JP6560013B2 - Reverse input cutoff clutch - Google Patents

Description

  The present invention relates to a reverse input cutoff clutch that transmits input torque applied from the input side to the output side and blocks the reverse input torque applied from the output side so as not to be transmitted to the input side.

  The reverse input cutoff clutch is incorporated in various devices for home use or business use. For example, an electromagnetic clutch is incorporated in office equipment such as a copying machine and a printer in order to easily pull out paper that has been jammed. As an alternative to this electromagnetic clutch, for example, Patent Document 1 below has been proposed.

  In the reverse input cutoff clutch of Patent Document 1, a cylindrical holding portion that holds a roller interposed between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring is provided, and the holding portion and the outer ring are interposed via a centering spring. It is connected.

  A pocket for accommodating the roller is formed at one end of the cage, and a shaft member is inserted into the other end of the cage. This shaft member is fixed in the rotational direction by a braking member, and is rotatable when receiving a rotational torque larger than the braking force of the braking member. In addition, a viscous fluid is sealed in a gap between the cage and the shaft member, and is sealed with an oil seal and a stopcock.

  In such a reverse input cutoff clutch, when the outer ring rotates, a cage connected to the outer ring via a centering spring rotates. At this time, the cage receives shear resistance from the viscous fluid interposed between the cage member and the cage member. Therefore, the centering spring bends in the rotation direction, and a relative rotation (delay of rotation of the cage) occurs between the cage and the outer ring. Then, due to the relative rotation of the cage, the roller held by the cage receives a force from the cage to be in a locked state, and rotational torque from the outer ring is transmitted to the inner ring.

  On the other hand, when the input source stops and the rotation of the outer ring and the cage stops, the shear resistance of the viscous fluid disappears, so that the cage rotates relative to the outer ring by the elastic restoring force of the centering spring (in the opposite direction to the above). Relative rotation), the circumferential position of both is centered. The locked state of the roller is released by the centering of the cage, and as a result, the inner ring becomes free relative to the outer ring.

JP-A-8-177878

  However, in the reverse input cutoff clutch of Patent Document 1, not only a viscous fluid is disposed between the cage and the shaft member, but also an oil seal is disposed to seal the viscous fluid. For this reason, since the centering spring receives the resistance of the oil seal even when the locked state is released by the elastic force of the centering spring, the locked state cannot be released unless the elastic force is increased.

  On the other hand, when the elastic force of the centering spring is increased, the centering spring becomes difficult to bend in the rotational direction even if it receives the shear resistance of the viscous fluid, so that the locked state is delayed or is not locked.

  As described above, the centering spring is responsible for the transition between the locked state and the unlocked state, and when considering the resistance of the oil seal, one side is smoothed between the locked state and the unlocked state. Attempting to do so results in a trade-off relationship where the other cannot be smoothed. For this reason, there has been a tendency that the clutch operation cannot be performed without hindrance unless the elastic force of the centering spring is strictly defined in consideration of the resistance of the oil seal.

  Therefore, the reverse input cutoff clutch of the present invention aims to smoothly execute the clutch operation.

  In order to solve the above problems, a reverse input cutoff clutch according to the present invention includes an input rotating member fixed to an inner ring or an outer ring disposed concentrically with the inner ring, an inner peripheral surface of the outer ring, and an outer peripheral surface of the inner ring. A torque transmitting member disposed between the retainer, a retainer that holds the torque transmitting member, a rotor that rotates in conjunction with the retainer, and a rotating member that is fixed so as not to rotate even when the input rotating member rotates; And when the input rotating member rotates in the first rotation direction, the housing member into which the rotor is fitted and the rotor member is disposed on the opposite side of the rotor from the side on which the housing member is fitted via the viscous fluid. An elastic member for connecting the input rotating member and the rotor so that the rotor rotates in the first rotation direction, and a shear resistance of the viscous fluid applied to the rotor When the rotational speed of the retainer interlocked with the rotor is slower than the rotational speed of the inner ring or the outer ring fixed to the input rotation shaft due to the torque transmission member, the inner peripheral surface of the outer ring And the elastic member deformed due to the rotation speed of the retainer being slower than the rotation speed of the inner ring or the outer ring is restored against the shear resistance. Thus, when the retainer is moved in the second rotation direction opposite to the first rotation direction, the torque transmission member in the locked state is released.

