U.S. patent application number 14/375253 was filed with the patent office on 2015-01-15 for automatic transmission control valve body structure.
This patent application is currently assigned to JATCO LTD.. The applicant listed for this patent is JATCO LTD. Invention is credited to Hideki Ishii, Kenji Matsumoto, Hideki Nakazawa, Akio Nonomura, Masaru Shimada, Masato Urushibata.
Application Number | 20150014557 14/375253 |
Document ID | / |
Family ID | 48905099 |
Filed Date | 2015-01-15 |
United States Patent
Application |
20150014557 |
Kind Code |
A1 |
Shimada; Masaru ; et
al. |
January 15, 2015 |
AUTOMATIC TRANSMISSION CONTROL VALVE BODY STRUCTURE
Abstract
Structure of control valve body of automatic transmission has
valve body enclosures having channels on opposing surfaces thereof;
a separate plate sandwiched between the valve body enclosures for
defining oil passages on both sides of the separate plate; and an
orifice provided at the separate plate. The oil passages on both
sides of the separate plate, which are upstream and downstream side
oil passages located on upstream and downstream sides of the
separate plate, communicate with each other through the orifice.
Depth h, in a part facing to the orifice, of the channel
corresponding to the downstream side oil passage is set to be
shallower than depth of the channel corresponding to the upstream
side oil passage, and the depth h of the channel in the part facing
to the orifice and a diameter d of the orifice are set so as to
satisfy relationship of h.ltoreq.3d.
Inventors: |
Shimada; Masaru; (Sunto-gun,
JP) ; Ishii; Hideki; (Numazu-shi, JP) ;
Urushibata; Masato; (Fuji-shi, JP) ; Nonomura;
Akio; (Isehara-shi, JP) ; Matsumoto; Kenji;
(Shizuoka-shi, JP) ; Nakazawa; Hideki; (Fuji-shi,
JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
JATCO LTD |
Fuji-shi, Shizuoka |
|
JP |
|
|
Assignee: |
JATCO LTD.
Fuji-shi, Shizuoka
JP
|
Family ID: |
48905099 |
Appl. No.: |
14/375253 |
Filed: |
January 24, 2013 |
PCT Filed: |
January 24, 2013 |
PCT NO: |
PCT/JP2013/051442 |
371 Date: |
July 29, 2014 |
Current U.S.
Class: |
251/118 |
Current CPC
Class: |
F15B 21/008 20130101;
F16H 2061/0279 20130101; B60Y 2306/09 20130101; F16H 61/0009
20130101; F16K 47/08 20130101; F15B 13/081 20130101; F16K 31/06
20130101; F15B 13/0871 20130101; F16H 61/0276 20130101; F16H
61/0265 20130101 |
Class at
Publication: |
251/118 |
International
Class: |
F16K 47/08 20060101
F16K047/08; F16K 31/06 20060101 F16K031/06; F16H 61/02 20060101
F16H061/02 |
Foreign Application Data
Date |
Code |
Application Number |
Jan 31, 2012 |
JP |
2012-017950 |
Claims
1. A structure of a control valve body of an automatic transmission
comprising: valve body enclosures coupled together to form the
control valve body, the valve body enclosures having channels on
opposing surfaces thereof; a separate plate sandwiched between the
valve body enclosures, the separate plate defining oil passages on
both sides of the separate plate by separating the channels between
the valve body enclosures; and an orifice provided at the separate
plate, the oil passages on both sides of the separate plate, which
are an upstream side oil passage and a downstream side oil passage
respectively located on an upstream side and a downstream side of
the separate plate, communicating with each other through the
orifice, and a depth h, at least in a part facing to the orifice,
of the channel corresponding to the downstream side oil passage
being set to be shallower than a depth of the channel corresponding
to the upstream side oil passage, and the death h of the channel in
the part facing to the orifice and a diameter d of the orifice
being set so as to satisfy a relationship of h.ltoreq.3d.
2. The structure of the control valve body of the automatic
transmission as claimed in claim 1, wherein: the valve body
enclosure in which the channel having the depth h in the part
facing to the orifice is formed is provided with a protruding
section that faces to the separate plate where the orifice is
formed, and the protruding section has an opposing surface that
faces to the orifice.
3. The structure of the control valve body of the automatic
transmission as claimed in claim 2, wherein: the opposing surface
formed at the protruding section is a surface that is parallel to
the separate plate where the orifice is formed.
4. The structure of the control valve body of the automatic
transmission as claimed in claim 3, wherein: an area of the
opposing surface is greater than an area of the orifice having the
diameter d.
5. The structure of the control valve body of the automatic
transmission as claimed in claim 1, wherein: the valve body
enclosure in which the channel having the depth h in the part
facing to the orifice is formed is provided, in the part facing to
the orifice, with a circular truncated cone-shaped protruding
section.
6. The structure of the control valve body of the automatic
transmission as claimed in claim 5, wherein: a top portion flat
surface section of the protruding section is parallel to the
separate plate where the orifice is firmed, and an area of the top
portion flat surface section of the protruding section is smaller
than an area of the orifice having the diameter d.
7. The structure of the control valve body of the automatic
transmission as claimed in claim 2, wherein: the opposing surface
formed at the protruding section is a surface that is not parallel
to the separate plate where the orifice is formed.
8. The structure of the control valve body of the automatic
transmission as claimed in claim 7, wherein: an area of the
opposing surface is greater than an area of the orifice having the
diameter d.
9. The structure of the control valve body of the automatic
transmission as claimed in claim 8, wherein: the opposing surface
is formed as an inclined surface that descends from an upstream
side toward a downstream side of the downstream side oil passage
while forming the channel having the depth h.
