Cam clutch

Abstract

To provide a cam clutch which can increase an allowable axial load by a simple structure, and is reducible in size and weight.SOLUTION: In a cam clutch 100 of the present invention, a cage ring 130 for holding a cam 140 and a roller 150 is constituted so as to be capable of holding the roller 150 in a state that an outer ring side portion of one end part of the roller 150 in an axial direction is protruded outward in a radial direction rather than an external peripheral face of the cage ring 130, a roller pocket part 136b is formed so as to hold the roller 150 in a state that both end parts of the roller 150 are protruded outward in the axial direction rather than both end faces of the cam 140 in the axial direction which is held to a cam pocket part 136a, and a column part 137 formed between the adjacent pocket parts is formed so as to be located at an inner side in the axial direction rather than an opening edge position of the roller pocket part 136b at the other side in the axial direction.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The present invention relates to a cam clutch that transmits and interrupts rotational torque. [Background technology]

[0002] A known cam clutch has a configuration in which multiple rollers are arranged between the inner and outer rings to maintain the concentricity of the inner and outer rings, simultaneously engage all of the multiple cams arranged between the inner and outer rings with equal load distribution, and receive the radial load acting on the outer or inner ring (see, for example, Patent Document 1).

[0003] The clutch described in Patent Document 1 includes an outer ring, an inner ring, a plurality of sprags and a plurality of rollers arranged circumferentially between the outer ring and the inner ring, a retainer that holds each sprag circumferentially, and an elastic member that biases each sprag. The cage has a pair of annular portions and pillar portions extending axially to connect the annular portions, and the space between adjacent pillar portions in the circumferential direction forms pocket portions for accommodating sprags and pocket portions for accommodating rollers. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2011-012762 Summary of the Invention [Problem to be solved by the invention]

[0005] In the above-mentioned clutch, when the roller and cam are housed in the pocket portion, the annular portions of the retainer are located outside each of the axial ends of the roller and cam, and these annular portions hold the roller and cam in the axial direction, thereby restricting relative movement in the axial direction. For this reason, in the above-mentioned clutch, the axial load must be supported by the cage ring, but in reality, it is difficult to ensure the rigidity to withstand the load. In particular, cage rings are often made of resin material in consideration of productivity and weight reduction, and this problem occurs particularly when the cage ring is made of resin. To address this issue, it may be possible to add a member to support the axial load, but this would require a large space.

[0006] The present invention has been made in light of the above circumstances, and aims to provide a cam clutch that can increase the allowable axial load with a simple structure without increasing the rigidity of the cage ring or arranging additional components, and that can be made smaller and lighter. [Means for solving the problem]

[0007] The present invention solves the above problem by providing a cam clutch comprising an outer ring and an inner ring that are coaxially rotatable relative to each other, a plurality of cams and a plurality of rollers that are arranged circumferentially between the outer ring and the inner ring, a cage ring having a plurality of cam pockets corresponding to each of the plurality of cams and a plurality of roller pockets corresponding to each of the plurality of rollers, and an annular spring that urges each of the plurality of cams into contact with the outer ring and the inner ring and urges the plurality of rollers to press them against the outer ring or the inner ring, wherein the cage ring is configured to be able to hold the rollers in a state where an outer ring side portion at one axial end thereof protrudes radially outward from an outer peripheral surface of the cage ring, and the roller pockets are formed to hold the rollers in a state where both ends of the rollers protrude axially outward from each of both axial end faces of the cam held in the cam pockets, and the pillar portions formed between adjacent pockets are configured so that their other axial end portions on the inner peripheral surface side are positioned axially inward from the opening edge position of the other axial end side of the roller pockets. [Effects of the Invention]

[0008] According to the invention of claim 1, when the rollers are held by the cage ring, the outer ring side portion of one axial end of the roller protrudes radially outward from the outer peripheral surface of the cage ring, and the other axial end of the roller protrudes outward from the other axial end of the column portion, allowing both ends of the roller to come into axial contact with the inner and outer rings, enabling the roller to bear the axial load from the outer or inner ring. This makes it possible to increase the allowable axial load with a simple structure without increasing the rigidity of the cage ring. Furthermore, since both end faces of the rollers can be exposed in the axial direction within the axial length region of the cage ring, a structure can be realized in which the rollers can bear axial loads without increasing the axial dimension of the cam clutch. Furthermore, existing rollers and cams can be used without requiring major changes to the shapes, etc., and therefore increases in manufacturing costs can be suppressed.