  Such a reverse input shut-off clutch is configured to be able to be locked by applying shear resistance to the rotor connected by the elastic member while utilizing the unlocking mechanism by the elastic member. Since this elastic member is disposed on the opposite side of the rotor from the side on which the housing member is fitted via the viscous fluid, it does not receive the shear resistance of the viscous fluid. Therefore, since the trade-off relationship as described above does not occur between the locked state and the unlocked state as in the reverse input cutoff clutch of Patent Document 1, the elastic force of the elastic member does not have to be strictly defined. The clutch operation can be executed without any trouble. Thus, a reverse input cutoff clutch that can smoothly execute the clutch operation is realized.

It is a disassembled perspective view which shows the reverse input interruption | blocking clutch of this embodiment. It is a disassembled perspective view which shows a reverse input interruption | blocking clutch from a viewpoint different from FIG. It is a perspective view which shows an input rotation member. It is a perspective view which shows a housing member. It is a perspective view which shows a rotor from the output side. It is a perspective view which shows a rotor from the input side. It is a perspective view which shows a centering spring. It is a perspective view which shows a retainer from the output side. It is a perspective view which shows a retainer from the input side. It is a figure which shows the mode of the cross section of a reverse input interruption | blocking clutch. It is a figure which shows the mode of a locked state and a lock release state. It is sectional drawing which shows the reverse input interruption | blocking clutch of other embodiment.

  DESCRIPTION OF EMBODIMENTS Hereinafter, preferred embodiments of a reverse input cutoff clutch according to the present invention will be described in detail with reference to the drawings.

  FIG. 1 is an exploded perspective view showing a reverse input cutoff clutch of the present embodiment, and FIG. 2 is an exploded perspective view showing the reverse input cutoff clutch from a different viewpoint from FIG. As shown in FIGS. 1 and 2, the reverse input cutoff clutch 1 of this embodiment includes a damper mechanism 2, a lock release mechanism 3, and a lock mechanism 4 as main components. The damper mechanism 2, the lock release mechanism 3, and the lock mechanism 4 are provided between the input rotation member 5 and the output rotation member 6 and on the rotation axis AX of the input rotation member 5 and the output rotation member 6.

  The damper mechanism 2 has a housing member 21, a rotor 22 and a viscous fluid 23, the lock release mechanism 3 has a rotor 22, a centering spring 31 and a retainer 32, and the lock mechanism 4 has a retainer 32, an inner ring 41 and an outer ring 42. .

  That is, in the reverse input cutoff clutch 1 of the present embodiment, the rotor 22 serves as both the damper mechanism 2 and the lock release mechanism 3, and the retainer 32 serves as both the lock release mechanism 3 and the lock mechanism 4.

  FIG. 3 is a perspective view showing the input rotation member 5. As shown in FIG. 3, the input rotation member 5 is a rod-shaped member, and a step is formed on the outer peripheral surface of the input rotation member 5 along the longitudinal direction of the input rotation member 5.

  In other words, the input rotating member 5 has a rod shape and has an input side end 51, a first intermediate portion 52, a second intermediate portion 53, and an output side end 54. The outer diameter of the first intermediate portion 52 is smaller than the outer diameter of the input side end portion 51, the outer diameter of the second intermediate portion 53 is smaller than the outer diameter of the first intermediate portion 52, and the outer diameter of the output side end portion 54. Is smaller than the outer diameter of the second intermediate portion 53.

