machine-side
speed adjusting rolls 1305, as shown in (B), the deflection absorbs
a length of the material when the transfer speed suddenly changes,
and the material 1 to be pressed is fed into the rolling mill 1303
at a speed as uniform as possible, but the deflection changes
depending on the magnitude of the speed change. Therefore, the
plate reduction press apparatus according to the present embodiment
can be applied also to a start-stop reduction press machine as well
as a flying press machine 1302.
[0560] Obviously from the above, according to the present
invention, a press machine and a rolling mill can be operated
simultaneously to press and roll a material, respectively, by
adjusting the transfer speed of the material to be pressed, when
the material flows through the upstream press machine and the
downstream rolling mill.
[0561] (Twenty-fifth Embodiment)
[0562] FIG. 81 is a view showing the configuration and operations
of the plate reduction press apparatus according to the
twenty-fifth embodiment of the present invention. Dies 1402 are
provided above and below a material 1 to be pressed, and the dies
1402 are moved up and down by crank devices 1403 and press the
material 1. The dies 1402 and the crank devices 1403 are moved
backwards and forwards in the direction of flow of the material to
be pressed, by means of reciprocating crank devices 1404. The crank
devices 1403 and the reciprocating crank devices 1404 are operated
in synchronism with each other. Item numbers indicate various
components; 1402a for an upper die, 1402b for a lower die, 1403a
for an upper crank device, 1403b for a lower crank device, 1404a
for an upper reciprocating crank device, and 1404b for a lower
reciprocating crank device. Pinch rolls 1405 are arranged upstream
and downstream of the dies 1402, and control the transfer speed of
the material 1 to be pressed, and are controlled by a control
device not illustrated. Transfer tables 1406 are installed near the
pinch rolls 1405 and transfer the material 1 to be pressed. A
looper 1407 is provided downstream of the downstream pinch rolls
1405 and the downstream transfer table 1406, on the downstream side
of the dies 1402, and the looper holds up a length of the material
1 to be pressed in a loop, to cope with the transfer speed of the
material 1 to be pressed in a subsequent system. The transfer
device specified in the Claim 56 refers to the pinch rolls
1405.
[0563] FIG. 82 is a diagram describing the operations of the crank
devices 1403, 1404. FIG. 83 is a curve showing the operations of
the crank devices 1403 shown in FIG. 82, developed along the crank
angle .theta., and FIG. 84 is a diagram showing the speed of the
material 1 to be pressed in the direction of flow by the dies 1402
driven by the reciprocating crank devices 1404 in FIG. 82, as a
function of the crank angle .theta.. In FIG. 82, the letter c
denotes the bottom dead center of the upstream crank devices 1403a
or the top dead center of the downstream crank devices 1403b, and
the material 1 to be pressed is reduced by the dies 1402 in a range
of crank angles .theta. from b to c1, which includes the point c.
The speed of the dies 1402 during pressing in the direction of flow
of the material to be pressed is shown in FIG. 84; Vb, Vc, and Vc1
indicate the speeds at the points b, c, and c1, respectively.
[0564] FIG. 85 shows the transfer speed of the material 1 to be
pressed, transferred by the pinch rolls 1405. Vb, Vc and Vc1
indicate the speeds of the dies 1402, shown in FIG. 84. The pinch
rolls 1405 convey the material 1 to be pressed at the same speed as
the speed of the dies 1402 moved by the reciprocating crank devices
1404 when the crank devices 1403 are causing the dies 1402 to
press. In other words, the speed becomes Vb when pressing begins,
the same as the dies 1402, and after reaching the maximum speed Vc,
it becomes Vc1, i.e. the speed when pressing ends, and after that,
the speed changes to the original speed Vb for the beginning of the
next pressing operation. The pinch rolls 1405 are controlled in
such a manner that the length L is less than the effective pressing
length L0 of the dies 1402 shown in FIG. 81, where one cycle of the
pinch rolls is defined by the time period from the speed Vb when
pressing starts to the next speed Vb when pressing starts again,
and L represents the distance moved by the material 1 to be pressed
during one cycle. As described above, the length L of the material
1 to be pressed is reduced during one cycle of the pinch rolls 1405
(which is the same length as that of one cycle of the crank devices
1403).