10. The structure of the control valve body of the automatic
transmission as claimed in claim 1, wherein: the orifice is an
orifice whose plane shape is noncircular and has a substantially
inner tooth shape.
Description
TECHNICAL FIELD
[0001] The present invention relates to a structure of a control
valve body of an automatic transmission, and more particularly to a
structure of anti-vibration measures of a separate plate of the
control valve body.
BACKGROUND ART
[0002] FIG. 6 is a drawing for explaining an outline of an oil
passage in a control valve body of an automatic transmission for a
vehicle in a related art. FIG. 6(a) is a sectional view
schematically showing the oil passage in the control valve body.
FIG. 6(b) is a sectional view taken along an A-A line of FIG. 6(a).
FIG. 6(c) is an enlarged view of an area B in FIG. 6(a), for
explaining vibration of a separate plate. FIG. 6(d) is an enlarged
explanatory view of an orifice adjacent area of the separate
plate.
[0003] The control valve body of the vehicle automatic transmission
has a basic structure in which a separate plate 120 is sandwiched
between valve body enclosures 100 and 110 which are coupled
together. The valve body enclosures 100 and 110 have, on opposing
surfaces thereof, channels 100a and 110a. Openings of these
channels 100a and 110a are closed with the separate plate 120
sandwiched between the valve body enclosures 100 and 110, thereby
separating the channels 100a and 110a and defining oil passages 101
and 102 in which working fluid flows.
[0004] The control valve body is provided with a solenoid, a spool
(both not shown), etc. besides the oil passage inside the control
valve body. The vehicle automatic transmission is configured so
that the working fluid is supplied to a certain frictional
engagement element by switching or changing the oil passage that
provides the working fluid by driving the solenoid and the
spool.
[0005] In the control valve body, there is a spot by which one side
oil passage 101 and the other side oil passage 102 sandwiching the
separate plate 120 communicate with each other through an orifice
121 that is provided at the separate plate 120. For instance, the
working fluid in the one side oil passage 101 is pushed out to the
other side oil passage 102 through the orifice 121 of this
spot.
[0006] Here, the working fluid pushed out to the oil passage 102
through the orifice 121 moves along a center axis X of the orifice
121, and forms a flow F1 (see FIG. 6 (c)) of the working fluid
which flows on an extended line of the orifice 121 along the center
axis X. Since there is a difference in a velocity of the flow
between this working fluid flow F1 and a flow F2 of the working
fluid positioned outside the extended line of the orifice 121, a
vortex ring S caused by this flow velocity difference appears in
the working fluid.
[0007] As shown in FIG. 6(b), since the orifice 121 is a small
circular hole viewed from above, the vortex ring S formed in the
oil passage 102 is formed cylindrically so as to surround the
center axis X of the orifice 121. The vortex ring S formed in the
oil passage 102 grows or develops while moving along the center
axis X in a direction moving away from the orifice 121. Then,
finally, a plurality of the vortex rings S continuously appear with
the center axis X being a coaxial axis in a penetration direction
(in an axial direction of the center axis X) of the orifice
121.
[0008] Here, the vortex ring S is a vortex that is different from a
so-called Karman vortex. The vortex ring S is a vortex that is
generated, caused by the orifice 121 of the separate plate 120, in
the downstream side oil passage 102, and is a vortex of a jet
passing through the orifice 121 of the control valve body.
[0009] With respect to the vortex ring S continuously appearing in
the penetration direction of the orifice 121, a pressure of a
segment Sd between contiguous vortex rings S and S becomes higher
than that of a core Sc of the vortex ring S. Because of this, when
the working fluid in the oil passage 101 is pushed out to the oil
passage 102 through the orifice 121, fluctuation in up-and-down
directions in the pressure adjacent to the orifice 121 in the oil
passage 102 repeatedly occurs due to the vortex ring S continuously
appearing.
[0010] Here, a section 120a of the separate plate 120, which is
adjacent to the orifice 121, is not supported by being sandwiched
between the valve body enclosures 100 and 110, thus rigidity of the
section 120a in the penetration direction of the orifice 121 (in a
direction orthogonal to the separate plate 120) is low. Therefore,
when the pressure adjacent to the orifice 121 in the oil passage
102 fluctuates in the up-and-down directions, the section 120a of
the separate plate 120, which is adjacent to the orifice 121,
vibrates in the penetration direction of the orifice 121 (see an
arrow a in the drawing) due to this pressure fluctuation, then a
noise resulting from this vibration might be generated.
[0011] As suppressing measures of the noise resulting from the
vibration of the separate plate 120, as shown in FIG. 6(d), it is
said that forming a cone surface 122 at a downstream side opening
edge of the orifice 121 formed at the separate plate 120, for
instance, by coining process is effective. This technique has been
disclosed, for instance, in a Patent Document 1.
[0012] According to this structure, as shown in FIG. 6(d), by
slowing down a flow F1' of the working fluid by the cone surface
122 and reducing a flow velocity difference between the working
fluid flow F1' and the working fluid flow F2, the vibration at the
section 120a of the separate plate 120, which is adjacent to the
orifice 121, is suppressed, then the noise resulting from this
vibration is suppressed.
[0013] However, only a flow velocity suppressing effect by the cone
surface 122 is not adequate for the noise suppression. The
vibration at the section 120a of the separate plate 120, which is
adjacent to the orifice 121, and the generation of the noise
resulting from this vibration are not adequately suppressed, and
thus a further measurement is required.