  A spring locking portion 55 that locks a part of the centering spring 31 is provided on the peripheral edge on the first intermediate portion 52 side so as to protrude toward the output side end portion 54. On the outer peripheral surface of the second intermediate portion 53, inner ring fitting grooves 56 that fit into predetermined portions of the inner ring 41 are formed, for example, at equal intervals around the axis of the second intermediate portion 53. A snap fit 57 is formed at the output side end 54 along the longitudinal direction of the input rotation member 5. The snap fit 57 is fitted into a predetermined part of the output rotation member 6.

  FIG. 4 is a perspective view showing the housing member 21. As shown in FIG. 4, the housing member 21 has a cylindrical side wall 21A and a bottom wall 21B connected to one end of the side wall 21A, and a housing space is formed by the side wall 21A and the bottom wall 21B.

  The side wall 21A is formed with a mounting portion 71 protruding from the outer peripheral surface of the side wall 21A. The mounting portion 71 is fixed to the outside of the reverse input cutoff clutch 1 such as a device in which the reverse input cutoff clutch 1 is incorporated. A through-hole 72 through which the first intermediate portion 52, the second intermediate portion 53, and the output side end portion 54 of the input rotation member 5 are inserted is formed in the bottom wall 21B. The inner diameter of the through hole 72 is approximately the same as the outer diameter of the first intermediate portion 52.

  In the present embodiment, when the input rotation member 5 is inserted into the through hole 72 of the housing member 21, the outer peripheral surface of the first intermediate portion 52 and the inner peripheral surface of the through hole 72 are in contact with each other, and the input rotation member 5 and the housing The member 21 is relatively rotatable.

  On the inner peripheral surface of the bottom wall 21 </ b> B, an annular convex portion 73 is provided concentrically along the periphery of the input rotation member 5 inserted through the through hole 72. The annular protrusion 73 is accommodated in the housing space of the housing member 21, and the annular protrusion 73 is formed with cuts 74 at predetermined intervals. The grooves sandwiched between the annular convex portions 73 provided concentrically by the notches 74 are communicated with each other. The inner peripheral surface of the bottom wall 21 </ b> B is one surface of the housing member 21 that faces the rotor 22.

  FIG. 5 is a perspective view showing the rotor 22 from the output side, and FIG. 6 is a perspective view showing the rotor 22 from the input side. As shown in FIGS. 5 and 6, the rotor 22 is an annular member and has a through hole 81. An annular protrusion 82 is formed along the periphery of the through-hole 81 on the output side of the rotor 22. On the outer peripheral surface of the annular protrusion 82, fitting recesses 83 that fit into predetermined portions of the retainer 32 are formed at regular intervals around the central axis of the through hole 81, for example. Further, a spring locking groove 84 for locking a part of the centering spring 31 is formed on the inner peripheral surface of the annular protrusion 82 between, for example, adjacent fitting recesses 83 and around the center axis of the through hole 81. Are formed at equal intervals.

  On the other hand, an annular recess 85 along the periphery of the input rotation member 5 inserted through the through hole 81 is provided concentrically on the surface on the input side of the rotor 22. The annular projection 73 of the housing member 21 can be moved along the annular recess 85. The surface on the input side of the rotor 22 is opposed to the inner peripheral surface of the bottom wall 21 </ b> B of the housing member 21.

  The space of the annular recess 85 is filled with the viscous fluid 23 (FIG. 1), and the rotor 22 is provided with an air flow passage 86 for releasing the air remaining in the viscous fluid 23 to the outside. One end of the air flow passage 86 is connected to a predetermined portion of the annular recess 85, and the other end of the air flow passage 86 is connected to a predetermined portion of the surface on the output side of the rotor 22.

  FIG. 7 is a perspective view showing the centering spring 31. As shown in FIG. 7, the centering spring 31 is an elastic member called a torsion spring, and includes a winding portion 91, a first braking terminal 92 connected to one end side of the winding portion 91, and the winding portion 91. And a second braking terminal 93 connected to the other end side. These winding part 91, the 1st braking terminal 92, and the 2nd braking terminal 93 are comprised with one wire.

