US20060090580A1 - Device for driving an output mechanism - Google Patents
Device for driving an output mechanism Download PDFInfo
- Publication number
- US20060090580A1 US20060090580A1 US11/301,366 US30136605A US2006090580A1 US 20060090580 A1 US20060090580 A1 US 20060090580A1 US 30136605 A US30136605 A US 30136605A US 2006090580 A1 US2006090580 A1 US 2006090580A1
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- US
- United States
- Prior art keywords
- output mechanism
- input shaft
- movement
- gripper
- alternating
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H31/00—Other gearings with freewheeling members or other intermittently driving members
- F16H31/007—Step-by-step mechanisms for linear motion
- F16H31/008—Step-by-step mechanisms for linear motion with friction means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
- F16H29/08—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of the path of movement, the location of the pivot, or the effective length, of an oscillating connecting member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
- F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/15—Intermittent grip type mechanical movement
- Y10T74/1503—Rotary to intermittent unidirectional motion
- Y10T74/1508—Rotary crank or eccentric drive
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/15—Intermittent grip type mechanical movement
- Y10T74/1558—Grip units and features
- Y10T74/1587—Grip features
- Y10T74/1598—Driven ratchet-bar and power dog
Definitions
- the invention relates to a device for driving an output mechanism with a rotating input shaft.
- 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.
- 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.
- 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.
- FIG. 1 is a cross-sectional view of the first exemplary embodiment of the device according to the invention.
- FIG. 2 is a further cross-sectional view of the device according to FIG. 1 ;
- FIG. 3 is a longitudinal sectional view of the device according to the invention.
- 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;
- FIG. 5 is a partial view of the device according to the invention, according to FIG. 3 and FIG. 4 ;
- FIG. 6 is the partial view of the device according to FIG. 5 shown in a side view
- 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;
- FIG. 8 shows a conversion mechanism of the device according to FIG. 7 .
- 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.
- 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.
- a first means 16 configured as oscillating crank
- 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.
- two oscillating cranks 16 A and 16 B of identical design are situated at 120° angles relative to each other and are arranged coaxially in tandem.
- 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.
- 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 is interconnected via a pivot pin 22 with a not-shown housing of the device 10 .
- the oscillating crank 16 is moved to and fro and/or is swiveled to and fro in alternating fashion around the pivot pin 22 .
- the sleeve 18 must also be configured as a single component with the input shaft 14 , e.g., as a cam of a camshaft.
- the oscillating crank 16 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 .
- 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 .
- 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 .
- 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.
- 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 .
- 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 , 26 A, 26 B drive the annular body 12 via the cylindrical bodies 34 , 34 A, 34 B and, therefore, the not-shown output mechanism, in succession and in stepwise fashion.
- 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.
- 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.
- 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.
- 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 .
- the first means is composed of two oscillating cranks 16 A and 16 B having essentially the same construction. For this reason, only the oscillating crank 16 A and the further construction of the device 10 in the region of the oscillating cranks 16 A 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 16 A and 16 B on the input shaft 14 , since the input shaft 14 comprises two eccentric elements 40 A, 40 B offset by 180° relative to each other on which the two oscillating cranks 16 A and 16 B are guided with two forks 41 A, 41 B, and that are set into motion phase-displaced by 180° relative to each other when the input shaft 14 rotates.
- the two eccentric elements 40 A, 40 B 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 16 A.
- the oscillating crank 16 A is interconnected with the output mechanism 46 via two further hubs 43 A, 56 A. Said oscillating crank is swiveled to and fro around said hubs depending on the position of the eccentric element 40 A.
- the alternating swiveling movement of the oscillating crank 16 A is transferred to a third means 42 A.
- the third means 42 A which are situated such that they are axially displaceable relative to the oscillating crank 16 A and/or the first means—are functionally interconnected with one annular body 48 A, 57 A, respectively, situated on the output mechanism 46 via one guide element 44 A, 60 A, respectively, each of which said guide elements 44 A, 60 A being situated with its end furthest from the annular bodies 48 A, 57 A, respectively, in a recess 50 A of the third means 42 A and, with its end closest to the annular bodies 48 A, 57 A, being interconnected in fixed fashion with one of the annular bodies 48 A, 57 A, respectively ( FIG. 5 ).