CITATION LIST
Patent Document
[0014] Patent Document 1: Japanese Patent Provisional Publication
No. 63-101355
SUMMARY OF THE INVENTION
[0015] The present invention was made in view of the above problem.
An object of the present invention is to provide a structure that
can adequately suppress the vibration at the section of the
separate plate 120, which is adjacent to the orifice formed at the
separate plate 120, and suppress the generation of the noise
resulting from this vibration.
[0016] The present invention is, as described above, a structure of
a control valve body of an automatic transmission, in which a
separate plate is sandwiched between valve body enclosures. Then,
channels are formed on opposing surfaces, which face to the
separate plate, of the valve body enclosures located on both sides
of the separate plate, and oil passages are defined by separating
the channels by the separate plate, and one side oil passage and
the other side oil passage located on both sides of the separate
plate communicate with each other through an orifice that is
provided at the separate plate. Further, in the valve body
enclosure in which the channel that corresponds to a downstream
side oil passage of the oil passages is formed, a depth, at least
in a part facing to the orifice, of the channel is set to be
shallower than a depth of the channel that corresponds to an
upstream side oil passage of the oil passages, and the depth h of
the channel in the part facing to the orifice and a diameter d of
the orifice are set so as to satisfy a relationship of
h.ltoreq.3d.
[0017] According to the present invention, in the valve body
enclosure in which the channel corresponding to the downstream side
oil passage is formed, the depth h of the channel facing to the
orifice is set to be shallower than a depth of the other channel,
and also the depth his set, with respect to the diameter d of the
orifice, so as to satisfy the relationship of h.ltoreq.3d. Thus,
the fluctuation in the up-and-down directions of the pressure
adjacent to the orifice in the downstream side oil passage, which
is caused by the vortex ring, can be prevented. It is therefore
possible to prevent the section of the separate plate, which is
adjacent to the orifice, from vibrating and prevent the noise
resulting from this vibration from being generated.
BRIEF DESCRIPTION OF DRAWINGS
[0018] FIG. 1 is a sectional view showing a first embodiment of a
control valve body structure according to the present
invention.
[0019] FIG. 2 is an enlarged view of a main part of FIG. 1
[0020] FIG. 3 is a sectional view showing a second embodiment of
the control valve body structure according to the present
invention.
[0021] FIG. 4 is a sectional view showing a third embodiment of the
control valve body structure according to the present
invention.
[0022] FIG. 5 is a sectional view showing some modifications of the
control valve body structure as a fourth embodiment of the present
invention.
[0023] FIG. 6 is a sectional view for explaining an oil passage in
the control valve body of an automatic transmission for a vehicle
in a related art.
EMBODIMENTS FOR CARRYING OUT THE INVENTION
[0024] FIG. 1 shows a first embodiment of a control valve body
structure according to the present invention. FIG. 1(a) is a
sectional view of the control valve body structure. FIG. 1(b) is a
sectional view taken along an A-A line of FIG. 1(a). FIG. 1(c) is a
sectional view taken along a C-C line of FIG. 1(a). FIG. 1(d) is a
sectional view taken along a B-B line of FIG. 1(a). Further, FIG.
2(a) is an enlarged view of an area D of FIG. 1(a). FIG. 2(b) is a
drawing for explaining formation of a vortex ring.
[0025] A control valve body 1 of an automatic transmission for a
vehicle has a basic structure in which a separate plate 30 is
sandwiched between valve body enclosures 10 and 20 which are
coupled together. The valve body enclosures 10 and 20 have, on
opposing surfaces thereof, channels 10a and 20a. Openings of these
channels 10a and 20a are closed with the separate plate 30
sandwiched between the valve body enclosures 10 and 20, thereby
separating the channels 10a and 20a and defining oil passages 11
and 21 in which working fluid flows.
[0026] In the control valve body, there is a spot by which one side
oil passage 11 and the other side oil passage 21 sandwiching the
separate plate 30 communicate with each other through an orifice 31
that is provided at the separate plate 30. For instance, the
working fluid in the one side oil passage 11 moves to the other
side oil passage 21 through the orifice 31 of this spot.
[0027] As shown in FIG. 1(d), the orifice 31 is formed into a small
circular hole viewed from above, and has a diameter d. The orifice
31 is formed by penetrating the separate plate 30 in a thickness
direction (in a coupling direction of the valve body enclosures 10
and 20). The working fluid coming from the oil passage 11 toward
the oil passage 21 through the orifice 31 flows along a center axis
X passing through a center of the orifice 31 in a penetration
direction of the orifice 31 as shown by an arrow F1 in FIG.
2(a).
[0028] In the oil passage 21 located on a downstream side in a flow
direction of the working fluid, a depth of the channel 20a of the
valve body enclosure 20 defining the oil passage 21 is different
between in an area facing to the orifice 31 and its adjacent area
and in the other area. A depth h of the area facing to the orifice
31 and its adjacent area is shallower than a depth H1 of the other
area. With this structure, as shown in FIGS. 1(b) and 1(c), in the
oil passage 21, a passage cross-sectional area D of the area facing
to the orifice 31 and its adjacent area is smaller than a passage
cross-sectional area D1 of the other area.
