Cam clutch
By designing the axial ends of the roller protruding contact with the outer and inner rings in the cam clutch, and using resin materials to make the partition ring, the problem of insufficient rigidity of the axial load in the prior art is solved, and the load is increased and the equipment is achieved. Miniaturize and lightweight.
Patent Information
- Application Number
- CN202410356870.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2023-06-13
- Filing Date
- 2024-03-27
- Publication Date
- 2024-12-13
AI Technical Summary
Existing cam clutches are not rigid enough when bearing axial loads, especially when using spacers made of resin materials, it is difficult to ensure uniform load sharing, and adding components to withstand loads will occupy a large space, resulting in a large size of the equipment and Lightweight.
By designing the socket and axial structure of the spacer ring and roller, cam, the roller protrudes at both ends of the axial direction to contact the outer ring and inner ring, forming a C-cavity or R-cavity shape to reduce the braking torque, and The spacer is made from resin materials to achieve light weight.
Without increasing the rigidity of the spacer and the components, the rollers are subjected to axial load, thereby increasing the load and miniaturizing the equipment, while reducing the braking torque. As the existing components are not required to be greatly changed, the Increase in production costs.
Smart Images
Figure CN119122947A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to a cam clutch for transmitting and cutting off torque. Background Art
[0002] As a cam clutch, a cam clutch having the following structure is known, in which a plurality of cams arranged between the inner ring and the outer ring are all engaged simultaneously under equal load sharing in order to maintain the concentricity of the inner ring and the outer ring, and a plurality of rollers are arranged between the inner ring and the outer ring (for example, refer to patent document 1).
[0003] The clutch described in Patent Document 1 includes an outer ring and an inner ring; a plurality of sprags and a plurality of rollers arranged along the circumferential direction between the outer ring and the inner ring; a retainer that retains the sprags along the circumferential direction; and an elastic member that applies force to the sprags.
[0004] The retainer includes: a pair of annular portions; and a column portion extending in the axial direction in a manner connecting the annular portions, and a socket portion for accommodating a wedge and a socket portion for accommodating a roller are formed by a space between circumferentially adjacent column portions.
[0005] Patent Literature
[0006] Patent Document 1: Japanese Patent Application Publication No. 2011-012762 Summary of the invention
[0007] Therefore, in the above-mentioned clutch, when the rollers and the cam are accommodated in the socket portion, there are annular portions of the retainer at positions closer to the outside than the axial ends of the rollers and the cam, respectively, and the rollers and the cam are retained in the axial direction by these annular portions, thereby limiting the relative movement in the axial direction.
[0008] Therefore, in the above-mentioned clutch, although the spacer is required to bear the axial load, it is difficult to ensure the rigidity that can bear the load. In particular, considering productivity and light weight, it is rare to form the spacer with resin material. In the case of a resin spacer, such a problem will occur significantly.
[0009] To solve this problem, it is also conceivable to additionally arrange a member for bearing the axial load, but this will require a large space.
[0010] The present invention is based on such a problem, and the technical problem to be solved is to provide a cam clutch that can increase the allowable axial load through a simple structure without increasing the rigidity of the spacer ring or configuring other components, thereby achieving miniaturization and weight reduction.
[0011] The present invention is a cam clutch, comprising: an outer ring and an inner ring, which are arranged to be relatively rotatable on the same axis; a plurality of cams and a plurality of rollers, which are arranged in a circumferential direction between the outer ring and the inner ring; a spacer, which has a plurality of socket portions for the cams respectively corresponding to the plurality of cams and a plurality of socket portions for the rollers respectively corresponding to the plurality of rollers; and an annular spring, which applies force to the plurality of cams respectively in a manner of contacting the outer ring and the inner ring, and applies force to the plurality of rollers in a manner of pressing against the outer ring or the inner ring, and is characterized in that the spacer is constructed as follows: , the roller can be held in a state where the outer ring side portion at one axial end portion protrudes radially outward more than the outer peripheral surface of the spacer, the socket portion for the roller is formed so that the roller is held in a state where the two ends of the roller protrude axially outward more than the axial end surfaces of the cam held in the socket portion for the cam, respectively, and the column portion formed between adjacent socket portions is formed so that the other axial end portion on the inner peripheral surface side is located closer to the axial inside than the opening edge position on the other axial end side of the socket portion for the roller, thereby solving the above-mentioned problem.