- a spring 52 A encircling the output mechanism 46 is situated between the annular bodies 48 A, 57 A, said spring 52 A being interconnected with the annular bodies 48 A, 57 A in fixed fashion via its ends closest to the annular bodies 48 A, 57 A.
- the recess 50 A of the third means 42 A 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 42 A effects a rotational movement limited in terms of time of one of the annular bodies 48 A or 57 A around the output mechanism 46 , and the rotational movement of one of the annular bodies 48 A, 57 A is transferred via the spring 52 A to the output mechanism 46 .
- the two annular bodies 48 A, 57 A are situated with play on the output mechanism 46 configured as a shaft.
- the recess 50 A of the plate 42 A 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 42 A is located in the position shown in FIG. 6 , the oscillating movement of the plate 42 A is transferred to the annular body 57 A and causes the annular body 57 A to twist. As a result of the twisting, the spring 52 A configured as a coil spring and interconnected with the annular body 57 A in fixed fashion is also twisted and wound, which results in a reduction of the cross-section of the spring 52 A and a temporary non-positive connection between the spring 52 A and the output mechanism 46 , and, finally, effects a rotational movement of the output mechanism 46 .
- the mode of action of the arrangement of the oscillating crank 16 A described hereinabove applies similarly for the arrangement of the oscillating crank 16 B having identically-structured elements.
- the output mechanism 46 is driven via the oscillating crank 16 B, this results in the oscillating crank 16 A being driven each time the position of the input shaft 12 is displaced by 180°.
- the driving of the output mechanism 46 corresponds to a plurality of individual, closely successive rotational movements which, due to the two oscillating cranks 16 A, 16 B, effect a nearly continuous rotational driving of the output mechanism 46 .
- the plate 42 A 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 44 A is located in the outer region of the recess 50 A—which is free in FIG. 6 —and the guide element 60 A is located in the center region of the recess 50 A configured with the larger diameter, the annular body 48 A of the oscillating crank 16 A is set into rotation via the plate 42 A.
- the output mechanism 46 is thereby driven in the opposite direction of the rotational movement effected by the annular body 57 A.
- the means and/or the plates 42 A and 42 B are displaced essentially simultaneously.
- 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 .
- 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 54 A, 54 B are turnably mounted on the ends of the crossbar of the first means or the oscillating cranks 16 via the bolts 55 A, 55 B serving as pivots.
- the two lever elements 54 A, 54 B extend substantially parallel to the output mechanism 46 and create a functional connection between the oscillating crank 16 and two gripper elements 58 A, 58 B via two bearing bolts 118 A, 118 B.
- the two gripper elements 58 A, 58 B 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 16 A.
- the further lever element 62 is connected hingedly with the gripper elements 58 A, 58 B via two pins 66 A, 66 B.
- the two pins 66 A, 66 B are displaced in translational fashion nearly parallel to the centerline 64 of the output mechanism 46 .
- bores for accommodating the pins 66 A, 66 B of the further lever element 62 are configured with a larger diameter than the diameter of the pins 66 A, 66 B.
- 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 58 A, 58 B extends across the output mechanism 46 with a hub-shaped gripper arm 72 A, 72 B, respectively, to transmit the alternating movement of the oscillating crank 16 .
- the gripper arms 72 A, 72 B comprise domes directed in the direction of the output mechanism 46 , said domes being in contact with the output mechanism 46 .
- the gripper arms 72 A, 72 B 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 58 A 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 58 B simultaneously releases the output element 46 .
- the gripper element 58 B 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 58 A simultaneously releases the output mechanism 46 .
- One spring element 82 A, 82 B, respectively, is located between a fastening 80 A of the first gripper element 58 A and a fastening 120 A of the first lever element 54 A, and between a fastening 80 B of the second gripper element 58 B and a fastening 120 B of the second lever element 54 B, which said spring elements ensure two stable end positions of the gripper elements 58 A, 58 B.
- 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 58 A, 58 B 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 .
- FIG. 8 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 .
- 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.
- 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 .
- 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 58 A and 58 B positioned by the spring elements 82 A, 82 B in terms of their associated lever arms 54 A and 54 B, respectively.
- the lever element 62 is displaced with its pin 104 transversely to the output mechanism 46 starting at pin 66 B in the direction of pin 66 A, which results in the gripper element 58 A tilting in the clockwise direction and the gripper element 58 B tilting in the counter-clockwise direction.
