Cam clutch

Abstract

Provided is a cam clutch which has a simple structure, good meshing performance, can transmit stable torque, and has high design freedom and excellent manufacturing cost. A cam clutch is provided with: a plurality of cams (130) disposed between an inner ring and an outer ring provided so as to be rotatable relative to each other on the same axis; at least one auxiliary member (150) disposed between the plurality of cams (130); and an urging means (160) for urging the plurality of cams (130) and the auxiliary member (150) in the radial direction, characterized in that the auxiliary member (150) has an engaging portion capable of engaging with the urging means (160), and the radial dimension of the auxiliary member (150) is equal to or less than the dimension between the inner ring and the outer ring.

Description

TECHNICAL FIELD

[0001] The present application relates to a cam clutch that includes a plurality of cams disposed between an inner ring and an outer ring configured to be coaxially rotatable relative to each other, at least one auxiliary member disposed between the plurality of cams, and a force applying unit that applies a force to the plurality of cams in a radial direction. BACKGROUND

[0002] Conventionally, a cam clutch that includes a plurality of cams disposed between an inner ring and an outer ring configured to be coaxially rotatable relative to each other, and a force applying unit that applies a force to the plurality of cams in a radial direction has been known (for example, refer to Patent Literature 1).

[0003] The cam clutch 100 (the names and symbols of the constituent parts in this paragraph follow the description in Patent Literature 1) known in Patent Literature 1 and the like is configured such that the inner ring 110 is disposed radially inward of the outer ring 120, the plurality of cams 131 is disposed between the outer ring 120 and the inner ring 110, the force applying unit 139 applies a force to the plurality of cams 131 radially inward, and when the outer ring 120 and the inner ring 110 rotate relative to each other, the radial height of the plurality of cams 131 is changed, whereby torque can be transmitted between the outer ring 120 and the inner ring 110.

[0004] PATENT LITERATURE

[0005] Patent Literature 1: Japanese Patent Application Laid-Open No. 2020-190255 SUMMARY

[0006] In the cam clutch 100 known in Patent Literature 1 and the like (the names and symbols of the constituent parts in this paragraph follow the description in Patent Literature 1), in order to ensure a high torque transmission capacity, the cams 131 are disposed without gaps in the circumferential direction.

[0007] Since the cams 131 are disposed without gaps, the number of cams 131 is determined by the diameter of the outer circumferential surface of the inner ring 110 and the size of the cams 131, and the degree of freedom in design is low, and when the required torque transmission capacity is low, there can be a problem of excess performance.

[0008] In addition, when the cams 131 are in operation, adjacent cams 131 slide while rotating in opposite directions to each other, the movement of the cams 131 is obstructed, and there can be a problem of a decrease in the meshing properties with the outer ring 120 and the inner ring 110, unstable transmission of torque, or wear of the cams 131.

[0009] In addition, when the structure in which the cam spacer 648 composed of the metal wire bent to form the housing portion 649 of the cam 131 is provided is adopted in order to maintain the posture of the cam 131, the cam spacer 648 corresponding to the number of the plurality of cams 131 needs to be produced, and the structure becomes complicated and the manufacturing cost can be increased.

[0010] The present application has been made to solve such a problem, and has an object to provide a cam clutch which is simple in structure, good in engagement and capable of transmitting stable torque, high in design freedom and excellent in manufacturing cost.

[0011] The cam clutch of the present application includes a plurality of cams arranged between an inner ring and an outer ring arranged so as to be relatively rotatable on the same axis, at least one auxiliary member arranged between the plurality of cams, and a force application unit applying force to the plurality of cams in the radial direction, the auxiliary member has an engagement portion engageable with the force application unit, and the radial dimension of the auxiliary member is equal to or smaller than the dimension between the inner ring and the outer ring, thereby solving the above problems.

[0012] According to the present application described in Technical Solution 1, since the cam clutch includes a plurality of cams arranged between an inner ring and an outer ring arranged so as to be relatively rotatable on the same axis, at least one auxiliary member arranged between the plurality of cams, and a force application unit applying force to the plurality of cams in the radial direction, the auxiliary member has an engagement portion engageable with the force application unit, and the radial dimension of the auxiliary member is equal to or smaller than the dimension between the inner ring and the outer ring, it is possible to reduce the sliding resistance of the cam without hindering the free rotation of the inner ring and the outer ring, and to improve the engagement and stabilize the torque transmission.

