JP4850544B2 - Reverse input cutoff clutch - Google Patents

Description

  The present invention relates to a reverse input cutoff clutch having a function of transmitting input torque from the input side to the output side and locking the reverse input torque from the output side so as not to return to the input side.

  For example, in a device that performs a required operation by transmitting input torque from a driving source to an output side mechanism, a function for holding the output side mechanism so that the position of the output side mechanism does not fluctuate may be required when the driving source is stopped. is there. Taking an electric shutter as an example, a forward or reverse input torque from a drive motor is input to an output-side opening / closing mechanism to perform opening / closing operation of the shutter. When the drive source is stopped due to a power failure or the like, if the reverse input torque due to the lowering of the weight of the shutter returns to the input side, the input side device may be damaged. Therefore, a mechanism having a function of holding the position of the shutter and preventing the reverse input torque from the shutter from returning to the input side is required.

  One of the mechanisms having a function of locking the reverse input torque from the output side and preventing the reverse input torque from returning to the input side is a reverse input cutoff clutch (see, for example, Patent Document 1).

  As shown in FIGS. 6 and 7, the conventional reverse input shut-off clutch has a structure in which an input shaft 2 and an output shaft 3 are supported on a stationary outer ring 1 in a stationary state via a rolling bearing 4 and 5 so as to be able to rotate forward and backward. It has. The input shaft 2 is provided with a pin 8 protruding in the axial direction at a position shifted radially outward from the shaft center, and the output shaft 3 is formed with a concave groove 7 along the radial direction on the end surface facing the input shaft 2. Has been. By projecting the tip of the pin 8 from the end surface facing the output shaft 3 and fitting it into a groove 7 formed on the end surface of the output shaft 3, the rotational torque from the input shaft 2 is transmitted to the output shaft 3. It is possible.

  On the other hand, a flange portion 2a whose diameter is increased outward in the radial direction is integrally formed at the output shaft side end portion of the input shaft 2, and a plurality (four in the figure) extending from the outer periphery of the flange portion 2a to the output shaft side in the axial direction. Column parts 2b are formed at equal intervals in the circumferential direction. The space between the column portions 2b adjacent to each other in the circumferential direction constitutes a pocket 9 that opens toward one side in the axial direction, and a pair of rollers 10a and 10b is disposed in each pocket 9. Reference numeral 14 in FIG. 7 is a spacer that is disposed between the input shaft 2, the output shaft 3, and the rolling bearing 5 and restricts the axial movement of the rollers 10 a and 10 b housed in the pocket 9.

  On the outer periphery of the output shaft 3 on the input shaft side, a plurality of pairs (four pairs in the figure) of cam surfaces 11a and 11b corresponding to the pockets 9 positioned between the column portions 2a of the input shaft 2 described above are equally spaced in the circumferential direction. Is formed. A plurality of pairs (four pairs in the figure) of rollers 10a and 10b are arranged between the cam surfaces 11a and 11b of the output shaft 3 and the inner peripheral surface of the fixed outer ring 1, and between the column portions 2a of the input shaft 2. It is accommodated in the formed pocket 9. Of the pair of rollers 10a and 10b, one roller 10a is disposed on one cam surface 11a of the pair of cam surfaces 11a and 11b, and the other roller 10b is disposed on the other cam surface 11b. ing.

  A pair of N-shaped elastic members 12a and 12b is inserted between the pair of rollers 10a and 10b, and each elastic member 12a and 12b elastically presses the pair of rollers 10a and 10b away from each other. To do. In addition, a pair of shielding plates 13 serving as partition members that make the pressing force of the elastic member 12a acting on one roller 10a and the pressing force of the elastic member 12b acting on the other roller 10b independent of each other when torque is transmitted from the input shaft 2 are paired. The elastic members 12a and 12b are fixed to both surfaces of the shielding plate 13, respectively, between the rollers 10a and 10b.