- the spring elements 82 A, 82 B now maintain the frictional connection for the opposed direction of movement of the output mechanism 46 .
- 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 .
- 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.
- 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.
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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.
Description
- The invention relates to a device for driving an output mechanism with a rotating input shaft.
- 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.
- 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.
- 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.
- 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.
- 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.
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FIG. 1 is a cross-sectional view of the first exemplary embodiment of the device according to the invention; -
FIG. 2 is a further cross-sectional view of the device according toFIG. 1 ; -
FIG. 3 is a longitudinal sectional view of the device according to the invention; -
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; -
FIG. 5 is a partial view of the device according to the invention, according toFIG. 3 andFIG. 4 ; -
FIG. 6 is the partial view of the device according toFIG. 5 shown in a side view; -
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 -
FIG. 8 shows a conversion mechanism of the device according toFIG. 7 . -
FIGS. 1 and 2 show adevice 10 for driving an output mechanism via anannular body 12, comprising a rotationallydriveable input shaft 14 of thedevice 10 that serves simultaneously as the output shaft of a not-shown electric motor. Means for transmitting a drive torque of theinput shaft 14 to the output mechanism or theannular body 12 installed upstream from the output mechanism are located between theinput shaft 14 and the output mechanism. - 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 oscillatingcrank 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 oscillatingcrank 16, two oscillatingcranks - The mode of action of the oscillating
crank 16 described hereinbelow applies equally for the oscillatingcranks - The output mechanism—not shown in
FIG. 1 andFIG. 2 —is interconnected with theannular body 12 via a suitable connection in a region located behind the plane of the drawing such that a rotational movement of theannular body 12 results in a rotational movement of the output mechanism. - The
input shaft 14 is equipped with asleeve 18 configured with an annular cross-section, which said sleeve is located in arecess 20 of the oscillatingcrank 16 and is provided as an eccentric element for driving the oscillatingcrank 16 in an alternating manner. The oscillatingcrank 16, in turn, is interconnected via apivot pin 22 with a not-shown housing of thedevice 10. When theinput shaft 14 and thesleeve 18—which is eccentrically situated relative to theinput shaft 14 and its axis of rotation—rotates, the oscillatingcrank 16 is moved to and fro and/or is swiveled to and fro in alternating fashion around thepivot pin 22. One skilled in the art understands as a matter of course that thesleeve 18 must also be configured as a single component with theinput shaft 14, e.g., as a cam of a camshaft. - On its end furthest from the
recess 20, the oscillatingcrank 16 comprises arecess 23 in which adriver 24 is located, which said driver is interconnected with asecond means 26. Thesecond means 26 is turnably supported on anaxis 28 and equipped with anarm 30 directed radially outwardly from theaxis 28. Instead of arms, disks arranged in tandem in the axial direction are also feasible in principle. The oscillatingcrank 16 and thesecond means 26 are turnably interconnected via thedriver 24 in such a way that the alternating movement of the oscillatingcrank 16 effected by the rotation of theinput shaft 14 effects a rotational movement or a rotation of thearm 30 around theaxis 28. - A transfer element formed by a
rolling element 34 is located in therecess 33 between aninner surface 32 of the annular element orouter ring 12 that surrounds thesecond means 26 and is situated coaxial to theaxis 28, and the end of thearm 30 configured with arecess 33. In the present exemplary embodiment, therolling element 34 is configured ascylindrical 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. - In the region of the
recess 33, thearm 30 comprises a blind-hole bore 36 in which aspring 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 therolling element 34. - When the
driver 24 moves in the counter-clockwise direction, as shown in the illustration inFIG. 2 , thecylindrical body 34 walks around between theinner surface 32 of theannular body 12 and the end of thearm 30 and becomes lodged between theinner surface 32 of theannular element 12 and the end of thearm 30 closest to theannular element 12. Theannular body 12 is set into rotation in the counter-clockwise direction. The second means 26, 26A, 26B drive theannular body 12 via thecylindrical bodies driver 24 moves in the clockwise direction, thecylindrical body 34—loaded by thespring 38—only rolls or walks around on theinner surface 32 of theannular body 12 without becoming lodged. It is also possible for thebody 34 to glide on theinner surface 32 when thedriver 24 moved in the clockwise direction. - The clearance between the
driver 24 and thepivot pin 22 can be changed and, with the clearance, a conversion ratio that sets in, namely by placing thepivot pin 22 radially inwardly in analternative 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. - With the different positioning of the
pivot pin 22, a scope of a reduction of the rotational speed coming from theinput 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. - 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 theannular 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. - 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.