[0009] According to the invention of claim 2, one end of the cage ring is disposed 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 cage ring is disposed between the outer circumferential surface of the inner ring-side roller abutment portion and the inner circumferential surface of the outer ring, with the outer ring-side roller abutment portion abutting one end face of the roller and the inner ring-side roller abutment portion abutting the other end face of the roller, thereby making it possible to position the cage ring while effectively utilizing the space between the outer ring and the inner ring.This makes it possible to realize a structure in which the rollers reliably bear axial loads in a small space, and to realize a compact cam clutch.

[0010] According to the invention of claim 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. This allows the inner ring side roller abutment portion and the outer ring side roller abutment portion to abut against both end faces of the roller so as to sandwich the roller in the axial direction, making it possible for the roller to withstand axial loads in both directions.

[0011] According to the invention of claim 4, the outer ring side roller abutment portion is formed by an inner flange portion integrally formed with the outer ring, and the inner ring side roller abutment portion is formed by an outer flange portion integrally formed with the inner ring, so that the cam clutch alone can withstand the axial load. Therefore, it is possible to reliably increase the allowable axial load with a simple structure without providing a separate member for withstanding the axial load.

[0012] According to the invention of claim 5, the rollers have C-chamfered or R-chamfered chamfers at both ends, and the roller contact surfaces of the outer ring-side roller contact portions and the inner ring-side roller contact portions are formed to be tapered or arc-shaped in cross section, so that the outer ring and inner ring contact the rollers in the axial direction at a contact angle. As a result, when an axial load is applied, a radial component force is applied, causing the rollers to come into rolling-sliding contact with the outer ring and inner ring, making it possible to reduce drag torque.

[0013] According to the invention of claim 6, by forming the cage ring from a resin material, the cage ring becomes easy to manufacture and lightweight, and the weight of the cam clutch can be reduced. [Brief explanation of the drawings]

[0014] [Figure 1] 1 is a perspective view showing one configuration example of a cam clutch according to a first embodiment of the present invention, with a part of an outer ring cut away; [Figure 2] 2 is a cross-sectional view perpendicular to the rotation axis at the axial center position of the cam clutch shown in FIG. 1. [Figure 3] FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. [Figure 4] FIG. 3 is a cross-sectional view taken along the line BB in FIG. [Figure 5] FIG. 2 is a perspective view showing the configuration of a cage ring. [Figure 6] FIG. 6 is a cross-sectional view taken along the rotation axis of the cage ring shown in FIG. 5. [Figure 7]FIG. 2 is a cross-sectional view taken along the rotation axis, showing a state in which the cam and roller are held by the cage ring. [Figure 8] FIG. 4 is a perspective view showing another example of the configuration of the cam clutch according to the first embodiment of the present invention, with a part of the outer ring cut away. [Figure 9] 9 is a diagram showing a part of a cross section of the cam clutch shown in FIG. 8 taken along a plane including a rotation axis and a swing center axis of a cam. [Figure 10] 9 is a diagram showing a part of a cross section taken along a plane including the rotation axis and the central axis of the roller in the cam clutch shown in FIG. 8.