[0029] In the present embodiment, a protruding section 22 that
protrudes toward an opening side of the channel 20a, namely toward
the orifice 31, is formed in the channel 20a of the valve body
enclosure 20, then the depth of the channel 20a becomes shallower
by this protruding section 22. The protruding section 22 is formed
integrally with the valve body enclosure 20. The protruding section
22 is provided directly below the orifice 31 and in a predetermined
area ranging from a position directly below the orifice 31 to
upstream and downstream sides in a longitudinal direction (i.e. in
right and left directions in FIG. 1(a)) of the channel 20a with a
position of the orifice 31 being a reference. An opposing surface
22a of the protruding section 22, which faces to the separate plate
30, has a flat surface that is parallel to the separate plate 30,
and this opposing surface 22a is orthogonal to the penetration
direction of the orifice 31. That is, the opposing surface 22a is
parallel to the separate plate 30 on which the orifice 31 is
formed, and an area of the opposing surface 22a is wider than an
area of the orifice 31 having the diameter d.
[0030] As shown in FIG. 2, in the present embodiment, the depth h
from the orifice 31 (a lower surface 30b of the separate plate 30)
to the opposing surface 22a is set to be smaller (shallower) than a
distance L that is required for a vortex ring S to be formed in the
penetration direction of the orifice 31 (in an orthogonal direction
to the separate plate 30). Regarding this distance L, simulation
and an experimental result showed that the distance L is dependent
on the diameter d of the orifice 31 and if the distance L exceeds a
distance that is three times that of the diameter d of the orifice
31, the vortex ring S is formed. Thus, in the present embodiment,
as shown in FIG. 1(a), a protrusion height H2 of the protruding
section 22 from a bottom of the channel 20a is set so as to satisfy
a relationship of h.ltoreq.3d (=L).
[0031] In the oil passage 21 having the protruding section 22, the
working fluid flowing into the oil passage 21 through the orifice
31 and forming the flow (the arrow F1 in FIG. 2) toward the
penetration direction of the orifice 31 in the oil passage 21 hits
against or strikes the protruding section 22, and as shown by an
arrow F2 in FIG. 2, the flow of the working fluid is bent or curved
in a different direction from the penetration direction of the
orifice 31.
[0032] As described above, the vortex ring S appears if the working
fluid flows the predetermined distance L(=3d) or more along the
penetration direction of the orifice 31. Thus, by setting the depth
h from the orifice 31 to the opposing surface 22a in the above
manner, the flow of the working fluid is disturbed before the
vortex ring S is generated, the vortex ring can therefore be
prevented from continuously appearing in the penetration direction
of the orifice 31.
[0033] Further, as shown in FIG. 2, due to the fact that the
working fluid passing through the orifice 31 strikes the opposing
surface 22a, a high pressure area H whose pressure is higher than
that of part where the protruding section 22 is not provided is
formed directly below the orifice 31. Since this high pressure area
H is formed directly below the orifice 31 and in its vicinity, a
pressure of an area R which is adjacent to the orifice 31 in the
oil passage 21 becomes high. Consequently, in this condition, the
flow of the working fluid that newly passes through the orifice 31
and forms the flow F1 toward the penetration direction of the
orifice 31 is impeded by the high pressure until the flow of the
working fluid passes through the orifice 31 and reaches the high
pressure area H, and its flow velocity decreases. With this
working, since a flow velocity difference between the working fluid
around the orifice 31 and the working fluid passing through the
orifice 31 becomes small, an influence by the working fluid passing
through the orifice 31 is lessened. Thus, even if a vortex flow
(the vortex ring) is generated, it is generation of a weak or poor
vortex. Hence, even if the vortex ring is formed in the oil passage
21, a size of the vortex formed in the oil passage 21 is small,
which is caused by the fact that the flow velocity difference
becomes small, as compared with a related art case where the high
pressure area H is not formed.
[0034] As a consequence, a difference between a pressure of a core
of the vortex ring (see Sc in FIG. 6) and a pressure around the
vortex ring (see Sd in FIG. 6) becomes small as compared with a
case where the pressure of the adjacent area R is not high. With
this working, even if the vortex ring continuously appears in the
penetration direction of the orifice 31 in the oil passage 21,
since a pressure on the lower surface 30b side of the separate
plate 30 does not periodically widely fluctuate in the up-and-down
directions, it is possible to suppress the vibration of a section
30a of the separate plate 30, which is adjacent to the orifice 31,
and the generation of the noise caused by the vibration of the
separate plate 30 can be suppressed.
[0035] As explained above, in the present embodiment,
anti-vibration measures of the separate plate 30 in the control
valve body 1 of the automatic transmission are premised on the
structure in which the control valve body 1 is formed by
sandwiching the separate plate 30 between the valve body enclosures
10 and 20 which are coupled together. Then, the openings of the
channels 10a and 20a formed on the respective opposing surfaces of
the valve body enclosures 10 and 20 are closed with the separate
plate 30, and the oil passages 11 and 21 are formed on one side and
the other side of the separate plate 30.
[0036] Further, one side oil passage 11 and the other side oil
passage 21 located on opposite sides of the separate plate 30
communicate with each other through the orifice 31 provided at the
separate plate 30. In addition, in the valve body enclosure 20 in
which the channel 20a corresponding to the downstream side oil
passage 21 of one side and the other side oil passages 11 and 21 is
formed, the protruding section 22 protruding toward the opening
side of the channel 20a is provided in the channel 20a, then the
depth h of the area facing to the orifice 31 in the channel 20a is
set to be shallower than the depth H1 of the other area where the
protruding section 22 is not provided.
[0037] With this structure, since the depth of the channel 20a
directly below the orifice 31 becomes shallower, the vortex ring is
prevented from continuously appearing in the penetration direction
of the orifice 31 in the downstream side oil passage 21. This can
inhibit the pressure of the area R adjacent to the orifice 31 of
the separate plate 30 from periodically fluctuating in the
up-and-down directions in the downstream side oil passage 21,
thereby preventing the generation of the noise caused by the fact
that the section 30a of the separate plate 30, which is adjacent to
the orifice 31, vibrates.