[0013] In addition, by reducing the number of the arrangement of the cams or the rollers, it is possible to realize the minimum number satisfying the performance requirement.

[0014] According to the configuration described in Technical Solution 2, since the auxiliary member has a cylindrical portion which can contact the adjacent cam, when the cam operates, the auxiliary member itself rotates in conjunction with the swing of the cam, and it is possible to further improve the engagement.

[0015] According to the configuration described in Technical Solution 3, since the circumferential dimension of the auxiliary member is equal to or larger than the circumferential dimension of the cam, it is possible to optimize the number of the cams to be arranged without depending on the diameter of the outer circumferential surface of the inner ring or the size of the cam, and to improve the design freedom while reducing the number of parts.

[0016] According to the configuration described in Technical Solution 4, since the auxiliary member has the overhang at both ends in the circumferential direction, the overhang is formed so as to extend toward the inner ring direction, and the lower end of the overhang contacts the outer circumferential surface of the inner ring when viewed from the axial direction, so the contact area of the auxiliary member with the outer circumferential surface of the inner ring can be reduced, and even if the auxiliary member is upsized, the sliding resistance with the outer circumferential surface of the inner ring can be reduced.

[0017] According to the configuration described in Technical Solution 5, since the holding recess that rotatably holds the cam is formed at the end in the circumferential direction of the auxiliary member, the auxiliary member can be prevented from moving in the radial direction, and the sliding resistance of the auxiliary member with the outer ring or the inner ring can be reduced.

[0018] According to the configuration described in Technical Solution 6, since the outer ring and the inner ring have the flange portion that restricts the axial movement of the cam and the auxiliary member, and the engagement portion is formed at one end in the axial direction, even if the urging unit is disposed at one end in the axial direction, the auxiliary member can be disposed. BRIEF DESCRIPTION OF DRAWINGS

[0019] Figure 1 is a front view of the cam clutch according to the first embodiment of the present application, viewed from the axial direction.

[0020] Figure 2 is a perspective view of the cam clutch according to the first embodiment of the present application, viewed from above. Figure 1

[0021] Figure 3 is an enlarged plan view of the cam clutch according to the first embodiment of the present application. Figure 1

[0022] Figure 4 is a front view and a side view of the cam according to the first embodiment of the present application. Figure 1

[0023] Figure 5 is a front view and a side view of the roller according to the first embodiment of the present application. Figure 1

[0024] Figure 6 is a front view and a side view of the auxiliary member according to the first embodiment of the present application. Figure 1

[0025] Figure 7 is a schematic view of the operation of the cam and the auxiliary member in a cross-sectional view of the A-A section in the first embodiment of the present application. Figure 3

[0026] is a front view of the cam clutch according to the second embodiment of the present application, viewed from the axial direction. Figure 8

[0027] Figure 9 ​​​​​​is a perspective view of the cam clutch from above. Figure 8

[0028] Figure 10 is an enlarged plan view of the cam clutch. Figure 8

[0029] Figure 11 is a front view and a side view of the auxiliary member involved in the cam clutch. Figure 8

[0030] Figure 12 is a front view of the cam clutch involved in the third embodiment of the present application, as viewed from the axial direction.

[0031] Figure 13 is a perspective view of the cam clutch from above. Figure 12

[0032] Figure 14 is an enlarged plan view of the cam clutch. Figure 12

[0033] Figure 15 is a front view and a side view of the auxiliary member involved in the cam clutch. Figure 12

[0034] Figure 16 is a schematic view of the operation of the cam and the auxiliary member in the cross-sectional view of the B-B section in Figure 14

[0035] Figure 17 is a front view of the cam clutch involved in the fourth embodiment of the present application, as viewed from the axial direction.

[0036] Figure 18 is a perspective view of the cam clutch from above. Figure 17

[0037] Figure 19 is an enlarged plan view of the cam clutch. Figure 17

[0038] Figure 20 is a cross-sectional view of the C-C section in Figure 17

[0039] Figure 21 is a front view and a side view of the cam involved in the cam clutch. Figure 17

[0040] Figure 22 is a front view and a side view of the roller involved in the cam clutch. Figure 17

[0041] Figure 23 is​​​​​​​​​​​​Figure 17 Fig. 1 is a front view of the cam clutch according to the first embodiment of the present application.

