U.S. patent application number 11/301366 was filed with the patent office on 2006-05-04 for device for driving an output mechanism.
Invention is credited to Jan Peter Houben.
Application Number | 20060090580 11/301366 |
Document ID | / |
Family ID | 7668892 |
Filed Date | 2006-05-04 |
United States Patent
Application |
20060090580 |
Kind Code |
A1 |
Houben; Jan Peter |
May 4, 2006 |
Device for driving an output mechanism
Abstract
A device for driving an output mechanism has a rotationally
driveable input shaft, whereby elements are located between the
input shaft and the output mechanism for transmitting a drive
torque of the input shaft to the output mechanism, whereby a
non-positive functional connection can be created between a first
element and the output mechanism, enabling an alternating movement
of the first element to be converted into a movement of the output
mechanism, whereby the elements are configured such that the
alternating rotational movement of the first element is capable of
being converted into a translational movement of the output
mechanism, wherein at least one lever element is turnably mounted
on the first element, via which the lever element the first
elements are functionally interconnected with at least one gripper
element.
Inventors: |
Houben; Jan Peter; (Pappel,
BE) |
Correspondence
Address: |
STRIKER, STRIKER & STENBY
103 East Neck Road
Huntington
NY
11743
US
|
Family ID: |
7668892 |
Appl. No.: |
11/301366 |
Filed: |
December 13, 2005 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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10451355 |
Dec 22, 2003 |
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PCT/DE01/04792 |
Dec 19, 2001 |
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11301366 |
Dec 13, 2005 |
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Current U.S.
Class: |
74/116 |
Current CPC
Class: |
F16H 29/02 20130101;
Y10T 74/1508 20150115; Y10T 74/1598 20150115; F16H 29/08 20130101;
F16H 31/008 20130101 |
Class at
Publication: |
074/116 |
International
Class: |
F16H 29/00 20060101
F16H029/00 |
Foreign Application Data
Date |
Code |
Application Number |
Dec 23, 2000 |
DE |
100 64 899.1 |
Claims
1-17. (canceled)
18. A device for driving an output mechanism, comprising a
rotationally drivable input shaft; means adapted to be located
between said input shaft and the output mechanism for transmitting
a drive torque of said input shaft to the output mechanism, said
means including first means providing a non-positive functional
connection between said first means and the output mechanism to
enable an alternating movement of said first means to be converted
into a movement of the output mechanism, said means being formed so
that the alternating rotational movement of said first means is
convertable into a translational movement of said output mechanism;
at least one lever element turnably mounted on said first means for
interconnecting said first means with at least one gripper
element.
19. A device as defined in claim 18; and further comprising another
gripper element, said two gripper elements being pivotally
interconnected via a further lever mechanism and being pressable
together tightly with the output mechanism depending on the
alternating movement of said first means.
20. A device as defined in claim 18, wherein said gripper element
is arranged so as to extend over the output mechanism with a
gripper arm which has inner sides adapted to be located closest to
the output mechanism and comprising a dome directed in a direction
of the output mechanism, said domes being arranged to have contact
with the output mechanism.
21. A device as defined in claim 18, wherein input shaft comprises
an eccentric element which is functionally interconnected with said
first means so that when said input shaft rotates, said first means
are moved in alternating fashion depending on a movement of said
eccentric element.
22. A device as defined in claim 18, wherein said spring element is
formed so as to apply a force for controlling the non-positive
functional connection.
23. A device as defined in claim 18, wherein said first means is
formed so that a conversion ratio between the alternating
rotational movement of said first means and the translational
movement of the output mechanism is variable.
Description
PRIOR ART
[0001] The invention relates to a device for driving an output
mechanism with a rotating input shaft.
[0002] Devices for driving an output mechanism with a rotating
input shaft are made known in the prior art, said devices being
used in drills, impact drills or the like. Devices of this type
comprise a plurality of gear wheels between the input shaft and the
output mechanism, which said gear wheels are provided for
ratio-conversion purposes and form a non-positive connection
between the input shaft and the output mechanism in order to
transform a high rotational speed of the input shaft serving as
drive into a lower frequency of motion or rotational speed of the
output mechanism while simultaneously increasing the drive force to
be transmitted to the output mechanism.