-
FIGS. 3 through 6 show a further exemplary embodiment of thedevice 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 thedevice 10 according toFIG. 1 andFIG. 2 . - As shown in
FIG. 3 , the first means is composed of two oscillatingcranks crank 16A and the further construction of thedevice 10 in the region of the oscillatingcranks 16A will be discussed in the description hereinbelow of the mode of action of thedevice 10. The only difference lies in the arrangement of the oscillatingcranks input shaft 14, since theinput shaft 14 comprises twoeccentric elements cranks forks input shaft 14 rotates. The twoeccentric elements input shaft 14. Their axes of rotation are arranged offset to the axis of rotation of theinput shaft 14. One rotation of theinput shaft 14 effects an alternating movement of the oscillatingcrank 16A. The oscillatingcrank 16A is interconnected with theoutput mechanism 46 via twofurther hubs 43A, 56A. Said oscillating crank is swiveled to and fro around said hubs depending on the position of theeccentric element 40A. - The alternating swiveling movement of the oscillating
crank 16A is transferred to athird means 42A. The third means 42A—which are situated such that they are axially displaceable relative to the oscillatingcrank 16A and/or the first means—are functionally interconnected with oneannular body output mechanism 46 via oneguide element guide elements annular bodies recess 50A of the third means 42A and, with its end closest to theannular bodies annular bodies FIG. 5 ). - A
spring 52A encircling theoutput mechanism 46 is situated between theannular bodies spring 52A being interconnected with theannular bodies annular bodies - 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 theplate 42A effects a rotational movement limited in terms of time of one of theannular bodies output mechanism 46, and the rotational movement of one of theannular bodies spring 52A to theoutput mechanism 46. To ensure an unimpeded, frictionless rotational movement of theannular bodies annular bodies output mechanism 46 configured as a shaft. - The
recess 50A of theplate 42A extends in the axial direction of theoutput mechanism 46 and has a greater diameter in its center region than the two outer regions, each of which abuts the center region. If theplate 42A is located in the position shown inFIG. 6 , the oscillating movement of theplate 42A is transferred to theannular body 57A and causes theannular body 57A to twist. As a result of the twisting, thespring 52A configured as a coil spring and interconnected with theannular body 57A in fixed fashion is also twisted and wound, which results in a reduction of the cross-section of thespring 52A and a temporary non-positive connection between thespring 52A and theoutput mechanism 46, and, finally, effects a rotational movement of theoutput mechanism 46. - 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 theinput shaft 12 is displaced by 180°. The driving of theoutput mechanism 46 corresponds to a plurality of individual, closely successive rotational movements which, due to the twooscillating cranks output mechanism 46. - If the
plate 42A is displaced from its position shown inFIG. 6 in the axial direction of theoutput mechanism 46 via a not-shown means in such a way that theguide element 44A is located in the outer region of therecess 50A—which is free inFIG. 6 —and theguide element 60A is located in the center region of therecess 50A configured with the larger diameter, theannular body 48A of the oscillating crank 16A is set into rotation via theplate 42A. Theoutput mechanism 46 is thereby driven in the opposite direction of the rotational movement effected by theannular body 57A. When a changeover takes place, the means and/or theplates -
FIGS. 7 and 8 show a further exemplary embodiment of thedevice 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 theinput shaft 14 is converted into a translational movement of theoutput 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 theoutput mechanism 46, and a leg extending substantially parallel with theoutput mechanism 46. - 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 theinput shaft 14. Twolever elements bolts lever elements output mechanism 46 and create a functional connection between the oscillating crank 16 and twogripper elements bolts - The two