[0042] Symbol explanation

[0043] 100, 200, 300, 400 - cam clutch; 410 - inner ring; 411 - flange portion; 420 - outer ring; 421 - flange portion; 130, 230, 330, 430 - cam; 131, 231, 331, 431 - engagement step portion; 140, 240, 340, 440 - roller; 141, 241, 341 - shaft portion; 142, 242, 342, 442 - cylindrical portion; 143, 243, 343 - engagement portion; 150, 250, 350, 450 - auxiliary member; 151 - shaft portion; 152 - cylindrical portion; 153, 253, 353, 453 - engagement portion; 254 - sag portion; 355, 455 - holding recess portion; 160, 260, 360, 460 - spring; 2so, 3so, 4so - outer peripheral surface radius of auxiliary member; 1sw - axial dimension of cylindrical portion of auxiliary member; 1rw - axial dimension of cylindrical portion of roller; 1sd - diameter of cylindrical portion of auxiliary member; 1rd - diameter of cylindrical portion of roller; 2sc - circumferential dimension of auxiliary member; 2cc - circumferential dimension of cam. DETAILED DESCRIPTION

[0044] Hereinafter, a cam clutch 100 according to a first embodiment of the present application will be described with reference to the drawings.

[0045] Further, in the first embodiment of the present application, the auxiliary member 150 is provided with a shaft portion 151, a cylindrical portion 152, and an engagement portion 153. Figures 1 to 3 , Figure 7 In the first embodiment of the present application, the inner ring 410 and the outer ring 420 are provided with a flange portion 411 and a flange portion 421, respectively.

[0046] Further, in the first embodiment of the present application, the auxiliary member 150 is provided with a shaft portion 151, a cylindrical portion 152, and an engagement portion 153. Figures 1 to 3

[0047] As shown in Fig. 1, the cam clutch 100 according to the first embodiment of the present application is provided with: a plurality of cams 130 as a mating member, which performs transmission and interruption of torque between the inner ring and the outer ring; a plurality of rollers 140, which are arranged between the cams 130 to allow the inner ring and the outer ring to freely rotate; a plurality of auxiliary members 150, which are arranged between the cams 130; and a force applying unit, i.e., a ring-shaped spring 160. Figure 4 The ring-shaped spring 160 applies force to the plurality of cams 130 in the radial direction to swing the cams 130 in the direction in which the cams 130 engage with the inner ring and the outer ring.

[0048] The plurality of cams 130 are arranged in a ring shape in the first embodiment of the present application.

[0049] Figure 5 ​​As shown, the cam 130 has an engagement step portion 131 in the axial center, which can engage with the annular spring 160.

[0050] The engagement step portion 131 is formed in an inclined shape having a convex portion at a position where eccentricity occurs, and the spring 160 presses the convex portion at the bottom of the engagement step portion 131, thereby applying a force to the cam 130 toward the inner periphery side, and the cam 130 swings in the direction of contacting the inner and outer races.

[0051] As shown, the roller 140 has a dumbbell shape, and has an axial portion 141 extending in the axial direction, a pair of cylindrical portions 142 respectively continuing to both ends of the axial portion 141, and an engagement portion 143 in the axial center, which can engage with the annular spring 160. Figure 6

[0052] The engagement portion 143 is formed by a space between the pair of cylindrical portions 142, and the spring 160 is arranged between the pair of cylindrical portions 142.

[0053] As shown, the auxiliary member 150 has a dumbbell shape, and has an axial portion 151 extending in the axial direction, a pair of cylindrical portions 152 respectively continuing to both ends of the axial portion 151, and an engagement portion 153 in the axial center, which can engage with the annular spring 160. Figure 1 The pair of cylindrical portions 152 are configured to contact the cam 130 adjacent to the auxiliary member 150, and the axial dimension 1sw is smaller than the axial dimension 1rw of the cylindrical portion 142 of the roller 140, the diameter 1sd of the cylindrical portion 152 is smaller than the radial dimension between the inner and outer races, and is smaller than the diameter 1rd of the cylindrical portion 142 of the roller 140.

[0054] Therefore, the auxiliary member 150 does not hinder the free rotation of the inner and outer races, and can rotate in conjunction with the swing of the cam 130 adjacent to the auxiliary member 150.

[0055] The engagement portion 153 is formed by a space between the pair of cylindrical portions 152, and the spring 160 is arranged between the pair of cylindrical portions 152.

[0056] The spring 160 is formed of, for example, a clamping spring, and is wound around the engagement step portion 131 of the cam 130, the engagement portion 143 of the roller 140, and the engagement portion 153 of the auxiliary member 150, so as to apply a force to the cam 130 in the radial direction, and to swing in the direction of engaging with the inner and outer races.

