Cam clutch

Abstract

A cam clutch (100) according to the present invention is configured as a cam (180) that is configured so as to be capable of meshing with an inner ring (110) and an outer ring (120) even when tilting in either the forward or reverse direction while being in a non-contact state with either or both of the inner ring (110) and the outer ring (120) in a neutral position. The spacer (100) is held by a fixed spacer (130) and a movable spacer (150) disposed so as to be rotatable relative to the fixed spacer (130) and movable in the axial direction, one of the fixed spacer (130) and the movable spacer (150) is provided with a guide groove (160), the other is provided with a pin member (140), and by moving the pin member (140) along the guide groove (160), the fixed spacer (130) and the movable spacer (150) are held by the fixed spacer (130) and the movable spacer (150). Thus, the phase between the movable spacer (150) and the fixed spacer (130) can be controlled.

Description

Technical Field

[0001] The present invention relates to a cam clutch, which is constructed to switch its action mode between a two-way simultaneous idling mode, a one-way transmission mode (one-way mode) and a two-way simultaneous transmission mode (two-way mode). The two-way simultaneous idling mode is a mode in which the inner ring or the outer ring idles in both the forward and reverse directions to cut off the torque transmission between the inner ring and the outer ring. The one-way transmission mode (one-way mode) is a mode in which the torque can be transmitted between the inner ring and the outer ring in either the forward or reverse direction. The two-way simultaneous transmission mode (two-way mode) is a mode in which the torque can be transmitted between the inner ring and the outer ring in both the forward and reverse directions. Background Art

[0002] For example, a clutch is known in which cams, which are engaging members that engage only in one direction of rotation, are arranged in a left-right symmetrical manner, and the clutch operation mode can be switched by tilting one or both of the cams on one side and the cams on the other side (for example, refer to patent document 1).

[0003] However, in the above-mentioned clutch, there is a possibility that "seizure" may occur in which all cams are engaged simultaneously.

[0004] That is, in the above-mentioned clutch, the first cam and the second cam, which are arranged in such a way that the meshing directions are opposite to each other, are subjected to force in such a way that they contact the outer ring and the inner ring, and when torque is applied to the outer ring or the inner ring, one of the cams will tilt so as to immediately start meshing with the outer ring and the inner ring. When the torque is removed, one of the cams will tilt in the direction of disengagement and transition to an idling state, but at this time, during the period until the meshing of one of the cams is disengaged, the other cam may tilt in the meshing direction and start meshing with the outer ring and the inner ring.

[0005] In this state, since all cams are engaged through a higher surface pressure, when the clutch operation mode is switched, a greater force is required to change the cam's posture, which may damage the cam's meshing surfaces on the outer and inner rings or the outer and inner ring track surfaces, thereby shortening the life of the clutch.

[0006] In addition, as a two-way clutch that can switch between drive and idling in both the forward direction and the reverse direction, the following clutch is known, which uses a so-called two-way type sprag as an engaging member and switches the clutch operation mode by tilting the sprag in one direction or the other (for example, refer to Patent Document 2).

[0007] The bidirectional clutch described in Patent Document 2 is composed of: an outer retainer having an outer long hole extending in the axial direction; and an inner retainer having an inner long groove which is inserted into the top end of a pin passing through the outer long hole and is inclined in the axial direction, and the outer retainer and the inner retainer are relatively displaced in the circumferential direction by moving the pin in the axial direction, so that the wedge block is tilted in a predetermined direction. In this bidirectional clutch, the tilting direction of the wedge block is switched by controlling the moving direction of the pin, so that the operation mode can be switched between a one-way transmission mode in which torque can be transmitted only in the forward direction between the inner ring and the outer ring and a one-way transmission mode in which torque can be transmitted only in the reverse direction between the inner ring and the outer ring.

[0008] Patent Literature

[0009] Patent Document 1: Japanese Patent Application Publication No. 2020-190255

[0010] Patent Document 2: Japanese Patent Application Publication No. 2003-301866 Summary of the invention

[0011] Therefore, in a two-way clutch using a two-way type sprag, when the transmission direction of the torque is switched, seizure does not occur.

[0012] However, in the two-way clutch described in Patent Document 2, since the pins are held in the state of being accommodated in the parallel grooves respectively provided at both ends of the internal long groove, the wedge block is held in the state of being tilted in a predetermined direction, and when the pin is not held in any of the parallel grooves, the pin can move along the internal long groove. Therefore, the wedge block cannot be held in a neutral posture in a state of non-contact with either or both of the inner ring and the outer ring, and the two-way simultaneous idling mode cannot be achieved.

[0013] In addition, the wedge cannot maintain a state in which it contacts the inner ring and the outer ring by actively changing its posture according to the rotation direction of the inner ring or the outer ring, and a bidirectional simultaneous transmission mode cannot be achieved.

[0014] The present invention has been made based on the above situation, and an object of the present invention is to provide a cam clutch which can smoothly switch an operation mode according to a use condition, prevent the cam from biting and the slip torque during idling, and can ensure a large torque capacity.