  The centering spring 31 is inserted into the input rotating member 5 together with the rotor 22. When the input rotating member 5 rotates, the first braking terminal 92 in the centering spring 31 is locked to the spring locking portion 55 of the input rotating member 5, and the second braking terminal 93 is locked to the spring locking groove 84 of the rotor 22. Stopped. That is, the centering spring 31 connects the input rotating member 5 and the rotor 22 so that the rotor 22 rotates when the input rotating member 5 rotates.

  8 is a perspective view showing the retainer 32 from the output side, and FIG. 9 is a perspective view showing the retainer 32 from the input side. As shown in FIGS. 8 and 9, the retainer 32 is a cylindrical member and has a through hole 101. A plurality of pockets 102 and slits 103 are formed at the output side end of the retainer 32.

  The pocket 102 is a columnar cutout that accommodates, for example, a cylindrical roller 104 (FIG. 1) that is a torque transmission member, and is formed at predetermined intervals along the circumferential direction. The opening diameter of the pocket 102 is slightly larger than the diameter of the roller 104. The slit 103 is a groove-shaped notch that accommodates the leaf spring 105 (FIG. 1), and is formed so as to communicate with portions facing each other in the circumferential direction of each pocket 102 and outward from the portion. The rollers 104 are arranged at predetermined intervals along the circumferential direction between the outer peripheral surface of the inner ring 41 and the inner peripheral surface of the outer ring 42 (FIGS. 1 and 2). On the other hand, at the input side end of the retainer 32, fitting convex portions 106 that fit into the fitting concave portions 83 of the rotor 22 are formed at equal intervals around the central axis of the through hole 101, for example.

  As shown in FIGS. 1 and 2, the inner ring 41 is an annular member that rotates in conjunction with the input rotation member 5. The inner peripheral surface of the inner ring 41 is formed in an outer shape of a hexagonal column, for example, and six side portions of the hexagonal column are fitted into an inner ring fitting groove 56 formed in the second intermediate portion 53 of the input rotating member. Thus, the inner ring 41 is fixed to the second intermediate portion 53. A plurality of cam surfaces 111 are formed on the outer peripheral surface of the inner ring 41. In this embodiment, the outer peripheral surface of the inner ring 41 is formed in the outer shape of a hexagonal column, and the outer surface corresponding to the six side surfaces of the hexagonal column is the cam surface 111. The outer ring 42 is an annular member having an inner diameter larger than the outer diameter of the inner ring 41 and is arranged concentrically with the inner ring 41.

  The output rotating member 6 is a cylindrical member and has a through hole 121. The outer ring 42 is fitted into the through hole 121 and fixed. A snap fit 57 formed on the output side end 54 of the input rotary member 5 is hooked on the peripheral portion of the through hole 121 at the output side end of the output rotary member 6.

  Next, an assembly example of the reverse input cutoff clutch 1 will be described.

  As shown in FIGS. 1 and 2, first, the inner ring 41 is fixed to the second intermediate portion 53 of the input rotating member 5, and the outer ring 42 is fixed to the through hole 121 of the output rotating member 6. Further, the viscous fluid 23 is filled in the space of the annular recess 85 in the rotor 22. Further, the rollers 104 are accommodated in the respective pockets 102 of the retainer 32, and the leaf springs 105 are accommodated in the respective slits 103 of the retainer 32, whereby the plurality of rollers 104 are held by the retainer 32.

  Next, the housing member 21, the rotor 22, the centering spring 31, the retainer 32, and the output rotating member 6 are sequentially inserted into the input rotating member 5, and the snap fit 57 of the input rotating member 5 is connected to the output side of the output rotating member 6. Hooked to the end.

  When the reverse input shut-off clutch 1 is assembled in this way, each component inserted into the input rotation member 5 is pressed by the snap fit 57 and is prevented from being removed by the input side end 51 of the input rotation member 5. It can be stopped. As a result, the damper mechanism 2, the lock release mechanism 3, and the lock mechanism 4 are not separated, and each component inserted through the input rotation member 5 is restricted from moving in the longitudinal direction of the input rotation member 5.

