Cam clutch unit

Abstract

The purpose of the present invention is to provide a cam clutch unit that can prevent a cam from falling off from a spacer ring and damage to a biasing member during assembly, and that can improve assemblability and processability, and can improve torque transmission efficiency. Specifically, the problem can be solved by the following contents: the cam (110) is provided with a head part (111) and a leg part (116), the head part (111) and the leg part (116) are configured such that the maximum cross-sectional widths (Wa, Wb) are larger than the opening width (Wp) of the notch part (125) of the spacer ring (120), and at least one of the head part (111) and the leg part (116) of the cam (110) is configured such that the maximum cross-sectional widths (Wa, Wb) are larger than the opening width (Wp) of the notch part (125) of the spacer ring (120). As the cam (110) is rotated while being inserted into the notch part (125) in an inclined posture in the opening direction of the notch part (125), the notch part (125) can be elastically deformed, and thus the cam (110) can pass through the notch part (125).

Description

Technical Field

[0001] The present invention relates to a cam clutch unit for transmitting and cutting off torque between an input shaft and an output shaft. Background Art

[0002] As a cam clutch unit, for example Fig.15 As shown, there is a known structure (for example, refer to patent document 1), which comprises: a plurality of cams 210, arranged between an inner ring and an outer ring, wherein the inner ring and the outer ring are configured to be coaxially rotatable relative to each other; a spacer ring 220, having a plurality of notches 225 for limiting the circumferential relative movement of the cam 210; and an annular spring as a biasing member 230, which is installed in a mounting groove 213 formed in a manner extending circumferentially on the cam surface on the outer peripheral side of the cam 210, and biases the cam 210 to make it contact with the inner ring and the outer ring.

[0003] The cam 210 in the cam clutch unit 200 includes: a main body portion, which is arranged in a through state in the notch portion 225; a head portion, which is connected to the outer peripheral side of the main body portion; and a foot portion, which is connected to the inner peripheral side of the main body portion. The head portion of the cam 210 is configured so that the maximum cross-sectional width Wa, which is the maximum interval between parallel lines when sandwiched by two parallel lines, is larger than the minimum opening width Wp of the notch portion 225. On the other hand, the foot portion of the cam 210 is configured so that the maximum cross-sectional width Wb, which is the maximum interval between parallel lines when sandwiched by two parallel lines, is smaller than the minimum opening width Wp of the notch portion 225, so that the cam 210 can pass through the notch portion 225 by being inserted obliquely into the notch portion 225 from the outer peripheral side.

[0004] In such a cam clutch unit 200, when the cam 210 is installed in the spacer ring 220, the cam 210 inserted into the notch 225 may rotate in the notch 225, causing the cam 210 to fall off the spacer ring 220. In addition, since the cam 210 needs to be inserted into the notch 225 at an angle, there is a problem that the assembly workability is reduced.

[0005] Furthermore, as a cam clutch unit, it is known to adopt a so-called snap-fit ​​structure in order to prevent the cam from falling out of the notch portion when the cam is mounted in the spacer ring (see, for example, Patent Document 2).

[0006] The head and foot of the cam used in such a cam clutch unit are respectively configured so that the maximum cross-sectional width is larger than the opening width of the notch. Therefore, by inserting the cam with pressure from the opening direction of the notch, the cam is locked on the opening edge of the notch, thereby preventing the cam from falling off from the notch.

[0007] In addition, there is known a structure in which a limiting step portion is provided on the other end face of a cam having a step portion for engaging a force-applying component on one axial end face, and a limiting protrusion for limiting the inclination of the cam is provided on the surface adjacent to the limiting step portion of the cam in the axial direction in the recessed portion of the spacer ring. By engaging the limiting step portion of the cam with the limiting protrusion of the recessed portion, the cam can be prevented from falling off the spacer ring (see patent document 3).

[0008] Patent Literature

[0009] Patent Document 1: Japanese Patent Application Publication No. 2021-177091

[0010] Patent Document 2: Japanese Utility Model Publication No. 63-001928

[0011] Patent Document 3: Japanese Patent Application Publication No. 2023-104553 Summary of the invention

[0012] Furthermore, in the structure described in Patent Document 2, since the spacer ring undergoes elastic deformation as the cam is inserted, a high dimensional accuracy is required for the opening width of the notch portion. However, since the spacer ring is formed of, for example, an integrally molded product made of resin, it is difficult to form the opening width of the notch portion with high dimensional accuracy, and the spacer ring may be damaged due to the pressure-insertion of the cam into the notch portion.