[0012] According to the invention involved in the first technical solution, when the roller is held by the spacer, the outer ring side portion at one axial end of the roller protrudes radially outward compared to the outer peripheral surface of the spacer, and the other axial end of the roller protrudes outward compared to the other axial end of the column portion, so that both ends of the roller can contact the inner ring and the outer ring in the axial direction, thereby enabling the roller to bear the axial load from the outer ring or the inner ring. Therefore, without increasing the rigidity of the spacer, the increase in the allowable axial load can be achieved through a simple structure.
[0013] Furthermore, both end faces of the roller can be exposed in the axial direction within the axial length region of the cage, so that the axial dimension of the cam clutch does not need to be increased, and a structure can be realized in which the axial load can be borne by the rollers.
[0014] Furthermore, as rollers or cams, existing components can be used without significantly changing the shapes or the like, and thus an increase in manufacturing costs can be suppressed.
[0015] According to the invention involved in the second technical solution, one end of the spacer is arranged between the inner circumference of the outer ring side roller contact portion and the outer circumference of the inner ring, and the other end of the spacer is arranged between the outer circumference of the inner ring side roller contact portion and the inner circumference of the outer ring, so that the outer ring side roller contact portion contacts one end face of the roller, and the inner ring side roller contact portion contacts the other end face of the roller, so that the spacer can be arranged by effectively utilizing the space between the outer ring and the inner ring. Therefore, a structure that can surely bear the axial load through the roller can be realized with a small space, and the cam clutch can be miniaturized.
[0016] According to the invention involved in Technical Solution 3, the outer ring has outer ring side roller abutment portions at both axial ends, and the inner ring has inner ring side roller abutment portions at both axial ends, thereby clamping the roller in the axial direction so that the inner ring side roller abutment portion and the outer ring side roller abutment portion respectively abut against the two end surfaces of the roller, thereby allowing the roller to bear bidirectional axial loads.
[0017] According to the invention involved in the fourth technical solution, the outer ring side roller contact portion is composed of the inner flange portion integrally formed on the outer ring, and the inner ring side roller contact portion is composed of the outer flange portion integrally formed on the inner ring, so that the cam clutch unit can bear the axial load. Therefore, without configuring other components for bearing the axial load, the increase in the allowable axial load can be reliably achieved through a simple structure.
[0018] According to the invention involved in the fifth technical solution, the roller has a chamfered portion in a C-chamfered shape or an R-chamfered shape at both ends, and the roller contact surface of the outer ring side roller contact portion and the roller contact surface of the inner ring side roller contact portion are formed in a conical shape or a cross-sectional arc shape, so the outer ring and the inner ring abut against the roller in the axial direction with a contact angle. Therefore, when an axial load is applied, a radial component force is applied, so the roller slides in contact with the outer ring and the inner ring, and the braking torque can be reduced.
[0019] According to the invention according to claim 6 , the spacer is formed of a resin material, so the spacer is easy to manufacture and lightweight, and the cam clutch can be made lighter. BRIEF DESCRIPTION OF THE DRAWINGS
[0020] Figure 1 This is a perspective view showing a configuration example of a cam clutch according to the first embodiment of the present invention, and is a view showing a portion of an outer ring in section.
[0021] Figure 2 is Figure 1 A cross-sectional view perpendicular to the rotation axis at an axial center position of the cam clutch is shown.
[0022] Figure 3 yes Figure 2 AA line section view in.
[0023] Figure 4 yes Figure 2 BB line section view in.
[0024] Figure 5 A perspective view showing the structure of a spacer.
[0025] Figure 6 It is along Figure 5 A cross-sectional view of the axis of rotation of the spacer is shown.
[0026] Figure 7 This is a cross-sectional view along the rotation axis, showing a state in which the cam and the roller are held by the cage.
[0027] Figure 8 It is a perspective view showing another configuration example of the cam clutch according to the first embodiment of the present invention, and is a view showing a portion of the outer ring in section.
[0028] Fig. 9 It means in Figure 8 The cam clutch shown is a partial cross-sectional view when cut along a plane including the rotation axis and the swing center axis of the cam.
[0029] Fig.10 It means in Figure 8 The cam clutch shown is a partial cross-sectional view when cut along a plane including the rotation axis and the center axis of the roller.