[0038] Further, only by setting the depth of the channel 20a of the
valve body enclosure 20 to be shallow, the vibration of the section
30a of the separate plate 30, which is adjacent to the orifice 31,
is suppressed and the noise resulting from the vibration can be
suppressed. Therefore, there is no need for the control valve body
to be machined more than necessary. As a consequence, the vibration
and the generation of the noise resulting from the vibration can be
suppressed without increasing a manufacturing cost.
[0039] In addition, the high pressure area H is formed directly
below the orifice 31, and the flow velocity of the working fluid
forming the flow F1 toward the penetration direction of the orifice
31 decreases, then the flow velocity difference between the working
fluid forming the flow F1 and the working fluid flowing outside the
area positioned directly below the orifice 31 becomes small. Thus,
even if the vortex flow (the vortex ring) is generated in the oil
passage 21, it is the generation of the weak or poor vortex, then
the vortex ring formed in the oil passage 21 becomes small.
[0040] As a result, since the difference between the pressure of
the core of the vortex ring and the pressure around the vortex ring
is small, even if the vortex ring is continuously formed on the
extended line of the orifice 31 in the oil passage 21, the pressure
difference between the core of the vortex ring and a segment
between contiguous vortex rings becomes small, thereby inhibiting
the pressure on the lower surface 30b side of the separate plate 30
from periodically widely fluctuating in the up-and-down directions.
It is therefore possible to suppress the vibration of the section
30a of the separate plate 30, which is adjacent to the orifice 31,
and suppress the generation of the noise resulting from the
vibration of the separate plate 30.
[0041] Furthermore, the relationship between the depth h from the
orifice 31 to the opposing surface 22a (a bottom of the oil
passage) of the protruding section 22 located directly below the
orifice 31 and the diameter d of the orifice 31 is set so as to
satisfy the relationship of h.ltoreq.3d (=L), then the depth h is
set to be smaller than or equal to the distance L that is required
for a first vortex ring to be formed in the penetration direction
of the orifice 31.
[0042] With these structure and setting, the depth of the channel
20a located directly below the orifice 31 becomes shallower than a
depth required for the generation and the growth of the vortex
ring, and flow of the working fluid is disturbed before the first
vortex ring is generated directly below the orifice 31. This thus
prevents the vortex ring from continuously appearing in the
penetration direction of the orifice 31 in the oil passage 21.
[0043] Here, even if the vortex ring S is formed, since the moving
or flowing direction of the working fluid passing through the
orifice 31 is bent or curved by the opposing surface 22a of the
protruding section 22, the vortex ring S does not grow and is not
continuously formed in the penetration direction of the orifice
31.
[0044] Moreover, since the high pressure area H is formed directly
below the orifice 31, the flow velocity of the working fluid
forming the flow F1 toward the penetration direction of the orifice
31 decreases, then the flow velocity difference between the working
fluid forming the flow F1 and the working fluid flowing outside the
area positioned directly below the orifice 31 becomes small. Thus,
even if the vortex flow (the vortex ring) is generated in the oil
passage 21, it is the generation of the weak or poor vortex, then
the vortex ring formed in the oil passage 21 becomes small.
[0045] As a result, since the difference between the pressure of
the core of the vortex ring and the pressure around the vortex ring
is small, even if the vortex ring is continuously formed on the
extended line of the orifice 31 in the oil passage 21, the pressure
difference between the core of the vortex ring and the segment
between contiguous vortex rings becomes small, thereby inhibiting
the pressure on the lower surface 30b side of the separate plate 30
from periodically widely fluctuating in the up-and-down
directions.
[0046] Next, as a second embodiment, the other example of the
protruding section in the downstream side oil passage will be
explained. FIG. 3 is a drawing for explaining the protruding
section according to the second embodiment. FIG. 3(a) is a
sectional view of the control valve body when cut along the
longitudinal direction of the oil passage 21. FIG. 3(b) is a
sectional view taken along an A-A line of FIG. 3(a). FIG. 3(c) is
an enlarged view of an area B of FIG. 3(a).
[0047] A protruding section 25 of the present embodiment has a
circular truncated cone shape. The protruding section 25 is
provided so that a top portion flat surface section 25a having a
small diameter faces toward the orifice 31 side on the center axis
X passing through the center of the orifice 31 and extending in the
penetration direction of the orifice 31.
[0048] The top portion flat surface section 25a has a flat surface
that is parallel to the separate plate 30, and is orthogonal to the
moving or flowing direction (see an arrow F1 in the drawing) of the
working fluid passing through the orifice 31. In the Present
embodiment, a depth h from the orifice 31 (the lower surface 30b of
the separate plate 30) to the top portion flat surface section 25a
is set to be smaller (shallower) than the distance L that is
required for the first vortex ring to be formed in the penetration
direction of the orifice 31. In the same manner as the first
embodiment explained above, a protrusion height H2 of the
protruding section 25 from a bottom of the channel 20a is set so as
to satisfy the relationship of h.ltoreq.3d (=L). Here, as can be
seen from FIG. 3, an area of the top portion flat surface section
25a of the protruding section 25 is smaller than an area of the
orifice 31 having the diameter d.
[0049] An outer peripheral surface 25b of the protruding section 25
is inclined at a predetermined angle .theta. with respect to the
center axis X. The working fluid flowing into the oil passage 21
through the orifice 31 is guided in a direction moving away from
the center axis X by this outer peripheral surface 25b, then the
working fluid flow is converted to a flow of a direction which
radially expands or spreads when viewed from the center axis X.