[0023] FIG. [Figure 11] 10 is a view showing a part of a cross section cut along a plane including the rotation axis and the oscillation central axis of the cam in yet another configuration example of the cam clutch according to the first embodiment of the present invention. FIG. [Figure 12] 12 is a diagram showing a part of a cross section of the cam clutch shown in FIG. 11 taken along a plane including a rotation axis and a central axis of a roller. FIG. [Figure 13] FIG. 10 is an exploded perspective view showing a configuration example of a cam clutch according to a second embodiment of the present invention. [Figure 14] 14 is a diagram showing a part of a cross section of the cam clutch shown in FIG. 13 taken along a plane including a rotation axis and a swing center axis of a cam. [Figure 15] 14 is a diagram showing a part of a cross section of the cam clutch shown in FIG. 13 taken along a plane including a rotation axis and a central axis of a roller. FIG. DETAILED DESCRIPTION OF THE INVENTION

[0015] [First embodiment] 1 to 4, a cam clutch 100 according to a first embodiment of the present invention includes an outer ring 110 and an inner ring 120 that are coaxially rotatable relative to each other, a cage ring 130 that is disposed coaxially with the outer ring 110 and the inner ring 120 and between the outer ring 110 and the inner ring 120, a plurality of cams 140 and a plurality of rollers 150 that are held by the cage ring 130 and arranged circumferentially in an annular space between the inner peripheral surface of the outer ring 110 and the outer peripheral surface of the inner ring 120, and an annular spring 160 that biases each of the plurality of cams 140 into contact with the outer ring 110 and the inner ring 120 and biases each of the plurality of rollers 150 against the inner ring 120. Reference symbol C in FIGS. 1 to 4 indicates the axis of rotation.

[0016] In this embodiment, the outer ring 110 has an inner flange portion integrally formed at one axial end that protrudes radially inward and extends around the entire circumference, and this inner flange portion forms an outer ring side roller abutment portion 115 that abuts against one end face of the roller 150.

[0017] In this embodiment, the inner ring 120 has an outer flange portion integrally formed at the other axial end that protrudes radially outward and extends around the entire circumference, and this outer flange portion forms an inner ring side roller abutment portion 125 that abuts against the other end face of the roller 150 so as to sandwich the roller 150 axially between itself and the outer ring side roller abutment portion 115.

[0018] As shown in Figures 5 and 6, the cage ring 130 in this embodiment has a large-diameter cylindrical portion 131 and a small-diameter cylindrical portion 133 that continues axially from one end of the large-diameter cylindrical portion 131 via a step portion 132, and is configured to form a two-stage cylindrical shape with the step portion 132 in the center in the axial direction.

[0019] The cage ring 130 is formed with a plurality of cam pocket portions 136a corresponding to each of the plurality of cams 140 and a plurality of roller pocket portions 136b corresponding to each of the plurality of rollers 150, which extend axially from the large diameter cylindrical portion 131 to the small diameter cylindrical portion 133 and penetrate radially from the outer circumferential side to the inner circumferential side. Therefore, the cam pocket 136a and the roller pocket 136b are configured to be able to accommodate the cam 140 and the roller 150 in a state in which one axial end of the cam 140 and the roller 150 protrudes radially outward from the outer circumferential surface of the small-diameter cylindrical portion 133. Therefore, when the cam 140 and the roller 150 are accommodated in the corresponding cam pocket 136a and roller pocket 136b, respectively, the outer ring side portion of one axial end face is exposed in the axial direction.

[0020] The pocket portion 136a for the cam and the pocket portion 136b for the roller are configured to surround the cam 140 and the roller 150 on all four sides when viewed in a radial plane, so that the circumferential and axial movement of the cam 140 and the roller 150 is restricted. In addition, the cam support surface and roller support surface of the pillar portion 137 formed between the adjacent cam pocket portion 136a and roller pocket portion 136b are formed in a shape that restricts movement of the cam 140 and roller 150 toward the inner wheel side.

[0021] In this embodiment, six roller pockets 136b are formed so that the six rollers 150 are arranged at equal intervals in the circumferential direction, and six cam pockets 136a are formed so that one cam 140 is positioned between each adjacent roller 150, and the six cams 140 are arranged at predetermined intervals. In this cam clutch 100, by providing rollers 150, it is possible to maintain the concentricity of the outer ring 110 and the inner ring 120 and to support a radial load without using other components such as bearings, but the number of rollers 150 is not particularly limited as long as it is at least three. Furthermore, the number and arrangement pattern of cams 140 are not particularly limited either and can be changed as appropriate depending on the purpose.