[0015] The present invention is a cam clutch, comprising: an inner ring and an outer ring, which are arranged to be relatively rotatable on the same axis; a fixed spacer, which has socket portions arranged at specified intervals in the circumferential direction and is fixed to the inner ring or the outer ring; a movable spacer, which has socket portions arranged at specified intervals in the circumferential direction and is configured to be relatively rotatable relative to the fixed spacer; a plurality of cams, which are configured to be held by the fixed spacer and the movable spacer, so as to be arranged along the circumferential direction between the inner ring and the outer ring, relative to a neutral posture that does not contact either or both of the inner ring and the outer ring, and can mesh with the inner ring and the outer ring even when tilted in either direction; and a force applying unit, which applies force in a manner that the plurality of cams are in a neutral posture or in an inclined posture that contacts the inner ring and the outer ring, and the movable spacer is arranged The movable spacer is movable in the axial direction. On one side of the fixed spacer and the movable spacer, a guide groove portion is provided in a manner extending along the axial direction. At the same time, on the other side of the fixed spacer and the movable spacer, a pin member is provided in a manner moving along the guide groove portion as the movable spacer moves axially. The guide groove portion includes: a phase limiting portion, which is configured to be able to maintain the movable spacer in a state where the socket portion of the movable spacer is in the same phase as the socket portion of the fixed spacer; a first phase change allowing portion, which is configured to be able to maintain the movable spacer in a state where it can move within a specified range in either the positive or negative direction relative to the fixed spacer; and a second phase change allowing portion, which is configured to be able to maintain the movable spacer in a state where it can move within a specified range in both the positive and negative directions relative to the fixed spacer, thereby solving the above-mentioned problem.

[0016] According to the invention involved in the first technical solution, since the guide groove portion provided on one side of the movable spacer and the fixed spacer is configured to include a phase limiting portion, a first phase change allowing portion, and a second phase change allowing portion, the circumferential movement freedom of the movable spacer relative to the fixed spacer can be controlled by the position of the pin member provided on the other side of the movable spacer and the fixed spacer. Therefore, the action mode of the cam clutch can be switched between a two-way simultaneous idling mode, a one-way transmission mode, and a two-way simultaneous transmission mode. When switching the action mode, the posture of the cam can be controlled and the posture of the cam can be maintained only by moving the movable spacer in the axial direction, so that the action mode corresponding to the use condition can be smoothly switched, and a high versatility can be obtained.

[0017] In addition, since the cam is configured so that it does not contact either or both of the inner ring and the outer ring in a neutral position, and can mesh with the inner ring and the outer ring even when it tilts in either direction, all cams behave in the same way, so that no biting occurs. Therefore, it is not necessary to use a large drive source as a drive source for moving the movable spacer in the axial direction, which can achieve energy saving and miniaturization. In addition, during idling, all cams are in a state where they do not contact the outer ring or the inner ring, which can reduce the torque during idling, so that the meshing surface of the cam, the track surface of the outer ring, and the track surface of the inner ring will not be damaged, which can achieve a long life and reduce noise. Moreover, since each cam can transmit torque in both the forward and reverse directions, the number of cams installed can be increased to increase the torque capacity.

[0018] According to the invention involved in Technical Solution 2, since the guide groove portion is formed so that the first phase change allowing portion is located between the phase limiting portion and the second phase change allowing portion, the circumferential movement freedom of the movable spacer relative to the fixed spacer can be controlled in stages, so the action mode can be switched smoothly.

[0019] According to the invention involved in Technical Solution 3 and the invention involved in Technical Solution 4, two unidirectional transmission modes, namely a unidirectional transmission mode capable of transmitting torque in the forward direction and a unidirectional transmission mode capable of transmitting torque in the reverse direction, can be realized, and four action modes including a bidirectional simultaneous idling mode and a bidirectional simultaneous transmission mode can be switched, thereby further improving versatility.

[0020] According to the invention involved in Technical Solution 5, since the movable spacer has a phase synchronization unit that enables the movable spacer to rotate synchronously with the inner ring or the outer ring, the cam can be actively tilted according to the rotation direction of the inner ring or the outer ring, so a bidirectional simultaneous transmission mode that can transmit torque in both positive and negative directions can be reliably realized.

[0021] In addition, according to the invention of claim 6 and the invention of claim 7, the phase synchronization unit is formed of a magnet or a tapered portion provided on the movable spacer and capable of contacting and meshing with the inner ring or the outer ring by axial movement, thereby making it possible to make the movable spacer rotate synchronously with the inner ring or the outer ring with a simple structure without complicating the structure. In particular, according to the invention of claim 7, the movable spacer can be mechanically integrally joined to the inner ring or the outer ring, thereby preventing the movable spacer from sliding on the joint surface of the movable spacer and the inner ring or the outer ring due to the change in the posture of the cam, and preventing the action mode from becoming unstable due to, for example, the adsorption of wear powder.