[0565] In FIG. 81, (A) shows the status at point a, (B) shows the
conditions during pressing from point b to c1, and (C) shows the
conditions at point d, corresponding to d in FIG. 82. The material
is pressed sequentially by the length L each cycle, while repeating
steps (A), (B) and (C).
[0566] (Twenty-sixth Embodiment)
[0567] The twenty-sixth embodiment is described next. FIG. 86 is a
view showing the configuration of the twenty-sixth embodiment. The
twenty-sixth embodiment is provided with the two-dimensional crank
devices 1408 which drive the dies 1402 backwards and forwards (the
direction of transfer and the direction opposite to the direction
of transfer) as well as in the up and down direction. In other
words, the two-dimensional crank devices 1408 function like a
combination of the crank devices 1403 and the reciprocating crank
devices 1404 in the twenty-fifth embodiment. The two-dimensional
crank devices 1408 move up, down, and backwards and forwards as
they are connected eccentrically to the rotating shafts 1409.
Although the operations are the same as those of the crank devices
1403 and the reciprocating crank devices 1404, the amplitude of the
movement in the up and down direction is the same as the amplitude
of the movement in the backward and forward direction. Except for
the crank devices 1408 the components are the same as those of the
twenty-fifth embodiment.
[0568] (Twenty-seventh Embodiment)
[0569] The twenty-seventh embodiment is explained below. FIG. 87 is
a view showing the configuration of the crank type stentering press
machine. Stentering dies 1412 are provided at both lateral ends
with a material 1 to be pressed between them, and the dies 1412
press the material 1 to be pressed in the lateral direction by
means of the lateral crank devices 1413. The lateral dies 1412 and
the lateral crank devices 1413 are moved backwards and forwards in
the direction of flow of the material to be pressed, by means of
the reciprocating lateral crank devices 1414. The lateral crank
devices 1413 and the reciprocating lateral crank devices 1414
operate in synchronism together. Pinch rolls 1415 are arranged
upstream and downstream of the stentering dies 1412, and control
the transfer speed of the material 1 to be pressed, and are
controlled by a control device not illustrated. Transfer tables
1416 are provided near the pinch rolls 1415 and transfer the
material 1 to be pressed. Although not illustrated, a looper 1417
is arranged downstream of the downstream pinch rolls 1415 of the
stentering dies 1412 and the transfer table 1416, in which the
material 1 to be pressed is looped and a surplus length thereof is
retained, to match the transfer speed of the material 1 conveyed to
a subsequent machine. The reciprocating devices specified in Claim
58 correspond to the reciprocating lateral crank devices 1414, and
the transfer devices are represented by the pinch rolls 1415.
Operations of the twenty-seventh embodiment are substantially the
same as those of the twenty-fifth embodiment.
[0570] In the above descriptions of the twenty-fifth and
twenty-seventh embodiments, the reciprocating devices were
described as crank devices, but hydraulic cylinders, ball screws,
etc. may also be used to give the reciprocating motions.
[0571] As shown in the descriptions above, the present invention
provides the following advantages as the dies are driven by the
crank devices to press the material, and the material is
transferred in synchronism with the reciprocating speed during
pressing, using transfer devices.
[0572] (1) Because the speed of the material to be pressed does not
change so much during transfer, no large-capacity transfer devices
such as pinch rolls and transfer tables are required.
[0573] (2) No high-capacity swinging devices are needed because
there are no heavy sliders such as those used in a flying
system.
[0574] (3) Vibration is moderate because of (2) above.
[0575] (4) The apparatus according to the present invention can be
easily operated together with a subsequent machine by using a
looper etc.
[0576] (Twenty-eighth Embodiment)
[0577] FIG. 88 is a view showing the plate reduction press
apparatus of the twenty-eighth embodiment. FIG. 89 shows the
operation of the twenty-eighth embodiment. Dies 1052 are arranged
above and below a material 1 to be pressed, and the dies 1502 are
connected to eccentric portions of the crank shafts 1504 of the
crank devices 1503. The crank devices 1503 are provided with
eccentric portions rotated by the crank shafts 1504, and move the
dies 1502 up and down, while moving them backwards and forwards in
the direction of flow of the material to be pressed. Item numbers
refer to components, such as 1502a for the upper die, 1502b for the
lower die, 1503a for the upper crank devices, and 1503b for the
lower crank devices. Pinch rolls 1505 are installed upstream of the
dies 1502 and control the transfer speed of the material 1 to be
pressed, and are controlled by a controller 1510. Pinch rolls may
also be installed downstream of the dies 1502. As shown in FIG. 89,
transfer tables 1506 are arranged in the vicinity of and on the
upstream side of the pinch rolls 1505, and on the downstream side
of the dies 1502, and convey the material 1 to be pressed. A looper
1507 is arranged downstream of the downstream transfer table 1506,
and retains the material 1 to be pressed in the shape of a loop, to
match the speed of processing the material 1 to be pressed in a
subsequent system.