[0022] As shown in FIG. 7, the roller pocket portion 136b is formed to hold the roller 150 with both ends of the roller 150 protruding axially outward from both axial end faces of the cam 140 housed in the cam pocket portion 136a.

[0023] Each of the plurality of cams 140 has a groove 141 at the center in the axial direction, which can be engaged with a spring 160 . In this embodiment, the bottom of groove portion 141 has an inclined shape with a convex portion at an eccentric position, and spring 160 is configured to press the convex portion at the bottom of groove portion 141, causing cam 140 to swing in the direction of contacting outer ring 110 and inner ring 120.

[0024] The rollers 150 are configured so that their axial dimension is larger than that of the cam 140, and have a groove 151 in the center in the axial direction that can engage with a spring 160. The outer peripheral edge of the groove 151 is chamfered to prevent it from getting caught on the spring 160.

[0025] The spring 160 is looped around the groove 141 of the cam 140 and the groove 151 of the roller 150 so as to restrict movement of the cam 140 and the roller 150 toward the outer ring side, and is engaged with the step 132 of the cage ring 130 .

[0026] In the cam clutch 100, a counterbore recess 134 is formed in the opening at the other end of the large-diameter cylindrical portion 131 of the casing 130. As shown in Fig. 6, the recess 134 is formed so that its bottom surface is located axially inward from the axial position of the edge of the opening at the other end of the roller pocket 136b, so that the other axial end of the inner circumferential surface of the pillar portion 137 is located axially inward from the edge of the opening at the other axial end of the roller pocket 136b. Therefore, as shown in Fig. 7, when the roller 150 is housed in the roller pocket 136b, the inner ring side portion of the other axial end face of the roller 150 is exposed in the axial direction, allowing the outer ring 110 and the inner ring 120 to come into contact with the roller 150 in the axial direction. In this way, both end faces of the rollers 150 can be exposed in the axial direction within the axial length region of the cage ring 130, making it possible to realize a structure in which the rollers 150 can withstand axial loads without increasing the axial dimension of the cam clutch 100.

[0027] One end of the small-diameter cylindrical portion 133 of the cage ring 130 is disposed between the inner circumferential surface of the outer-ring-side roller abutment portion 115 and the outer circumferential surface of the inner ring 120, and the other end of the large-diameter cylindrical portion 131 of the cage ring 130 is disposed between the outer circumferential surface of the inner-ring-side roller abutment portion 125 and the inner circumferential surface of the outer ring 110. This causes the outer-ring-side roller abutment portion 115 to abut against one end surfaces of the rollers 150, and the inner-ring-side roller abutment portion 125 to abut against the other end surfaces of the rollers 150. This makes it possible to effectively utilize the space between the outer ring 110 and the inner ring 120, and to support an axial load in one direction from the outer ring 110 or the inner ring 120 in a small space. Therefore, without increasing the rigidity of the cage ring 130 or providing a separate member for supporting the axial load, a larger allowable axial load can be achieved with a simple structure, and the cam clutch 100 can be made more compact. Furthermore, existing cams 140 and rollers 150 can be used without requiring significant changes to their shapes, etc., and therefore, increases in manufacturing costs can be suppressed.

[0028] As described above, in the cam clutch 100, the outer ring 110 and the inner ring 120 do not come into axial contact with the cam 140 or the cage ring 130, but only come into axial contact with the rollers 150, allowing the rollers 150 to bear the axial load. For this reason, the cage ring 130 only needs to have enough rigidity to regulate and hold the positions of the cam 140 and the rollers 150, and the cage ring 130 can be made of a resin material. By making the cage ring 130 out of a resin material, the cage ring 130 becomes easy to manufacture and lightweight, making it possible to reduce the weight of the cam clutch 100.

[0029] In the above embodiment, the axial load is received by the flat end surface of the roller, but the axial load may be received obliquely by a surface that is inclined relative to the axial direction.