[0022] According to the invention of claim 8 , when the operation mode is set to the one-way transmission mode, the followability of the tilting operation of the cam in the meshing direction accompanying the rotation of the inner ring or the outer ring can be improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is an exploded perspective view showing a configuration example of a cam clutch according to the first embodiment of the present invention.

[0024] Figure 2 Observed from the front side Figure 1 A perspective view of the cam clutch is shown.

[0025] Figure 3 It is cut by a plane containing the axis of rotation Figure 1 A cutaway perspective view of a cam clutch is shown.

[0026] Figure 4 It is cut by a plane containing the axis of rotation Figure 1 An axial cross-section of the cam clutch is shown.

[0027] Figure 5 It is cut by a plane perpendicular to the axis of rotation. Figure 1 A radial cross-section of a cam clutch is shown.

[0028] Figure 6 This is a perspective view showing the structure of the fixed spacer as viewed from the front side.

[0029] Figure 7 It is a perspective view showing the structure of the movable spacer as seen from the front side.

[0030] Figure 8 (a) and (b) are a perspective view and a cross-sectional view showing the structure of a cam.

[0031] Fig. 9A It is a summary representation Figure 7 A diagram showing the structure of the guide groove portion in the movable spacer is shown.

[0032] Fig. 9B This is a diagram schematically showing a state where the pin member is located in the first phase change allowing portion.

[0033] Fig. 9C This is a diagram schematically showing a state where the pin member is located in the second phase change allowing portion.

[0034] Fig. 10A It means when Figure 1 The illustrated cam clutch is in a side view showing a state of the cam clutch when the operation mode of the cam clutch is the bidirectional simultaneous idling mode.

[0035] Fig. 10B It is a summary representation of Figure 1 The illustrated operation mode of the cam clutch is a schematic diagram showing the state of the cam when the operation mode of the cam clutch is a bidirectional simultaneous idling mode.

[0036] Fig.11A It is a summary representation of Figure 1 The schematic diagram of the state of the cam when the operation mode of the cam clutch is transitioned from the two-way simultaneous idling mode to the one-way transmission mode.

[0037] Fig. 11B It means when Figure 1 The cam clutch is shown in a side view showing a state when the operation mode of the cam clutch is the one-way transmission mode.

[0038] Fig. 12A It means when Figure 1 The illustrated cam clutch is in a side view showing a state of the cam clutch when the operation mode of the cam clutch is the bidirectional simultaneous transmission mode.

[0039] Fig. 12B It is a summary representation of Figure 1 The operation mode of the cam clutch shown is a schematic diagram of the behavior of the cam in the bidirectional simultaneous transmission mode.

[0040] Fig. 12C It is a summary representation of Figure 1 The illustrated cam clutch operation mode is a schematic diagram showing the behavior of the cam when the cam clutch is in a bidirectional simultaneous transmission mode.

[0041] Fig.13 It is a plan view showing another configuration example of the movable spacer.

[0042] Fig.14 It is a summary representation Fig.13 A diagram showing the structure of the guide groove portion in the movable spacer is shown.

[0043] Fig.15A This is a diagram schematically showing the structure of the guide groove portion in still another structural example of the movable spacer.

[0044] Fig. 15B This is a diagram schematically showing the structure of the guide groove portion in still another structural example of the movable spacer.

[0045] Fig.16 It is an exploded perspective view showing the structure of a cam clutch according to a second embodiment of the present invention.

[0046] Fig.17 It is cut by a plane containing the axis of rotation Fig.16 A cutaway perspective view of a cam clutch is shown.

[0047] Fig.18 It is cut by a plane containing the axis of rotation Fig.16 An axial cross-section of a cam clutch is shown.

[0048] Fig.19 It is cut by a plane perpendicular to the axis of rotation. Fig.16 A radial cross-section of a cam clutch is shown.

[0049] Fig. 20 It is a perspective view showing the structure of the fixed spacer.

[0050] Fig.21 It is a perspective view showing the structure of a movable spacer.

[0051] Fig. 22 (a) and (b) are a perspective view and a cross-sectional view showing the structure of a cam.

[0052] Fig.23 This is a diagram schematically showing the structure of the guide groove portion in the fixed spacer.

[0053] Fig.24A It means when Fig.16 The illustrated cam clutch is in a side view showing a state of the cam clutch when the operation mode of the cam clutch is the bidirectional simultaneous idling mode.

[0054] Fig. 24B It is a summary representation of Fig.16 The illustrated operation mode of the cam clutch is a schematic diagram showing the state of the cam when the operation mode of the cam clutch is a bidirectional simultaneous idling mode.

[0055] Fig.25A It means when Fig.16 The illustrated cam clutch is a side view showing a state of the cam clutch when the operation mode of the cam clutch is the one-way transmission mode.

[0056] Fig.25B It means when Fig.16 The schematic diagram of the state of the cam clutch when the operation mode of the cam clutch is the one-way transmission mode is shown.

[0057] Fig.26A It means when Fig.16 The illustrated cam clutch is in a side view showing a state of the cam clutch when the operation mode of the cam clutch is the bidirectional simultaneous transmission mode.