[0030] Fig.11 This is a diagram showing a part of a cross section when the cam clutch according to the first embodiment of the present invention is cut along a plane including the rotation axis and the swing center axis of the cam.
[0031] Fig.12 It means in Fig.11 The cam clutch shown is a partial cross-sectional view when cut along a plane including the rotation axis and the center axis of the roller.
[0032] Fig.13 It is an exploded perspective view showing a configuration example of a cam clutch according to a second embodiment of the present invention.
[0033] Fig.14 It means in Fig.13 The cam clutch shown is a partial cross-sectional view when cut along a plane including the rotation axis and the swing center axis of the cam.
[0034] Fig.15 It means in Fig.13 The cam clutch shown is a partial cross-sectional view when cut along a plane including the rotation axis and the center axis of the roller.
[0035] Explanation of symbols
[0036] 100-cam clutch; 110-outer ring; 115-outer ring side roller contact portion; 115a-first outer ring side roller contact portion; 115b-second outer ring side roller contact portion; 116-inner surface; 117-support plate; 118-retaining ring; 120-inner ring; 125-inner ring side roller contact portion; 125a-first inner ring side roller contact portion; 125b-second inner ring side roller contact portion Part; 126-inner surface; 130-spacer; 131-large diameter cylindrical portion; 132-step portion; 133-small diameter cylindrical portion; 134-recessed portion; 136a-socket portion for cam; 136b-socket portion for roller; 137-column portion; 140-cam; 141-groove portion; 150-roller; 151-groove portion; 152-chamfered portion; 160-spring; C-rotation axis. DETAILED DESCRIPTION
[0037] First Embodiment
[0038] like Figures 1 to 4 As shown, the cam clutch 100 involved in the first embodiment of the present invention comprises: an outer ring 110 and an inner ring 120, which are configured to be relatively rotatable on the same axis; a spacer 130, which is arranged between the outer ring 110 and the inner ring 120 and is coaxial with the outer ring 110 and the inner ring 120; a plurality of cams 140 and a plurality of rollers 150, which are held by the spacer 130 and are arranged circumferentially in the annular space between the inner circumferential surface of the outer ring 110 and the outer circumferential surface of the inner ring 120; and an annular spring 160, which applies force to the plurality of cams 140 respectively in a manner of contacting the outer ring 110 and the inner ring 120, and applies force to the plurality of rollers 150 respectively in a manner of pressing against the inner ring 120. Figures 1 to 4 The symbol C in the figure is the axis of rotation.
[0039] In this embodiment, an inner flange portion is integrally formed at one axial end portion of the outer ring 110 , protruding radially inward and extending over the entire circumference. The inner flange portion constitutes an outer ring side roller abutment portion 115 that abuts against one end surface of the roller 150 .
[0040] At the other axial end portion of the inner ring 120 in the present embodiment, an outer flange portion is integrally formed which protrudes radially outward and extends over the entire circumferential span. The inner ring side roller abutment portion 125 is constituted by the outer flange portion, which abuts against the other end face of the roller 150 in a manner of clamping the roller 150 in the axial direction between the outer ring side roller abutment portion 115.
[0041] like Figure 5 and Figure 6As shown, the spacer 130 in this embodiment has: a large diameter cylindrical portion 131; and a small diameter cylindrical portion 133 which is axially continuous at one end of the large diameter cylindrical portion 131 via a step portion 132, and is constructed into a two-section cylindrical shape having a step portion 132 in the center of the axial direction.
[0042] On the spacer 130, over the span from the large diameter cylindrical portion 131 to the small diameter cylindrical portion 133, there are formed socket portions 136a for multiple cams corresponding to the multiple cams 140 and socket portions 136b for multiple rollers corresponding to the multiple rollers 150 in a manner that extends in the axial direction and penetrates in the radial direction from the outer peripheral side to the inner peripheral side.
[0043] Thus, the cam socket 136a and the roller socket 136b are configured to accommodate the cam 140 and the roller 150 in a state where one axial end portion of the cam 140 and the roller 150 protrudes radially outward compared to the outer peripheral surface of the small-diameter cylindrical portion 133. Therefore, when the cam 140 and the roller 150 are accommodated in the corresponding cam socket 136a and the roller socket 136b, the outer ring side portion on the axial one end surface is exposed in the axial direction.