  In this reverse input cut-off clutch, when a reverse input torque in the clockwise direction is input to the output shaft 3 in the neutral state shown in an enlarged manner in FIG. 8, the counterclockwise direction (rear in the rotational direction) is caused by the elastic force of the elastic member 12a. The roller 10 a engages with the wedge gap in that direction, and the output shaft 3 is locked in the clockwise direction with respect to the fixed outer ring 1. On the contrary, when the counterclockwise reverse input torque is input to the output shaft 3, the roller 10b in the clockwise direction (rear in the rotation direction) is engaged with the wedge gap in that direction by the elastic force of the elastic member 12b, and the output The shaft 3 is locked counterclockwise with respect to the fixed outer ring 1. Therefore, the reverse input torque from the output shaft 3 is locked in both forward and reverse rotation directions by the pair of rollers 10a and 10b.

  On the other hand, when rotational torque is input to the input shaft 2 and rotated clockwise, for example, as shown in an enlarged view in FIG. 9, first, the column portion 2b of the input shaft 2 in the counterclockwise direction (backward in the rotational direction) It is engaged with the roller 10a in the direction (backward in the rotational direction) and pressed in the clockwise direction (forward in the rotational direction) against the elastic force of the one elastic member 12a. As a result, the counterclockwise (backward in the rotational direction) roller 10a is released from the wedge gap in that direction, the locked state of the output shaft 3 is released, and the output shaft 3 can be rotated clockwise.

  When the input shaft 2 further rotates in the clockwise direction, the pin 8 of the input shaft 2 comes into contact with the wall surface of the concave groove 7 of the output shaft 3, so that the clockwise rotational torque from the input shaft 2 causes the pin 8 and the concave groove. 7 is transmitted to the output shaft 3 through the engagement portion with the output shaft 3, and the output shaft 3 rotates clockwise. At this time, the roller 10b in the clockwise direction (forward in the rotation direction) does not engage with the wedge clearance in that direction, and idles in a state where it contacts the cam surface 11b of the output shaft 3 and the inner peripheral surface of the fixed outer ring 1.

  When a counterclockwise rotational torque is input to the input shaft 2, the output shaft 3 rotates counterclockwise by the reverse operation to that described above. Accordingly, the rotational torque in the forward and reverse rotational directions from the input shaft 2 is transmitted to the output shaft 3 through the engaging portion between the pin 8 and the concave groove 7, and the output shaft 3 rotates in the forward and reverse rotational directions. To do.

  When torque is transmitted from the input shaft 2, the shielding plate 13 disposed between the pair of rollers 10a and 10b causes the pressing force of the elastic member 12a acting on one roller 10a and the elastic member acting on the other roller 10b. The pressing force of 12b is made independent. Therefore, only the elastic member 12a that presses the roller 10a (see FIG. 8) positioned rearward in the rotational direction is deformed between the shielding plate 13 and the elastic member 12b that presses the roller 10b positioned forward in the rotational direction is Does not deform.

Thus, since the pressing force of the elastic member 12a acting on one roller 10a does not affect the magnitude of the pressing force of the elastic member 12b acting on the other roller 10b, the elasticity acting on the other roller 10b. The spring load of the member 12b does not increase. As a result, torque loss in rotation transmission from the input shaft 2 to the output shaft 3 can be reduced.
JP 2003-343601 A

  By the way, in the reverse input cutoff clutch described above, when the drive motor coupled to the input shaft 2 is stopped rotating, it is between the inner peripheral surface of the fixed outer ring 1 and the cam surfaces 11a and 11b of the output shaft 3. When the rollers 10a and 10b are engaged with each other through the formed wedge gap, a locked state is maintained in which the reverse input torque is cut off. A state in which the reverse input torque is continuously applied when the rotation torque is input to the input shaft 2 by the start of rotation of the drive motor and the lock state is released while maintaining the lock state in which the reverse input torque is cut off. Since there is a frictional force between the fixed outer ring 1 or the output shaft 3 and the rollers 10a and 10b and elastic deformation of the components within the wedge gap, a release force larger than the reverse input torque, that is, from the input shaft 2 Rotational torque is required. Therefore, a large output from the drive motor is required.

