Cam clutch unit

Abstract

To provide a cam clutch unit which prevents component parts from floating or dropping even in an item state, is easy to handle, can reduce man-hours when manufacturing a cam clutch, can reduce difficulty and can reduce width.SOLUTION: A cam clutch unit includes: a plurality of cams arranged between an inner ring and an outer ring relatively rotatable provided coaxially; a cage ring having a plurality of pocket parts regulating a relative movement of the cam in a circumferential direction; and an annular spring energizing the cam. The cam has an engaging step part engageable with the spring on one end surface in the axial direction. The cage ring has a plurality of hook parts regulating movements of the annular into an axial direction of the spring. The hook part has a pressing part which can press the cam with the spring to the other end surface side in the axial direction.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a cam clutch unit that transmits and blocks torque between an input shaft and an output shaft.

Background Art

[0002] As a cam clutch unit, there are known ones having a plurality of cams and a plurality of rollers disposed between an inner ring and an outer ring that are relatively rotatable coaxially, and a cage ring having a plurality of pocket portions that regulate the relative circumferential movement of the cams and the rollers, and an annular spring that biases the cams. A cam clutch unit 500 provided with cams and rollers, as shown in FIGS. 17 to 21 for example, has a plurality of cams 530 and a plurality of rollers 540 circumferentially disposed between an inner ring and an outer ring that are relatively rotatable coaxially. The cams 530 and the rollers 540 are accommodated in the pocket portions 551 of a cage ring 550, and the relative circumferential movement of the cams 530 and the rollers 540 is regulated. The cams 530 and the rollers 540 each have circumferential groove portions 535 and 545, and an annular spring 560 is accommodated in the groove portions 535 and 545 so as to bias the cams 530 and the rollers 540 toward the inner ring side.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In known cam clutch units, the cam 530 and roller 540, which require materials resistant to wear and impact, have circumferential grooves 535 and 545 in the center where an annular spring 560 is housed. As a result, the manufacturing process for the cam 530 and roller 540 is complex and requires many machining steps, and there are limitations on the width dimension during manufacturing, making it impossible to reduce the width. For example, as shown in Patent Document 1, a system is known in which a spring-driven biasing portion is provided on both axial ends of the cam and roller. However, the cam requires a locking structure to prevent the spring from falling out in the axial direction, and although the difficulty of machining the cam and roller is somewhat reduced, the number of machining steps cannot be reduced.

[0005] To address the above-mentioned problems, for example, as shown in Figure 22(a), an engagement step portion that can engage with an annular spring 660 is formed on one axial end face of the cam 630, thereby biasing the cam 630 radially inward by the spring 660, and a hook portion 653 is formed on the outer circumference of the cage ring 650 to restrict the axial movement of the spring 660. However, in such a cam clutch unit 600, as shown in Figure 22(b), the cam 630 is pressurized radially inward (downward in Figure 22), so a moment is applied to the cam 630, causing it to tilt and float outward. As a result, before assembly of the cam clutch unit 600, the cam 630 may fall off the cage ring 650 during transport or other situations, potentially creating a new problem of extremely poor handling during assembly of the cam clutch unit 600. By adjusting the position of the spring engagement step in the cage ring and forcibly pressurizing the cam in the axial direction, it is possible to prevent the cam from falling off even when the cam clutch unit is in a standalone state. However, this makes the assembly of the spring difficult, and when such a cam clutch unit is assembled, the sliding resistance with the cam increases during the normal operation of the cam clutch, resulting in poor wear resistance and a deterioration of drag torque.