gripper elements further lever element 62 extending transversely to theoutput mechanism 46. Said gripper elements are capable of being tilted relative to acenterline 64 of theoutput mechanism 46 depending on the alternating movement of the oscillating crank 16A. - The
further lever element 62 is connected hingedly with thegripper elements pins pins centerline 64 of theoutput mechanism 46. In order to ensure that thepins pins further lever element 62 are configured with a larger diameter than the diameter of thepins - 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 itsattachment point 84 in the clockwise direction and in the counter-clockwise direction. Each of the twogripper elements output mechanism 46 with a hub-shapedgripper arm inner sides output mechanism 46, thegripper arms output mechanism 46, said domes being in contact with theoutput mechanism 46. - The
gripper arms 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, thegripper element 58A locks up with theoutput mechanism 46 and effects a stepwise translational movement of theoutput mechanism 46 in the direction away from theinput shaft 14, whereby thesecond gripper element 58B simultaneously releases theoutput element 46. - When the oscillating crank 16 makes a swivelling movement in the clockwise direction, the
gripper element 58B locks up with theoutput mechanism 46 and effects a stepwise translational movement of theoutput mechanism 46 in the direction away from theinput shaft 14, whereby thefirst gripper element 58A simultaneously releases theoutput mechanism 46. - One
spring element fastening 80A of thefirst gripper element 58A and afastening 120A of thefirst lever element 54A, and between afastening 80B of thesecond gripper element 58B and afastening 120B of thesecond lever element 54B, which said spring elements ensure two stable end positions of thegripper elements gripper elements FIG. 7 , more or fewer gripper elements arranged in tandem on theoutput mechanism 46 can be provided to drive theoutput mechanism 46. - An automatically-operating changeover device for reversing the direction of movement of the
output mechanism 46 is shown inFIG. 8 . Abolt 88 is interconnected with theoutput mechanism 46, which said bolt engages in anopening 90 of atriangular plate element 96 tiltably situated between a snap-inelement 92 and athird lever element 94 extending substantially transversely to theoutput mechanism 46. The snap-inelement 92 is turnably supported via afurther bolt 98 in a not-shown housing of thedevice 10, and it is turnably interconnected via abolt 100 with theplate element 96. Furthermore, the snap-inelement 92 comprises a wave-shapedrecess 102 on its end furthest from theplate element 96, in which said recess apin 104 interconnected in fixed fashion with thefurther lever element 62 is located. - A
spring 106 that is interconnected in fixed fashion via its one end with the housing of thedevice 10 and, via its other end, with the snap-inelement 92 enables the snap-inelement 92 to always bear against thepin 104 with itsrecess 102. - When the
plate element 96 is moved by theoutput mechanism 46 in the direction of the snap-inelement 92—which is effected by the alternating movement of thegripper elements bolt 88 rests on asurface 108 after a certain displacement travel of theoutput mechanism 46, whereby thesurface 108 forms an end of aslot 110 of theopening 90. - If the
bolt 88 is displaced further in the direction of the snap-inelement 92 after it comes to rest on thesurface 108, a rotational movement of the snap-inelement 92 around thebolt 98 in the clockwise direction is triggered. Thespring element 106 thereby causes two stable end positions to be reached. - From this, a displacement of the lever system according to
FIG. 7 results such that thefurther lever element 62 displaces and/or drives thegripper elements spring elements lever arms lever element 62 is displaced with itspin 104 transversely to theoutput mechanism 46 starting atpin 66B in the direction ofpin 66A, which results in thegripper element 58A tilting in the clockwise direction and thegripper element 58B tilting in the counter-clockwise direction. Thespring elements output mechanism 46. As a result, theoutput mechanism 46 is subsequently driven in translational fashion from left to right as seen inFIG. 8 . If thebolt 88 comes to rest in theslot 110 on asurface 124 of theplate element 96 opposite thesurface 108, the changeover device is returned to its home position, and theoutput mechanism 46 is driven in translational fashion from right to left once more as seen inFIG. 8 . - The