[0044] The cam socket portion 136 a and the roller socket portion 136 b are configured to surround the cam 140 and the roller 150 in a radial plan view so as to restrict the circumferential and axial movements of the cam 140 and the roller 150 .
[0045] Furthermore, the cam support surface and the roller support surface of the column portion 137 formed between the adjacent cam socket portion 136a and the roller socket portion 136b are formed in a shape that restricts the movement of the cam 140 and the roller 150 toward the inner ring side.
[0046] In this embodiment, the six roller sockets 136b are formed so that the six rollers 150 are arranged at equal intervals in the circumferential direction, and the six cam sockets 136a are formed so that one cam 140 is located between adjacent rollers 150 and the six cams 140 are arranged at predetermined intervals.
[0047] In the cam clutch 100, since the rollers 150 are provided, the radial load can be supported while maintaining the concentricity of the outer ring 110 and the inner ring 120 without using other components such as balls, but the number of rollers 150 is not particularly limited, and at least 3 or more is sufficient. In addition, the number and arrangement pattern of the cams 140 are not particularly limited, and can be appropriately changed according to the purpose.
[0048] Also like Figure 7As shown, the roller socket portion 136b is formed to hold the roller 150 in a state where both ends of the roller 150 protrude axially outward from both axial end surfaces of the cam 140 accommodated in the cam socket portion 136a.
[0049] Each of the plurality of cams 140 has a groove portion 141 at the center in the axial direction that can engage with the spring 160 .
[0050] In this embodiment, the bottom of the groove 141 is inclined to form a convex portion at the eccentric position, and the spring 160 presses the convex portion at the bottom of the groove 141, thereby causing the cam 140 to swing in a direction contacting the outer ring 110 and the inner ring 120.
[0051] The axial dimension of the plurality of rollers 150 is larger than the axial dimension of the cam 140, and a groove 151 is provided at the center of the axial direction to engage with the spring 160. The outer peripheral edge of the groove 151 is chamfered to prevent the spring 160 from being caught.
[0052] The spring 160 is wound around the groove 141 of the cam 140 and the groove 151 of the roller 150 and is locked to the step 132 of the cage 130 so as to restrict the cam 140 and the roller 150 from moving toward the outer ring side.
[0053] Therefore, in the above-mentioned cam clutch 100, the countersunk recess 134 is formed at the other end opening of the large diameter cylindrical portion 131 of the spacer 130. Figure 6 As shown in FIG. 1 , the concave portion 134 is formed so that the bottom surface is located axially inwardly relative to the axial position of the opening edge of the other end side of the roller socket portion 136b, thereby the other axial end portion of the inner circumferential surface side of the column portion 137 is located axially inwardly relative to the opening edge of the other axial end side of the roller socket portion 136b. Figure 7 As shown, when the roller 150 is accommodated in the roller socket portion 136 b , the inner ring side portion of the other axial end surface of the roller 150 is exposed in the axial direction, so that the outer ring 110 and the inner ring 120 can contact the roller 150 in the axial direction.
[0054] In this way, both end faces of the roller 150 can be exposed in the axial direction within the axial length region of the spacer 130, so that there is no need to increase the axial dimension of the cam clutch 100, and a structure that can withstand axial loads through the roller 150 can be achieved.
[0055] One end of the small diameter cylindrical portion 133 on the spacer 130 is arranged between the inner circumference of the outer ring side roller contact portion 115 and the outer circumference of the inner ring 120, and the other end of the large diameter cylindrical portion 131 on the spacer 130 is arranged between the outer circumference of the inner ring side roller contact portion 125 and the inner circumference of the outer ring 110, so that the outer ring side roller contact portion 115 contacts one end face of the roller 150, and the inner ring side roller contact portion 125 contacts the other end face of the roller 150. Thus, the space between the outer ring 110 and the inner ring 120 is effectively utilized, and the axial load in one direction from the outer ring 110 or the inner ring 120 can be received by the roller 150 in a small space. Therefore, without increasing the rigidity of the spacer 130 or arranging other components for receiving the axial load, the permissible axial load can be increased with a simple structure, and the cam clutch 100 can be miniaturized. Furthermore, as the cam 140 or the roller 150 , existing components can be used without significantly changing the shape or the like, and thus an increase in manufacturing cost can be suppressed.