[0030] Figure 8 is an oblique view showing another example of the configuration of the cam clutch according to the first embodiment of the present invention, with a portion of the outer ring broken away; Figure 9 is a view showing a portion of a cross section of the cam clutch shown in Figure 8 taken along a plane including the rotation axis and the cam oscillation center axis; and Figure 10 is a view showing a portion of a cross section of the cam clutch shown in Figure 8 taken along a plane including the rotation axis and the roller center axis. This cam clutch 100 has the same configuration as the above-mentioned cam clutch 100, except for the configuration of the roller 150, and the configurations of the outer ring side roller abutment portion 115 and the inner ring side roller abutment portion 125.For convenience, the same components are given the same symbols and their explanations will be omitted.

[0031] The roller 150 has chamfered portions 152 at both ends, each having a C-chamfer shape that is configured so that the diameter decreases axially outward, and is configured so that the chamfered portions 152 are exposed in the axial direction when the roller 150 is accommodated in the roller pocket portion 136b of the cage ring 130.

[0032] The outer ring 110 has an inner flange portion integrally formed at one axial end that protrudes radially inward and extends around the entire circumference, and this inner flange portion forms an outer ring side roller abutment portion 115 that abuts against one end face of the roller 150. In this embodiment, an inner surface 116 constituting the roller contact surface of the outer ring side roller contact portion 115 is formed in a tapered shape so as to extend at an angle toward the inner ring as it approaches one end in the axial direction.

[0033] The inner ring 120 has an outer flange portion integrally formed at the other axial end thereof that protrudes radially outward and extends around the entire circumference, and this outer flange portion forms an inner ring side roller abutment portion 125 that abuts against the other end face of the roller 150 so as to sandwich the roller 150 axially between itself and the outer ring side roller abutment portion 115. In this embodiment, an inner surface 126 constituting the roller contact surface of the inner ring side roller contact portion 125 is formed in a tapered shape so as to extend at an angle toward the outer ring side as it approaches the other axial end side.

[0034] With the cam clutch 100 configured as described above, when one end of the small diameter cylindrical portion 133 is disposed between the inner circumferential surface of the outer ring side roller abutment portion 115 and the outer circumferential surface of the inner ring 120 and the other end of the large diameter cylindrical portion 131 is disposed between the outer circumferential surface of the inner ring side roller abutment portion 125 and the inner circumferential surface of the outer ring 110, the outer ring side roller abutment portion 115 of the outer ring 110 and the inner ring side roller abutment portion 125 of the inner ring 120 abut against the roller 150 in the axial direction at a contact angle. For this reason, when an axial load is applied, a radial component force acts, causing the roller 150 to come into rolling and sliding contact with the outer ring 110 and the inner ring 120, making it possible to reduce drag torque.

[0035] Furthermore, as shown in Figures 11 and 12, the same effect as above can be obtained by forming the chamfered portions 152 at both ends of the roller 150 into an R-chamfered shape and forming the roller contact surfaces at the outer wheel side roller contact portion 115 and the inner wheel side roller contact portion 125 into arc-shaped cross sections.

[0036] The above describes a configuration in which the roller abutment portion is formed integrally with the outer and inner rings by configuring the roller abutment portion using a flange portion, but 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 and inner rings, and may instead be configured by providing separate members that abut against the end faces of the rollers in a state in which axial movement is prohibited. Furthermore, although the cage ring has been described as having a two-stage cylindrical shape, the cage ring may be configured in any manner so that, when the rollers are placed in the roller pockets, the outer ring side portion of one end face of the roller and the inner ring side portion of the other end face of the roller are exposed in the axial direction. For example, the cage ring may be configured as a cylindrical member having a uniform thickness in the axial direction, with a step formed on the outer peripheral surface of one end of the cylindrical member that extends around the entire circumferential direction so as to expose the outer ring side portion of one end face of the roller in the axial direction, and a countersunk recess formed in the opening of the other end of the cylindrical member so as to expose the inner ring side portion of the other end face of the roller in the axial direction.

[0037] [Second embodiment] The cam clutch in the first embodiment is configured so that rollers receive axial loads in one direction, but below we will explain a cam clutch that is configured so that rollers can receive axial loads in both directions.