[0050] In the oil passage 21 having the protruding section. 25, the
flow (see the arrow F1 in FIG. 3(c)) of the working fluid flowing
into the oil passage 21 through the orifice 31 is interfered by the
protruding section 25, and is bent or curved in a different
direction from the penetration direction of the orifice 31 (see an
arrow F2).
[0051] Here, since the depth h from the orifice 31 (the lower
surface 30b of the separate plate 30) to the top portion flat
surface section 25a, which is the narrowest separation distance
between the orifice 31 (the lower surface 30b of the separate plate
30) and the protruding section 25, is set to be smaller (shallower)
than the distance L that is required for the first vortex ring to
be formed in the penetration direction of the orifice 31 (i.e.
h.ltoreq.3d), the flow of the working fluid is disturbed before the
vortex ring is generated. It is therefore possible to prevent the
vortex ring from continuously appearing in the penetration
direction of the orifice 31 and prevent the vortex ring from
growing.
[0052] Further, also in the case of the protruding section 25,
since the high pressure area H is formed directly below the orifice
31, even if the vortex flow (the vortex ring) is generated in the
oil passage 21, it is the generation of the weak or poor vortex,
then the vortex ring formed in the oil passage 21 becomes small.
Therefore, since the difference between the pressure of the core of
the vortex ring and the pressure around the vortex ring is small,
even if the vortex ring is continuously formed on the extended line
of the orifice 31 in the oil passage 21, the pressure difference
between the core of the vortex ring and the segment between
contiguous vortex rings becomes small, thereby inhibiting the
pressure on the lower surface 30b side of the separate plate 30
from periodically widely fluctuating in the up-and-down
directions.
[0053] As explained above, the second embodiment has the structure
in which the circular truncated cone-shaped protruding section 25
is formed in the position directly below the orifice 31 in the
channel 20a with the top portion flat surface section 25a facing
toward the orifice 31 side, and the depth h from the orifice 31
(the lower surface 30b of the separate plate 30) to the top portion
flat surface section 25a is set to be smaller (shallower) than a
depth H1 of the other area where the protruding section 25 is not
provided.
[0054] Also with this structure, since the vortex ring is prevented
from continuously appearing in the penetration direction of the
orifice 31 and the pressure of the area R adjacent to the orifice
31 of the separate plate 30 is inhibited from periodically
fluctuating in the up-and-down directions in the downstream side
oil passage 21, the generation of the noise caused by the fact that
the section 30a of the separate plate 30, which is adjacent to the
orifice 31, vibrates can be prevented.
[0055] Here, although the present embodiment shows, as an example,
the circular truncated cone-shaped protruding section 25, a conical
shape or a cylindrical shape could be possible. Further, polygonal
pyramid shape, polygonal truncated pyramid shape and polygonal
prism shape such as quadrangular pyramid, truncated square pyramid
and quadrangular prism could be possible. Also in this case, the
same effect can be obtained.
[0056] Next, as a third embodiment, the other example of the
protruding section in the downstream side oil passage will be
explained. FIG. 4 is a drawing for explaining the protruding
section according to the third embodiment. FIG. 4(a) is a sectional
view of the control valve body when cut along the longitudinal
direction of the oil passage 21. FIG. 4(b) is a sectional view
taken along an A-A line of FIG. 4(a). FIG. 4(c) is an enlarged view
of an area B of FIG. 4(a).
[0057] A protruding section 26 of this third embodiment is formed
integrally with the valve body enclosure 20. The protruding section
26 is provided directly below the orifice 31 and in a predetermined
area ranging from a position directly below the orifice 31 to
upstream and downstream sides in a longitudinal direction (i.e. in
right and left directions in FIG. 4(a)) of the channel 20a.
[0058] An opposing surface 26a of the protruding section 26, which
faces to the separate plate 30, is not parallel to the separate
plate 30, and has a flat inclined surface that is inclined at a
predetermined angle 61. A separation distance from the lower
surface 30b of the separate plate 30 on the oil passage 21 side to
the opposing surface 26a of the protruding section 26 is greater,
as a position on the opposing surface 26a gets closer to the
downstream side of the oil passage 21. Further, a minimum depth h
from the orifice 31 to the opposing surface 26a in a part directly
below the orifice 31 is set to be smaller (shallower) than the
distance L that is required for the first vortex ring to be formed
in the penetration direction of the orifice 31. In the same manner
as the first embodiment explained above, the angle .theta.1 of the
opposing surface 26a is set so as to satisfy the relationship of
h.ltoreq.3d (=L). Here, as can be seen from FIG. 4, an area of the
opposing surface 26a is greater than the area of the orifice 31
having the diameter d.
[0059] In the oil passage 21 having the protruding section 26, a
flow direction of the working fluid flowing into the oil passage 21
through the orifice 31 and forming the flow (an arrow F1 in FIG. 4)
toward the penetration direction of the orifice 31 in the oil
passage 21 is bent or curved to a downward direction of the oil
passage 21 by the opposing surface 26a of the protruding section 26
(see an arrow F2). Here, in an upstream side U directly below the
orifice 31 in the oil passage 21, since the minimum depth h from
the orifice 31 to the opposing surface 26a is set to be smaller
(shallower) than the distance L that is required for the first
vortex ring to be formed in the penetration direction of the
orifice 31 (i.e. h.ltoreq.3d), the flow of the working fluid is
disturbed before the vortex ring is generated. It is therefore
possible to prevent the vortex ring from continuously appearing in
the penetration direction of the orifice 31 and prevent the vortex
ring from growing.