[0013] On the other hand, the structure described in Patent Document 3 has the following problems. First, the cam is easy to loosen during installation, and a locking structure for preventing the cam from axially falling off needs to be provided on one axial end side of the notch. Therefore, when the cam clutch unit is inserted between the inner ring and the outer ring, the spring will be clamped in the axial direction by the cam and the spacer ring, thereby causing damage to the spring and possibly making it impossible to obtain proper force on the cam. In addition, in the structure for engaging the limiting step portion of the cam with the limiting convex portion of the notch, it is necessary to provide a limiting step portion on each of the cam and the spacer ring, which will increase the processing hours and the processing burden in terms of cost. In addition, since the cam needs to be inserted obliquely into the notch, the assembly workability is reduced.

[0014] The present invention is based on the above situation, and the technical problem to be solved is to provide a cam clutch unit that can prevent the cam from falling off the spacer ring and damage to the force-applying component during assembly, and can improve the assembly and processability, and can improve the torque transmission efficiency.

[0015] The present invention is a cam clutch unit, comprising: a plurality of cams arranged between an inner ring and an outer ring arranged to be relatively rotatable on the same axis; a resin spacer ring having a plurality of notches for limiting the relative movement of the cam in the circumferential direction; and a force member for applying force to the cam so as to contact the inner ring and the outer ring. The cam can solve the problem by the following contents, that is, the cam has: a main body arranged in the notches in a through state; a head connected to the outer peripheral side of the main body; and a foot connected to the inner peripheral side of the main body. The head and the foot are connected to each other on the side and are constructed so that their axial dimension is smaller than the axial dimension of the notch portion. The head and the foot are constructed so that, in a cross section perpendicular to the rotation center of the cam, the maximum cross-sectional width at which the interval between the parallel lines when clamped by two parallel lines is largest is larger than the opening width of the notch portion. At least one of the head and the foot is constructed so that as the cam is inserted into the notch portion along the opening direction of the notch portion in an inclined posture while rotating, the notch portion undergoes elastic deformation, thereby being able to pass through the notch portion.

[0016] According to the invention involved in Technical Solution 1, since the notches of the cam and the spacer ring are constructed so that the cam can be snap-fitted by rotating while being inserted into the notch during installation, the cam can be inserted along the opening direction of the notch, and the cam can be easily installed without damaging the spacer ring, and the cam can be prevented from falling out.

[0017] In addition, since the cam and the notch constitute a snap-fit ​​structure, there is no need to provide a structure on the cam and the spacer to prevent the cam from coming out. Therefore, it is possible to reduce the processing burden. In addition, since when the cam clutch unit is inserted between the inner ring and the outer ring, the problem of damage to the force-applying component caused by the force-applying component being clamped axially by the cam and the spacer can be avoided, the force-applying component can be used to apply appropriate force to the cam, thereby improving the torque transmission performance. Moreover, since the notch does not require high dimensional accuracy, the degree of freedom of assembly can be improved.

[0018] According to the invention of claim 2 , when the cam is inserted into the notch, the amount of elastic deformation of the notch (the amount of snapping) can be reduced, thereby facilitating the mounting of the cam to the spacer ring.

[0019] According to the invention involved in the third technical solution, when the cam is inserted into the notch, the cam is moved along the cam insertion guide portion, so that the installation of the cam relative to the spacer ring can be facilitated, thereby achieving improved assemblability.

[0020] According to the invention according to claim 4 , the cam can be inserted into the notch portion in an appropriate inclined posture, and thus the assembling efficiency can be improved.

[0021] According to the invention of claim 5 , since the spring as the urging member is not caught between the cam and the spacer ring, the spring is not damaged when the cam clutch unit is inserted between the inner ring and the outer ring.

[0022] According to the invention involved in the sixth technical solution, since the surface of the roller recess of the spacer ring adjacent to the roller in the circumferential direction is formed into a shape that restricts the movement of the roller to the outer ring side and the inner ring side, the roller can be prevented from falling off to the outer circumferential side during installation, thereby improving the assembly performance. In addition, as the roller, a simple cylindrical or cylindrical roller without processing can be used, thereby reducing the processing burden. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a perspective view showing the structure of a cam clutch unit according to the first embodiment of the present invention.