[0056] As described above, in the cam clutch 100, the outer ring 110 and the inner ring 120 do not contact the cam 140 and the spacer 130 in the axial direction, but only contact the roller 150 in the axial direction, so that the axial load can be received by the roller 150. Therefore, the spacer 130 only needs to have a rigidity that can restrict and hold the position of the cam 140 and the roller 150, and the spacer 130 can be formed of a resin material. By forming the spacer 130 with a resin material, the spacer 130 is easy to manufacture and lightweight, and the cam clutch 100 can be lightweight.
[0057] In the above-mentioned embodiment, although the structure which receives the axial load by the flat end surface of a roller is demonstrated, it is also possible to configure so that the axial load is received obliquely by the surface which inclines with respect to an axial direction.
[0058] Figure 8 1 is a perspective view showing another configuration example of the cam clutch according to the first embodiment of the present invention, and is a view showing a portion of the outer ring in section. Fig. 9 It means that Figure 8 The cam clutch shown is a partial cross-sectional view when cut along a plane including the rotation axis and the swing center axis of the cam. Fig.10 It means that Figure 8 The cam clutch shown is a partial cross-sectional view when cut along a plane including the rotation axis and the center axis of the roller.
[0059] Except for the different structures of the roller 150, the outer ring side roller abutment portion 115 and the inner ring side roller abutment portion 125, the cam clutch 100 has the same structure as the above-mentioned cam clutch 100. For convenience, the same symbols are marked for the same components and the description is omitted.
[0060] The roller 150 has a C-chamfered chamfered portion 152 at both ends thereof, the diameter of which decreases toward the axial outer side. When the roller 150 is accommodated in the roller insertion opening 136 b of the cage 130 , the chamfered portion 152 is exposed in the axial direction.
[0061] An inner flange portion is integrally formed at one axial end portion of the outer ring 110 , protruding radially inward and extending over the entire circumference. The inner flange portion constitutes an outer ring side roller contact portion 115 that contacts one end surface of the roller 150 .
[0062] In the present embodiment, the inner surface 116 constituting the roller contact surface of the outer ring side roller abutment portion 115 is formed in a tapered shape so as to extend obliquely toward the inner ring side as it goes toward the axial one end side.
[0063] At the other axial end portion of the inner ring 120, an outer flange portion is integrally formed, which protrudes radially outward and extends over the entire circumference. The inner ring side roller abutment portion 125 is constituted by the outer flange portion, which abuts against the other end face of the roller 150 in a manner of clamping the roller 150 in the axial direction between the outer ring side roller abutment portion 115.
[0064] In the present embodiment, the inner surface 126 constituting the roller contact surface of the inner ring side roller abutment portion 125 is formed in a tapered shape so as to extend obliquely toward the outer ring side as it goes toward the other axial end side.
[0065] According to the cam clutch 100 constructed in this way, when one end of the small-diameter cylindrical portion 133 is arranged between the inner circumferential surface of the outer ring side roller contact portion 115 and the outer circumferential surface of the inner ring 120, and the other end of the large-diameter cylindrical portion 131 is arranged between the outer circumferential surface of the inner ring side roller contact portion 125 and the inner circumferential surface of the outer ring 110, the outer ring side roller contact portion 115 of the outer ring 110 and the inner ring side roller contact portion 125 of the inner ring 120 axially contact the roller 150 with a contact angle. Therefore, when an axial load is applied, a radial component force is applied, so the roller 150 slides in contact with the outer ring 110 and the inner ring 120, and the braking torque can be reduced.
[0066] In addition, if Fig.11 and Fig.12As shown, the chamfered portions 152 at both ends of the roller 150 are formed in an R-chamfered shape, and the inner surface 116 of the roller contact surface in the outer ring side roller abutment portion 115 and the inner surface 126 of the roller contact surface in the inner ring side roller abutment portion 125 are formed in a circular arc cross-section, so that the same effect as the above content can be obtained.
[0067] In the above, although the structure in which the roller abutment portion is formed by a flange portion and the roller abutment portion is formed integrally on the outer ring and the inner ring is described, the outer ring side roller abutment portion and the inner ring side roller abutment portion do not need to be formed integrally with the outer ring and the inner ring, but can also be constructed as other components that are set to abut against the end face of the roller in a state that prohibits axial movement.