  When the reverse input cutoff clutch 1 is assembled, as shown in FIG. 10, the viscous fluid 23 packed in the space of the annular recess 85 of the rotor 22 is inserted into the annular recess 85 of the housing member 21. It is enclosed between the convex part 73 and the annular recessed part 85. FIG.

  Examples of the viscous fluid 23 include oil and grease. When the viscous fluid 23 is grease, since the grease is in a semi-fixed state or a plastic state, it does not flow outside even if an oil seal is not provided. Therefore, the viscous fluid 23 is preferably grease. In addition, it is especially preferable when the grease which uses a silicone type synthetic oil as a base oil, and makes the ratio of a thickener 3-30% is used.

  When the centering spring 31 is inserted, at least a part of the first braking terminal 92 connected to one end side of the winding portion 91 in the centering spring 31 is formed on the periphery of the first intermediate portion 52 in the input rotation member 5. It is arranged in the space around the spring locking portion 55 to be made. Further, at least a part of the second braking terminal 93 connected to the other end side of the winding portion 91 is disposed in a spring locking groove 84 formed on the inner peripheral surface of the annular protrusion 82 in the rotor 22. .

  Next, the operation of the reverse input cutoff clutch 1 will be described.

  The reverse input cutoff clutch 1 is incorporated in a predetermined device. That is, at least the attachment portion 71 of the housing member 21 in the reverse input cutoff clutch 1 is fixed to a predetermined part of the device, the input rotation member 5 is connected to the input mechanism of the device, and the output rotation member 6 is connected to the output mechanism of the device. Is done.

  When the input rotation member 5 is rotated in the first rotation direction by the input mechanism of the device, the first braking terminal 92 of the centering spring 31 inserted through the input rotation member 5 comes into contact with the spring locking portion 55, and the centering spring 31. Rotates.

  When the centering spring 31 rotates, the second braking terminal 93 of the centering spring 31 comes into contact with the groove wall of the spring locking groove 84 of the rotor 22 and the rotor 22 rotates. Since the fitting convex portion 106 of the retainer 32 is fitted in the fitting concave portion 83 of the rotor 22 and the rotor 22 and the retainer 32 are coupled, the retainer 32 rotates with the rotor 22 when the rotor 22 rotates. .

  By the way, the housing member 21 disposed on the input side of the rotor 22 is fixed to a predetermined part of the device via the mounting portion 71 of the housing member 21, so that it does not rotate with the input rotating member 5. For this reason, when the rotor 22 rotates, the rotor 22 receives the shear resistance of the viscous fluid 23 enclosed between the annular convex portion 73 of the housing member 21 and the annular concave portion 85 of the rotor 22. When this shear resistance becomes larger than the elastic force acting on the first braking terminal 92 and the second braking terminal 93 of the centering spring 31, the rotational speed of the rotor 22 becomes slower than the rotational speed of the input rotating member 5, and the first The brake terminal 92 and the second brake terminal 93 are deformed so as to bend in the rotation direction.

  When the rotational speed of the rotor 22 becomes slower than the rotational speed of the input rotary member 5, the rotation of the retainer 32 coupled to the rotor 22 also slows, and the retainer 32 and the inner ring 41 fixed to the input rotary member 5 A difference occurs in the rotation speed. As a result, as shown in FIG. 11, a change in the relative positional relationship between the inner ring 41 and the outer ring 42 results in a wedge-shaped constriction NP in which the space between the outer peripheral surface of the inner ring 41 and the inner peripheral surface of the outer ring 42 is narrowed. The roller 104 is engaged so as to bite and is locked. As a result, the roller 104 transmits input torque from the inner ring 41 to the outer ring 42, and the outer ring 42 rotates together with the inner ring 41.