[0024] Figure 2 Yes means Figure 1 A perspective view showing the structure of a spacer ring in a cam clutch unit.

[0025] Figure 3 Yes means Figure 1 An end view of the structure of the cam in the cam clutch unit is shown.

[0026] Figure 4A It is a diagram showing the structure of the head of the cam.

[0027] Figure 4B It is a diagram showing the structure of the leg portion of the cam.

[0028] Figure 5 It is a schematic representation Figure 1 A partial cross-sectional view along the rotation axis showing the structure of the cam clutch unit.

[0029] Fig. 6A It is a schematic diagram schematically showing a process of mounting the cam to the spacer ring, and is a diagram showing a state where the cam is inserted into the notch portion.

[0030] Figure 6B It is a schematic diagram schematically showing a process of mounting the cam to the spacer ring, and is a diagram showing a state in which the cam is rotated and a part of the leg portion of the cam is inserted into the notch portion.

[0031] Figure 6C It is a schematic diagram schematically showing the installation process of the cam with respect to the spacer ring, and is a diagram showing a state after the leg portion of the cam passes through the notch portion.

[0032] Figure 7It is a perspective view showing a part of the structure in another example of the spacer ring.

[0033] Figure 8 This is a partial cross-sectional view showing the structure of still another example of the spacer ring.

[0034] Fig. 9 It is a perspective view showing the structure of a cam clutch unit according to a second embodiment of the present invention.

[0035] Fig.10 yes Fig. 9 A side view of a cam clutch unit is shown.

[0036] Fig.11 Yes means Fig. 9 A perspective view showing the structure of a spacer ring in a cam clutch unit.

[0037] Fig.12 Yes means Fig. 9 (a) is a side view and (b) is an end view of the structure of the cam in the cam clutch unit shown.

[0038] Fig.13 It is a schematic representation Fig. 9 A partial cross-sectional view along the rotation axis showing the structure of the cam clutch unit.

[0039] Fig.14 Yes means Fig.10 A partial cross-sectional view of a portion of the AA line cross section.

[0040] Fig.15 This is a cross-sectional view perpendicular to the rotation axis, showing an outline of the structure of an example of a conventional cam clutch unit.

[0041] Explanation of symbols

[0042] 100, 200-cam clutch unit; 110, 210-cam; 111-head; 112-outer cam surface; 113, 213-installing groove; 115-main body; 116-foot; 117-inner cam surface; 118-step portion for engagement of the force-applying member; 120, 220-spacer ring; 121-annular plate on one end side; 122-annular plate on the other end side; 123-rib; 124-limiting wall portion; 125, 225-notch portion; 125a-notch portion for cam; 125b-notch portion for roller; 126-cam insertion guide portion; 127-cam insertion posture stabilizing portion; 128-limiting portion; 130, 230-force-applying member; 140-roller. DETAILED DESCRIPTION

[0043] Hereinafter, a cam clutch unit according to the present invention will be described with reference to the drawings.

[0044] like Figure 1 As shown, the cam clutch unit 100 involved in the first embodiment of the present invention comprises: a plurality of cams 110, which are arranged in an annular space between the track surface of the inner ring and the track surface of the outer ring which are arranged to be coaxially rotatable relative to each other; a spacer ring 120, which has a plurality of notches 125 for limiting the circumferential relative movement of the cam 110; and a force-applying component 130, which applies force to each of the plurality of cams 110 in the meshing direction relative to the inner ring and the outer ring so that each of the plurality of cams 110 is in contact with the inner ring and the outer ring.

[0045] First, the structure of the spacer ring 120 is described in detail. Figure 2 As shown, the spacer ring 120 includes: a one-end side annular plate 121 and a second end side annular plate 122, which are arranged opposite to each other in the axial direction; and a plurality of columnar ribs 123, which connect the one-end side annular plate 121 and the second end side annular plate 122. The inner diameter of the one-end side annular plate 121 is larger than the outer diameter of the second end side annular plate 122, and one axial end of the rib 123 is fixed to the inner circumferential surface of the one-end side annular plate 121, while the other axial end is fixed to the outer circumferential surface of the second end side annular plate 122, and the one-end side annular plate 121 is formed with a flange portion protruding radially outward over the entire circumference.

[0046] The ribs 123 are arranged at equal intervals in the circumferential direction, and notches 125 are formed between adjacent ribs 123 .