[0578] In FIG. 88, the crank device 1503 is provided with a load
cell 1511 which measures the pressing force applied to the die
1502a. A crank shaft rotation sensor 1512 is also provided and
measures the rotation of the crank shaft. Measurement data from the
load cell 1511 and the crank shaft rotation sensor 1512 are
transmitted to the controller 1510.
[0579] The pinch rolls 1505 are equipped with a pinch roll rotation
sensor 1513 that measures the rotation of the pinch rolls 1505, and
outputs the measurement to the controller 1510. The pinch rolls
1505 are provided with a cylinder 1514 for pressing the material 1
to be pressed, a changeover valve 1515 for switching the direction
of supplying fluid to the cylinder 1514, a pump 1516 for supplying
pressurized fluid, a regulating valve 1517 to reduce the output
pressure of the pump 1516, and a tank 1518 for storing the fluid.
The regulating valve 1517 is controlled by the controller 1510, to
change the pressure of the pinch rolls 1505 applied to the material
1 to be pressed, to P1 or P2.
[0580] The operations are described next. FIG. 89 shows the
operations of the crank devices 1503 and the dies 1502 during a
period of one revolution of the crank shafts 1504 of the crank
devices 1503 (this period is defined as one cycle). FIG. 90 is a
diagram showing the relationship between the angle of rotation and
pressing for the crank shafts 1504 of the crank devices 1503. The
operations of the upper crank device 1503a are described. The
operations of the lower crank device 1503b are the same as those of
the upper crank device 1503a as far as backward and forward
movements are concerned (movement in the downstream direction is
considered the forward movement), although the up and down
movements are in the opposite direction. Points a, c, b and d
represent top dead center, bottom dead center, most upstream point
and most downstream point, respectively, of the movement of the
dies 1502. The starting point of a cycle is point b, and in the
range b-c-d, movement is in the forward direction, and in the range
d-a-b, movement is in the backward direction. From the time R, the
material 1 begins to be pressed and pressing is completed at S
after passing c. FIG. 89 (A) shows the status at point b, and (B)
at point c and (C) at point d. The distance between points b and d
is the distance that the dies move in one cycle. The distance L
that the material 1 to be pressed moves in a cycle is adjusted so
as not to exceed the effective pressing length L0 of the dies 1502
in the transfer direction, to assure complete pressing.
[0581] FIG. 91 shows the output of the load cell 1511, the crank
shaft rotation sensor 1512 and pinch roll rotation sensor 1513, and
the pressing force on the pinch rolls 1505, adjusted by controlling
the regulating valve 1517 with the controller 1510 using the
measurement data. (a) is a graph of the movements or speeds of the
dies 1502 as a function of the crank angle, obtained by developing
FIG. 90 along the crank angle. The pressing range R to S is shown
by the hatched areas. (b) shows the outputs of the load cell,
produced during the pressing range R to S with a peak intermediate
between R and S. (c) shows the feeding speeds of the pinch rolls
1505; the speed in the pressing range R to S is the speed of the
dies 1502 between R and S, plus or minus the elongation speed of
the material 1 due to pressing, and when the pinch rolls 1505 are
located on the upstream side of the dies 1502 as shown in FIG. 88,
the elongation speed in the upstream direction is subtracted from
the transfer speed to compensate for the speed of the material
extending in the upstream direction, and when the rolls are located
the downstream side as shown in FIG. 90, the elongation speed in
the downstream direction is added to the transfer speed to correct
for the speed of the material extending in the downstream
direction.