  If the shape of the outer peripheral surface of the inner ring 41 is varied, the other rollers 104 are engaged with the narrowed portion NP even though some of the rollers 104 are locked to the narrowed portion NP. There may be cases where it has not stopped. Even in such a case, one of the leaf springs 105 urging the roller 104 from both sides in the circumferential direction is bent, so that the retainer 32 moves to the narrowed portion NP and is locked to the narrowed portion NP. The other roller 104 that has not been engaged is locked to the narrowed portion NP.

  On the other hand, when the rotation of the input rotating member 5 is stopped by the input mechanism of the device, the shear resistance of the viscous fluid 23 enclosed between the annular convex portion 73 of the housing member 21 and the annular concave portion 85 of the rotor 22 is reduced. For this reason, the shear resistance is weaker than the elastic force acting on the first braking terminal 92 and the second braking terminal 93 of the centering spring 31. When the elastic force is weaker than the shear resistance, the first braking terminal 92 and the second braking terminal 93 that have been deformed are restored, and the retainer 32 moves in the second rotational direction opposite to the first rotational direction. Is done.

  As a result, the relative positional relationship between the inner ring 41 and the outer ring 42 changes, so that the roller 104 is detached from the narrowed portion NP, and the lock is released. As a result, the roller 104 returns to the reference position (centering position) where it does not mesh with the constriction NP. As a result, the reverse input torque from the output rotating member 6 is idled without being transmitted to the input side.

  As described above, the reverse input cutoff clutch 1 of the present embodiment is configured such that the rotor 22 connected by the centering spring 31 can be locked by being sheared while the unlocking mechanism by the centering spring 31 is utilized. The

  Since the centering spring 31 is disposed on the opposite side of the rotor 22 to the side on which the housing member 21 is fitted via the viscous fluid 23, the centering spring 31 does not receive the shear resistance of the viscous fluid 23. Accordingly, the trade-off relationship as described above does not occur between the locked state and the unlocked state as in the reverse input cutoff clutch of Patent Document 1. For this reason, even if the elastic force of the centering spring 31 is not strictly defined, the clutch operation can be executed without hindrance. Thus, the reverse input cutoff clutch 1 that can smoothly execute the clutch operation is realized.

  In the case of this embodiment, an annular convex portion 73 is provided concentrically on the surface of the housing member 21 facing the rotor 22, and an annular concave portion 85 is provided concentrically on the surface of the rotor 22 facing the housing member 21. It is done. The viscous fluid 23 is sealed between the annular convex portion 73 and the annular concave portion 85. Therefore, the shear resistance of the viscous fluid 23 applied to the rotor 22 can be increased as compared with the case where the annular convex portion 73 and the annular concave portion 85 are not provided concentrically. As a result, it is possible to quickly shift the clutch operation.

  Further, when grease is used as the viscous fluid 23, the grease has a characteristic (thixotropic property) that the shear resistance does not increase when the rotational speed per unit time increases to some extent. For this reason, it is possible to prevent excessive torque transmission without providing the braking member or the like of Patent Document 1 as compared with the case where oil or the like whose shear resistance continues to increase is used as the viscous fluid 23.

  Although the embodiment has been described above as an example, the present invention is not limited to the reverse input cutoff clutch 1 of the above embodiment, and various components of the reverse input cutoff clutch 1 are appropriately set within the scope of the present invention. It can be deformed.

For example, in the above embodiment, the annular convex portion 73 is provided on the surface of the housing member 21 that faces the rotor 22, and the annular concave portion 85 is provided on the surface of the rotor 22 that faces the housing member 21. However, the annular recess 85 may be provided on the surface of the housing member 21 that faces the rotor 22, and the annular protrusion 73 may be provided on the surface of the rotor 22 that faces the housing member 21. In the housing member 21 and the rotor 22, an annular recess 85 is provided concentrically along one of the pair of surfaces facing each other, and the annular protrusion 73 is provided on the other of the pair of surfaces. May be.
Moreover, it replaces with the cyclic | annular convex part 73, and the rod-shaped convex part may be provided so that it may protrude from the internal peripheral surface of the bottom wall 21B. That is, it is only necessary to provide a convex portion that can move along the annular concave portion 85.
Furthermore, the annular convex portion 73 and the annular concave portion 85 may be omitted, and a housing portion that covers the surface of the rotor 22 that faces the housing member 21 via the viscous fluid 23 may be applied. In short, any housing member into which the rotor 22 is fitted via the viscous fluid 23 may be used.

  Moreover, in the said embodiment, while each component penetrated by the input rotation member 5 is pushed by the snap fit 57, it is restrained and stopped by the input side edge part 51 of the said input rotation member 5, and the said component was fixed. . However, both or one of the snap fit 57 and the input side end 51 may be changed to a retaining ring. Moreover, each part penetrated by the input rotation member 5 may be fixed by providing a through-hole in the predetermined site | part of the input rotation member 5, and inserting a stop pin in the through-hole.

  Moreover, in the said embodiment, although the housing member 21 and the rotor 22 were made into the different body, these may be shape | molded integrally. Moreover, although the input rotation member 5 and the inner ring | wheel 41 were made into the different body, these may be shape | molded integrally. Furthermore, although the output rotation member 6 and the outer ring 42 are separated, they may be integrally formed.

  In the above embodiment, the cam surface 111 is formed on the outer peripheral surface of the inner ring 41, and the narrowed portion NP is provided between the outer peripheral surface of the inner ring 41 and the inner peripheral surface of the outer ring 42. However, the cam surface 111 may be formed on the inner peripheral surface of the outer ring 42, and a narrowed portion may be provided between the inner peripheral surface of the outer ring 42 and the outer peripheral surface of the inner ring 41. A pocket having a cam surface may be provided on the inner peripheral surface of the outer ring 42 or the outer peripheral surface of the inner ring 41.

  In the above embodiment, the leaf spring 105 is separated from the retainer 32. However, the leaf spring 105 may be formed integrally with the retainer 32. In this case, the slit 103 of the roller 104 can be omitted. Each of the leaf spring 105 and the slit 103 may be omitted.

  In the above embodiment, a bidirectional clutch that can rotate the inner ring 41 clockwise and counterclockwise is applied. However, a one-way clutch that can rotate the inner ring 41 only in one direction clockwise or counterclockwise may be applied. When such a one-way clutch is applied, for example, the range in which the retainer 32 and the inner ring 41 can be moved is halved on one side, and the number of leaf springs 105 is halved.

In the above embodiment, the input shaft member 5 has a rod shape, and the outer ring 42 is fixed to the outer peripheral surface of the input shaft member 5. However, the input shaft member may be tubular, and the outer ring may be fixed to the inner peripheral surface of the input shaft member.
For example, the reverse input cut-off clutch shown in FIG. 12 in which the same reference numerals are assigned to the parts corresponding to FIG. The input shaft member 110 of the reverse input shut-off clutch includes an outer cylinder 111 and a gear 112. When the rotation axes of the outer cylinder 111 and the gear 112 coincide with each other, the outer cylinder 111 and the gear 112 have a knock pin 113. It is fixed by. The inner diameter of the outer cylinder 111 is substantially the same as the outer diameter of the outer ring 42, and a groove or a through-hole is formed in a predetermined part of the outer cylinder 111 to provide the spring locking portion 55.
On the other hand, the output rotation member 120 of the reverse input shut-off clutch is a columnar shaft member, and the outer peripheral surface on one end side of the output rotation member 120 is cut out to have a semicircular cross section. Further, the inner ring 130 of the reverse input cutoff clutch is a hollow rod member, and a protruding portion 131 called a D-cut is formed on one end side of the inner surface of the inner ring 130. The output rotating member 120 inserted into the inner ring 130 is fixed at the cutout portion 121 by the protrusion 131.
As an assembly example of such a reverse input cutoff clutch, first, the inner ring 130 is inserted into the output rotating member 120, and the outer ring 42 is fixed in the outer cylinder 111 of the input shaft member 110. Next, the housing member 21, the rotor 22, the centering spring 31, the retainer 32, and the input shaft member 110 are sequentially inserted into the inner ring 130. Thereafter, the stoppers 140 are fitted into the inner ring 130 from both ends of each member inserted through the inner ring 130, and the respective parts are fixed.
In the example shown in FIG. 12, the rotor 22 and the retainer 32 are integrally formed. However, the rotor 22 and the retainer 32 of the above embodiment may be formed separately. Moreover, the rotor 22 and the retainer 32 of the said embodiment may be shape | molded integrally.

  The reverse input cutoff clutch of the present invention can be used in the case where it is incorporated in a device that transmits input torque applied from the input side to the output side and blocks the reverse input torque applied from the output side not to be transmitted to the input side. There is.

DESCRIPTION OF SYMBOLS 1 ... Reverse input interruption | blocking clutch 2 ... Damper mechanism 3 ... Lock release mechanism 4 ... Lock mechanism 5 ... Input rotation member 6 ... Output rotation member 21 ... Housing member 22 ...・ Rotor 23 ... Viscous fluid 31 ... Centering spring 32 ... Retainer 41 ... Inner ring 42 ... Outer ring

Claims (6)

An input rotating member fixed to an inner ring or an outer ring arranged concentrically with the inner ring;
A torque transmission member disposed between an inner peripheral surface of the outer ring and an outer peripheral surface of the inner ring;
A retainer for holding the torque transmission member;
A rotor that rotates in conjunction with the retainer;
A housing member that is fixed so as not to rotate even when the input rotating member rotates, and in which the rotor is fitted via a viscous fluid;
The rotor is disposed on a side opposite to the side on which the housing member is fitted via the viscous fluid, and the rotor rotates in the first rotation direction when the input rotation member rotates in the first rotation direction. An elastic member connecting the input rotating member and the rotor;
With
When the rotational speed of the retainer interlocked with the rotor is slower than the rotational speed of the inner ring or the outer ring fixed to the input rotating member due to the shear resistance of the viscous fluid applied to the rotor, The torque transmission member is locked to the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring;
The elastic member that is deformed due to the rotation speed of the retainer being slower than the rotation speed of the inner ring or the outer ring is restored against the shear resistance so that the first rotation direction is opposite to the first rotation direction. When the retainer is moved in two rotation directions, the torque transmission member in the locked state is released ,
The elastic member includes a winding part wound around a rotation axis of the input rotating member, a first braking terminal connected to one end side of the winding part and extending in a radial direction of the winding part, A torsion spring having a second braking terminal connected to the other end of the winding portion and extending in a radial direction of the winding portion;
The input rotation member is provided with a spring locking portion that protrudes in the rotation axis direction of the input rotation member and that locks the first braking terminal,
The rotor is provided with a spring locking groove that is recessed in the rotation axis direction of the input rotation member and that locks the second braking terminal,
The reverse input cutoff clutch , wherein the spring locking groove is covered with the retainer in the direction of the rotation axis of the input rotation member . One of a pair of surfaces facing each other in the housing member and the rotor is concentrically provided around the input rotation member, and the other of the pair of surfaces moves along the annular recess. The reverse input cutoff clutch according to claim 1, wherein a possible convex portion is provided, and the viscous fluid is sealed between the annular concave portion and the convex portion. The reverse input blocking clutch according to claim 2, wherein the convex portion is an annular convex portion around the input rotation member, and the annular convex portion is provided concentrically. 4. The reverse input blocking clutch according to claim 3, wherein grooves sandwiched between annular convex portions provided concentrically are communicated with each other, and a part of the annular concave portion is communicated with the outside. The reverse input cutoff clutch according to claim 1, wherein the viscous fluid is grease. The grease is reverse input blocking clutch according to claim 5, characterized in that the silicone-based synthetic oil as the base oil, and 3% to 30% the proportion of thickener.

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