[0057] Therefore, the auxiliary member 150 does not hinder the free rotation of the inner and outer races, and can rotate in conjunction with the swing of the cam 130 adjacent to the auxiliary member 150.

[0058] ​Based on the overall diameter of the cam clutch 100, the diameter of the roller 140 and the auxiliary member 150, and the depth of the engagement step portion 131 of the cam 130, the engagement portion 143 of the roller 140, and the engagement portion 153 of the auxiliary member 150, the spring 160 can also apply a force to the roller 140 and the auxiliary member 150 in the radial direction.

[0059] like Figure 2 and Figure 7 As shown, in this embodiment, the roller 140 and the auxiliary component 150 are arranged between two cams 130, and are alternately arranged in the manner of roller 140-cam 130-auxiliary component 150-cam 130-auxiliary component 150-cam 130-roller 140...

[0060] By configuring the auxiliary component 150, the number of cams 130 and rollers 140 can be reduced, achieving the minimum number required to meet performance requirements.

[0061] Here, there is no particular limitation on the number and configuration of the cam 130, roller 140 and auxiliary component 150, as long as it includes multiple cams 130 and at least one auxiliary component 150.

[0062] The following is based on Figure 7 The rotational operation of the cam 130 and the auxiliary member 150 in the cam clutch 100 according to the first embodiment of the present invention will be described.

[0063] First, in the cam clutch 100, when the inner or outer ring rotates and Figure 7 When the cam 130 swings in the direction indicated by the black arrow, the cylindrical portion 152 of the auxiliary member 150 can contact the cam 130. Therefore, even when the two cams 130 adjacent to the auxiliary member 150 are pressed in a direction that brings them closer together, the auxiliary member 150 will also swing in accordance with the direction of the cam 130's movement. Figure 7 As indicated by the black arrow, it rotates in the opposite direction to the swing of cam 130.

[0064] Conversely, when cam 130 is in Figure 7 When the cam 130 swings in the direction indicated by the white arrow, the auxiliary component 150 swings in tandem with the cam 130. Figures 8 to 10 Rotate in the direction indicated by the white arrow.

[0065] Therefore, when the cam 130 is activated, the auxiliary component 150 rotates itself, thereby reducing the sliding resistance of the cam 130, improving meshing and making torque transmission more stable.

[0066] Next, a cam clutch 200 according to a second embodiment of the present application will be described with reference to the drawings.

[0067] In this embodiment, the same as the first embodiment described above except for a part of the structure, and therefore the description and the symbols shown in the drawings of the 100 series will be replaced by the symbols of the 200 series, and thus the description of the structure except for the different points will be omitted.

[0068] Also, Figures 8 to 11 In this embodiment, the illustration of the inner ring and the outer ring is omitted.

[0069] As Figure 8 shown, the auxiliary member 250 according to the cam clutch 200 is configured in a bridge shape when viewed in the axial direction, has an engaging portion 253 engageable with the annular spring 260 in the center in the axial direction, and has a drooping portion 254 at both ends in the circumferential direction.

[0070] The drooping portion 254 is formed so as to extend toward the inner ring side in the radial direction, and is configured so that the lower end portion of the drooping portion 254 contacts the outer circumferential surface of the inner ring when viewed in the axial direction, thereby being able to reduce the contact area of the auxiliary member 250 with the outer circumferential surface of the inner ring, and even in the case where the auxiliary member 250 is upsized, being able to reduce the sliding resistance with the outer circumferential surface of the inner ring.

[0071] As Figure 8 shown, the circumferential dimension 2sc of the auxiliary member 250 is equal to or greater than the circumferential dimension 2cc of the cam 230, and thereby being able to optimize the number of cams to be arranged independently of the diameter of the outer circumferential surface of the inner ring or the size of the cam, and being able to improve the design freedom while reducing the number of parts.

[0072] In addition, the outer circumferential surface of the auxiliary member 250 when the drooping portions 254 at both ends in the circumferential direction contact the outer circumferential surface of the inner ring is shaped so as not to contact the inner circumferential surface of the outer ring (in this embodiment, the outer circumferential surface of the auxiliary member 250 is formed in a circular arc shape, and the radius 2so is equal to or smaller than the radius of the inner circumferential surface of the outer ring), and in addition, since the annular spring 260 always applies a force to the auxiliary member 250 toward the inner ring side, the contact opportunity with the inner circumferential surface of the outer ring is reduced, and even in the case where the auxiliary member 250 is upsized, the contact resistance with the inner circumferential surface of the outer ring is reduced.