[0047] In this embodiment, if Figure 3 As shown, the cross-sectional shape of each rib 123 is substantially trapezoidal in shape so that the width dimension decreases toward the radially inner side, and the opening shape of the notch portion 125 is rectangular and is configured to have a uniform opening width Wp in the radial direction.

[0048] like Figure 3 As shown in FIG. 1 , each of the plurality of cams 110 includes a main body 115 disposed in a through state in the notch 125 of the spacer 120, a head 111 connected to the outer circumference of the main body 115, and a leg 116 connected to the inner circumference of the main body 115. Here, the head 111 refers to a portion protruding toward the outer circumference than the opening edge of the notch 125 when the cam 110 is disposed between the inner ring and the outer ring, and the leg 116 refers to a portion protruding toward the outer circumference than the opening edge of the notch 125. In the present embodiment, the main body 115 is configured in a columnar shape with a uniform width dimension in the radial direction, but may be configured in a shape in which the width dimension varies in the radial direction.

[0049] The head 111 of the cam 110 has an outer peripheral cam surface 112 that engages with the track surface of the outer ring, and is constructed so that in a cross section perpendicular to the rotation center of the cam 110, the maximum cross-sectional width Wa at which the interval between two parallel lines is the largest when the cam is clamped by the two parallel lines is larger than the opening width Wp of the notch portion 125.

[0050] In addition, in this embodiment, if Figure 4A As shown in FIG. 1 , the head 111 of the cam 110 is configured such that the first oblique direction width W1 and the second oblique direction width W2 are larger than the opening width Wp of the notch 125. Here, the first oblique direction width W1 refers to the minimum width between two straight lines when the other side portion of the head 111 is sandwiched by a first imaginary straight line L1 and a straight line parallel to the first imaginary straight line L1, the first imaginary straight line L1 being a straight line connecting two arbitrary points a1 and b1 whose closest distance from the head 111 on one side surface of the cam 110 to the head side region of the main body 115 is the same as the thickness t of the notch 125. In addition, the second inclined direction width W2 refers to the minimum width between the two straight lines when one side of the head 111 is clamped by the second imaginary straight line L2 and a straight line parallel to the second imaginary straight line L2, and the second imaginary straight line L2 is a straight line connecting any two points a2 and b2 whose closest distance from the head 111 on the other side of the cam 110 to the head side area of ​​the main body 115 is the same as the thickness t of the notch 125.

[0051] like Figure 3 As shown, the foot 116 of the cam 110 has an inner circumferential cam surface 117 that engages with the track surface of the inner ring, and is constructed so that in a cross section perpendicular to the rotation center of the cam 110, the maximum cross-sectional width Wb at which the interval between two parallel lines is the largest when the two parallel lines are clamped is larger than the opening width Wp of the notch portion 125.

[0052] In addition, in this embodiment, if Figure 4BAs shown in FIG. 1 , the leg portion 116 of the cam 110 is configured such that the third oblique direction width W3 and the fourth oblique direction width W4 are larger than the opening width Wp of the notch portion 125. Here, the third oblique direction width W3 refers to the width at which the interval between two straight lines when the other side portion of the leg portion 116 is sandwiched by the third virtual straight line L3 and a straight line parallel to the third virtual straight line L3 is the smallest, and the third virtual straight line L3 is a straight line connecting any two points c1 and d1 whose closest distance from the main body 115 on one side of the cam 110 to the leg side region of the leg portion 116 is the same as the thickness t of the notch portion 125. In addition, the fourth inclined direction width W4 refers to the minimum width between the two straight lines when the fourth imaginary straight line L4 and the straight line parallel to the fourth imaginary straight line L4 are used to clamp one side portion of the foot 116, and the fourth imaginary straight line L4 is a straight line connecting any two points c2 and d2 whose closest distance from the main body 115 on the other side of the cam 110 to the foot side area of ​​the foot 116 is the same as the thickness t of the notch 125.

[0053] In the present embodiment, both end faces of each cam 110 in the axial direction are flat, and are configured such that the axial dimension is smaller than the axial dimension of the notch 125. Therefore, during assembly, the cam 110 is not tilted relative to the axial direction, and can approach the notch 125 with both end faces extending in the opening direction (radial direction) of the notch 125.

[0054] When the cam 110 is disposed in the notch portion 125, the circumferential position of the cam 110 is restricted by the rib 123. Figure 5 As shown, the axial position of the cam 110 is restricted by the one-end side annular plate 121 and the other-end side annular plate 122 .