[0068] In addition, although the structure of the spacer formed by two-stage cylindrical shape is described, the structure of the spacer can be configured as follows, that is, when the roller is accommodated in the roller socket portion, the outer ring side portion on one end face of the roller and the inner ring side portion on the other end face are exposed in the axial direction. For example, it is also possible to configure the spacer to be formed by a cylindrical member with uniform thickness in the axial direction, and a step portion extending over the entire circumference is formed on the outer peripheral surface of one end of the cylindrical member so that the outer ring side portion of one end face of the roller is exposed in the axial direction, and at the same time, a countersunk recessed portion is formed in the opening portion of the other end side of the cylindrical member so that the inner ring side portion of the other end face of the roller is exposed in the axial direction.
[0069] Second Embodiment
[0070] The cam clutch according to the first embodiment is configured so that rollers can bear axial loads in one direction. Hereinafter, a cam clutch configured so that rollers can bear axial loads in two directions will be described.
[0071] like Figures 13 to 15 As shown, the cam clutch 100 involved in the second embodiment comprises: an outer ring 110 and an inner ring 120, which are arranged to be relatively rotatable on the same axis; a spacer 130, which is arranged between the outer ring 110 and the inner ring 120 and is coaxial with the outer ring 110 and the inner ring 120; a plurality of cams 140 and a plurality of rollers 150, which are held by the spacer 130 and are arranged in the circumferential direction in the annular space between the inner circumferential surface of the outer ring 110 and the outer circumferential surface of the inner ring 120; an annular spring 160, which applies force to the plurality of cams 140 respectively in a manner of contacting the outer ring 110 and the inner ring 120, and applies force to the plurality of rollers 150 respectively in a manner of pressing against the inner ring 120; a support plate 117, which is arranged between the outer ring 110 and the inner ring 120 and is in abutment with the other end surface of the roller 150; and a retaining ring 118, which limits the axial movement of the support plate 117. Figures 13 to 15 The symbol C in the figure is the axis of rotation.
[0072] In this embodiment, an inner flange portion is integrally formed at one axial end portion of the outer ring 110 , protruding radially inward and extending over the entire circumference. The inner flange portion constitutes a first outer ring side roller abutment portion 115a that abuts against one end face of the roller 150 .
[0073] A groove extending over the entire circumference is formed on the inner circumferential surface of the other end of the outer ring 110, and a circular ring-shaped retaining ring 118 is embedded in the groove, thereby fixing the circular ring-shaped support plate 117 in the axial direction to the outer ring 110. In this embodiment, the support plate 117 and the retaining ring 118 constitute the second outer ring side roller abutment portion 115b that abuts against the other end face of the roller 150.
[0074] In the present embodiment, outer flange portions protruding radially outward and extending over the entire circumference are formed integrally at both axial ends of the inner ring 120, and the outer flange portion at one end side constitutes a first inner ring side roller contact portion 125a, which contacts one end face of the roller 150 in a manner of sandwiching the roller 150 in the axial direction between the second outer ring side roller contact portion 115b. In addition, the outer flange portion at the other end side constitutes a second inner ring side roller contact portion 125b, which contacts the other end face of the roller 150 in a manner of sandwiching the roller 150 in the axial direction between the first outer ring side roller contact portion 115a.
[0075] The spacer 130 has the same structure as the spacer 130 in the cam clutch 100 involved in the first embodiment described above, and when the roller 150 is accommodated in the roller socket portion 136b, it is constructed so that the outer ring side portion on one end face of the roller 150 and the inner ring side portion on the other end face of the roller 150 are exposed in the axial direction.
[0076] One end of the small diameter cylindrical portion 133 on the spacer 130 is arranged between the outer circumferential surface of the first inner ring side roller abutment portion 125a and the inner circumferential surface of the first outer ring side roller abutment portion 115a, and the other end of the large diameter cylindrical portion 131 is arranged between the outer circumferential surface of the second inner ring side roller abutment portion 125b and the inner circumferential surface of the support plate 117 constituting the second outer ring side roller abutment portion 115b.
[0077] Thus, the first outer ring side roller abutment portion 115a and the second inner ring side roller abutment portion 125b respectively abut against one end face and the other end face of the roller 150 in a manner of clamping the roller 150 in the axial direction, and the second outer ring side roller abutment portion 115b and the first inner ring side roller abutment portion 125a respectively abut against the other end face and one end face of the roller 150 in a manner of clamping the roller 150 in the axial direction.