[0058] Fig.26B It is a summary representation of Fig.16 The operation mode of the cam clutch shown is a schematic diagram of the behavior of the cam in the bidirectional simultaneous transmission mode.

[0059] Fig.26C It is a summary representation of Fig.16 The illustrated cam clutch operation mode is a schematic diagram showing the behavior of the cam when the cam clutch is in a bidirectional simultaneous transmission mode.

[0060] Fig. 27 (a) and (b) are a perspective view and a cross-sectional view showing another configuration example of the cam.

[0061] Fig.28A This is a schematic diagram schematically showing the behavior of the cam when the operation mode of the cam clutch is the one-way transmission mode.

[0062] Fig.28B This is a schematic diagram schematically showing the behavior of the cam when the operation mode of the cam clutch is the bidirectional simultaneous transmission mode.

[0063] Fig.29 This is a diagram schematically showing the structure of the guide groove portion in another configuration example of the fixed spacer.

[0064] Fig.30 This is a diagram schematically showing the structure of a guide groove portion in still another configuration example of a fixed spacer.

[0065] Explanation of symbols

[0066] 100-cam clutch; 110-inner ring; 111-track surface; 120-outer ring; 121-track surface; 123-chamfered portion; 125-fixing screw; 130-fixing spacer; 131-shaft; 132-socket group; 133-socket; 134-end wall; 135-outer flange; 136-screw mounting hole; 140-pin member; 140a-first pin member; 140b-second pin member; 150-movable spacer; 151-shaft; 152-socket group; 153-socket; 154-end wall; 155-outer flange; 156-tapered portion; 160-guide groove Part; 160a-the guide groove part on one side; 160b-the guide groove part on the other side; 161-the mounting part; 162-the guide groove; 163-the phase limiting part; 164-the first phase change allowing part; 165-the second phase change allowing part; 166-the first continuous setting part; 167-the second continuous setting part; 168-the third phase change allowing part; 170-the phase synchronization unit; 180-the cam; 181-the reduced diameter part; 182-the foot part; 183-the inner ring side meshing surface; 184-the head part; 185-the outer ring side meshing surface; 186-the flat surface; 187-the clamping spring mounting groove; 190-the force applying unit. DETAILED DESCRIPTION

[0067] <First Embodiment>

[0068] like Figure 1 As shown, the cam clutch 100 of the present invention includes an inner ring 110 , an outer ring 120 , a fixed spacer 130 , a movable spacer 150 , a cam 180 as an engagement member, and a biasing unit 190 .

[0069] like Figures 2 to 5 As shown, in the state where the cam clutch 100 is assembled, the inner ring 110 and the outer ring 120 are arranged to be relatively rotatable on the same rotation axis X, and the track surface 111 of the inner ring 110 and the track surface 121 of the outer ring 120 are arranged to be opposite to each other. In this embodiment, for example, the inner ring 110 is configured as a rotating wheel on the input side, and the outer ring 120 is configured as a rotating wheel on the output side.

[0070] like Figure 6 As also shown, the fixed spacer 130 includes: a cylindrical shaft portion 131 extending along the rotation axis; and an outer flange portion 135 extending radially outwardly over the entire circumference at one end of the shaft portion 131 .

[0071] The shaft portion 131 is formed with a plurality of insertion openings 133 arranged at predetermined intervals in the circumferential direction.

[0072] In this embodiment, four sockets 133 arranged at equal intervals in the circumferential direction are regarded as one socket group 132, and a plurality of socket groups 132 are arranged at equal intervals in the circumferential direction. Each socket 133 is formed so that its opening shape is rectangular.

[0073] The outer flange portion 135 is formed to face one end surface of the outer ring 120 , and has a plurality of screw mounting holes 136 penetrating in the thickness direction so as to be arranged at predetermined intervals in the circumferential direction.

[0074] like Figures 2 to 5 As shown, the shaft portion 131 of the fixed spacer 130 is inserted into the annular space between the inner ring 110 and the outer ring 120 in a manner coaxial with the inner ring 110 and the outer ring 120 with a gap therebetween, and is fixed to the outer ring 120 as a rotating wheel on the output side by a fixing screw 125 installed from the axial outside.

[0075] like Figure 7 As also shown, the movable spacer 150 has: a cylindrical shaft portion 151 extending along the axis of rotation; an annular plate-shaped end wall portion 154 formed at one end of the shaft portion 151 to be opposite to an end face of the inner ring 110; and an outer flange portion 155 at one end of the shaft portion 151 to protrude and extend radially outward over the entire circumferential span.

[0076] The shaft portion 151 is provided with a plurality of insertion openings 153 arranged at predetermined intervals in the circumferential direction so as to face the insertion openings 133 of the fixing spacer 130 , respectively.

[0077] In this embodiment, four sockets 153 arranged at equal intervals in the circumferential direction are regarded as one socket group 152, and a plurality of socket groups 152 are arranged at equal intervals in the circumferential direction. Each socket 153 is formed so that its opening shape is rectangular.