[0038] As shown in Figures 13 to 15, the cam clutch 100 of the second embodiment includes an outer ring 110 and an inner ring 120 that are coaxially rotatable relative to each other, a cage ring 130 that is arranged coaxially with the outer ring 110 and the inner ring 120 and between them, a plurality of cams 140 and a plurality of rollers 150 that are held by the cage ring 130 and arranged circumferentially in the annular space between the inner surface of the outer ring 110 and the outer surface of the inner ring 120, an annular spring 160 that urges each of the plurality of cams 140 to contact the outer ring 110 and the inner ring 120 and urges each of the plurality of rollers 150 to press them against the inner ring 120, a backing plate 117 that is arranged between the outer ring 110 and the inner ring 120 so as to abut the other end face of the roller 150, and a retaining ring 118 that restricts axial movement of the backing plate 117. 13 to 15, the symbol C indicates the rotation axis.

[0039] In this embodiment, the outer ring 110 has an inner flange portion integrally formed at one axial end that protrudes radially inward and extends around the entire circumference, and this inner flange portion forms a first outer ring side roller abutment portion 115a that abuts against one end face of the roller 150. A groove extending over the entire circumference is formed on the inner peripheral surface at the other end of the outer ring 110, and a circular plate-shaped retaining ring 118 is fitted into this groove, thereby fixing a circular plate-shaped receiving plate 117 in the axial direction to the outer ring 110. In this embodiment, the receiving plate 117 and the retaining ring 118 form a second outer ring side roller abutment portion 115b that abuts against the other end surface of the roller 150.

[0040] In this embodiment, the inner ring 120 is integrally formed with outer flange portions that protrude radially outward and extend around the entire circumferential direction at both axial ends, and the outer flange portion at one end forms a first inner ring side roller abutment portion 125a that abuts against one end face of the roller 150 so as to sandwich the roller 150 axially between it and the second outer ring side roller abutment portion 115b.Furthermore, the outer flange portion at the other end forms a second inner ring side roller abutment portion 125b that abuts against the other end face of the roller 150 so as to sandwich the roller 150 axially between it and the first outer ring side roller abutment portion 115a.

[0041] The cage ring 130 has the same configuration as the cage ring 130 in the cam clutch 100 of the first embodiment described above, and is configured so that when the roller 150 is accommodated in the roller pocket portion 136b, 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.

[0042] One end of the small diameter cylindrical portion 133 in the cage ring 130 is positioned between the outer peripheral surface of the first inner wheel side roller abutment portion 125a and the inner peripheral surface of the first outer wheel side roller abutment portion 115a, and the other end of the large diameter cylindrical portion 131 is positioned between the outer peripheral surface of the second inner wheel side roller abutment portion 125b and the inner peripheral surface of the receiving plate 117 that constitutes the second outer wheel side roller abutment portion 115b. As a result, the first outer wheel side roller abutment portion 115a and the second inner wheel side roller abutment portion 125b are respectively brought into contact with one end face and the other end face of the roller 150 so as to sandwich the roller 150 in the axial direction, and the second outer wheel side roller abutment portion 115b and the first inner wheel side roller abutment portion 125a are respectively brought into contact with the other end face and one end face of the roller 150 so as to sandwich the roller 150 in the axial direction.

[0043] This configuration makes it possible for the roller 150 to receive axial loads in both directions from the outer ring 110 or the inner ring 120 in a small space by effectively utilizing the space between the outer ring 110 and the inner ring 120.

[0044] In this embodiment, an example has been described in which the other-end roller contact portion of the outer ring is configured with a backing plate and a snap ring, but the other-end roller contact portion may also be configured with an inner flange portion, thereby being formed integrally with the outer ring. Furthermore, the one-end roller contact portion of the outer ring may also be configured with a backing plate provided to restrict axial movement with a snap ring, thereby being formed separately from the outer ring. The same is true for the roller contact portions of the inner ring, where the one-end roller contact portion and / or the other-end roller contact portion may also be configured with a backing plate provided to restrict axial movement with a snap ring, thereby being formed separately from the inner ring. Furthermore, in this embodiment, the axial load is received by flat surfaces at both ends of the roller, but similar to the cam clutch in the first embodiment, the axial load may be received obliquely by surfaces inclined relative to the axial direction.