[0073] In this embodiment, as Figures 12 to 14 shown, the roller 240 and the auxiliary member 250 are arranged between the two cams 230, and on one side in the circumferential direction of the roller 240, two cams 230 are continuously arranged, and on the other side, three cams 230 are continuously arranged, and the cams 230 at the ends of the respective continuous arrangements are arranged adjacent to the auxiliary member 250.

[0074] Next, the cam clutch 300 according to the third embodiment of the present application will be described with reference to the drawings.

[0075] In this embodiment, the same as the above-described second embodiment except for a part of the structure, and therefore the description and the symbols shown in the drawings with respect to the 200 series will be replaced with the 300 series, and thus the description of the structure except for the difference will be omitted.

[0076] Also, in Figure 16 , Figures 12 to 15 , the illustration of the inner ring and the outer ring is omitted.

[0077] Further, Figure 16 , only the auxiliary member 350 and the cam 330 adjacent thereto are illustrated.

[0078] As shown in Figure 16 , the auxiliary member 350 according to the cam clutch 300 has an engaging portion 353 engageable with the annular spring 360 in the central portion in the axial direction, and a holding recess 355 rotatably holding the cam 330 in both end portions in the circumferential direction.

[0079] The holding recess 355 is a recess formed toward the circumferential central side of the auxiliary member 350, and is configured to rotatably hold the cam 330.

[0080] Here, in the cam clutch 300, as shown in Figure 16 , when the inner ring or the outer ring rotates and the cam 330 swings in the direction indicated by the black arrow in Figure 12 , the holding recess 355 of the auxiliary member 350 does not hinder the movement of the cam 330 adjacent to the auxiliary member 350, and rotatably holds the cam 330.

[0081] On the contrary, even when the cam 330 swings in the direction indicated by the white arrow in Figure 17 , the holding recess 355 of the auxiliary member 350 does not hinder the movement of the cam 330 adjacent to the auxiliary member 350, and rotatably holds the cam 330.

[0082] The radial position of the cam 330 is limited by the inner ring and the outer ring, and the circumferential side surface of the cam 330 is engaged with the holding recess 355 of the auxiliary member 350, thereby preventing the auxiliary member 350 from moving in the radial direction, and enabling the reduction of the sliding resistance of the auxiliary member 350 with the outer ring or the inner ring.

[0083] Further, in this embodiment, as shown in Figure 18As shown, the roller 340 and the auxiliary component 350 are arranged between two cams 330. On one side of the roller 340 in the circumferential direction, there is a cam 330, and on the other side, there are two cams 330 in succession. The cams 330 are arranged to be adjacent to the auxiliary component 350.

[0084] Next, the cam clutch 400 according to the fourth embodiment of the present invention will be described with reference to the accompanying drawings.

[0085] In this embodiment, except for a portion of the structure, it is the same as the aforementioned third embodiment. Therefore, the 300 series symbols shown in the description and drawings of the third embodiment are replaced with 400 series symbols, and the description of the structure other than the differences is omitted.

[0086] Furthermore, regarding the outer circumference 420, Figure 19 and Figures 17 to 20 Only the outline is shown in the diagram.

[0087] in addition, Figure 21 The diagram of the outer ring 420 is omitted.

[0088] like Figure 22 As shown, in the annular space between the track surfaces of the inner ring 410 and the outer ring 420, which are set to rotate relative to each other on the same central axis, the cam clutch 400 according to the fourth embodiment of the present invention includes: a plurality of cams 430 as mating members, which transmit and cut off torque between the inner ring 410 and the outer ring 420; a plurality of rollers 440 disposed between the cams 430, allowing the inner ring 410 and the outer ring 420 to rotate freely; a plurality of auxiliary members 450 disposed between the cams 430; and a force-applying unit, namely an annular spring 460.

[0089] The annular spring 460 applies a force to a plurality of cams 430 in the radial direction, causing them to oscillate in the direction in which they engage with the inner ring 410 and the outer ring 420.

[0090] like Figure 20 As shown, the cam 430 has an engagement step 431 at one end in the axial direction, which can engage with the annular spring 460.