[0006] The present invention aims to solve the above-mentioned problems and to provide a cam clutch unit that is easy to handle, with no loosening or detachment of components even when the cam clutch unit is in a standalone state, and that reduces the number of processing steps and difficulty during manufacturing, as well as enabling a thinner width. [Means for solving the problem]

[0007] The present invention relates to a cam clutch unit comprising: a plurality of cams disposed between an inner ring and an outer ring that are coaxially rotatable relative to each other; a cage ring having a plurality of pockets that restrict the relative movement of the cams in the circumferential direction; and an annular spring that biases the cams, The cam has an engagement step on one axial end face that can engage with the spring, The cage ring has a plurality of hook portions that restrict the axial movement of the annular spring, The aforementioned hook portion has a pressing portion that can press the cam against the other end face in the axial direction by the spring, thereby solving the aforementioned problem. [Effects of the Invention]

[0008] According to the cam clutch unit of the present invention, the hook portion has a pressing portion that can press the cam to the other axial end face side by a spring, so that the cam is pressed to the other axial end face side by the spring and pressed against the cage ring, which prevents the cam and other components from floating or falling off when the cam clutch unit is in its standalone state, and provides excellent handling when the cam clutch unit is in its standalone state. Furthermore, the cam has an engagement step on one axial end face that can engage with the spring, resulting in a simpler structure, fewer processing steps during manufacturing, and a thinner design. In addition, the cage ring has multiple hooks that restrict the axial movement of the annular spring, eliminating the need to machine the engagement step on the end face of the cam into a shape that restricts the axial movement of the spring, further reducing processing time and difficulty.

[0009] Furthermore, in this invention, because a tapered surface inclined toward the cam is formed on the hook portion, in the standalone state of the cam clutch unit, there are no members that obstruct the oscillating rotation of the inner ring and the cam. As a result, the cam is displaced radially inward, causing the spring to automatically move to the bottom of the tapered groove space formed between the tapered surface of the hook portion and the cam, which has a narrower axial width. Consequently, the cam is pressed toward the other end face in the axial direction, and ultimately, the lifting or detachment of components such as the cam can be reliably prevented. On the other hand, by utilizing the difference in the amount of cam drop between the standalone cam clutch unit and when assembled, the cam is displaced to its original radially outward position in the cam clutch after assembly. As a result, the spring automatically moves to the upper part of the tapered groove space, eliminating the axial pressure on the other end face of the spring. Consequently, the spring and the cage ring are not in contact, and the sliding resistance between one end face of the cam and the spring, as well as the sliding resistance between the other end face of the cam and the cage ring, is suppressed. This results in excellent wear resistance and prevents deterioration of drag torque. Furthermore, since the radial and axial widths of the tapered groove space are variable, if the maximum distance between the cam and the cage ring in the tapered groove space is designed to be greater than or equal to the spring diameter, sufficient insertion width can be secured when inserting the spring between the cage ring and the cam positioned in the pocket, thus simplifying the assembly of the cam clutch unit. Furthermore, even if the dimensional accuracy of each component is somewhat low, a stable pressing force can be obtained on the cam by the spring, resulting in a high yield of cam clutch units and excellent productivity.

[0010] Furthermore, in the present invention, since the hook portion is provided with a stepped portion that protrudes toward the cam, in the standalone state of the cam clutch unit, there is no member that obstructs the oscillating rotation of the inner ring and the cam. As a result, the cam is displaced radially inward (drops in), and the spring automatically fits into the step with a narrow axial width at the bottom of the stepped groove space formed between the stepped portion of the hook and the cam. Consequently, the cam is pressed toward the other end face in the axial direction, and as a result, it is possible to reliably prevent the cam and other components from floating or falling off. On the other hand, by utilizing the difference in the amount of cam drop between the standalone cam clutch unit and when assembled, the cam is displaced to its original radially outward position in the cam clutch after assembly. As a result, the spring automatically moves to the wider upper step in the stepped groove space, eliminating the axial pressure on the other end face of the spring. Consequently, the spring and the cage ring remain in non-contact, and the sliding resistance between one axial end face of the cam and the spring, as well as the sliding resistance between the other axial end face of the cam and the cage ring, is suppressed. This results in excellent wear resistance and prevents deterioration of drag torque. Furthermore, since the radial and axial widths of the stepped groove space are variable, if the maximum distance between the cam and the cage ring in the stepped groove space is designed to be greater than or equal to the spring diameter, sufficient insertion width can be secured when inserting the spring between the cage ring and the cam positioned in the pocket, thus simplifying the assembly of the cam clutch unit. Furthermore, even if the dimensional accuracy of each component is somewhat low, a stable pressing force can be obtained on the cam by the spring, resulting in a high yield of cam clutch units and excellent productivity.