  When the lock is released, the frictional force between the fixed outer ring 1 or the output shaft 3 and the rollers 10a and 10b and the elastic deformation of the components within the wedge gap are released at a stretch, so that the rollers 10a and 10b have a narrower wedge gap. May be squeezed out to the wider side, and may collide with the elastic members 12a and 12b vigorously. When this phenomenon is repeated, the elastic members 12a and 12b are subjected to a bending load exceeding the allowable stress, and abnormal deformation of the elastic members 12a and 12b or breakage from the bent portion may occur. FIG. 10 illustrates a case where abnormal deformation of the elastic member 12a or breakage from the bent portion occurs due to clockwise rotational torque.

  Therefore, the present invention has been proposed in view of the above-described problems, and the object of the present invention is to abnormally deform or bend the elastic member due to the pressing of the roller when releasing the lock during torque transmission from the input shaft. An object of the present invention is to provide a reverse input shut-off clutch that can prevent the occurrence of breakage.

As a technical means for achieving the above-described object, the reverse input cutoff clutch of the present invention includes an input side member to which rotational torque is input, an output side member to which rotational torque is output, and a stationary member whose rotation is restricted. and side members, respectively stationary member roller pairs provided so as to be disengaged, and is disposed between the rollers of each pair on both sides of the roller between the output member and the stationary member output A lock that consists of an elastic member that urges the side member to engage with it, locks the output side member against reverse input torque from the output side member, and releases the locked state against input torque from the input side member And a torque transmission means that is provided between the input side member and the output side member and transmits the input torque from the input side member to the output side member when in the unlocked state . Acts on roller A shielding plate for independently a pressing force of the bent portion of the elastic member acting on the pressing force and the other roller of the bent portion of the elastic member is provided at the base of the elastic member that, the elastic member side of the cam surface of the output-side member formed on the end portion has a locking surface of the cross-sectional concave R-shape extending from the cam surface, the locking surface of the position of the roller to move against the elastic force of the bent portion of the elastic member during the unlocking by the locking means A raised portion to be regulated by the above is provided on the output side member.

In the reverse input shut-off clutch of the present invention, when the rotational torque from the input side member is not input, the reverse input is obtained by engaging the roller in the wedge gap formed between the stationary side member and the output side member. The locked state that cuts off the torque is maintained. While maintaining the locked state that cuts off this reverse input torque, when the rotational torque from the input side member is input and the aforementioned locked state is released, the reverse input torque continues to be applied, and the stationary side Because of the frictional force between the member or the output side member and the roller and the elastic deformation of the components within the wedge gap, a release force larger than the reverse input torque is required. As a result, a large rotational torque from the input side member, time release, since the elastic deformation of the components in frictional force and the wedge gaps between the stationary-side member or the output member and the roller is released at once, the roller Will be ejected from the narrowest wedge gap to the wider one.

In the present invention, there is an engaging surface having a concave R-shaped cross section formed at the elastic member side end of the cam surface of the output side member and extending from the cam surface, and the elasticity of the bent portion of the elastic member when unlocked by the locking means By providing the output side member with a raised portion that restricts the position of the roller that moves against the force by the locking surface, the roller that is ejected from the narrowest to the wider wedge clearance when unlocked is The position is restricted by the locking surface of the raised portion . As a result, it is possible to prevent the roller from colliding with the elastic member vigorously, so that the elastic member is not subjected to a bending load exceeding the allowable stress, and from an abnormal deformation or bending portion of the elastic member. There will be no breakage.

Locking means include those that apply rotational restraint force by wedge engagement force, uneven engagement force, friction force, magnetic force, electromagnetic force, fluid pressure, fluid viscosity resistance force, particulate medium, etc., but the structure and control mechanism From the viewpoint of simplification, smooth operation, cost, etc., it is preferable to apply a rotation restraining force by a wedge engaging force. Specifically, it is preferable that a wedge gap is formed between the output side member and the stationary side member, and the lock / idling is switched by engaging / disengaging a roller with respect to the wedge gap.