[0078] The outer flange portion 155 is formed so as to be locked to one end surface of the fixed spacer 130 , thereby restricting the movable spacer 150 from moving toward the axial front side.

[0079] like Figures 2 to 5 As shown, on the inner side of the fixed spacer 130, the shaft portion 151 of the movable spacer 150 is inserted into the annular space between the inner ring 110 and the outer ring 120 at a distance from the track surface 111 of the inner ring 110 so as to be coaxial with the inner ring 110 and the outer ring 120, and is configured to be relatively rotatable relative to the fixed spacer 130 and axially movable.

[0080] The cam 180 is configured to mesh with the inner ring 110 and the outer ring 120 even when tilted in either the forward direction or the reverse direction. Figure 5 The clockwise direction is called the "positive direction", and the counterclockwise direction is called the "reverse direction".

[0081] like Figure 8 As also shown, the cam 180 according to the present embodiment has a reduced diameter portion 181 in the radially central portion when viewed from above, and is configured in a substantially gourd-shaped, for example, bilaterally symmetrical shape.

[0082] The leg portion 182 closer to the inner ring side than the reduced diameter portion 181 has an arc-shaped inner ring side meshing surface 183, which is formed as a curved surface smoothly continuing from the inner ring side meshing surface 183 and contacting both side surfaces of the movable spacer 150 along the arc.

[0083] In addition, the head portion 184 closer to the outer ring side than the reduced diameter portion 181 has a flat surface 186 and an outer ring side meshing surface 185 that is continuous on both sides of the flat surface 186, and is formed as a curved surface that is smoothly continuous with the outer ring side meshing surface 185 and contacts the two side surfaces of the fixed spacer 130 along the arc.

[0084] In the present embodiment, for example, an annular garter spring is used as the urging means 190 , and a garter spring mounting groove 187 extending in the circumferential direction is formed on the inner ring side meshing surface 183 of the cam 180 .

[0085] The garter spring installation groove 187 is configured such that the bottom surface is formed to extend parallel to the flat surface 186, and the garter spring is installed in a compressed state, thereby applying force to the cam 180 toward the outer ring 120. Therefore, the cam 180 is in a state of not contacting the inner ring 110 in the neutral posture.

[0086] The foot portion 182 of the cam 180 is inserted into the socket portion 153 of the movable spacer 150, and the head portion 184 is inserted into the socket portion 133 of the fixed spacer 130, so that it is maintained in a changeable posture by the fixed spacer 130 and the movable spacer 150, and is arranged at a predetermined interval in the circumferential direction between the inner ring 110 and the outer ring 120.

[0087] Therefore, in the cam clutch 100, the movable spacer 150 is provided with a guide groove portion 160 extending in the axial direction, and the fixed spacer 130 is provided with a pin member 140 that moves along the guide groove portion 160 along with the axial movement of the movable spacer 150. Thus, by controlling the phase of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130, the operation mode of the cam clutch 100 can be switched.

[0088] like Figure 7 As shown, guide grooves 160 are provided at equal intervals in the circumferential direction in one end side region between adjacent socket groups 152 on the outer surface of the shaft portion 151 of the movable spacer 150. In this embodiment, since the socket groups 152 are provided at equal intervals in the circumferential direction, the guide grooves 160 are also provided at equal intervals in the circumferential direction, thereby being able to stably guide the axial movement of the movable spacer 150 and smoothly switch the action mode of the cam clutch 100.

[0089] The guide groove portion 160 is configured such that a guide groove 162 extending in the axial direction is formed on the outer surface of a mounting portion 161 protruding from the outer surface of the shaft portion 151 of the movable spacer 150 .

[0090] like Fig. 9A As shown, the guide groove 162 includes a phase restricting portion 163 , a first phase change allowing portion 164 , and a second phase change allowing portion 165 .

[0091] The phase limiting portion 163 is formed in a manner extending linearly in the axial direction with a groove width equal to the outer diameter of the pin member 140, and is capable of maintaining the movable spacer 150 in a state where the socket portion 153 of the movable spacer 150 and the socket portion 133 of the fixed spacer 130 are in the same phase.

[0092] Therefore, when the pin member 140 is located at the phase restricting portion 163, the relative rotation of the movable spacer 150 in both the forward and reverse directions with respect to the fixed spacer 130 is prohibited, and the cam 180 is maintained in the neutral posture. Thus, the operation mode of the cam clutch 100 is maintained in the two-way simultaneous idling mode.

[0093] The first phase change allowing portion 164 is continuous with the phase restricting portion 163 via a first continuous portion 166 extending obliquely in the reverse direction toward one axial end. The first phase change allowing portion 164 is formed in such a manner that a groove width larger than the outer diameter of the pin member 140 is extended in the axial direction, and is capable of maintaining the movable spacer 150 in a state of being movable within a prescribed range in the forward rotation direction relative to the fixed spacer 130.