[0582] The status shown in (d) is that the controller 1510 has
detected the point R where pressing begins by means of the crank
shaft rotation sensor 1512, or has detected the point R when the
pressing load increases by means of the load cell 1511, and the
controller has reduced the pressing force of the pinch rolls 1505
from P1 to P2 which is lower than P1, and then at the point S where
pressing ends, the force has been returned to the original value
P1. By decreasing the pressing force of the pinch rolls 1505 as
described above, the material 1 to be pressed, the press machine
and pinch rolls 1505 can be protected from the occurrence of flaws
or damage even if the combination speed of the speed of the dies
1502 subtracted by the elongation speed of the material deviates
from the speed of the pinch rolls 1505. In the above, either the
load cell 1511 or the crank shaft rotation sensor 1512 has to be
provided.
[0583] (e) shows a case in which the controller 1510 detects an
angle at a time earlier than the point R where pressing begins by a
time t by means of the crank shaft rotation sensor 1512, and at
that time, the pressing force of the pinch rolls 1505 has been
reduced from P1 to P2 lower than P1, and at the point S where
pressing ends, the pressing force has been returned to the original
value P1. Thus, the pinch rolls 1505 reduce the gripping force on
the material 1 to be pressed before the dies 1502 catch the
material 1, so that the material 1 to be pressed can be firmly
caught by the dies 1502 without slipping. As in the case of (d),
the material 1 to be pressed, the press machine and the pinch rolls
1505 can be protected from the occurrence of flaws or damage even
if the combination speed of the speed of the dies 1502 subtracted
by the elongation speed of the material differs from the speed of
the pinch rolls 1505.
[0584] (Twenty-ninth Embodiment)
[0585] FIG. 92 shows the twenty-ninth embodiment. With the present
embodiment, the pinch rolls 1505 of the twenty-eighth embodiment
shown in FIG. 88 are changed to the downstream side of the dies
1502, and all other components are the same as those of the
twenty-eighth embodiment. According to such a downstream
arrangement, the transfer speed of the pinch rolls 1505 while the
dies 1502 are pressing, becomes the combination speed of the speed
of the dies plus the elongation speed of the material 1 to be
pressed.
[0586] (Thirtieth Embodiment)
[0587] FIG. 93 illustrates the thirtieth embodiment. The present
embodiment combines the twenty-eighth embodiment shown in FIG. 88
and the twenty-ninth embodiment in FIG. 93.
[0588] As can easily be understood from the explanation above,
according to the present invention, the material is transferred
while being pressed by the dies, and the pressing force of the
pinch rolls is reduced when the dies are pressing, so the following
advantages are provided.
[0589] (1) Because the transfer speed of the material to be pressed
does not change significantly, the transfer devices such as pinch
rolls and transfer tables do not need to have a large capacity.
[0590] (2) Because no heavy sliders are provided, unlike a flying
system, no high-capacity swinging devices are needed.
[0591] (3) Even a long (heavy) slab can be securely speeded up and
slowed down to feed it precisely at the required rate.
[0592] (4) The material to be pressed is protected from being
flawed due to slipping without applying an excessive load on the
equipment, even when there is a difference between the speeds of
feeding the material by the dies and the pinch rolls, during
pressing.
[0593] (5) Slipping between the material to be pressed and the dies
is minimized.
[0594] (Thirty-first Embodiment)
[0595] FIG. 94 shows the configuration of the plate reduction press
apparatus of the present embodiment. Dies 1602a, 1602b are provided
above and below a material (slab) 1 to be pressed, and each of the
dies 1602a, 1602b is connected to an eccentric portion of crank
shafts 1604 provided on each of the upper and lower crank devices
1603a, 1603b. The dies 1602a, 1602b connected to the eccentric
portions are driven up and down to press the material 1 to be
pressed, while the material is transferred in the direction of
flow.
[0596] On the upstream and downstream sides of the material 1 to be
pressed with respect to the dies 1602a, 1602b, inlet transfer
devices 1605 and outlet transfer devices 1606 are provided,
respectively; each of transfer devices 1605, 1606 is composed of,
from the closest point to the farthest point from the dies 1602a,
1602b, feed rolls 1607, pinch rolls 1608 and a transfer table 1609.