[0055] In the present embodiment, the urging member 130 is formed of an annular spring and is mounted in a mounting groove 113 formed on the head 111 of the cam 110 .

[0056] The mounting groove 113 is formed at the central portion in the axial direction. By installing the force member 130, one side portion of the mounting groove 113 can be pressed toward the inner circumference, thereby causing the cam 110 to move in the meshing direction (for example, in the direction of the meshing direction). Figure 3 The inner ring (in the middle) rotates clockwise and is forced to contact the inner and outer rings.

[0057] As described above, in the present embodiment, since the head portion 111 and the foot portion 116 of the cam 110 are constructed such that the first inclination direction width W1, the second inclination direction width W2, the third inclination direction width W3 and the fourth inclination direction width W4 are all larger than the opening width Wp of the notch portion 125, it is possible to construct such that, regardless of the posture of the cam 110, as long as the cam 110 is inserted along the opening direction (radial direction) of the notch portion 125 during assembly, or the cam 110 arranged in the notch portion 125 is moved radially, the head portion 111 and the foot portion 116 of the cam 110 cannot pass through the notch portion 125.

[0058] However, in the cam clutch unit 100 according to the present embodiment, the first oblique direction width W1, the second oblique direction width W2, the third oblique direction width W3, and the fourth oblique direction width W4 are all such that the notch 125 can be elastically deformed by rotating the cam 110 while inserting the cam 110 into the notch 125 in an inclined posture along the opening direction of the notch 125. That is, since the head 111 and the foot 116 of the cam 110 each form a snap-fitting structure with the notch 125, the cam 110 can be attached to the spacer ring 120 regardless of whether the cam 110 is inserted into the notch 125 from the head 111 side or the foot 116 side, and the cam 110 can be prevented from falling off regardless of the posture taken by the cam 110 rotating in the notch 125.

[0059] In addition, as long as at least one of the first inclined direction width W1, the second inclined direction width W2, the third inclined direction width W3 and the fourth inclined direction width W4 is set to a size that allows the notch portion 125 to be elastically deformed by inserting the cam 110 into the notch portion 125 in an inclined posture along the opening direction of the notch portion 125 while rotating it, the cam 110 can be installed relative to the spacer ring 120, and the cam 110 can be prevented from falling off regardless of the posture of the cam 110 when it rotates in the notch portion 125.

[0060] An example of a method for mounting the cam 110 relative to the spacer ring 120 is described in detail. Fig. 6A As shown in FIG. 1 , the cam 110 is rotated in the disengagement direction with an inclined posture, and the cam 110 is inserted into the notch 125 from the leg 116 side of the cam 110 along the opening direction of the notch 125. At this time, since the fourth inclined direction width W4 of the cam 110 is larger than the opening width Wp of the notch 125, the leg 116 of the cam 110 cannot pass through the notch 125, and the cam 110 is locked with the opening edge of the notch 125. In this state, as shown in FIG. Figure 6BAs shown, by using the contact point between the other side of the main body 115 of the cam 110 and the opening edge of the notch 125 as a fulcrum, the cam 110 is rotated in the meshing direction, and the notch 125 is elastically deformed to be able to pass through the notch 125. Figure 6C As shown, by further inserting the cam 110, the cam 110 can be installed in the spacer ring 120. When the cam 110 is arranged in the notch portion 125, since the first oblique direction width W1, the second oblique direction width W2, the third oblique direction width W3 and the fourth oblique direction width W4 of the cam 110 are larger than the opening width Wp of the notch portion 125, when other cams 110 are installed in the spacer ring 120, the cam 110 will not fall out of the notch portion 125 regardless of the posture of the cam 110 when rotating in the notch portion 125.

[0061] In the above, although the following situation is described, namely, the cam 110 is inserted into the recessed portion 125 from the foot 116 side of the cam 110 in an inclined posture rotated in the engagement release direction, the cam 110 may also be inserted into the recessed portion 125 from the head 111 side of the cam 110. Furthermore, the cam 110 may also be inserted into the recessed portion 125 from the head 111 side of the cam 110 or from the foot 116 side of the cam 110 in an inclined posture rotated in the engagement direction.