[0094] Therefore, when the pin member 140 is located at the first phase change allowance portion 164, the movable spacer 150 moves relative to the fixed spacer 130 in the normal rotation direction, whereby the cam 180 is tilted. Fig. 9B As shown by the dotted line in , the phase change of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130 due to the relative rotation of the movable spacer 150 relative to the fixed spacer 130 is allowed. Therefore, for example, when the inner ring 110 rotates in the forward direction, the cam 180 is maintained in the meshing standby state so as to immediately start meshing with the inner ring 110 and the outer ring 120, and the operation mode of the cam clutch 100 is maintained in the one-way transmission mode in which the cam 180 can transmit torque in the forward direction.

[0095] The second phase change allowing portion 165 is continuous with the first phase change allowing portion 164 by means of a second continuous setting portion 167 which is configured in such a manner that the groove width increases toward one axial end. The second phase change allowing portion 165 is configured to be formed in such a manner as to extend in the circumferential direction so as to be able to keep the movable spacer 150 in a state where it can move within a prescribed range in both the forward and reverse directions relative to the fixed spacer 130.

[0096] Therefore, when the pin member 140 is located at the second phase change allowing portion 165, Fig. 9C As shown by the dotted line in , the phase change of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130 in both the forward and reverse directions due to the relative rotation of the movable spacer 150 relative to the fixed spacer 130 is allowed. Therefore, even when the inner ring 110 rotates in either the forward or reverse direction, the cam 180 is maintained in the meshing standby state so as to start meshing with the inner ring 110 and the outer ring 120, and the operation mode of the cam clutch 100 is maintained in the bidirectional simultaneous transmission mode in which the cam 180 can transmit torque in either the forward or reverse direction.

[0097] Since the guide groove portion 160 is formed such that the first phase change allowing portion 164 is located between the phase limiting portion 163 and the second phase change allowing portion 165, the circumferential movement freedom of the movable spacer 150 relative to the fixed spacer 130 can be controlled in stages, so the action mode can be switched smoothly.

[0098] In one end region between adjacent socket groups 132 on the inner surface of the shaft portion 131 of the fixed spacer 130 , the pin member 140 is provided to protrude radially inwardly with its tip portion inserted into the guide groove portion 160 .

[0099] In the cam clutch 100 , the movable spacer 150 includes a phase synchronization unit 170 , and when the movable spacer 150 moves axially so that the pin member 140 is located in the second phase change allowing portion 165 , the phase synchronization unit 170 causes the movable spacer 150 to rotate synchronously with the inner ring 110 .

[0100] In this embodiment, the phase synchronization unit 170 is composed of, for example, a magnet, so that the movable spacer 150 and the inner ring 110 are magnetically coupled to each other and rotate synchronously with the rotation direction of the inner ring 110. In the cam clutch 100 involved in this embodiment, three columnar magnets are located at equal intervals in the circumferential direction and are embedded in the end wall portion 154 of the movable spacer 150 with one end surface exposed.

[0101] Next, the operation of the above-mentioned cam clutch 100 will be described.

[0102] First, if Fig. 10A As shown, when the pin member 140 is fixed in the axial position of the phase limiting portion 163 in the guide groove portion 160, the relative movement of the movable spacer 150 in both the positive and negative directions relative to the fixed spacer 130 is prohibited, and the socket portion 153 in the movable spacer 150 and the socket portion 133 in the fixed spacer 130 are kept in the same phase. In this state, Fig. 10B As shown, all cams 180 keep the inner ring side meshing surface 183 away from the track surface 111 of the inner ring 110. Therefore, the action mode of the cam clutch 100 becomes a bidirectional simultaneous idling mode that cuts off the torque transmission between the inner ring 110 and the outer ring 120, and the inner ring 110 idles even when the inner ring 110 rotates in either the forward or reverse direction.

[0103] When the movable spacer 150 is moved in the axial direction, the pin member 140 moves along the first continuous portion 166, so that the movable spacer 150 moves relative to the fixed spacer 130 in the normal rotation direction. Fig.11A As shown, the foot portion 182 of the cam 180 is pressed by the movable spacer 150, and the cam 180 tilts in the meshing direction of the normal rotation direction.

[0104] like Fig. 11BAs shown, when the movable spacer 150 is fixed relative to the fixed spacer 130 at the axial position of the first phase change allowing portion 164 of the pin member 140 in the guide groove portion 160, the phase change of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130 in the forward direction is allowed. As a result, the cam 180 is maintained in the meshing standby state so that it immediately starts to mesh with the inner ring 110 and the outer ring 120 as the inner ring 110 rotates in the forward direction, and the operation mode of the cam clutch 100 is switched to a one-way transmission mode that can transmit torque in the forward direction.