Moreover, it is desirable that the clearance dimension between the raised portion of the output side member and the stationary side member be equal to or smaller than the outer diameter of the roller . In this way, the roller does not enter between the raised portion of the output side member and the stationary side member, and the position of the roller can be reliably regulated by the locking surface of the raised portion. If the gap size is larger than the outer diameter of the roller, there is a possibility that the roller enters between the raised portion and the stationary-side member, it is difficult to reliably position restriction roller in locking surface of the raised portion .

According to the present invention, the elastic member side end portion formed on the elastic member side end portion of the cam surface of the output side member has a concave R-shaped engaging surface extending from the cam surface, and the bent portion of the elastic member when unlocked by the locking means by providing the position of the rollers to move against the elastic force to the output side member of the ridges regulated by locking surface, rollers ejected toward wider from the side narrow wedge gap, the above-mentioned ridges The position is regulated by the locking surface . As a result, it is possible to prevent the roller from colliding with the elastic member vigorously, so that the elastic member is not subjected to a bending load exceeding the allowable stress, and from an abnormal deformation or bending portion of the elastic member. There will be no breakage. As a result, it is possible to stabilize the quality and improve the reliability of the reverse input cutoff clutch.

  An embodiment of the reverse input cutoff clutch according to the present invention will be described in detail below. 1 to 3 show the overall configuration of a reverse input cutoff clutch in an embodiment of the present invention. FIG. 3 shows an assembled and disassembled state of the input shaft, output shaft, roller, elastic member, and shielding plate.

  As shown in FIGS. 1 to 3, the reverse input cutoff clutch of this embodiment has a stationary outer ring 21 as a stationary side member whose rotation is restrained, and a distal end portion inserted into the inner periphery of the stationary outer ring 21, and rotational torque is reduced. An input shaft 22 as an input side member to be input, an output shaft 23 as an output side member that is inserted into the inner periphery of the fixed outer ring 21 in a state of facing the input shaft 22 and outputs a rotational torque, and the fixed outer ring 21 and a plurality of pairs (four pairs in the figure) of rollers 30a and 30b provided between the output shaft 23 and the output shaft 23, and both sides of the rollers 30a and 30b. The rollers 30 a and 30 b are elastic members 42 that urge the rollers 30 a and 30 b in a direction to engage between the fixed outer ring 21 and the output shaft 23, and lock the output shaft 23 and the fixed outer ring 21 against reverse input torque from the output shaft 23. And from the input shaft 22 Torque that is provided between the input shaft 22 and the output shaft 23, and that transmits the input torque from the input shaft 22 to the output shaft 23 when in the unlocked state. Of the pair of rollers 30a and 30b, the transmission means 45 and a shielding member as a partition member that makes independent the pressing force of the elastic member 42 acting on one roller 30a and the pressing force of the elastic member 42 acting on the other roller 30b. And a structure in which an input shaft 22 and an output shaft 23 are supported on the fixed outer ring 21 via rolling bearings 24 and 25 so as to be rotatable forward and backward.

  The structure of the torque transmission means 45 is as follows. The input shaft 22 is provided with a pin 28 protruding in the axial direction at a position shifted radially outward from the shaft center, and the output shaft 23 is formed with a concave groove 27 along the radial direction on the end surface facing the input shaft 22. Has been. By projecting the tip of the pin 28 from the end surface facing the output shaft 23 and fitting it into a concave groove 27 formed on the end surface of the output shaft 23, the rotational torque from the input shaft 22 is transmitted to the output shaft 23. It is possible.