[0060] Further, as can be seen from FIG. 4(c), in a downstream side
D directly below the orifice 31 in the oil passage 21, a minimum
depth h' from the orifice 31 to the opposing surface 26a is greater
(deeper) than the minimum depth h in the upstream side U, and the
vortex ring is formed more easily than the upstream side U.
However, since the opposing surface 26a is inclined so that the
flow F2 of the working fluid whose moving or flowing direction is
changed at the opposing surface 26a in the upstream side U crosses
the downstream side D, the generation of the vortex ring in the
downstream side D is inhibited by this working fluid flow F2.
[0061] Furthermore, since the working fluid passing through the
orifice 31 hits against or strikes the opposing surface 26a and its
moving direction is changed, in the same manner as the embodiments
explained above, the high pressure area H is momentarily formed
directly below the orifice 31.
[0062] Then, in this condition, the flow of the working fluid that
newly passes through the orifice 31 and forms the flow F1 toward
the penetration direction of the orifice 31 is impeded by the high
pressure until the flow of the working fluid passes through the
orifice 31 and reaches the high pressure area H, and its flow
velocity decreases. With this working, since the flow velocity
difference between the working fluid around the orifice 31 and the
working fluid passing through the orifice 31 becomes small, the
influence by the working fluid passing through the orifice 31 is
lessened. Thus, even if the vortex flow is generated, it is
generation of the weak or poor vortex.
[0063] Consequently, even if the vortex ring is continuously formed
on the extended line of the orifice 31 in the oil passage 21, since
the pressure difference between the core of the vortex ring and the
segment between contiguous vortex rings becomes small as compared
with the case where the high pressure area H is not formed, the
pressure on the lower surface 30b side of the separate plate 30 is
inhibited from periodically widely fluctuating in the up-and-down
directions. It is therefore possible to suppress the vibration of
the section 30a of the separate plate 30, which is adjacent to the
orifice 31, and suppress the generation of the noise resulting from
the vibration of the separate plate 30.
[0064] As explained above, the protruding section 26 having the
opposing surface 26a that is inclined with respect to the separate
plate 30 is formed directly below the orifice 31 and in its
vicinity in the channel 20a, and the depth h from the orifice 31
(the lower surface 30b of the separate plate 30) to the opposing
surface 26a is greater, as the position on the opposing surface 26a
gets closer to the downstream side of the oil passage 21. Further,
the relationship between the minimum depth h from the orifice 31 to
the opposing surface 26a in the part directly below the orifice 31
and the diameter d of the orifice 31 is set so as to satisfy the
relationship of h.ltoreq.3d (=L), then the depth h is set to be
smaller than or equal to the distance L that is required for the
first vortex ring to be formed in the penetration direction of the
orifice 31.
[0065] Also with this structure, since the vortex ring is prevented
from being continuously formed in the penetration direction of the
orifice 31 and the pressure of the area R adjacent to the orifice
31 of the separate plate 30 is inhibited from periodically
fluctuating in the up-and-down directions in the downstream side
oil passage 21, the generation of the noise caused by the fact that
the section 30a of the separate plate 30, which is adjacent to the
orifice 31, vibrates can be prevented.
[0066] Here, in each of the embodiments described above, as the
example, the case where the shape of the orifice 31 is such
circular shape that a distance from the center axis X is the same
is explained. Meanwhile, simulation and an experimental result
about the vortex ring formed in the downstream side oil passage
showed that the shape of the orifice 31 also has an influence on
the formation of the vortex ring, and if a flow of the working
fluid that is faster than that around the orifice 31 is formed a
predetermined distance X or more along the penetration direction (a
center axis X direction) of the orifice 31 directly below the
orifice 31 by the working fluid passing through the orifice 31, the
vortex ring is continuously generated.
[0067] Thus, as modifications of the above-mentioned orifice shape,
shapes of the orifice which can suppress the generation of the
vortex ring will be explained here.
[0068] FIG. 5 is a drawing for explaining the shape of the orifice
and a speed (the velocity) of the working fluid in the downstream
side oil passage. FIG. 5(a) is a drawing for explaining an orifice
35 having a substantially cruciform shape. FIG. 5(c) is a drawing
for explaining an orifice 36 having an almost star shape. FIG. 5(e)
is a drawing for explaining an orifice 37 having the other shape.
FIGS. 5(b), 5(d) and 5(f) are drawings that show the speed (the
velocity) of the flow of the working fluid formed in the downstream
side oil passage by sizes of arrows. As can be appreciated from
FIG. 5, it can be understood that each of the orifices 35, 36 and
37 shown in FIGS. 5(a), 5(c) and 5(e) is comprehensively an orifice
whose plane shape is noncircular and has a substantially inner
tooth shape.
[0069] The orifice 35 shown in FIG. 5(a) has such shape that two
long holes whose both ends have an R-shape are arranged with a
phase of one of the two long holes shifted by 90 degrees on the
center axis X, which is the substantially cruciform shape viewed
from above.
[0070] In a case of the orifice 35 having this shape, a velocity
difference, which results from the passage cross-sectional area,
between the working fluid passing through a middle area D1 where
the two long holes cross and the working fluid passing through a
peripheral area D2 that encloses the middle area D1 arises. A flow
velocity of a flow Fa of the working fluid passing through the
middle area D1 is higher than that of a flow Fb of the working
fluid passing through the peripheral area D2.