opening 90 in theplate element 96 and/or its shape is provided such that it comprises a plurality ofguide slots plate element 96, thethird lever element 94 is turnably interconnected via abolt 74 with arotary disk 68. If an operator rotates therotary disk 68, theplate element 96 is tilted such that aguide slot bolt 88 as a guide for the movement of thebolt 88 that is desired depending on the requirement. Therotary disk 68 is therefore a means for adjusting a total stroke of theoutput mechanism 68 resulting from the individual strokes and/or for limiting its travel. -
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
Claims (7)
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.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/301,366 US20060090580A1 (en) | 2000-12-23 | 2005-12-13 | Device for driving an output mechanism |
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10064899.1 | 2000-12-23 | ||
DE10064899A DE10064899A1 (en) | 2000-12-23 | 2000-12-23 | Device for driving an output member |
US10/451,355 US7040185B2 (en) | 2000-12-23 | 2001-12-19 | Device for driving an output mechanism |
PCT/DE2001/004792 WO2002052173A1 (en) | 2000-12-23 | 2001-12-19 | Device for driving an output mechanism |
US11/301,366 US20060090580A1 (en) | 2000-12-23 | 2005-12-13 | Device for driving an output mechanism |
Related Parent Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/451,355 Division US7040185B2 (en) | 2000-12-23 | 2001-12-19 | Device for driving an output mechanism |
PCT/DE2001/004792 Division WO2002052173A1 (en) | 2000-12-23 | 2001-12-19 | Device for driving an output mechanism |
Publications (1)
Publication Number | Publication Date |
---|---|
US20060090580A1 true US20060090580A1 (en) | 2006-05-04 |
Family
ID=7668892
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/451,355 Expired - Fee Related US7040185B2 (en) | 2000-12-23 | 2001-12-19 | Device for driving an output mechanism |
US11/301,366 Abandoned US20060090580A1 (en) | 2000-12-23 | 2005-12-13 | Device for driving an output mechanism |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/451,355 Expired - Fee Related US7040185B2 (en) | 2000-12-23 | 2001-12-19 | Device for driving an output mechanism |
Country Status (6)
Country | Link |
---|---|
US (2) | US7040185B2 (en) |
EP (3) | EP1348084B1 (en) |
JP (1) | JP2004516437A (en) |
CN (2) | CN1811229A (en) |
DE (4) | DE10064899A1 (en) |
WO (1) | WO2002052173A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10240666B2 (en) * | 2013-03-12 | 2019-03-26 | Motus Labs, LLC | Simplified gearbox mechanism |
US10151375B2 (en) * | 2013-03-12 | 2018-12-11 | Motus Labs, LLC | Motorized gearbox mechanism |
CN108145210A (en) * | 2016-11-04 | 2018-06-12 | 南安市耀森智能设备有限公司 | A kind of perforating mechanism |
CN109058408B (en) * | 2018-08-16 | 2021-05-11 | 西安工业大学 | Telescopic multifunctional mechanical intermittent transmission device |
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- 2001-12-19 CN CNB018206816A patent/CN1287104C/en not_active Expired - Fee Related
- 2001-12-19 EP EP01990320A patent/EP1348084B1/en not_active Expired - Lifetime
- 2001-12-19 DE DE50107076T patent/DE50107076D1/en not_active Expired - Fee Related
- 2001-12-19 EP EP04014047A patent/EP1460312B1/en not_active Expired - Lifetime
- 2001-12-19 US US10/451,355 patent/US7040185B2/en not_active Expired - Fee Related
- 2001-12-19 DE DE50111026T patent/DE50111026D1/en not_active Expired - Fee Related
- 2001-12-19 EP EP04014046A patent/EP1457709B1/en not_active Expired - Lifetime
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Also Published As
Publication number | Publication date |
---|---|
JP2004516437A (en) | 2004-06-03 |
US20040087404A1 (en) | 2004-05-06 |
EP1457709B1 (en) | 2006-09-13 |
US7040185B2 (en) | 2006-05-09 |
DE50107076D1 (en) | 2005-09-15 |
CN1287104C (en) | 2006-11-29 |
EP1457709A3 (en) | 2005-05-25 |
EP1457709A2 (en) | 2004-09-15 |
EP1348084A1 (en) | 2003-10-01 |
DE50111027D1 (en) | 2006-10-26 |
WO2002052173A1 (en) | 2002-07-04 |
EP1348084B1 (en) | 2005-08-10 |
DE50111026D1 (en) | 2006-10-26 |
CN1811229A (en) | 2006-08-02 |
EP1460312A3 (en) | 2005-05-25 |
EP1460312B1 (en) | 2006-09-13 |
DE10064899A1 (en) | 2002-07-25 |
CN1481485A (en) | 2004-03-10 |
EP1460312A2 (en) | 2004-09-22 |
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Legal Events
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |