WO2016190206A1

WO2016190206A1 - Reverse input blocking clutch

Info

Publication number: WO2016190206A1
Application number: PCT/JP2016/064849
Authority: WO
Inventors: 高田　声一
Original assignee: Ntn株式会社
Priority date: 2015-05-27
Filing date: 2016-05-19
Publication date: 2016-12-01

Abstract

Provided is a reverse input blocking clutch in which: when an input torque is applied simultaneously to a first input shaft (1) and a second input shaft (2), a cam receiver (5) that has been slidably fit into the inner periphery of a housing (7) rotates integrally with the first input shaft (1), an eccentric cam (4) rotates integrally with the second input shaft (2), and a spacer (6) revolves between the cam receiver (5) and the eccentric cam (4), whereby an output shaft (3) rotates integrally with the eccentric cam (4); and, in response to a reverse input torque, revolving motion of the spacer (6), pressed by the eccentric cam (4) which is integrated with the output shaft (3), is restricted by the housing (7) via the cam receiver (5), whereby the output shaft (3) does not rotate.

Description

Reverse input cutoff clutch

The present invention relates to a reverse input cutoff clutch that transmits rotation of an input side member to an output side member when input torque is applied, and prevents the input side member from rotating in response to reverse input torque.

The reverse input cutoff clutch transmits the rotation to the output side member when an input torque is applied to the input side member, and prevents the input side member from rotating when the reverse input torque is applied to the output side member. It is to make. There is a type of the reverse input cutoff clutch that locks the output side member against the reverse input torque (hereinafter, this method is referred to as “lock type”) (for example, see Patent Document 1 below).

The lock-type reverse input shut-off clutch described in Patent Document 1 is configured such that the input side member rotates with a slight angular delay between the input side member and the output side member that rotate about the same axis. Torque transmission means for transmitting to the member is provided, a fixed outer ring having a cylindrical surface on the inner peripheral side is arranged on the radially outer side of the output side member, and a plurality of cam surfaces are provided on the outer peripheral surface of the output side member. A wedge-shaped space gradually narrowing on both sides in the circumferential direction is formed between the inner peripheral cylindrical surface and each cam surface of the output side member, and a pair of rollers and the rollers are pushed into the narrow portion of the wedge-shaped space in each wedge-shaped space. In addition to incorporating a spring, a cage having pillar portions inserted on both sides in the circumferential direction of each wedge-shaped space is connected so as to rotate integrally with the input side member.

In this reverse input shut-off clutch, each roller is pushed into the narrow portion of the wedge-shaped space by the elasticity of the spring. By engaging the side member, the output side member is locked, and rotation is not transmitted from the output side member to the input side member.

On the other hand, when an input torque is applied to the input side member, the pillar portion of the cage that rotates integrally with the input side member pushes the roller on the rear side in the rotation direction against the large side of the wedge-shaped space against the elasticity of the spring. Thus, after the engagement of the roller with the fixed outer ring and the output side member is released and the output side member is released from the locked state, rotation is transmitted from the input side member to the output side member by the torque transmitting means. (At this time, the roller on the front side in the rotational direction moves relative to the wide portion of the wedge-shaped space, so that it does not engage with the fixed outer ring and the output side member).

JP-A-2-271116

In the lock-type reverse input shut-off clutch of Patent Document 1, a plurality of cam surfaces are provided on the outer peripheral surface of the output side member, and a pair of wedge-shaped spaces between these cam surfaces and the inner peripheral cylindrical surface of the fixed outer ring are provided. Since a roller and a spring that pushes the roller into the narrow part of the wedge-shaped space are incorporated, complicated processing (formation of the cam surface) is required when manufacturing the output side member, and when assembling, it is compact into multiple wedge-shaped spaces There is a problem that it takes time and effort to incorporate rollers and springs as parts.

In addition, when transmitting rotation from the input side member to which the input torque is applied to the output side member, the column portion of the cage that rotates integrally with the input side member pushes the roller on the rear side in the rotation direction to lock the output side member. Since the pin of the input side member pushes the output side member to transmit the rotation to the output side member after releasing the clearance, the clearance between the pillar portion of the cage and the roller at the time of assembly is the gap between the pin and the output side member. It is necessary to design the dimensions of each component so as to be smaller than the gap, and this tends to be a design constraint. And since there is a time difference from when the cage releases the locked state of the output side member until the input side member starts to transmit rotation to the output side member, the output side member and the input side member immediately after the lock release. In some cases, it may rotate.

In addition, when the output side member is locked against the reverse input torque, a large surface pressure acts on the roller that is engaged between the cam surface of the output side member and the inner peripheral cylindrical surface of the fixed outer ring. The roller cannot be formed of a soft material, and it is difficult to reduce the weight of the entire clutch by using resin or the like as the material of the roller.

Therefore, an object of the present invention is to provide a lock-type reverse input cutoff clutch that is easy to design, manufacture, and assemble parts and that can be easily reduced in weight.

In order to solve the above problems, the reverse input cutoff clutch of the present invention has a first input shaft, a second input shaft, and an output shaft arranged on the same axis, and the second input shaft and the output shaft are arranged between the second input shaft and the output shaft. A cylindrical eccentric cam having an eccentric axis parallel to the axis is provided, a cylindrical cam receiver having the same axis as the axis is provided on the first input shaft, and the cam receiver has the same axis as the eccentric cam. An eccentric hole is formed, and the eccentric cam is inserted into the eccentric hole, and the cam receiver is rotatably fitted to the inner peripheral cylindrical surface of the fixing member, and the inner peripheral surface of the eccentric hole of the cam receiver and the eccentric cam A cylindrical spacer is fitted between the outer peripheral surface of the first input shaft so as to be rotatable relative to the outer peripheral surface of the first input shaft. And input torque on the second input shaft at the same time When it is obtained, the cam receiver rotates integrally with the first input shaft, the eccentric cam rotates integrally with the second input shaft, and the spacer revolves between the cam receiver and the eccentric cam. Thus, when the output shaft rotates integrally with the eccentric cam and a reverse input torque is applied to the output shaft, a spacer pushed by the eccentric cam integral with the output shaft is fixed to the fixing member via the cam receiver. The output shaft does not rotate by restricting the revolution turning motion.

According to the above configuration, except for the outer shape of the fixing member and the swivel support mechanism, it can be formed in a cylindrical shape, and complicated processing such as cam surface formation in the conventional lock-type reverse input cutoff clutch is not required at the time of manufacture. Therefore, it becomes easy to manufacture parts and ensure dimensional accuracy, and since there are no small rollers and springs incorporated in a conventional clutch, the number of parts is small and assembly is easy. In addition, since there is no design restriction of ensuring the size relationship between a plurality of internal gaps in a conventional clutch, it is easy to design parts. In addition, the parts that lock against reverse input torque have a larger diameter than conventional clutch rollers and the surface pressure is reduced. Therefore, the weight of the entire clutch can be reduced by using resin or the like as the material of the parts. Is also possible.

As means for simultaneously applying input torque to the first input shaft and the second input shaft, the second input shaft is fitted into the inner periphery of the first input shaft so as to be relatively rotatable, and the lengths of both the input shafts are the same in the longitudinal direction. Provided with a concave portion at each position, and provided with a convex portion that is inserted into the concave portion of both input shafts with a clearance in the rotational direction and can be engaged with both input shafts at the input member to which the input torque is input, or It is advisable to adopt a structure in which the eccentric hole of the cam receiver is provided with a small-diameter hole portion into which the eccentric cam is inserted with a gap without passing through the spacer. Here, a clearance in the rotational direction is provided between the concave portion of both input shafts and the convex portion of the input member, or a clearance is provided between the small diameter hole portion of the eccentric hole of the cam receiver and the eccentric cam. Even if the second input shaft rotates slightly together with the output shaft due to backlash inside the clutch before the output shaft is locked against the reverse input torque, the first input shaft does not rotate together, This is to ensure that the output shaft is locked.

Further, the eccentric cam can be divided into an input side eccentric cam integrated with the second input shaft and an output side eccentric cam integrated with the output shaft. In this way, even if the output shaft and the output-side eccentric cam rotate slightly due to backlash inside the clutch before the output shaft is locked against the reverse input torque, each input shaft rotates together. Is unlikely to occur. Therefore, as means for simultaneously applying input torque to the first input shaft and the second input shaft, the input side eccentric cam is fixed to the spacer in the eccentric hole of the cam receiver, or the input shaft is fixed to each other with a screw. What provided the small diameter hole part inserted without going through can be employ | adopted.

Furthermore, when the eccentric cam is divided as described above, a bearing may be provided between the output-side eccentric cam and the spacer. Even if the output shaft and the output side eccentric cam rotate slightly with respect to the reverse input torque, it becomes difficult for the spacer to revolve, and it is possible to more reliably prevent the rotation of each input shaft via the spacer. is there.

As described above, the reverse input cut-off clutch of the present invention eliminates complicated processing at the time of manufacturing parts and reduces the number of parts as compared with the conventional lock type, and is easy to design, manufacture and assemble. In addition, since the surface pressure generated in a component that locks when a reverse input torque is applied, the weight of the entire clutch can be reduced by employing a resin or the like as the material of the component. In terms of operation, since the output shaft also rotates simultaneously with the rotation of the first input shaft and the second input shaft, there is no risk of the output shaft rotating regardless of the input side, and the output shaft can be smoothly moved. Rotational transmission can be performed.

Transverse plan view of the reverse input cutoff clutch of the first embodiment 1 is an exploded perspective view of FIG. Sectional view along line III-III in FIG. Sectional drawing explaining clutch operation corresponding to FIG. 3A Transverse plan view showing a modification of the first embodiment Transverse plan view of the reverse input cutoff clutch of the second embodiment Transverse plan view showing a modification of the second embodiment Transverse plan view of the reverse input cutoff clutch of the third embodiment Transverse plan view showing a modification of the third embodiment Transverse plan view showing another modification of the third embodiment Cross-sectional plan view of the reverse input cutoff clutch of the fourth embodiment

Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 to 3B show a first embodiment. The reverse input cutoff clutch includes a cylindrical first input shaft 1, a second input shaft 2 slidably fitted on the inner periphery of the first input shaft 1, and an extension line on one end side of the second input shaft 2. An output shaft 3 disposed in the cylinder, a cylindrical eccentric cam 4 integrally formed between the second input shaft 2 and the output shaft 3, and a cylindrical cam integrally formed on one end side of the first input shaft 1. A cylindrical spacer 6 slidably fitted between the receiver 5, the inner peripheral surface of the cam receiver 5 and the outer peripheral surface of the eccentric cam 4, and a cylindrical surface on which the cam receiver 5 is slidably fitted on the inner periphery. The housing (fixing member) 7 having the above and the turning support mechanism 8 that supports the spacer 6 so that it cannot rotate and can revolve between the spacer 6 and the housing 7 are basically configured.

The housing 7 has a lid portion 7a for passing the output shaft 3 on one end side thereof and a plurality of mounting portions 7b protruding from the outer periphery, and a lid 9 for retaining the cam receiver 5 is fitted on the inner periphery of the other end side. ing. A circle constituting a part of the swivel support mechanism 8 is disposed at a position sandwiched in the axial direction between the lid portion 7a of the housing 7 and an inward flange-shaped connecting portion 6a provided at one end of the spacer 6. A plate-like connecting member 10 is arranged.

An input gear (input member) 11 is slidably fitted on the outer periphery of the protruding portion from the lid 9 of the housing 7 of the first input shaft 1, and the outer periphery of the protruding portion from the housing lid portion 7 a of the output shaft 3. The output gear 12 is fitted and fixed. And the 1st input shaft 1 and the 2nd input shaft 2 are each provided with the recessed

part

1a, 2a in the same position of a longitudinal direction, and these recessed

parts

1a, 2a are provided in the inner periphery of the input gear 11. The convex portion 11a is inserted with a gap in the rotational direction. As a result, when input torque is input to the input gear 11, the convex portion 11 a is engaged simultaneously with both the

input shafts

1 and 2, and the input torque is applied simultaneously to both the

input shafts

1 and 2. Yes. In addition, although the recessed part of each input shaft was notched in the example of FIG. 1 and FIG. 2, you may form in a hole shape.

The protruding portion of the second input shaft 2 from the first input shaft 1 and the outer portion of the output shaft 3 from the mounting position of the output gear 12 are rotatably supported by bearings 13. That is, this reverse input cutoff clutch has only the

input shafts

1 and 2 and the output shaft 3 projecting from the housing 7, and the input gear 11 is attached to the first input shaft 1 and the output gear 12 is attached to the output shaft 3, respectively. Since the second input shaft 2 and the output shaft 3 are supported by the bearings 13, the structure can be easily incorporated into the machine and transported.

The first input shaft 1, the second input shaft 2, the output shaft 3 and the housing 7 are arranged on the same axis, and the cam receiver 5 integrated with the first input shaft 1 is also the same axis as the axis of the input shaft 1. have. On the other hand, the eccentric cam 4 integrated with the second input shaft 2 and the output shaft 3 has an eccentric axis parallel to the axes of the second input shaft 2 and the output shaft 3. The cam receiver 5 is formed with an eccentric hole 5a having the same axis as the eccentric cam 4 and into which the spacer 6 and the eccentric cam 4 are inserted.

Here, the axial length of the sliding portion between the cam receiver 5 and the housing 7 and the axial length of the sliding portion between the eccentric cam 4 and the spacer 6 have the same dimensions. The balance of the rotational movement is good and vibration is less likely to occur.

Although not shown in the figure, one end face of the cam receiver 5 is provided with a marking indicating the position farthest from the axis of the first input shaft 1 in the inner periphery of the eccentric hole 5a. The end face is marked with a position indicating the position farthest from the axis of the second input shaft 2 and the output shaft 3 in the outer periphery. That is, when the clutch is assembled, the eccentric cam 4 is incorporated into the cam receiver 5 with the markings of the cam receiver 5 and the eccentric cam 4 facing each other in the radial direction, whereby the assembling work can be performed efficiently. ing.

The swivel support mechanism 8 includes first concave and convex fitting portions that extend in the radial direction of the spacer 6 and are slidably fitted to each other on the axially opposed surfaces of the connecting member 10 and the connecting portion 6a of the spacer 6. And a second concavo-convex fitting that extends in a direction orthogonal to the first concavo-convex fitting portion and is slidably fitted to each other in the axially opposed surfaces of the connecting member 10 and the lid portion 7a of the housing 7 A part is provided.

Here, the first concavo-convex fitting portion includes a convex portion 6b formed so as to extend in the radial direction on an outer surface of the connecting portion 6a of the spacer 6 (an axially facing surface with the connecting member 10), and a connecting member. 10 is formed on the inner side surface (surface facing the connecting portion 6a of the spacer 6 in the axial direction), and the convex portion 6b of the spacer 6 is slidably fitted therein.

The second concave-convex fitting portion is a convex formed on the outer side surface of the connecting member 10 (the axially facing surface with the lid portion 7a of the housing 7) so as to extend in a direction perpendicular to the concave portion 10a on the inner side surface. The portion 10b is formed on the inner surface of the lid portion 7a of the housing 7 (the surface facing the connecting member 10 in the axial direction), and the convex portion 10b of the connecting member 10 is slidably fitted therein.

The rotation support mechanism 8 supports the spacer 6 so that it cannot rotate and revolve with respect to the housing 7 as described above. The connecting portion 6a and the connecting member 10 of the spacer 6 are respectively provided with

center holes

6c and 10c through which the output shaft 3 passes. The

holes

6c and 10c are connected to the connecting member 10 at the same time as the spacer 6 revolves. Is formed in a size that does not interfere with the output shaft 3 when moving in parallel.

The turning support mechanism is not limited to that of the above-described embodiment, and any mechanism may be used as long as it has a function of supporting the spacer so that it cannot rotate and can revolve between the spacer and a fixing member such as a housing. .

This reverse input shut-off clutch has the above-described configuration. When the clockwise input torque is simultaneously applied to the first input shaft 1 and the second input shaft 2 via the input gear 11 in the state shown in FIG. The cam receiver 5 slidably fitted on the inner peripheral cylindrical surface of the first input shaft 1 rotates integrally with the first input shaft 1, and the eccentric cam 4 integrated with the second input shaft 2 rotates eccentrically. At this time, as shown in FIG. 3B, the spacer 6 is guided by the connecting member 10 and moved upward, and at the same time, the connecting member 10 is guided by the lid portion 7a of the housing 7 and moved rightward. The spacer 6 revolves clockwise between the cam receiver 5 and the eccentric cam 4 without rotating with respect to the housing 7 and does not hinder the rotation of the

input shafts

1 and 2. Therefore, the output shaft 3 integrated with the eccentric cam 4 also rotates. Since the output shaft 3 rotates simultaneously with the rotation of the first input shaft 1 and the second input shaft 2 in this way, there is no fear that the output shaft 3 rotates regardless of the input side as in the conventional lock type. The rotation transmission to the output shaft 3 can be performed smoothly.

On the other hand, when a reverse input torque is applied to the output shaft 3 via the output gear 12, the spacer 6 pushed by the eccentric cam 4 integral with the output shaft 3 performs a revolving turning motion on the housing 7 via the cam receiver 5. By being regulated, the output shaft 3 is locked and does not rotate, and the first input shaft 1 integral with the cam receiver 5 and the second input shaft 2 integral with the eccentric cam 4 also do not rotate.

Here, even if the eccentric cam 4 and the second input shaft 2 are slightly rotated together with the output shaft 3 due to backlash inside the clutch before the output shaft 3 is locked against the reverse input torque, Since a clearance in the rotational direction is provided between the

concave portions

1a and 2a of the

shafts

1 and 2 and the convex portion 11a of the input gear 11, the first input shaft 1 does not rotate together, and the output shaft 3 Locks securely.

And this reverse input shut-off clutch configuration does not require complicated processing such as cam surface formation at the time of manufacture, compared to the conventional lock type incorporating multiple small rollers and springs. Accuracy is easy to ensure, and the number of parts is small and assembly is easy. Also, because there are fewer design restrictions than the conventional one, it is easier to design the parts, and the surface pressure of the parts to be locked against the reverse input torque is small. The weight of the entire clutch can also be reduced.

FIG. 4 shows a modification in which two bearings 14 are provided between the first input shaft 1 and the second input shaft 2 of the first embodiment. In this modification, since the first input shaft 1 is not in direct contact with the second input shaft 2, when the second input shaft 2 is slightly rotated integrally with the output shaft 3 with respect to the reverse input torque, The first input shaft 1 is less likely to rotate together with the example of FIGS. 1 to 3B, and the output shaft 3 can be locked more reliably.

FIG. 5 shows a second embodiment. In this embodiment, the means for applying input torque to the first input shaft 1 and the second input shaft 2 simultaneously is changed based on the first embodiment.

That is, in the second embodiment, the input gear 11 is fitted and fixed to the outer periphery of the first input shaft 1, and the

concave portions

1 a and 2 a of the

input shafts

1 and 2 and the convexity of the input gear 11 of the first embodiment. The part 11a is eliminated. The spacer 6 is slightly shortened in the axial direction, and a small-diameter hole portion 5 b into which the eccentric cam 4 is inserted with a gap without the spacer 6 is provided in the eccentric hole 5 a of the cam receiver 5. The second input shaft 2 is shortened in the axial direction so as not to protrude from the first input shaft 1, and a portion outside the mounting position of the input gear 11 of the first input shaft 1 is rotatably supported by a bearing 15. This is also different from the first embodiment.

When an input torque is applied to the first input shaft 1 via the input gear 11, the first input shaft 1 and the cam receiver 5 rotate integrally, and with a slight delay, the eccentric hole 5a of the cam receiver 5 is rotated. Input torque is applied to the eccentric cam 4 pushed by the small-diameter hole 5b and the second input shaft 2 integrated therewith. Thereby, similarly to 1st Embodiment, the spacer 6 revolves and the output shaft 3 rotates.

Further, even if the output shaft 3 is slightly rotated integrally with the eccentric cam 4 and the second input shaft 2 when a reverse input torque is applied, the small diameter hole portion 5b of the eccentric cam 4 and the eccentric hole 5a of the cam receiver 5 is used. As in the first embodiment, the cam receiver 5 and the first input shaft 1 do not rotate and the output shaft 3 is securely locked.

FIG. 6 shows a modification in which two bearings 14 are provided between the first input shaft 1 and the second input shaft 2 of the second embodiment as in the example of FIG. 4 of the first embodiment. Therefore, in this modification, when the second input shaft 2 is slightly rotated integrally with the output shaft 3 with respect to the reverse input torque, the first input shaft 1 is less likely to rotate together than the example of FIG. The output shaft 3 can be reliably locked.

FIG. 7 shows a third embodiment. In this embodiment, the eccentric cam 4 of the first embodiment is divided into two, and the means for simultaneously applying input torque to the first input shaft 1 and the second input shaft 2 is changed.

That is, in the third embodiment, the eccentric cam 4 of the first embodiment is divided into an input side eccentric cam 4a integrated with the second input shaft 2 and an output side eccentric cam 4b integrated with the output shaft 3. Yes. The input-side eccentric cam 4a and the output-side eccentric cam 4b are opposed to each other with a slight gap so that the shaft centers coincide with each other and do not rotate together by fitting the concaves and convexes provided on the opposing surfaces. The input side eccentric cam 4 a is directly inserted into the spacer 6 as in the first embodiment, but a bearing 16 is provided between the output side eccentric cam 4 b and the spacer 6.

Further, the input gear 11 is fitted and fixed to the outer periphery of the first input shaft 1, and a set screw 17 is screwed into the outer periphery of the second input shaft 2 from the outer periphery of the first input shaft 1, so that both the

input shafts

1 and 2 are connected to each other. By fixing, input torque can be applied to both

input shafts

1 and 2 simultaneously.

When input torque is applied to both

input shafts

1 and 2 via the input gear 11, the first input shaft 1 and the cam receiver 5 rotate together, and the second input shaft 2 and the input side eccentric cam 4a By rotating integrally, the spacer 6 revolves similarly to the first embodiment, and the output side eccentric cam 4b inserted into the spacer 6 via the bearing 16 rotates eccentrically, and the output side eccentric cam 4b and The integral output shaft 3 rotates.

On the other hand, when reverse input torque is applied to the output shaft 3 via the output gear 12, the output-side eccentric cam 4b integral with the output shaft 3 pushes the spacer 6 via the bearing 16, so that the first embodiment and Similarly, the output shaft 3 is locked when the spacer 6 is restricted from rotating or revolving by the housing 7 via the cam receiver 5.

Here, even if the output shaft 3 and the output-side eccentric cam 4b are slightly rotated due to backlash inside the clutch before the output shaft 3 is locked against the reverse input torque, the output-side eccentric cam 4b Since it is separated from the input side eccentric cam 4 a, the second input shaft 2 and the first input shaft 1 fixed to the second input shaft 2 do not rotate integrally with the output shaft 3. Further, since the bearing 16 is provided between the output side eccentric cam 4b and the spacer 6, the revolution of the spacer 6 hardly occurs. Thereby, it is possible to reliably prevent the

input shafts

1 and 2 from rotating together via the spacer 6 and lock the output shaft 3.

FIG. 8 shows a modification of the third embodiment in which a bearing is provided between the sliding parts in the example of FIG. 7 so that the parts can be rotated relative to each other. That is, in this modified example, the same bearing 16 as that between the output side eccentric cam 4b and the spacer 6 is provided between the input side eccentric cam 4a and the spacer 6, and the lid 9 of the housing 7 and the first input are provided.

Bearings

18 and 19 are provided between the shafts 1 and between the lid 7a on one end side of the housing 7 and the output shaft 3, respectively. Further, between the cam receiver 5 and the spacer 6 is provided a needle roller 20 with a cage that serves as a bearing.

Further, in another modification of the third embodiment shown in FIG. 9, in addition to the changes in FIG. 8, the same holding between the housing 7 and the cam receiver 5 as that between the cam receiver 5 and the spacer 6 is performed. A needle roller 20 with a vessel is provided.

As shown in the modified examples of FIGS. 8 and 9, by changing the portion where the parts slide in the example of FIG. 7 to the bearing support, a smoother clutch operation can be obtained than in the example of FIG.

FIG. 10 shows a fourth embodiment. This embodiment is based on the third embodiment (example of FIG. 7), and instead of fixing the first input shaft 1 and the second input shaft 2 to each other with a set screw 17, a spacer is used as in the second embodiment. 6 is slightly shortened in the axial direction, and a small-diameter hole portion 5b into which the input-side eccentric cam 4a is inserted without the spacer 6 is provided in the eccentric hole 5a of the cam receiver 5. At the same time, input torque can be applied.

In the fourth embodiment, similarly to the third embodiment, the input side eccentric cam 4a and the output side eccentric cam 4b are disconnected, and the output shaft 3 rotates slightly with respect to the reverse input torque. Since it is difficult for the

input shafts

1 and 2 to rotate together, there is no need to provide a gap between the eccentric cam 4 of the second embodiment and the small-diameter hole portion 5b of the eccentric hole 5a of the cam receiver 5.

Further, in the third and fourth embodiments, when the part where the parts slide is changed to the bearing support, a sliding ring may be used instead of the rolling bearing.

DESCRIPTION OF SYMBOLS 1 1st input shaft 1a Recessed part 2 2nd input shaft 2a Recessed part 3 Output shaft 4 Eccentric cam 4a Input side eccentric cam 4b Output side eccentric cam 5 Cam receiver 5a Eccentric hole 5b Small diameter hole part 6 Spacer 6a Connection part 7 Housing (fixing member) )
7a Lid 8 Rotation support mechanism 9 Lid 10 Connecting member 11 Input gear 11a Convex 12 Output gears 13, 14, 15, 16 Bearing 17

Set screw

18, 19 Bearing 20 Needle roller with cage

Claims

A first eccentric input shaft, a second input shaft, and an output shaft are arranged on the same axis, and a cylindrical eccentric cam having an eccentric axis parallel to the axis is provided between the second input shaft and the output shaft, A cylindrical cam receiver having the same axis as the axis is provided on the first input shaft, an eccentric hole having the same axis as the eccentric cam is formed in the cam receiver, and the eccentric cam is inserted into the eccentric hole. In addition, the cam receiver is rotatably fitted on the inner peripheral cylindrical surface of the fixing member, and a cylindrical spacer is fitted between the inner peripheral surface of the eccentric hole of the cam receiver and the outer peripheral surface of the eccentric cam so as to be relatively rotatable. A turning support mechanism is provided between the spacer and the fixing member to support the spacer so that it cannot rotate and revolve.
When input torque is simultaneously applied to the first input shaft and the second input shaft, the cam receiver rotates integrally with the first input shaft and the eccentric cam rotates integrally with the second input shaft. The output shaft rotates integrally with the eccentric cam by revolving and rotating the spacer between the cam receiver and the eccentric cam.
When a reverse input torque is applied to the output shaft, a spacer pushed by an eccentric cam integral with the output shaft is regulated by the fixed member via the cam receiver so that the revolving motion is controlled. Reverse input cutoff clutch that prevents rotation.
The means for simultaneously applying input torque to the first input shaft and the second input shaft fits the second input shaft on the inner periphery of the first input shaft so as to be relatively rotatable, and the same position in the longitudinal direction of both the input shafts. The input member to which the input torque is input is provided with a convex portion that is inserted into the concave portions of the input shafts with a clearance in the rotational direction and can be engaged simultaneously with the input shafts. The reverse input cut-off clutch according to claim 1.
The means for simultaneously applying input torque to the first input shaft and the second input shaft is provided with a small-diameter hole portion into which the eccentric cam is inserted with a gap without passing through the spacer in the eccentric hole of the cam receiver. The reverse input cutoff clutch according to claim 1, wherein the reverse input cutoff clutch is provided.
2. The reverse input cutoff clutch according to claim 1, wherein the eccentric cam is divided into an input side eccentric cam integrated with the second input shaft and an output side eccentric cam integrated with the output shaft.
5. The reverse input cutoff clutch according to claim 4, wherein the means for simultaneously applying input torque to the first input shaft and the second input shaft fixes the both input shafts with screws.
The means for simultaneously applying input torque to the first input shaft and the second input shaft is provided with a small-diameter hole portion into which the input-side eccentric cam is inserted without the spacer in the eccentric hole of the cam receiver. The reverse input cutoff clutch according to claim 4, wherein the reverse input cutoff clutch is provided.
The reverse input cutoff clutch according to any one of claims 4 to 6, wherein a bearing is provided between the output side eccentric cam and the spacer.