[0071] Here, the generation and the growth of the vortex ring
become noticeable when the velocity difference between the working
fluid flowing directly below the orifice 35 and the working fluid
flowing outside the area positioned directly below the orifice 35
is great. In the case of the orifice 35, when looking at the flow
of the working fluid in cross section of the line L1 (in cross
section of the line L1, passing along the center axis X), the flow
velocities Fa and Fb of the working fluid are lower from a middle
of the orifice 35 toward a vicinity of the orifice 35. Then, a
difference from a flow velocity Fc of the working fluid flowing
outside the area positioned directly below the orifice 35 becomes
small (Fa>Fb>Fc). Therefore, the generation and the growth of
the vortex ring in the oil passage 21 located on the downstream
side of the orifice 35 can be suppressed as compared with the
orifice 31 of the above embodiments.
[0072] Further, in a cross section of a line L2 (in a cross section
of the line L2, passing along the center axis X), since the
peripheral area D2 is not present, the flow velocity difference
between the flow Fa of the working fluid flowing directly below the
orifice 35 and the flow Fc of the working fluid flowing outside the
area positioned directly below the orifice 35 is still large.
Meanwhile, regarding the flow velocity difference between the flow
of the working fluid flowing at the part positioned directly below
the orifice 35 and the flow Fc of the working fluid flowing outside
the area positioned directly below the orifice 35, a large flow
velocity difference part (the cross section of the line L1) and a
small flow velocity difference part (the cross section of the line
L2) are alternately positioned on the center axis X of the orifice
35. Then, the flow velocity difference becomes small as compared
with the above embodiments. Thus, the generation and the growth of
the vortex ring can be suppressed as compared with the orifice 31
of the above embodiments.
[0073] In addition, by setting the flow velocity difference so that
the flow velocity difference between the flow of the working fluid
flowing directly below the orifice 35 and the flow of the working
fluid flowing outside the area positioned directly below the
orifice 35 is different according to an angle position on the
center axis X of the orifice 35, an annular vortex ring whose core
is positioned at the center axis X is not easily formed in the
downstream side of the oil passage 21. Here, even if the vortex
ring appears, since the vortex ring is not circular, the shape of
the vortex ring changes due to an inductive speed of the vortex,
and its secondary generation is lost or extinguished. Thus, a
change or fluctuation of a force acting on the separate plate 30 is
lessened. Also with these workings, since the pressure of the area
R adjacent to the orifice 35 of the separate plate 30 can be
inhibited from periodically fluctuating in the up-and-down
directions, the generation of the noise caused by the fact that the
section 30a of the separate plate 30, which is adjacent to the
orifice 35, vibrates can be prevented.
[0074] As explained above, by employing the substantially
cruciform-shaped orifice 35 having such shape that the two long
holes whose both ends have the R-shape are arranged with the phase
of one of the two long holes shifted by 90 degrees on the center
axis X, the generation and the growth of the vortex ring in the
downstream side oil passage 21 can be suppressed. Then, the
pressure of the area R adjacent to the orifice 35 of the separate
plate 30 can be inhibited from periodically fluctuating in the
up-and-down directions, and the generation of the noise caused by
the fact that the section 30a of the separate plate 30, which is
adjacent to the orifice 35, vibrates can be prevented.
[0075] The orifice 36 shown in FIG. 5(c) has the almost star shape
viewed from above. Also in the case of the orifice 36 having this
shape, a velocity difference, which results from the passage
cross-sectional area, between the working fluid passing through a
middle area D1 and the working fluid passing through a peripheral
area D2 that encloses the middle area D1 arises. Then, as shown in
FIG. 5(d), in a part where the peripheral area D2 is provided in an
area positioned directly below the orifice 36, a difference from a
flow velocity Fc of the working fluid flowing outside the area
positioned directly below the orifice 36 becomes small
(Fa>Fb>Fc). Therefore, the generation and the growth of the
vortex ring in the oil passage 21 located on the downstream side of
the orifice 36 can be suppressed as compared with the orifice 31 of
the above embodiments.
[0076] As explained above, also by employing the orifice 36 having
the star shape viewed from a direction orthogonal to the separate
plate 30 and by forming an opening of the orifice 36 by the middle
area D1 located on a center axis X of the orifice 36 and the
peripheral area D2 located around the middle area D1 with the
peripheral area D2 arranged at a predetermined interval in a
circumferential direction of the center axis X, the generation and
the growth of the vortex ring in the downstream side oil passage 21
can be suppressed.
[0077] In the case of the orifice 37 shown in FIG. 5(e), a
plurality of peripheral areas D2 are formed so that the peripheral
areas D2 extend from a circumference of a middle area D1 formed by
an imaginary circle Im1 in a direction moving away from the
imaginary circle Im1. Each peripheral area D2 has a different
passage cross-sectional area, and is arranged at random on a center
axis X of the orifice 37.
[0078] Therefore, different flow speeds (different flow velocities)
(flows Fb, Fb') exist around a middle area (a flow Fa) whose flow
speed (flow velocity) is highest, and an area whose flow velocity
is lower than the flow Fa and is higher than the flow Fc of the
working fluid flowing outside the area positioned directly below
the orifice 37 is formed at random. Also in the case of the orifice
37 having the shape shown in FIG. 5(e), the generation and the
growth of the vortex ring in the oil passage 21 located on the
downstream side of the orifice 37 can be suppressed as compared
with the orifice 31 of the above embodiments.
[0079] Here, the orifice 35, 36 or 37 shown in FIG. 5 could be
combined with the control valve body 1 having the protruding
section 22, 25 or 26 of the above embodiments. Also with this
combination, it is possible to prevent the vortex ring from being
continuously formed in an orthogonal direction of the orifice.
* * * * *