[0062] As described above, in the cam clutch unit 100 according to the present embodiment, the cam 110 and the notch 125 of the spacer ring 120 are configured so that, during installation, the cam 110 is inserted into the notch 125 and rotated to engage with each other. Therefore, according to the cam clutch unit 100 according to the present embodiment, the cam 110 can be inserted along the opening direction of the notch 125, and the cam 110 can be easily installed without damaging the spacer ring 120, and the cam 110 can be prevented from falling out.

[0063] In addition, since the cam 110 and the notch 125 form a snap-fit ​​structure, there is no need to provide a structure for preventing the cam 110 from coming out on the cam 110 and the spacer ring 120. Therefore, it is possible to reduce the processing burden.

[0064] Furthermore, when the cam clutch unit 100 is inserted between the inner ring and the outer ring, the urging member 130 is installed in the installation groove 113 provided in the axial center of the cam 110, and the urging member 130 is clamped in the axial direction by the cam 110 and the spacer ring 120, so that the urging member 130 is damaged, can be avoided. Thus, the urging member 130 can apply an appropriate urging force to the cam 110, and the torque transmission performance can be improved. In addition, since the notch portion 125 does not require high dimensional accuracy, the degree of freedom of assembly can be improved.

[0065] The spacer ring 120 may also be configured to have a cam insertion guide portion on at least one circumferential side of the opening edge of the notch portion 125. According to such a configuration, when the cam 110 is inserted into the notch portion 125, the cam 110 can be easily installed relative to the spacer ring 120 by moving the cam 110 along the cam insertion guide portion, thereby improving the assembly performance.

[0066] Specifically, for example, when the cam 110 is installed in the notch portion 125 from the leg portion 116 side, as shown in FIG. Figure 7 As shown in the figure, by forming both side edges on the outer surface of the rib 123 into a C-chamfered shape, the cam insertion guide portion 126 can be formed. It is also possible to form only one side edge on the outer surface of the rib 123 into a C-chamfered shape, and it is also possible to form an R-chamfered shape instead of a C-chamfered shape. In addition, when the cam 110 is installed in the notch portion 125 from the head 111 side, it is sufficient to provide a cam insertion guide portion on at least one side edge on the inner surface of the rib 123.

[0067] Furthermore, the spacer ring 120 may be configured so that when the cam 110 is inserted into the notch 125, the cam insertion posture stabilizing portion is provided on the opening edge of the notch 125 so as to contact one side surface or the other side surface of the main body 115 when the cam 110 is in an inclined posture. With such a configuration, the cam 110 can be inserted into the notch 125 in an appropriate inclined posture, thereby improving the ease of assembly.

[0068] Specifically, for example, when the cam 110 is installed in the notch portion 125 from the leg portion 116 side in an inclined posture rotated in the meshing release direction, as shown in FIG. Figure 8 As shown, a plate-shaped guide member extending obliquely in the opening direction of the notch 125 is provided on one side edge of the outer surface of the rib 123 to form a cam insertion posture stabilizing portion 127. Of course, the position of the guide member can be appropriately changed according to the installation direction of the cam 110.

[0069] In addition, Figure 8 The spacer ring 120 having the structure shown may also be configured such that a cam insertion guide is provided on the rib 123 on the side edge opposite to the side edge on which the guide member is provided.

[0070] Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments. The cam clutch unit involved in the present invention may also be configured as follows: Figure 1In the cam clutch unit 100 shown, a part of the plurality of cams 110 is replaced with freely rotatable rollers in order to ensure the coaxiality between the inner ring and the outer ring. A cam clutch unit according to a second embodiment of the present invention having such a configuration will be described below.

[0071] like Fig. 9 and Fig.10 As shown, the cam clutch unit 100 according to the second embodiment of the present invention includes a plurality of cams 110 and a plurality of rollers 140 arranged together in an annular space between the track surface of the inner ring and the track surface of the outer ring, wherein the track surface of the inner ring and the track surface of the outer ring are arranged to be relatively rotatable on the same axis. The number and arrangement of the cams 110 and the rollers 140 can be arbitrary.

[0072] like Fig.11 As shown, the spacer ring 120 includes a cam notch 125 a for restricting the relative movement of the cam 110 in the circumferential direction, and a roller notch 125 b for accommodating the roller 140 and restricting the relative movement of the roller 140 in the circumferential direction.

[0073] like Fig.12 As shown, each of the plurality of cams 110 has a biasing member engaging step 118 on one axial end face that can engage with the biasing member 130, i.e., an annular spring. Other than that, the plurality of cams 110 have the same structure as the cam 110 in the cam clutch unit 100 according to the first embodiment.