  On the other hand, the structure of the locking means 44 is as follows. A flange portion 22a whose diameter is increased radially outward is integrally formed at the output shaft side end portion of the input shaft 22, and a plurality (four in the figure) extending from the outer periphery of the flange portion 22a toward the output shaft side in the axial direction. Column portions 22b are formed at equal intervals in the circumferential direction. The space between the column portions 22b adjacent to each other in the circumferential direction constitutes a pocket 29 that opens toward one side in the axial direction, and a pair of rollers 30a and 30b are arranged in each pocket 29, respectively. Reference numeral 34 in FIG. 2 is a spacer that is disposed between the input shaft 22, the output shaft 23, and the rolling bearing 25 and restricts the axial movement of the rollers 30 a and 30 b accommodated in the pocket 29.

  On the outer periphery of the output shaft 23 on the input shaft side, a plurality of pairs (four pairs in the figure) of cam surfaces 31a and 31b are arranged at equal intervals in the circumferential direction so as to correspond to the pockets 29 located between the column portions 22b of the input shaft 22 described above. Is formed. Between the cam surfaces 31 a and 31 b of the output shaft 23 and the inner peripheral surface of the fixed outer ring 21, a plurality of pairs (four pairs in the figure) of rollers 30 a and 30 b are respectively arranged between the column portions 22 b of the input shaft 22. It is accommodated in the formed pocket 29. Of the pair of rollers 30a and 30b, one roller 30a is positioned on one cam surface 31a of the pair of cam surfaces 31a and 31b, and the other roller 30b is positioned on the other cam surface 31b. ing.

  A pair of cam surfaces 31a and 31b formed on the input shaft side outer periphery of the output shaft 23 is provided with a locking means 33 for restricting the positions of the rollers 30a and 30b that move against the elastic force of the elastic member 42 when unlocked. Is provided. The locking means 33 is formed at the elastic member side ends of the cam surfaces 31a and 31b of the output shaft 23, and has a raised portion 36a having locking surfaces 35a and 35b having a concave R shape extending from the cam surfaces 31a and 31b. 36b. The clearance between the raised portions 36a and 36b of the output shaft 23 and the fixed outer ring 21 is set to be equal to or smaller than the outer diameter of the rollers 30a and 30b.

  An elastic member 42 is inserted between the pair of rollers 30a and 30b, and the elastic member 42 elastically presses the pair of rollers 30a and 30b in a direction in which they are separated from each other. The elastic member 42 has a structure in which a U-shaped base portion 42c at the center of the expansion / contraction direction and substantially N-shaped bent portions 42a and 42b extending from both sides of the base portion 42c are integrally formed. The elastic member 42 has a base portion 42 fitted in a slit groove 32 formed on the outer peripheral surface of the output shaft 23, and the outermost portions of the bent portions 42a and 42b are in contact with the rollers 30a and 30b, respectively.

  The pressing force of the bent portion 42a of the elastic member 42 acting on the one roller 30a and the pressing force of the bent portion 42b of the elastic member 42 acting on the other roller 30b are independent from each other when torque is transmitted from the input shaft 22. A U-shaped shielding plate 43 to be inserted is inserted into the base 42 c of the elastic member 42.

  In this reverse input shut-off clutch, when a reverse input torque in the clockwise direction is input to the output shaft 23 in the neutral state shown in an enlarged manner in FIG. 4, the counterclockwise direction (by the elastic force of the bent portion 42a of the elastic member 42) The roller 30 a in the rear (rotating direction) is engaged with the wedge clearance in that direction, and the output shaft 23 is locked in the clockwise direction with respect to the fixed outer ring 21. Conversely, when a counterclockwise reverse input torque is input to the output shaft 23, the roller 30b in the clockwise direction (rear in the rotational direction) is engaged with the wedge clearance in that direction by the elastic force of the bent portion 42b of the elastic member 42. Accordingly, the output shaft 23 is locked counterclockwise with respect to the fixed outer ring 21. Accordingly, the reverse input torque from the output shaft 23 is locked in both forward and reverse rotation directions by the pair of rollers 30a and 30b.