[0045] 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 modifications can be made without departing from the present invention as set forth in the claims. [Explanation of symbols]

[0046] 100 ··· Cam clutch 110 Outer ring 115 Outer ring roller contact portion 115a... First outer ring side roller contact portion 115b Second outer ring side roller contact portion 116 ··· Interior 117 ··· Receiving plate 118 ··· Retaining ring 120 ··· Inner circle 125 Inner ring roller contact portion 125a... First inner ring side roller contact portion 125b Second inner ring side roller contact portion 126 ··· Interior 130 ··· Cage ring 131 Large diameter cylindrical portion 132 ··· Stepped section 133 Small diameter cylindrical portion 134 Recess 136a Cam pocket 136b Roller pocket 137 · · Column part 140 Cam 141 Groove 150 ··· Laura 151 Groove 152... Chamfered part 160 ··· Spring C...Rotation axis center

Claims

1. A cam clutch comprising: an outer ring and an inner ring which are coaxially arranged to be relatively rotatable; a plurality of cams and a plurality of rollers which are arranged to be aligned in a circumferential direction between the outer ring and the inner ring; a cage ring having a plurality of cam pockets corresponding to each of the plurality of cams and a plurality of roller pockets corresponding to each of the plurality of rollers; and an annular spring which biases each of the plurality of cams into contact with the outer ring and the inner ring and biases the plurality of rollers to press against the outer ring or the inner ring, the cage ring is configured to be capable of holding the rollers in a state in which an outer ring side portion at one axial end of the roller protrudes radially outward from an outer peripheral surface of the cage ring, the roller pocket portion is formed to hold the roller in a state in which both ends of the roller protrude axially outward from both axial end faces of the cam held in the cam pocket portion, a pillar portion formed between adjacent pocket portions is formed so that the other axial end portion on the inner circumferential surface side is positioned axially inward from the opening edge position on the other axial end side of the pocket portion for the roller.

2. the outer ring has an outer ring side roller abutment portion formed at one axial end thereof so as to protrude radially inward and extend over the entire circumferential direction and abut against one end surface of the roller, the inner ring has an inner ring side roller abutment portion formed at the other axial end portion thereof so as to protrude radially outward and extend over the entire circumferential direction and abut against the other end surface of the roller, 2. A cam clutch as described in claim 1, characterized in that one end of the cage ring is disposed between the inner peripheral surface of the outer ring side roller abutment portion and the outer peripheral surface of the inner ring, and the other end of the cage ring is disposed between the outer peripheral surface of the inner ring side roller abutment portion and the inner peripheral surface of the outer ring.

3. the outer ring has outer ring side roller abutment portions formed at both axial ends thereof so as to protrude radially inward and extend over the entire circumferential direction and abut against both end faces of the rollers, the inner ring has inner ring side roller abutment portions formed at both axial ends thereof so as to protrude radially outward and extend over the entire circumferential direction and abut against both end faces of the rollers, 2. The cam clutch according to claim 1, wherein one end and the other end of the cage ring are disposed between the outer peripheral surface of the inner ring side roller abutment portion and the inner peripheral surface of the outer ring side roller abutment portion.

4. The outer ring side roller contact portion is constituted by an inner flange portion integrally formed with the outer ring, 4. A cam clutch according to claim 2, wherein the inner ring side roller contact portion is constituted by an outer flange portion formed integrally with the inner ring.

5. The roller has chamfered portions at both ends, the chamfered portions being C-chamfered or R-chamfered, 5. The cam clutch according to claim 4, wherein a roller contact surface of the outer ring side roller contact portion and a roller contact surface of the inner ring side roller contact portion are formed into a tapered shape or a cross-sectional arc shape.

6. 2. The cam clutch according to claim 1, wherein the cage ring is made of a resin material.

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