[0011] In this invention, the cam has a regulating step on the end face opposite to the engaging step, and the cage ring has a regulating projection in its pocket. As a result, the regulating step of the cam is locked to the regulating projection of the cage ring, preventing the cam from tilting axially even when it is pressed axially by a spring. Therefore, in the standalone state of the cam clutch unit, it is possible to reliably prevent the cam and other components from floating or falling off. Furthermore, compared to a case where the cam's lifting or detachment is suppressed solely by the axial pressure of the spring, it becomes possible to configure the spring pressure of the cam clutch unit in its standalone state to be smaller. As a result, the spring is less likely to press against the cam during assembly, thus reliably suppressing the occurrence of sliding resistance between one axial end face of the cam and the spring, and sliding resistance between the other axial end face of the cam and the cage ring. Furthermore, by reducing the clearance between the other end face of the cam in the axial direction and the cage ring, the axial protrusion height of the regulating step can be reduced. Therefore, if the overall axial width of the cam is designed to be smaller than the axial width of the pocket portion of the cage ring, the ease of assembly of the cam clutch unit can be further improved.

[0012] In this invention, the roller is positioned between the inner and outer rings, and the axial dimension of the roller is less than or equal to the axial dimension excluding the engagement step of the cam. As a result, the roller is only constrained in the axial direction and can rotate freely, and there is almost no frictional sliding between it and the spring, thus reducing the rotational resistance caused by the roller. [Brief explanation of the drawing]

[0013] [Figure 1] A perspective view of the cam clutch unit of one embodiment of the present invention. [Figure 2] Figure 1 shows a front view of the cam clutch unit as seen in the direction of the rotation axis. [Figure 3] Figure 1 shows a cross-sectional view of the cam clutch unit, cut along a plane horizontal to the axis of rotation. [Figure 4](a) Front view and (b) side view of the cam of the cam clutch unit shown in FIG. 1. [Figure 5] (a) Front view and (b) side view of the roller of the cam clutch unit shown in FIG. 1. [Figure 6] Perspective view of the cage ring of the cam clutch unit shown in FIG. 1. [Figure 7] Cross-sectional view of the cam clutch unit shown in FIG. 1 cut along a plane horizontal to the rotation axis. [Figure 8] (a) Partial cross-sectional view of the cam clutch unit in a single-piece state and (b) partial cross-sectional view when assembled to the cam clutch, of the cam clutch unit shown in FIG. 1. [Figure 9] (a) Partial front view of the cam clutch unit in a single-piece state and (b) partial front view when assembled to the cam clutch, which is a partial front view of the cam clutch unit shown in FIG. 1 seen in the direction of the rotation axis. [Figure 10] Partial cross-sectional view of the cam clutch unit of another embodiment of the present invention. [Figure 11] Bottom view showing the other end face in the axial direction of the cam of the cam clutch unit shown in FIG. 10. [Figure 12] Partial cross-sectional view of the cam clutch unit of yet another embodiment of the present invention. [Figure 13] Perspective view of the cage ring of the cam clutch unit shown in FIG. 12. [Figure 14] Partial cross-sectional view of the cam clutch unit of yet another embodiment of the present invention. [Figure 15] Perspective view of the cage ring of the cam clutch unit shown in FIG. 14. [Figure 16] Perspective view of the cage ring related to the cam clutch unit of yet another embodiment of the present invention. [Figure 17] Perspective view of a conventional cam clutch unit. ​​​​​​​Figure 17 shows a side view and a front view of the rollers of the cam clutch unit. [Figure 21] Partial side view and cross-sectional view of the cam clutch unit shown in Figure 17. [Figure 22] A schematic, partially enlarged cross-sectional view of an example of a cam clutch unit. [Modes for carrying out the invention]