  On the other hand, when rotational torque is input to the input shaft 22 and rotated clockwise, for example, as shown in an enlarged view in FIG. 5, first, the column portion 22b of the input shaft 22 in the counterclockwise direction (backward in the rotational direction) It is engaged with the roller 30a in the direction (backward in the rotational direction) and is pressed clockwise (forward in the rotational direction) against the elastic force of the bent portion 42a of one elastic member 42. As a result, the counterclockwise (backward in the rotational direction) roller 30a is released from the wedge gap in that direction, the output shaft 23 is unlocked, and the output shaft 23 can be rotated clockwise.

  When the input shaft 22 rotates further in the clockwise direction, the pin 28 of the input shaft 22 abuts against the wall surface of the concave groove 27 of the output shaft 23, so that the clockwise rotational torque from the input shaft 22 causes the pin 28 and the concave groove to move. The output shaft 23 is transmitted to the output shaft 23 through the engaging portion 27, and the output shaft 23 rotates clockwise. At this time, the roller 30b in the clockwise direction (forward in the rotation direction) does not engage with the wedge gap in that direction, and idles in a state where it contacts the cam surface 31b of the output shaft 23 and the inner peripheral surface of the fixed outer ring 21.

  When a counterclockwise rotational torque is input to the input shaft 22, the output shaft 23 rotates counterclockwise by the reverse operation to that described above. Accordingly, the rotational torque in the forward and reverse rotational directions from the input shaft 22 is transmitted to the output shaft 23 through the engaging portion between the pin 28 and the groove 27, and the output shaft 23 rotates in the forward and reverse rotational directions. To do.

  When torque is transmitted from the input shaft 22, the shielding plate 43 disposed between the pair of rollers 30a and 30b causes the pressing force of the bent portion 42a of the elastic member 42 acting on one roller 30a and the other roller 30b. Since the pressing force of the bent portion 42b of the elastic member 42 acting on the roller 30a is made independent, the pressing force of the bent portion 42a of the elastic member 42 acting on the one roller 30a acts on the other roller 30b. Since it does not affect the magnitude of the pressing force of the bent portion 42b of the elastic member 42, the spring load of the bent portion 42b of the elastic member 42 acting on the other roller 30b does not increase. As a result, torque loss in rotation transmission from the input shaft 22 to the output shaft 23 can be reduced.

  In this reverse input shut-off clutch, when the rotational torque from the input shaft 22 is not input, the rollers 30a and 30b are engaged by the wedge clearance formed between the fixed outer ring 21 and the output shaft 23, and the reverse is achieved. The locked state that cuts off the input torque is maintained. When the rotational torque from the input shaft 22 is input and the above-described locked state is released while maintaining the locked state for blocking the reverse input torque, the reverse input torque is continuously applied. 21 or the output shaft 23 and the rollers 30a and 30b, and the elastic deformation of the components within the wedge gap requires a release force larger than the reverse input torque. When the lock is released, the frictional force between the fixed outer ring 21 or the output shaft 23 and the rollers 30a and 30b and the elastic deformation of the components within the wedge gap are released all at once, so that the rollers 30a and 30b have the narrower wedge gap. It is pushed out to the wider one.

  In this embodiment, raised portions 36a and 36b having engaging surfaces 35a and 35b having concave R-shaped sections extending from the cam surfaces 31a and 31b are provided at the elastic member side ends of the cam surfaces 31a and 31b of the output shaft 23. As a result, when the lock is released, the positions of the rollers 30a and 30b ejected from the narrowest wedge gap to the wider one are restricted by the locking surfaces 35a and 35b of the raised portions 36a and 36b. FIG. 5 illustrates a state in which the position of the roller 30a is restricted by the locking surface 35a by the clockwise rotational torque.

  In this case, if the clearance between the raised portions 36 a and 36 b and the fixed outer ring 21 is set to be equal to or smaller than the outer diameter of the rollers 30 a and 30 b, the rollers 30 a and 30 b are provided between the raised portions 36 a and 36 b and the fixed outer ring 21. The rollers 30a and 30b can be reliably regulated by the locking surfaces 35a and 35b of the raised portions 36a and 36b without entering. If the clearance dimension is larger than the outer diameter of the rollers 30a and 30b, the rollers 30a and 30b may enter between the raised portions 36a and 36b and the fixed outer ring 21, and the rollers 30a and 30b are moved into the raised portions 36a and 36b. It becomes difficult to reliably position-control the locking surfaces 35a and 35b.