[0003] The disadvantage of this, however, is the fact that the use
of gear wheels translates into high production costs in the
fabrication of the known devices, and, when used in drills, impact
hammers or rotating impact hammers, their total costs are increased
by said gear wheels.
ADVANTAGES OF THE INVENTION
[0004] With the devices according to the invention for driving an
output mechanism with a rotationally driveable input shaft, in the
case of which means are located between the input shaft and the
output mechanism for transmitting a drive torque of the input shaft
to the output mechanism, and a non-positive functional connection
can be created between a first means and the output mechanism,
enabling an alternating movement of the first means into be
converted into a movement of the output mechanism, the driving of
the output mechanism takes place in simple fashion without gear
wheels, by way of which the production costs are advantageously
reduced considerably, especially when larger conversion ratios are
involved.
[0005] Moreover, the device according to the invention offers the
advantage that a high rotational speed of the input shaft can be
converted into a considerably slower movement or frequency of
motion of the output mechanism, enabling a desired strong driving
force of the output mechanism to be generated.
SUMMARY OF THE DRAWINGS
[0006] Further advantages result from the description of drawings
hereinbelow. A plurality of exemplary embodiments of the invention
are presented in the drawings. The drawings, the description, and
the claims contain numerous features in combination. One skilled in
the art will advantageously consider them individually as well and
combine them into reasonable further combinations.
[0007] FIG. 1 is a cross-sectional view of the first exemplary
embodiment of the device according to the invention;
[0008] FIG. 2 is a further cross-sectional view of the device
according to FIG. 1;
[0009] FIG. 3 is a longitudinal sectional view of the device
according to the invention;
[0010] FIG. 4 shows an oscillating crank of the device according to
claim 3 by itself. The oscillating crank is functionally connected
with the input shaft and the output mechanism;
[0011] FIG. 5 is a partial view of the device according to the
invention, according to FIG. 3 and FIG. 4;
[0012] FIG. 6 is the partial view of the device according to FIG. 5
shown in a side view;
[0013] FIG. 7 is a further exemplary embodiment of the device
according to the invention. A rotational movement of the input
shaft is converted into a translational movement of the output
mechanism; and
[0014] FIG. 8 shows a conversion mechanism of the device according
to FIG. 7.
[0015] FIGS. 1 and 2 show a device 10 for driving an output
mechanism via an annular body 12, comprising a rotationally
driveable input shaft 14 of the device 10 that serves
simultaneously as the output shaft of a not-shown electric motor.
Means for transmitting a drive torque of the input shaft 14 to the
output mechanism or the annular body 12 installed upstream from the
output mechanism are located between the input shaft 14 and the
output mechanism.
[0016] A non-positive functional connection can be created between
a first means 16 configured as oscillating crank and the output
mechanism, by means of which an alternating movement of the
oscillating crank 16 can be converted into a plurality of
successive movements or rotational movements of the output
mechanism in one direction, whereby the multiple movements effect a
continuous operation of the output mechanism. In addition to the
first oscillating crank 16, two oscillating cranks 16A and 16B of
identical design are situated at 120.degree. angles relative to
each other and are arranged coaxially in tandem.
[0017] The mode of action of the oscillating crank 16 described
hereinbelow applies equally for the oscillating cranks 16A and 16B
as well.
[0018] The output mechanism--not shown in FIG. 1 and FIG. 2--is
interconnected with the annular body 12 via a suitable connection
in a region located behind the plane of the drawing such that a
rotational movement of the annular body 12 results in a rotational
movement of the output mechanism.
[0019] The input shaft 14 is equipped with a sleeve 18 configured
with an annular cross-section, which said sleeve is located in a
recess 20 of the oscillating crank 16 and is provided as an
eccentric element for driving the oscillating crank 16 in an
alternating manner. The oscillating crank 16, in turn, is
interconnected via a pivot pin 22 with a not-shown housing of the
device 10. When the input shaft 14 and the sleeve 18--which is
eccentrically situated relative to the input shaft 14 and its axis
of rotation--rotates, the oscillating crank 16 is moved to and fro
and/or is swiveled to and fro in alternating fashion around the
pivot pin 22. One skilled in the art understands as a matter of
course that the sleeve 18 must also be configured as a single
component with the input shaft 14, e.g., as a cam of a
camshaft.
[0020] On its end furthest from the recess 20, the oscillating
crank 16 comprises a recess 23 in which a driver 24 is located,
which said driver is interconnected with a second means 26. The
second means 26 is turnably supported on an axis 28 and equipped
with an arm 30 directed radially outwardly from the axis 28.
Instead of arms, disks arranged in tandem in the axial direction
are also feasible in principle. The oscillating crank 16 and the
second means 26 are turnably interconnected via the driver 24 in
such a way that the alternating movement of the oscillating crank
16 effected by the rotation of the input shaft 14 effects a
rotational movement or a rotation of the arm 30 around the axis
28.
[0021] A transfer element formed by a rolling element 34 is located
in the recess 33 between an inner surface 32 of the annular element
or outer ring 12 that surrounds the second means 26 and is situated
coaxial to the axis 28, and the end of the arm 30 configured with a
recess 33. In the present exemplary embodiment, the rolling element
34 is configured as cylindrical body 34, although one skilled in
the art will understand as a matter of course that the rolling
element can be configured as balls, barrel-shaped bodies or the
like. Furthermore, various types of sliding blocks, etc. would be
feasible as well.
[0022] In the region of the recess 33, the arm 30 comprises a
blind-hole bore 36 in which a spring 38 is located, one end of
which rests against the bottom of the blind-hole bore 36 and the
other end of which rests against the rolling element 34.
[0023] When the driver 24 moves in the counter-clockwise direction,
as shown in the illustration in FIG. 2, the cylindrical body 34
walks around between the inner surface 32 of the annular body 12
and the end of the arm 30 and becomes lodged between the inner
surface 32 of the annular element 12 and the end of the arm 30
closest to the annular element 12. The annular body 12 is set into
rotation in the counter-clockwise direction. The second means 26,
26A, 26B drive the annular body 12 via the cylindrical bodies 34,
34A, 34B and, therefore, the not-shown output mechanism, in
succession and in stepwise fashion. When the driver 24 moves in the
clockwise direction, the cylindrical body 34--loaded by the spring
38--only rolls or walks around on the inner surface 32 of the
annular body 12 without becoming lodged. It is also possible for
the body 34 to glide on the inner surface 32 when the driver 24
moved in the clockwise direction.
[0024] The clearance between the driver 24 and the pivot pin 22 can
be changed and, with the clearance, a conversion ratio that sets
in, namely by placing the pivot pin 22 radially inwardly in an
alternative recess 126. A stepless displacement of a pivot pin and,
therefore, a stepless adjustment of a conversion ratio would be
feasible in principle as well.
[0025] With the different positioning of the pivot pin 22, a scope
of a reduction of the rotational speed coming from the input shaft
14 that is ultimately transmitted to the output mechanism can be
adjusted in simple fashion, thereby enabling an adjustment of the
level of the value of the output torque applied to the output
mechanism.
[0026] In contrast to the manner described herein, according to
which the annular body 12 can be set into rotation only in the
counter-clockwise direction, a further exemplary embodiment that
deviates from the present exemplary embodiment can provide that the
arm of the second means is structurally configured such that the
annular body 12 can be set into rotation in the clockwise direction
and in the counter-clockwise direction. An embodiment of the device
of this nature can be provided for use in a drill having two
different directions of rotation, although it can also be used in
other machines appearing practical to one skilled in the art.
[0027] Moreover, it is also possible, of course, to provide more
than or fewer than the proposed number of arms to drive the output
mechanism, in order to obtain a drive system adapted to the
specific application at hand.
[0028] FIGS. 3 through 6 show a further exemplary embodiment of the
device 10. Components having the identical construction or the same
functionality are labelled with the same reference numerals as in
the description of the exemplary embodiment of the device 10
according to FIG. 1 and FIG. 2.
[0029] As shown in FIG. 3, the first means is composed of two
oscillating cranks 16A and 16B having essentially the same
construction. For this reason, only the oscillating crank 16A and
the further construction of the device 10 in the region of the
oscillating cranks 16A will be discussed in the description
hereinbelow of the mode of action of the device 10. The only
difference lies in the arrangement of the oscillating cranks 16A
and 16B on the input shaft 14, since the input shaft 14 comprises
two eccentric elements 40A, 40B offset by 180.degree. relative to
each other on which the two oscillating cranks 16A and 16B are
guided with two forks 41A, 41B, and that are set into motion
phase-displaced by 180.degree. relative to each other when the
input shaft 14 rotates. The two eccentric elements 40A, 40B are
configured as circular cams integral with the input shaft 14. Their
axes of rotation are arranged offset to the axis of rotation of the
input shaft 14. One rotation of the input shaft 14 effects an
alternating movement of the oscillating crank 16A. The oscillating
crank 16A is interconnected with the output mechanism 46 via two
further hubs 43A, 56A. Said oscillating crank is swiveled to and
fro around said hubs depending on the position of the eccentric
element 40A.
[0030] The alternating swiveling movement of the oscillating crank
16A is transferred to a third means 42A. The third means 42A--which
are situated such that they are axially displaceable relative to
the oscillating crank 16A and/or the first means--are functionally
interconnected with one annular body 48A, 57A, respectively,
situated on the output mechanism 46 via one guide element 44A, 60A,
respectively, each of which said guide elements 44A, 60A being
situated with its end furthest from the annular bodies 48A, 57A,
respectively, in a recess 50A of the third means 42A and, with its
end closest to the annular bodies 48A, 57A, being interconnected in
fixed fashion with one of the annular bodies 48A, 57A, respectively
(FIG. 5).
[0031] A spring 52A encircling the output mechanism 46 is situated
between the annular bodies 48A, 57A, said spring 52A being
interconnected with the annular bodies 48A, 57A in fixed fashion
via its ends closest to the annular bodies 48A, 57A.
[0032] The recess 50A of the third means 42A--which is configured
as a plate in the present exemplary embodiment--is provided in such
a way that the oscillating movement or swivelling movement of the
plate 42A effects a rotational movement limited in terms of time of
one of the annular bodies 48A or 57A around the output mechanism
46, and the rotational movement of one of the annular bodies 48A,
57A is transferred via the spring 52A to the output mechanism 46.
To ensure an unimpeded, frictionless rotational movement of the
annular bodies 48A, 57A, the two annular bodies 48A, 57A are
situated with play on the output mechanism 46 configured as a
shaft.
[0033] The recess 50A of the plate 42A extends in the axial
direction of the output mechanism 46 and has a greater diameter in
its center region than the two outer regions, each of which abuts
the center region. If the plate 42A is located in the position
shown in FIG. 6, the oscillating movement of the plate 42A is
transferred to the annular body 57A and causes the annular body 57A
to twist. As a result of the twisting, the spring 52A configured as
a coil spring and interconnected with the annular body 57A in fixed
fashion is also twisted and wound, which results in a reduction of
the cross-section of the spring 52A and a temporary non-positive
connection between the spring 52A and the output mechanism 46, and,
finally, effects a rotational movement of the output mechanism
46.
[0034] The mode of action of the arrangement of the oscillating
crank 16A described hereinabove applies similarly for the
arrangement of the oscillating crank 16B having
identically-structured elements. When the output mechanism 46 is
driven via the oscillating crank 16B, this results in the
oscillating crank 16A being driven each time the position of the
input shaft 12 is displaced by 180.degree.. The driving of the
output mechanism 46 corresponds to a plurality of individual,
closely successive rotational movements which, due to the two
oscillating cranks 16A, 16B, effect a nearly continuous rotational
driving of the output mechanism 46.
[0035] If the plate 42A is displaced from its position shown in
FIG. 6 in the axial direction of the output mechanism 46 via a
not-shown means in such a way that the guide element 44A is located
in the outer region of the recess 50A--which is free in FIG. 6--and
the guide element 60A is located in the center region of the recess
50A configured with the larger diameter, the annular body 48A of
the oscillating crank 16A is set into rotation via the plate 42A.
The output mechanism 46 is thereby driven in the opposite direction
of the rotational movement effected by the annular body 57A. When a
changeover takes place, the means and/or the plates 42A and 42B are
displaced essentially simultaneously.
[0036] FIGS. 7 and 8 show a further exemplary embodiment of the
device 10, in the case of which an alternating swivelling movement
of a further structural embodiment of the first means 16 that is
triggered by a rotation of the input shaft 14 is converted into a
translational movement of the output mechanism 46 configured as
tool holder of a power handsaw or the like. The first means 16 is
configured in the shape of a "T", namely with a first crossbar
extending substantially at a right angle to the output mechanism
46, and a leg extending substantially parallel with the output
mechanism 46.
[0037] The first means 16 is supported in pivoting fashion at an
attachment point 84 in the vertex of the crossbar and the leg. At
its end, the leg is configured in the shape of a fork and grips
around an eccentric element 70 driven by the input shaft 14. Two
lever elements 54A, 54B are turnably mounted on the ends of the
crossbar of the first means or the oscillating cranks 16 via the
bolts 55A, 55B serving as pivots. The two lever elements 54A, 54B
extend substantially parallel to the output mechanism 46 and create
a functional connection between the oscillating crank 16 and two
gripper elements 58A, 58B via two bearing bolts 118A, 118B.
[0038] The two gripper elements 58A, 58B are interconnected via a
further lever element 62 extending transversely to the output
mechanism 46. Said gripper elements are capable of being tilted
relative to a centerline 64 of the output mechanism 46 depending on
the alternating movement of the oscillating crank 16A.
[0039] The further lever element 62 is connected hingedly with the
gripper elements 58A, 58B via two pins 66A, 66B. During operation,
the two pins 66A, 66B are displaced in translational fashion nearly
parallel to the centerline 64 of the output mechanism 46. In order
to ensure that the pins 66A, 66B move in this fashion, bores for
accommodating the pins 66A, 66B of the further lever element 62 are
configured with a larger diameter than the diameter of the pins
66A, 66B.
[0040] The oscillating crank 16 is capable of being driven with an
alternating movement by the input shaft 14 via the eccentric
element 70, namely in a manner that allows it to pivot around its
attachment point 84 in the clockwise direction and in the
counter-clockwise direction. Each of the two gripper elements 58A,
58B extends across the output mechanism 46 with a hub-shaped
gripper arm 72A, 72B, respectively, to transmit the alternating
movement of the oscillating crank 16. On their inner sides 76A, 76B
closest to the output mechanism 46, the gripper arms 72A, 72B
comprise domes directed in the direction of the output mechanism
46, said domes being in contact with the output mechanism 46.
[0041] The gripper arms 72A, 72B and the output mechanism 46 are
arranged relative to each other in such a way that, when the
oscillating crank 16 makes a swivelling movement in the
counter-clockwise direction, the gripper element 58A locks up with
the output mechanism 46 and effects a stepwise translational
movement of the output mechanism 46 in the direction away from the
input shaft 14, whereby the second gripper element 58B
simultaneously releases the output element 46.
[0042] When the oscillating crank 16 makes a swivelling movement in
the clockwise direction, the gripper element 58B locks up with the
output mechanism 46 and effects a stepwise translational movement
of the output mechanism 46 in the direction away from the input
shaft 14, whereby the first gripper element 58A simultaneously
releases the output mechanism 46.
[0043] One spring element 82A, 82B, respectively, is located
between a fastening 80A of the first gripper element 58A and a
fastening 120A of the first lever element 54A, and between a
fastening 80B of the second gripper element 58B and a fastening
120B of the second lever element 54B, which said spring elements
ensure two stable end positions of the gripper elements 58A, 58B.
One skilled in the art understands as a matter of course that, with
consideration for a specific application, in deviation from the
number of gripper elements 58A, 58B shown in FIG. 7, more or fewer
gripper elements arranged in tandem on the output mechanism 46 can
be provided to drive the output mechanism 46.
[0044] An automatically-operating changeover device for reversing
the direction of movement of the output mechanism 46 is shown in
FIG. 8. A bolt 88 is interconnected with the output mechanism 46,
which said bolt engages in an opening 90 of a triangular plate
element 96 tiltably situated between a snap-in element 92 and a
third lever element 94 extending substantially transversely to the
output mechanism 46. The snap-in element 92 is turnably supported
via a further bolt 98 in a not-shown housing of the device 10, and
it is turnably interconnected via a bolt 100 with the plate element
96. Furthermore, the snap-in element 92 comprises a wave-shaped
recess 102 on its end furthest from the plate element 96, in which
said recess a pin 104 interconnected in fixed fashion with the
further lever element 62 is located.
[0045] A spring 106 that is interconnected in fixed fashion via its
one end with the housing of the device 10 and, via its other end,
with the snap-in element 92 enables the snap-in element 92 to
always bear against the pin 104 with its recess 102.
[0046] When the plate element 96 is moved by the output mechanism
46 in the direction of the snap-in element 92--which is effected by
the alternating movement of the gripper elements 58A, 58B--the bolt
88 rests on a surface 108 after a certain displacement travel of
the output mechanism 46, whereby the surface 108 forms an end of a
slot 110 of the opening 90.
[0047] If the bolt 88 is displaced further in the direction of the
snap-in element 92 after it comes to rest on the surface 108, a
rotational movement of the snap-in element 92 around the bolt 98 in
the clockwise direction is triggered. The spring element 106
thereby causes two stable end positions to be reached.
[0048] From this, a displacement of the lever system according to
FIG. 7 results such that the further lever element 62 displaces
and/or drives the gripper elements 58A and 58B positioned by the
spring elements 82A, 82B in terms of their associated lever arms
54A and 54B, respectively. Namely, the lever element 62 is
displaced with its pin 104 transversely to the output mechanism 46
starting at pin 66B in the direction of pin 66A, which results in
the gripper element 58A tilting in the clockwise direction and the
gripper element 58B tilting in the counter-clockwise direction. The
spring elements 82A, 82B now maintain the frictional connection for
the opposed direction of movement of the output mechanism 46. As a
result, the output mechanism 46 is subsequently driven in
translational fashion from left to right as seen in FIG. 8. If the
bolt 88 comes to rest in the slot 110 on a surface 124 of the plate
element 96 opposite the surface 108, the changeover device is
returned to its home position, and the output mechanism 46 is
driven in translational fashion from right to left once more as
seen in FIG. 8.
[0049] The opening 90 in the plate element 96 and/or its shape is
provided such that it comprises a plurality of guide slots 112, 114
and 116 having different lengths. At its end furthest from the
connection point with the plate element 96, the third lever element
94 is turnably interconnected via a bolt 74 with a rotary disk 68.
If an operator rotates the rotary disk 68, the plate element 96 is
tilted such that a guide slot 110, 112, 114 or 116 is set for the
bolt 88 as a guide for the movement of the bolt 88 that is desired
depending on the requirement. The rotary disk 68 is therefore a
means for adjusting a total stroke of the output mechanism 68
resulting from the individual strokes and/or for limiting its
travel.
REFERENCE NUMERALS
[0050] TABLE-US-00001 10 Device 12 Annular element 14 Input shaft
16 Means 18 Sleeve 20 Recess 22 Pivot pin 23 Recess 24 Driver 26
Means 28 Axis 30 Arm 32 Inner surface 33 Recess 34 Body 36
Blind-hole bore 38 Spring 40 Eccentric element 41 Hub 42 Means 43
Hub 44 Guide element 46 Output mechanism 48 Annular body 50 Recess
52 Spring 54 Lever element 55 Bolt 56 Hub 57 Annular body 58
Gripper element 60 Guide element 62 Lever element 64 Centerline 66
Pin 68 Rotary disk 70 Eccentric element 72 Gripper arm 74 Bolt 76
Inner side 78 Corner 80 Fastening 82 Spring element 84 Attachment
point 88 Bolt 90 Opening 92 Snap-in element 94 Lever element 96
Plate element 98 Bolt 100 Bolt 102 Recess 104 Pin 106 Spring
element 108 Surface 110 Slot 112 Guide slot 114 Guide slot 116
Guide slot 118 Bearing bolt 120 Fastening 124 Surface 126
Recess
* * * * *