[0014] The cam clutch unit of the present invention comprises a plurality of cams arranged between an inner ring and an outer ring that are coaxially rotatable relative to each other, a cage ring having a plurality of pockets that restrict the relative movement of the cams in the circumferential direction, and an annular spring that biases the cams, wherein the cams have an engagement step on one axial end face that can engage with the spring, the cage ring has a plurality of hooks that restrict the axial movement of the annular spring, and the hooks have a pressing portion that can press the cams to the other axial end face by the spring, thereby providing a basically simple structure, reducing the number of processing steps and difficulty during manufacturing, and enabling a thinner width, further reducing the number of processing steps and difficulty by eliminating the need to process the engagement step on the end face of the cam to a shape that restricts the axial movement of the spring, and moreover, preventing the detachment of components such as the cams when the cam clutch unit is in a standalone state, and providing a cam clutch unit that offers excellent handling when the cam clutch unit is in a standalone state, the specific configuration of the cam clutch unit may be any. [Examples]

[0015] As shown in Figures 1 to 9, the cam clutch unit 100 according to the first embodiment of the present invention comprises a plurality of cams 130 as engaging elements that transmit and interrupt torque between the inner ring and the outer ring in an annular space between the raceway surface of the inner ring and the raceway surface of the outer ring, which are provided to be rotatable relative to each other on the same axis; a plurality of rollers 140 that allow the inner ring and the outer ring to rotate freely; a cage ring 150 having a plurality of pockets 151, 152 that restrict the relative movement of the cams 130 and rollers 140 in the circumferential direction; and an annular spring 160 that biases each of the plurality of cams 130 in the direction of meshing with the inner ring and the outer ring.

[0016] Each of the multiple cams 130 has an engagement step 131 on one axial end face that can engage with an annular spring 160, as shown in Figure 4. In this embodiment, the engagement step 131 has an inclined shape with the left side of the figure facing the outer circumference when the cam 130 is free. When the spring 160 presses the left side of the engagement step 131, the cam 130 is biased toward the inner ring and is also biased to swing in the direction in which the cam 130 operates. As shown in Figure 5, the multiple rollers 140 do not have grooves or steps, and in this embodiment, the axial dimension rw of the roller 140 is less than or equal to the axial dimension cw of the cam 130 excluding the engagement step 131. In this embodiment, the outer edges of both end faces of the roller 140 are chamfered to prevent snagging with the spring 160.

[0017] As shown in Figure 6, the cage ring 150 has a pocket portion 151 that houses the cam 130 and restricts its relative movement in the circumferential direction, a pocket portion 152 that houses the roller 140 and restricts its relative movement in the circumferential direction, and a plurality of hook portions 153 that restrict the movement of the annular spring 160 to one side in the axial direction. Specifically, the cage ring 150 has an annular support base 157 that connects the plurality of pocket portions 151 and 152 and restricts the movement of the cam 130 and roller 140 to the other side in the axial direction. In this embodiment, the pocket portion 151 that accommodates the cam 130 and the pocket portion 152 that accommodates the roller 140 of the cage ring 150 are arranged alternately in the circumferential direction, with pocket portions 151 for two adjacent cams 130 and pocket portions 152 for one roller 140. That is, the pocket portions 152 for the rollers 140 are arranged regularly every two. In each pocket section 151, 152, the axial movement of the cam 130 and roller 140 to the other side is restricted by the other side in the axial direction, while movement to one side in the axial direction is restricted by the spring 160. Furthermore, in this embodiment, as shown in Figure 7, the surface 152A of the pocket portion 152 that houses the roller 140, adjacent to the roller 140 (the surface of the partition wall 158, described later, that faces the roller 140), has a shape that conforms to the outer shape of the roller 140 and is formed in a shape that restricts the movement of the roller 140 toward the outer ring and inner ring sides. This prevents the roller 140 from falling out toward the outer circumference during the manufacturing process of the cam clutch. In this specification, "one side in the axial direction" refers to one end face side of the cam clutch unit where the engagement step of the cam is provided, and "the other side in the axial direction" refers to the opposite side.