  5 illustrates the case where the rotational torque from the input shaft 22 acts in the clockwise direction as indicated by the arrow in the drawing, and therefore the roller 30a ejected from the narrower one to the wider wedge gap is raised. A state where the position is restricted by the locking surface 35a of 36a is shown. When the rotational torque from the input shaft 22 acts counterclockwise, the position of the roller 30b ejected from the narrowest wedge gap to the wider one is restricted by the locking surface 35b of the raised portion 36b.

  As a result, even if a phenomenon occurs in which the rollers 30a and 30b are ejected from the narrow wedge gap to the wide one, the rollers 30a and 30b can be locked by the locking surfaces 35a and 35b of the raised portions 36a and 36b. Therefore, it is possible to prevent the rollers 30a and 30b from colliding with the bent portions 42a and 42b of the elastic member 42 vigorously. As a result, the bent portions 42a and 42b of the elastic member 42 are not subjected to a bending load exceeding the allowable stress, and abnormal deformation of the bent portions 42a and 42b of the elastic member 42 and breakage from the bent portions occur. There is no need to do.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

FIG. 3 is a cross-sectional view taken along line BB in FIG. 2 in the embodiment of the reverse input cutoff clutch according to the present invention. It is sectional drawing which follows the AA line of FIG. It is an assembly exploded perspective view which shows an input shaft, an output shaft, a roller, an elastic member, and a shielding board. It is a principal part expanded sectional view which shows the neutral state of FIG. It is a principal part expanded sectional view which shows the state into which rotational torque was input from the input shaft. FIG. 8 is a cross-sectional view taken along line DD of FIG. 7 in a conventional example of a reverse input cutoff clutch. It is sectional drawing which follows the CC line of FIG. It is a principal part expanded sectional view which shows the neutral state of FIG. It is a principal part expanded sectional view which shows the state into which rotational torque was input from the input shaft. It is a principal part expanded sectional view which shows the phenomenon where a roller collides with an elastic member vigorously in the state in which rotational torque was input from the input shaft.

Explanation of symbols

21 Static side member (fixed outer ring)
22 Input side member (input shaft)
23 Output side member (output shaft)
30a, 30b Engagement element (roller)
33 Locking means 35a, 35b Locking surfaces 36a, 36b Raised portion 42 Elastic member 44 Locking means 45 Torque transmitting means

Claims (2)

An input side member to which rotational torque is input, an output side member to which rotational torque is output, a stationary side member to which rotation is constrained, and engagement and disengagement between the stationary side member and the output side member are possible. A plurality of pairs of rollers provided, and an elastic member disposed between each pair of rollers and biasing the rollers on both sides in a direction to engage the stationary side member and the output side member, respectively. Locking means for locking the output side member against the reverse input torque and releasing the locked state against the input torque from the input side member, provided between the input side member and the output side member, and unlocked. And a torque transmitting means for transmitting the input torque from the input side member to the output side member, and the pressing force of the bent portion of the elastic member acting on one of the rollers during the transmission of the input torque and acting on the other roller. Bending of elastic member A shielding plate for independent and pressure a reverse input blocking clutch provided in the base portion of the elastic member,
An elastic surface of a bent portion of the elastic member at the time of releasing the lock by the locking means , having a locking surface having a concave R-shape formed at the elastic member side end of the cam surface of the output side member and extending from the cam surface. A reverse input blocking clutch, wherein the output side member is provided with a raised portion that restricts the position of the roller that moves against the locking surface . The reverse input cutoff clutch according to claim 1 , wherein a clearance dimension between the raised portion of the output side member and the stationary side member is equal to or less than an outer diameter of the roller .

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