[0091] The engagement step portion 431 is configured to have an inclined shape with a protrusion at the position where eccentricity occurs. The spring 460 presses the protrusion at the bottom of the engagement step portion 431, thereby applying a force to the cam 430 in the radial direction towards the inner ring 410. The cam 430 swings in the direction of contacting the inner and outer rings.

[0092] like Figure 20As shown, the roller 440 is cylindrical and has a cylindrical portion 442 whose axial dimension is approximately equal to that of the cam 430 after removing the engagement step portion 431.

[0093] like Figure 23 As shown, the inner ring 410 has a flange 411 on the side opposite to the axial direction of the engagement step 431 of the cam 430, so as to restrict the movement of the cam 430, roller 440 and auxiliary member 450 to one axial direction (hereinafter referred to as "right direction").

[0094] In addition, such as Figure 17 As shown, the outer ring 420 has a flange 421 on the side in the same direction as the engagement step 431 of the cam 430, so as to restrict the movement of the cam 430, the auxiliary member 450 and the spring 460 to the other side of the axial direction (hereinafter referred to as the "left direction").

[0095] like Figure 19 As shown, the auxiliary member 450 has an engagement portion 453 at its left end that can engage with the annular spring 460, and retaining recesses 455 at both ends in the circumferential direction that rotatably retain the cam 430.

[0096] The retaining recess 455 is a recess formed toward the circumferential central side, configured to rotatably retain the cam 430.

[0097] Spring 460, for example, is a clamping spring, which is wound around the engagement step 431 of cam 430 and the engagement part 453 of auxiliary member 450 to restrict the roller 440 from moving to the left.

[0098] In this embodiment, such as Figure 20 As shown, the roller 440 and the auxiliary component 450 are arranged between two cams 430. Three cams 430 are continuously arranged on one side of the roller 440 in the circumferential direction, and four cams 430 are continuously arranged on the other side. The end cams 430 of the continuously arranged rollers are arranged to be adjacent to the auxiliary component 450.

[0099] In addition, such as ​ and ​ As shown, the engagement step portion 431 of the cam 430 and the engagement portion 453 of the auxiliary member 450 are disposed on the direction side of the flange portion 421 of the outer ring 420. Between the cams 430, the roller 440 is disposed between the flange portion 411 of the inner ring 410 and the spring 460.

[0100] Therefore, even when the spring 460 is positioned at the end, the auxiliary member 450 can be configured.

[0101] While the embodiments of the present application have been described in detail, the present application is not limited to the above-described embodiments, and various design changes can be made without departing from the scope of the present application described in the claims.

[0102] In the above-described embodiments, while the end portions in the circumferential direction of the auxiliary member 250 are in a convex shape, the auxiliary member 350 can be formed with a holding recess that rotatably holds the cam 230.

[0103] In addition, the circumferential dimension of the auxiliary member 350 and the auxiliary member 450 can also be equal to or greater than the circumferential dimension of the cam 230 and the cam 330, as with the auxiliary member 250.

[0104] In addition, as with the auxiliary member 250, a drooping portion can also be formed at both end portions in the circumferential direction of the auxiliary member 350 and the auxiliary member 450.

Claims

1. A cam clutch comprising: a plurality of cams disposed between an inner ring and an outer ring configured to rotate relative to each other on the same axis; at least one auxiliary member disposed between the plurality of cams; and a force-applying unit that applies a force radially to the plurality of cams, characterized in that, The auxiliary component has an engaging portion that can engage with the force-applying unit. The radial dimension of the auxiliary component is less than or equal to the dimension between the inner and outer rings.

2. The cam clutch according to claim 1, characterized in that, The auxiliary component has a cylindrical portion that can contact the adjacent illustrated cam.

3. The cam clutch according to claim 1, characterized in that, The circumferential dimension of the auxiliary component is greater than or equal to the circumferential dimension of the cam.

4. The cam clutch according to claim 1, characterized in that, The auxiliary component has drooping portions at both ends in the circumferential direction. The drooping portion is formed in a manner that extends toward the inner ring, and when viewed from the axial direction, the lower end of the drooping portion contacts the outer peripheral surface of the inner ring.

5. The cam clutch according to claim 1, characterized in that, At the circumferential end of the auxiliary member, a retaining recess is formed to rotatably hold the cam.

6. The cam clutch according to claim 1, characterized in that, The outer ring and the inner ring have flange portions that restrict the axial movement of the cam and the auxiliary component. The meshing portion is formed at one end in the axial direction.

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