[0018] In this embodiment, the cage ring 150 has a plurality of hook portions 153 that restrict the axial movement of the annular spring 160 to one side. The cage ring 150 has a partition wall 158 that separates two circumferentially adjacent pocket portions 151, 152 that house the cam 130 or roller 140, and is formed so as to protrude outward at one end in the axial direction. The hook portion 153 has a tapered surface 156 that slopes from the radial outer circumference to the inner circumference, and from one side in the axial direction to the other, approaching the cam 130. The tapered surface 156 facing the cam 130 functions as a pressing portion that can press the cam 130 to the other side in the axial direction by the spring 160. To explain in more detail, as shown in Figure 8, if we virtually superimpose the tapered surface 156 of the hook portion 153 and the cam 130 in a cross-section along the axial direction, a tapered groove space S1 is formed between them, where the axial width decreases as you move from one side (left side in Figure 8) to the other side (right side in Figure 8) in the axial direction. Then, as shown in Figures 8(a) and 9(a), in the standalone state of the cam clutch unit 100, there are no members that hinder the oscillating rotation of the inner ring and the cam 130, so the cam 130 is displaced radially inward (drops in), causing the spring 160 to automatically move to the narrower bottom S1a of the tapered groove space S1 in the axial direction. Consequently, the cam 130 is pressed to the other side in the axial direction (right side in Figure 8), and as a result, the other axial end face of the cam 130 is pressed against the support base 157 of the cage ring 150. On the other hand, in the cam clutch after the cam clutch unit 100 has been assembled, by utilizing the difference in the amount of cam 130 drop between the standalone state of the cam clutch unit 100 and the assembled state (see symbol d in Figure 8), the cam 130 is displaced to its original radially outward position, as shown in Figures 8(b) and 9(b), causing the spring 160 to automatically move to the upper part S1b of the tapered groove space S1. Consequently, the pressing force on the other axial side of the spring 160 (right side in Figure 8) is eliminated, resulting in non-contact between the spring 160 and the cage ring 150. Furthermore, the sliding resistance between the non-protruding surface 132 without the engagement step 131 on one axial end face of the cam 130 and the spring 160, and the sliding resistance between the other axial end face of the cam 130 and the cage ring 150 are suppressed.

[0019] In this embodiment, the number of cams 130 is twice the number of rollers 140, and the rollers 140 are arranged every two cams 130. However, the number and arrangement of the cams 130 and rollers 140 can be any number. Furthermore, the shape of the cam 130 can be anything, for example, it may be sprag-shaped. Furthermore, the arrangement of the hook portions 153 can be any arrangement depending on the number and arrangement of the cams 130 and rollers 140, and the radial height of each hook portion 153 may be uniform, or the height may differ depending on the circumferential position. Furthermore, the tapered surface 156 only needs to be formed on at least one of the multiple hook portions 153 provided in the circumferential direction. By appropriately setting the arrangement and height of the hook portion 153, as well as the presence or absence of the tapered surface 156, according to the number and arrangement of the cams 130 and rollers 140, each cam 130 can be operated with uniform precision, similar to the embodiment described above.

[0020] In the cam clutch unit 100 according to the above embodiment, as shown in Figure 10, the cam 130 can also be configured to have a restricting step portion 133 that protrudes axially from the end face opposite to the engaging step portion 131. Specifically, the pocket portion 151 of the cage ring 150 has a restricting projection 155 that restricts the inclination of the cam 130 on the surface adjacent to the restricting step portion 133 of the cam 130 in the axial direction, i.e., on the radially inward side of the support base 157. As a result, even when pressed radially inward by the spring 160 along with the other side in the axial direction, the restricting step portion 133 of the cam 130 will be locked into the restricting projection 155 of the cage ring 150, thus reliably preventing the cam 130 from lifting or falling off the cage ring 150. The restricting step portion 133 on the cam 130 can have various shapes, as long as it is in a position and shape that does not interfere with the cage ring 150 when the cam 130 is free-rotating or engaged, as shown in the shaded area of ​​Figure 11. In other words, the position where the restricting step portion 133 is formed varies depending on the shape of the cage ring 150 and the operating range (rolling amount) of the cam 130. [Examples]