[0074] In this embodiment, the step portion 118 for the engagement of the urging member is formed to be inclined from one side of the cam 110 toward the other side and toward the radial inner peripheral side. By installing the urging member 130, one side portion of the installation groove 113 can be pressed toward the inner peripheral side, thereby causing the cam 110 to move in the meshing direction (in the direction of the engagement direction). Fig.12 (b) The inner ring rotates (clockwise in the figure) and is forced to contact the inner ring and the outer ring.

[0075] The two axial end faces of the cam 110 are flat, so that the cam 110 does not tilt relative to the axial direction during assembly, and can approach the cam notch 125a with the two end faces extending in the opening direction (radial direction) of the notch 125.

[0076] When the cam 110 is disposed in the cam notch 125a, the circumferential position of the cam 110 is restricted by the rib 123. Fig.13 As shown, the axial position of the cam 110 is restricted by the one-end side annular plate 121 and the other-end side annular plate 122 constituting the flange portion.

[0077] The plurality of rollers 140 are simple cylindrical or columnar shapes without grooves or step portions. Fig.10 As shown, the axial dimension of the roller 140 is smaller than the axial dimension of the cam 110 excluding the step portion 118 for engagement with the biasing member.

[0078] In the present embodiment, outer peripheral edge portions of both end surfaces of the roller 140 are chamfered to prevent the roller 140 from being caught by the urging member 130 .

[0079] The surface of the roller recess 125b in the spacer ring 120 adjacent to the roller 140 in the circumferential direction is formed into a shape that can restrict the movement of the roller 140 to the outer ring side and the inner ring side. Fig.14 As shown in FIG. 1 , the roller recess 125b is formed by providing a pair of restricting portions 128 on the respective side surfaces facing each other on the two ribs 123 that divide the roller recess 125b, and the pair of restricting portions 128 can form a columnar space capable of accommodating the roller 140. The distance Wr1 between the outer peripheral end edges and the distance Wr2 between the inner peripheral end edges of the restricting portions 128 are configured to be smaller than the roller diameter D, and since the roller 140 is elastically deformed as it is inserted, the roller 140 can be arranged in the roller recess 125b.

[0080] In addition, if Fig.11 As shown, the roller recess 125b is configured to have an axial dimension smaller than the axial dimension of the cam recess 125a, and has a limiting wall 124 that protrudes axially toward the other end side from one surface of the one end side annular plate 121. Thus, the axial movement of the roller 140 is limited by the other end side annular plate 122 and the limiting wall 124.

[0081] like Fig.13 As shown in the figure, the urging member 130, i.e., the annular spring, is attached to the urging member engagement step 118 in a state where there is a gap between one end face of the cam 110 (the end face of the portion of the cam 110 excluding the urging member engagement step 118) and the end face of the one-end side annular plate 121 constituting the flange portion. Therefore, since the urging member 130 is not caught by the cam 110 and the spacer ring 120, the urging member 130 is not damaged when the cam clutch unit 100 is inserted between the inner ring and the outer ring.

[0082] According to the cam clutch unit 100 involved in this embodiment, since the cam 110 and the cam recess 125a and the roller 140 and the roller recess 125b are constructed as snap-fit, the cam 110 and the roller 140 can be easily installed without damaging the spacer ring 120, and the cam 110 and the roller 140 can be prevented from falling out.

[0083] Furthermore, since there is no need to separately provide a structure for preventing the cam 110 from coming out on the cam 110 and the spacer ring 120, and a simple cylindrical or cylindrical roller without processing can be used as the roller 140, the processing burden can be reduced.

[0084] 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 present invention described in the claims.

[0085] For example, although in the above-mentioned embodiment, the head 111 and the foot 116 of the cam 110 are configured so that the first inclination direction width W1, the second inclination direction width W2, the third inclination direction width W3 and the fourth inclination direction width W4 are all larger than the opening width Wp of the notch 125, when the cam is installed relative to the spacer ring with the force-applying component installed, the head and the foot of the cam can also be configured so that, by installing the force-applying component on the cam, the inclination direction width of the cam in an inclined posture in which the cam is inclined in a direction opposite to the direction of rotation of the cam is smaller than the opening width of the notch.