The feed rolls 1607 are comprised of rolls that convey the material
1 to be pressed and hydraulic cylinders that raise and lower the
rolls, thereby the transfer height of the material 1 to be pressed
can be adjusted. Although feed rolls 1607 are installed on the
upstream and downstream sides of the dies 1602a, 1602b, a plurality
of feed rolls may also be provided. Pinch rolls 1608 are composed
of rolls arranged above and below the material 1 to be pressed, and
hydraulic cylinders that press each roll, and the pinch rolls pinch
and press the material 1 to be pressed; the upstream pinch rolls
1608 push the material into the dies 1602a, 1602b, and the
downstream pinch rolls 1608 pull it out of the dies 1602a,
1602b.
[0597] The transfer table 1609 is composed of a frame 1609a
extending in the direction of flow of the material 1 to be pressed,
a plurality of transfer rollers 1609b arranged above the frame
1609a, up/down guides 1609c that guide the frame 1609a when moving
up and down, and up/down cylinders 1609d for moving the frame 1609a
up and down. The up and down movement can also be replaced with
either a parallel lifting or a tilting method. A controller 1610
controls the crank devices 1603a, 1603b, the feed rolls 1607, pinch
rolls 1608 and transfer tables 1609.
[0598] The operation is described next. The controller 1610 is
previously provided with information about the thickness of the
material to be input and pressed, the amount of reduction during
pressing, etc., therefore based on these data, the controller sets
the transfer height of feed rolls 1607, pinch rolls 1608 and
transfer table 1609 of the inlet transfer device 1605 to the height
of the pressing center line (particular to the press machine)
subtracted by 1/2 of the thickness of the material 1 to be pressed,
and the controller also sets the transfer height of the feed rolls
1607, pinch rolls 1608 and transfer table 1609 of the outlet
transfer device 1606, to the height of the pressing center line
subtracted by 1/2 of the thickness of the material 1 after being
pressed. In addition, the upper rolls of the upstream and
downstream pinch rolls 1608 are raised to the highest limit, and
the upper and lower dies 1602a, 1602b are also fully opened. Under
these circumstances, the material 1 to be pressed is transferred
between the dies 1602a, 1602b, and while the material is being
pressed by the upper and lower dies 1602a, 1602b, the material is
fed out in the forward direction (the direction of flow of the
material 1 to be pressed).
[0599] FIG. 95 shows the up and down movements of the press machine
and the backward and forward movements during one cycle. (A) is the
starting state of one cycle, and the dies 1602a, 1602b are open and
located in the most upstream position. (B) shows the status in
which the dies are moving in the downstream direction while
pressing. (C) is the state in which pressing is completed and the
dies have moved to the most downstream position. During these
operations the transfer speeds of the feed rolls 1607, pinch rolls
1608 and transfer tables 1609 of the inlet transfer devices 1605
and outlet transfer devices 1606 are adjusted to be identical to
the forward moving speed of the dies 1602a, 1602b during
pressing.
[0600] (Thirty-second Embodiment)
[0601] FIG. 96 shows the thirty-second embodiment. The equipment
configuration is the same as that of the thirty-first embodiment
shown in FIG. 94, but the operation is different. When a material 1
to be pressed is bypassed through the press machine or the material
is conveyed backwards because of a problem that has occurred in the
material 1 being pressed, the transfer levels of the inlet transfer
devices 1605 and the outlet transfer devices 1606 are made the same
as each other, and the upper and lower dies 1602a, 1602b are fully
opened, and the material is conveyed in the condition that the
upper surface of the lower die 1602b is lower than the transfer
level. At that time, the upper rolls of the inlet and outlet pinch
rolls 1608 are raised to the highest point, so that the material 1
to be pressed is not constrained.
[0602] Obviously from the description above, according to the
present invention, the transfer level of the inlet transfer device
is adjusted to the height of the press center line subtracted by
one half of the thickness of the material to be input and pressed,
and the transfer level of the outlet transfer device is set to the
height of the press center line subtracted by a half of the
thickness of the material after being pressed, thereby the material
after being pressed will not warp or otherwise be deflected, and
the transfer devices can be protected from being damaged. When the
material to be or being pressed is bypassed through the press
machine, the inlet and outlet transfer devices are set at the same
transfer level, and the dies are fully opened, so that the material
can be conveyed smoothly through the press machine.
[0603] Although the present invention has been explained by
referring to a number of preferred embodiments, it should be
understood that the scope of claims included in the specification
of the present invention should not be limited only to the
embodiments described above. To the contrary, the scope of rights
according to the present invention shall include all modifications,
corrections or the like as long as they are included in the scope
of the claims attached. What is claimed is
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