[0021] The cam clutch unit 200 according to the second embodiment of the present invention differs in the shape of the hook portion 153 in the cam clutch unit 100 according to the first embodiment, but the other configurations are the same as those of the first embodiment described above. In Figures 12 and 13 showing the second embodiment, components that have the same configuration as the cam clutch unit 100 according to the first embodiment are denoted by the same reference numerals. In this embodiment, the hook portion 253 of the cage ring 250 of the cam clutch unit 200 is provided with a stepped portion 256 that protrudes toward the cam 130 on the radial inner circumference side (lower side in Figure 12) so as it moves from one side in the axial direction toward the other side toward the cam 130, and the stepped portion 256 facing the cam 130 functions as a pressing portion that can press the cam 130 toward the other side in the axial direction (right side in Figure 12) by the spring 160. In Figure 12, the staircase section 256 may consist of one step or two or more steps. Furthermore, the stair section 256 only needs to be formed on at least one of the multiple hook sections 253 provided in the circumferential direction.

[0022] In the cam clutch unit 200, if the stepped portion 256 of the hook portion 253 and the cam 130 are virtually superimposed in a cross-section along the axial direction, a stepped groove space S2 is formed between them, where the axial width gradually decreases as you move from one side in the axial direction (left side in Figure 12) to the other side (right side in Figure 12). In the standalone state of the cam clutch unit 200, since there are no members that hinder the oscillating rotation of the inner ring and the cam 130, the cam 130 is displaced radially inward (drops in), causing the spring 160 to automatically move to the bottom stepped portion S2a of the stepped groove space S2, which has a narrower axial width. Consequently, the cam 130 is pressed to the other side in the axial direction (right side in Figure 12), and as a result, the other axial end face of the cam 130 is pressed against the support base 157 of the cage ring 150. On the other hand, in the cam clutch after the cam clutch unit 200 has been assembled, the pressing force on the other axial side of the spring 160 (right side in Figure 12) is eliminated, and as a result, the spring 160 and the cage ring 150 are not in contact, and the sliding resistance between the non-protruding surface 132 without the engagement step 131 on one axial end face of the cam 130 and the spring 160, and the sliding resistance between the other axial end face of the cam 130 and the cage ring 150 are suppressed. [Examples]

[0023] As shown in Figures 14 and 15, the cam clutch unit 300 according to the third embodiment of the present invention is provided with engaging steps 331 on both axial ends of the cam 330, and a recess 353 is provided adjacent to the support base 157 on the other axial side of the partition wall 158 so that a tapered groove space S3 is also formed on the other axial side of the cage ring 350, and is biased by two annular springs 160 and 360. The other configurations are the same as those of the first embodiment described above. In Figures 14 and 15 showing the third embodiment, the same reference numerals are used for components that are the same as those in the cam clutch unit 100 according to the first embodiment.

[0024] The recess 353 has a tapered surface 356 that slopes from the radial outer circumference to the inner circumference, and from the other side to the one side in the axial direction, approaching the cam 330. The tapered surface 356 facing the cam 330 functions as a pressing part that can press the cam 330 to one side in the axial direction by the spring 360. The tapered groove space S3 is formed such that its axial width decreases as it moves from the annular support base 157 from the other side in the axial direction (right side in Figure 14) to the one side in the axial direction (left side in Figure 14). [Examples]