[0078] With such a structure, the space between the outer ring 110 and the inner ring 120 is effectively utilized, and the rollers 150 can bear the bidirectional axial load from the outer ring 110 or the inner ring 120 in a small space.
[0079] In the present embodiment, although an example is described in which the other end side roller contact portion on the outer ring is constituted by a support plate and a retaining ring, it can also be constituted by an inner flange portion to constitute the other end side roller contact portion, thereby forming the other end side roller contact portion and the outer ring as one body. In addition, the one end side roller contact portion on the outer ring can also be constituted by a support plate that is set to be restricted in axial movement by the retaining ring, thereby forming a separate body from the outer ring. The same is true for the roller contact portion on the inner ring. The one end side roller contact portion and / or the other end side roller contact portion can also be constituted by a support plate that is set to be restricted in axial movement by the retaining ring, thereby forming a separate body from the inner ring.
[0080] Furthermore, in the present embodiment, the structure in which the axial load is received by the flat surfaces at both ends of the roller has been described. However, similarly to the cam clutch according to the first embodiment, the axial load may be received obliquely by surfaces inclined to the axial direction.
[0081] Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the scope of the present invention described in the claims.
Claims
1. A cam clutch, comprising: an outer ring and an inner ring, which are arranged to be relatively rotatable on the same axis; a plurality of cams and a plurality of rollers, which are arranged to be arranged in a circumferential direction between the outer ring and the inner ring; a spacer, which has a plurality of cam sockets corresponding to the plurality of cams and a plurality of roller sockets corresponding to the plurality of rollers; and an annular spring, which applies force to the plurality of cams in a manner of contacting the outer ring and the inner ring, and applies force to the plurality of rollers in a manner of pressing against the outer ring or the inner ring, Its characteristics are: The cage is configured to hold the roller in a state where an outer ring side portion at one axial end portion of the roller protrudes radially outward relative to an outer peripheral surface of the cage, The roller socket is formed so as to hold the roller in a state where both ends of the roller protrude further outward in the axial direction than both end surfaces of the cam held in the cam socket, The column portion formed between adjacent socket portions is formed so that the other axial end portion on the inner peripheral surface side is located axially inward of the opening edge position on the other axial end side of the socket portion for the roller.
2. The cam clutch according to claim 1, Its characteristics are: The outer ring has an outer ring side roller contact portion at one axial end portion, which is formed in a manner of protruding radially inward and extending over the entire circumference and contacts one end surface of the roller. The inner ring has an inner ring side roller contact portion at the other axial end portion, which is formed in a manner of protruding radially outward and extending over the entire circumference and contacts the other end surface of the roller. One end of the spacer is arranged between the inner circumferential surface of the outer ring side roller abutment portion and the outer circumferential surface of the inner ring, and the other end of the spacer is arranged between the outer circumferential surface of the inner ring side roller abutment portion and the inner circumferential surface of the outer ring.
3. The cam clutch according to claim 1, Its characteristics are: The outer ring has outer ring side roller contact portions at both axial ends, which are formed in a manner of protruding radially inward and extending over the entire circumference and contacting both end surfaces of the roller. The inner ring has inner ring side roller contact portions at both axial ends, which are formed in a manner of protruding radially outward and extending over the entire circumference and contacting with both end surfaces of the roller. One end portion and the other end portion of the cage are arranged between an outer peripheral surface of the inner ring side roller contact portion and an inner peripheral surface of the outer ring side roller contact portion.
4. The cam clutch according to claim 2 or claim 3, characterized in that: The outer ring side roller contact portion is composed of an inner side flange portion integrally formed on the outer ring. The inner ring side roller contact portion is composed of an outer flange portion integrally formed on the inner ring.
5. The cam clutch according to claim 4, Its characteristics are: The roller has chamfered portions in a C-chamfered shape or an R-chamfered shape at both ends. The roller contact surface of the outer ring side roller contact portion and the roller contact surface of the inner ring side roller contact portion are formed in a tapered shape or a circular arc shape in cross section.
6. The cam clutch according to claim 1, Its characteristics are: The spacer is formed of a resin material.