[0105] In addition, when the movable spacer 150 is moved axially as shown in FIG. Fig. 12A As shown, when the movable spacer 150 is fixed relative to the fixed spacer 130 at the axial position of the second phase change allowing portion 165 of the pin member 140 in the guide groove portion 160, the movable spacer 150 is maintained in a state where relative movement in both the forward and reverse directions relative to the fixed spacer 130 is allowed. At this time, the movable spacer 150 is magnetically integrally joined to the inner ring 110 through the phase synchronization unit 170 in the movable spacer 150. In this state, when the inner ring 110 rotates in the forward direction, as shown in FIG. Fig. 12B As shown in FIG. 1 , the movable spacer 150 rotates integrally with the inner ring 110 and presses the foot portion 182 of the cam 180. As a result, the cam 180 tilts in the meshing direction in the forward direction and meshes with the inner ring 110 and the outer ring 120, transmitting torque in the forward direction. On the other hand, when the inner ring 110 rotates in the reverse direction, as shown in FIG. Fig. 12C As shown, the movable spacer 150 rotates integrally with the inner ring 110 and presses the foot portion 182 of the cam 180. As a result, the cam 180 tilts in the meshing direction of the reverse direction and meshes with the inner ring 110 and the outer ring 120, transmitting torque in the reverse direction. In this way, the pin member 140 is in the state of the second phase change allowance portion 165 in the guide groove portion 160, so that the cam 180 can be actively tilted according to the rotation direction of the inner ring 110 of the rotating wheel as the input side, and the operation mode of the cam clutch 100 is switched to a bidirectional simultaneous transmission mode that can transmit torque in both the forward and reverse directions.

[0106] Thus, according to the above-mentioned cam clutch 100, since the guide groove portion 160 provided on the movable spacer 150 is configured to include the phase restricting portion 163, the first phase change allowing portion 164 and the second phase change allowing portion 165, the circumferential movement freedom of the movable spacer 150 relative to the fixed spacer 130 can be controlled by the position of the pin member 140 provided on the fixed spacer 130. Therefore, the action mode of the cam clutch 100 can be switched between the two-way simultaneous idling mode, the one-way transmission mode and the two-way simultaneous transmission mode. When switching the action mode, the posture of the cam 180 can be controlled and the posture of the cam 180 can be maintained only by moving the movable spacer 150 in the axial direction, so that the action mode corresponding to the use condition can be smoothly switched, and high versatility can be obtained.

[0107] In addition, since the cam 180 is configured so as not to contact the inner ring 110 in a neutral position and to mesh with the inner ring 110 and the outer ring 120 even when tilted in either the forward or reverse direction, all the cams 180 behave in the same manner, so that no biting occurs. Therefore, it is not necessary to use a large drive source as a drive source for axially moving the movable spacer 150, and energy saving and miniaturization can be achieved.

[0108] In addition, in the bidirectional simultaneous idling mode, during idling, all cams 180 are in a state of not contacting the inner ring 110 and the outer ring 120, thereby reducing the torque during idling. Therefore, the inner ring side meshing surface 183 and the outer ring side meshing surface 185 of the cam 180, as well as the track surface 111 of the inner ring 110 and the track surface 121 of the outer ring 120 will not be damaged, thereby achieving a long service life and reducing noise.

[0109] Furthermore, since each cam 180 is configured to transmit torque in both the forward and reverse directions, the number of installed cams 180 can be increased to increase the torque capacity.

[0110] In the above, although a cam clutch is described that is configured to switch the action mode among three action modes, namely, a two-way simultaneous idling mode, a one-way transmission mode, and a two-way simultaneous transmission mode, the cam clutch involved in the present invention can also be configured to switch the action mode among four action modes, including two one-way transmission modes, namely, a one-way transmission mode that can transmit torque in the forward direction and a one-way transmission mode that can transmit torque in the reverse direction.

[0111] A cam clutch that can correspond to four action modes can be realized by using a movable spacer 150 having the following structure, that is, for example, Fig.13As shown, the guide grooves are provided in one end side region and the other end side region on the outer surface of the shaft portion 151, respectively. The first phase change allowing portion 164 in the guide groove portion 160a on one side and the first phase change allowing portion 164 in the guide groove portion 160b on the other side keep the movable spacer 150 movable within a predetermined range in different directions relative to the fixed spacer 130. When such a movable spacer 150 is used, the fixed spacer ( Fig.13 The shaft portion 131 (indicated by two-dot chain lines) is configured such that a first pin member 140a and a second pin member 140b are provided in one end side region and the other end side region of the inner surface of the shaft portion 131, respectively.

[0112] In the cam clutch having such a movable spacer 150, when the operation mode is the bidirectional simultaneous idling mode, as shown in FIG. Fig.14 As shown, the first pin member 140a and the second pin member 140b are respectively located in the phase restricting portion 163 in the one guide groove portion 160a and the phase restricting portion 163 in the other guide groove portion 160b.

[0113] When the other end side of the axis ( Fig.14 When the movable spacer 150 is moved (to the left side in the figure), the first pin member 140a moves along the first continuous portion 166 in the guide groove portion 160a on one side, so that the movable spacer 150 moves relative to the fixed spacer 130 in the normal rotation direction, thereby causing the cam 180 to tilt. When the movable spacer 150 is fixed relative to the fixed spacer 130 at the axial position of the first phase change allowing portion 164 in the guide groove portion 160a on one side of the first pin member 140a, the phase change in the normal rotation direction of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130 is allowed. As a result, the operation mode of the cam clutch 100 is switched to a one-way transmission mode capable of transmitting torque in the normal rotation direction. In addition, the second pin member 140b is in a state of being disengaged from the guide groove portion 160b on the other side.