[0025] The cam clutch unit according to the fourth embodiment of the present invention differs from the cam clutch unit 100 according to the first embodiment in the position where the hook portion is formed, but the other configurations are the same as those of the first embodiment described above. In Figure 16, which shows the cage ring 450 of the cam clutch unit according to the fourth embodiment, the same reference numerals are used for parts that have the same configuration as the cage ring 150 of the cam clutch unit 100 according to the first embodiment. The cage ring 450 of the cam clutch unit according to this embodiment has a plurality of hook portions 453 that restrict the axial movement of the annular spring 160 to one side. The hook portions 453 are formed in the circumferential middle of two circumferentially adjacent partition walls 158, 158 and protrude outward at one axial end (left end in Figure 16). In the cage ring 450 of the cam clutch unit according to this embodiment, pocket portions 151 for housing the cam 130 and pocket portions 152 for housing the roller 140 are arranged alternately in the circumferential direction, and the hook portion 453 is positioned at the circumferential center and one axial end (left end in Figure 16) of the pocket portion 151 for housing the cam 130. The hook portion 453 has a tapered surface 456 that slopes from the radial outer circumference to the inner circumference, and from one side in the axial direction to the other, approaching the cam 130. The tapered surface 456 facing the cam 130 functions as a pressing portion that can press the cam 130 to the other side in the axial direction by the spring 160. Specifically, a tapered groove space is formed between the tapered surface 456 of the hook portion 453 and the cam 130, where the axial width decreases as you move from one side to the other in the axial direction. This tapered groove space functions similarly to the tapered groove space S1 of the cam clutch unit 100 according to the first embodiment. As a standalone unit, the other axial end face of the cam 130 is pressed against the support base 157 of the cage ring 450. In the assembled cam clutch unit, sliding resistance between the non-protruding surface 132 without the engagement step 131 on one axial end face of the cam 130 and the spring 160, and sliding resistance between the other axial end face of the cam 130 and the cage ring 450 are suppressed. Furthermore, the tapered surface 456 only needs to be formed on at least one of the multiple hook portions 453 provided in the circumferential direction.

[0026] Although 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 described in the claims. For example, in the above embodiment in which a stepped portion is provided on the hook portion, a restricting step portion that protrudes axially may be provided on the end face opposite to the engaging step portion of the cam, and a restricting protrusion that restricts the tilt of the cam may be provided on the cage ring on the face adjacent to the restricting step portion of the cam in the axial direction. Alternatively, for example, engagement steps may be provided on both axial ends of the cam, and a stepped groove space may also be provided on the other axial side of the cage ring, and the configuration may be biased by two annular springs. [Explanation of symbols]

[0027] 100, 200, 300, 500, 600... Cam clutch unit 130, 330, 530, 630... Cam 131, 331, ... Engagement stepped portion 132 ... non-protruding surface 133 ··· Regulatory section 535 ··· Groove 140, 540... Laura 545... Groove 150, 250, 350, 450, 550, 650... Cage rings 151, 551... Pocket section (for cam) 152, 552... Pocket section (for rollers) 152A... surface 153, 253, 453, 653... Hook section 353 ··· Recess 155 ··· Regulatory protrusions 156, 356, 456... Tapered surface 256 · · Stairs 157 ... support stand 158 ··· Partition wall 160, 360, 560... Spring S1, S3... Tapered groove space S2 ··· Stepped groove space

Claims

1. A cam clutch unit comprising: a plurality of cams positioned between an inner ring and an outer ring that are coaxially rotatable relative to each other; a cage ring having a plurality of pockets that restrict the relative movement of the cams in the circumferential direction; and an annular spring that biases the cams, The cam has an engagement step on one axial end face that can engage with the spring, The cage ring has a plurality of hook portions that restrict the axial movement of the annular spring, The cam clutch unit is characterized in that the hook portion has a pressing portion that can press the cam to the other end face in the axial direction by the spring.

2. The cam clutch unit according to claim 1, characterized in that the hook portion has a tapered surface that slopes toward the cam side from the outer circumference to the inner circumference, and the tapered surface constitutes the pressing portion.

3. The cam clutch unit according to claim 1, characterized in that the hook portion is provided with a stepped portion on the inner circumference side that protrudes toward the cam side, and the stepped portion constitutes the pressing portion.

4. The cam has a restricting step on the end face opposite to the engaging step, The cam clutch unit according to claim 1, characterized in that the pocket portion of the cage ring has a restricting projection on the surface adjacent to the restricting step portion of the cam in the axial direction that restricts the inclination of the cam.

5. Multiple rollers are arranged between the inner ring and the outer ring. The cam clutch unit according to claim 1, characterized in that the axial dimension of the roller is less than or equal to the axial dimension of the cam excluding the engagement step portion.

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