[0086] In addition, although the configuration using an annular spring as the biasing member is described, the biasing member may be, for example, a strip spring or a torsion spring. In addition, for the cam clutch unit involved in the second embodiment, although in the above-mentioned embodiment, a biasing member engagement step portion is provided only on one end face in the axial direction of the cam, a biasing member engagement step portion may be provided on both end faces in the axial direction of the cam, and the cam may be biased by two annular springs.

Claims

1. A cam clutch unit comprising: a plurality of cams arranged between an inner ring and an outer ring arranged to be relatively rotatable on the same axis; a resin spacer ring having a plurality of notches for limiting the relative movement of the cams in the circumferential direction; and a biasing member for biasing the cams so as to contact the inner ring and the outer ring, characterized in that: The cam comprises: a main body portion, which is arranged in the recess portion in a penetrating state; a head portion, which is connected to the outer peripheral side of the main body portion; and a foot portion, which is connected to the inner peripheral side of the main body portion and is configured to have an axial dimension smaller than the axial dimension of the recess portion. The head and the foot are configured such that, in a cross section perpendicular to the rotation center of the cam, a maximum cross-sectional width at which the interval between two parallel lines is the largest when the two parallel lines are sandwiched is larger than an opening width of the notch. At least one of the head and the leg is configured to be able to pass through the notch by elastically deforming the notch as the cam is inserted into the notch along the opening direction of the notch in an inclined posture and rotated.

2. The cam clutch unit according to claim 1, characterized in that The cam, in a cross section perpendicular to the rotation center of the cam, At least one of the first oblique direction width W1, the second oblique direction head width W2, the third oblique direction width W3, and the fourth oblique direction width W4 is a size that allows the notch to be elastically deformed as the cam is inserted into the notch. The first inclined direction width W1 is the minimum width of the interval between two straight lines when the other side portion of the head portion is clamped by the first imaginary straight line L1 and a straight line parallel to the first imaginary straight line L1, wherein the first imaginary straight line L1 is a straight line connecting any two points whose closest distance is the same as the thickness of the notch portion in the head side region on one side surface of the cam, The second tilt direction head width W2 is the minimum width of the interval between two straight lines when one side of the head is clamped by the second imaginary straight line L2 and a straight line parallel to the second imaginary straight line L2, and the second imaginary straight line L2 is a straight line connecting any two points whose closest distance is the same as the thickness of the notch in the head side area on the other side of the cam, The third inclination direction width W3 is the minimum width of the interval between two straight lines when the other side of the foot is clamped by the third imaginary straight line L3 and a straight line parallel to the third imaginary straight line L3, wherein the third imaginary straight line L3 is a straight line connecting any two points whose closest distance is the same as the thickness of the notch in the foot side region on one side of the cam. The fourth inclined direction width W4 is the minimum width of the interval between two straight lines when one side of the foot is clamped by the fourth imaginary straight line L4 and a straight line parallel to the fourth imaginary straight line L4, and the fourth imaginary straight line L4 is a straight line connecting any two points whose closest distance is the same as the thickness of the notch in the foot side area on the other side of the cam.

3. The cam clutch unit according to claim 1, characterized in that: The spacer ring has a cam insertion guide portion on at least one side in the circumferential direction of the opening edge of the notch portion.

4. The cam clutch unit according to claim 1, characterized in that: The spacer ring has a cam insertion posture stabilizing portion on an opening edge of the notch portion, and the cam insertion posture stabilizing portion contacts one side surface or the other side surface of the main body portion when the cam is inserted into the notch portion and the cam is tilted.

5. The cam clutch unit according to claim 1, characterized in that: The cam has a step portion for engaging a force applying member on one end face in the axial direction. The spacer ring has a flange portion at one axial end portion that protrudes radially outward over the entire circumference. The urging member is composed of an annular spring, and the annular spring is attached to the urging member engagement step portion in a state where a gap is provided between one end surface of the cam and an end surface of the flange portion.

6. The cam clutch unit according to claim 1, characterized in that: It also includes a plurality of rollers arranged between the inner ring and the outer ring, The spacer ring has a roller retaining recess, and a surface of the roller retaining recess adjacent to the roller in the circumferential direction is formed in a shape that restricts movement of the roller to the outer ring side and the inner ring side. The roller holding recess is configured to elastically deform as the roller is inserted into the roller holding recess along the opening direction of the roller holding recess, thereby enabling the roller to be arranged in the roller holding recess.

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