[0114] On the other hand, when the axial end side ( Fig.14When the movable spacer 150 is moved (on the right side in the figure), the second pin member 140b moves along the first continuous portion 166 in the guide groove portion 160b on the other side, so that the movable spacer 150 moves relative to the fixed spacer 130 in the reverse direction, thereby causing the cam 180 to tilt. When the movable spacer 150 is fixed relative to the fixed spacer 130 at the axial position of the first phase change allowing portion 164 in the guide groove portion 160b on the other side of the second pin member 140b, the phase change in the reverse direction of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130 is allowed. As a result, the operation mode of the cam clutch 100 is switched to a one-way transmission mode capable of transmitting torque in the reverse direction. In addition, the first pin member 140a is in a state of being disengaged from the guide groove portion 160a on one side.

[0115] In the movable spacer 150, the guide groove portion 160a on one side and the guide groove portion 160b on the other side respectively have a second phase change allowing portion 165, which can smoothly switch the action mode from a unidirectional transmission mode that can transmit torque in the forward direction to a bidirectional simultaneous transmission mode, or from a unidirectional transmission mode that can transmit torque in the reverse direction to a bidirectional simultaneous transmission mode.

[0116] In addition, even if the guide groove portion also includes a third phase change allowing portion, a cam clutch corresponding to four action modes can be realized. In this case, the third phase change allowing portion is configured to keep the movable spacer 150 movable within a specified range in a direction opposite to the moving direction of the movable spacer 150 when the pin member 140 is located in the first phase change allowing portion 164.

[0117] For example, Fig.15A As shown in FIG. 1 , the third phase change allowing portion 168 may be formed to be continuous with one end side of the second phase change allowing portion 165, or Fig. 15B As shown, it can also be formed to be continuous with the other end side of the phase restriction portion 163, and any configuration can be used.

[0118] Although an embodiment of a phase synchronization unit is described above by magnetically bonding a movable spacer to a magnet of an inner ring, it is sufficient to configure the phase synchronization unit so that the movable spacer can rotate synchronously with the inner ring or the outer ring. The following describes a cam clutch according to a second embodiment of a phase synchronization unit in which a movable spacer is mechanically bonded to an inner ring or an outer ring.

[0119] <Second Embodiment>

[0120] like Figures 16 to 19As shown, the cam clutch 100 involved in the second embodiment basically has the same structure as the cam clutch 100 involved in the first embodiment, and is composed of an inner ring 110, an outer ring 120, a fixed spacer 130, a movable spacer 150, a cam 180 as an engaging member, and a force unit 190.

[0121] In the present embodiment, for example, the inner ring 110 is configured as a rotating wheel on the output side, and the outer ring 120 is configured as a rotating wheel on the input side.

[0122] like Fig. 20 As also shown, the fixed spacer 130 has: a cylindrical shaft portion 131, on which a plurality of socket portions 133 are arranged at predetermined intervals in the circumferential direction and extend along the rotation axis; an annular plate-shaped end wall portion 134, formed at one end of the shaft portion 131 so as to face one end face of the inner ring 110; and an outer flange portion 135, which protrudes and extends radially outward over the entire circumferential span at one end of the shaft portion 131. In this embodiment, five socket portions 133 arranged at equal intervals in the circumferential direction are regarded as one socket portion group 132, and a plurality of socket portion groups 132 are arranged at equal intervals in the circumferential direction.

[0123] like Fig.17 and Fig.18 As shown, the shaft portion 131 of the fixed spacer 130 is inserted into the annular space between the inner ring 110 and the outer ring 120 at a distance from the raceway surface 111 of the inner ring 110 so as to be coaxial with the inner ring 110 and the outer ring 120, and is fixed to the inner ring 110 as a rotating wheel on the output side by a fixing screw 125 installed from the axial outside.

[0124] like Fig.21 As also shown, the movable spacer 150 has: a cylindrical shaft portion 151, on which a plurality of socket portions 153 corresponding to the socket portions 133 of the fixed spacer 130 are formed in a manner arranged at predetermined intervals in the circumferential direction and extending along the rotation axis; and an outer flange portion 155, which protrudes and extends radially outward over the entire circumferential span at one end of the shaft portion 151. In this embodiment, five socket portions 153 arranged at equal intervals in the circumferential direction are regarded as one socket portion group 152, and a plurality of socket portion groups 152 are arranged at equal intervals in the circumferential direction. Each socket portion 153 is formed to have an opening shape in a rectangular shape.

[0125] like Fig.17 and Fig.18As shown, on the outside of the fixed spacer 130, the shaft portion 151 of the movable spacer 150 and the track surface 121 of the outer ring 120 are inserted into the annular space between the inner ring 110 and the outer ring 120 in a manner coaxial with the inner ring 110 and the outer ring 120 with a gap therebetween, and are configured to be relatively rotatable relative to the fixed spacer 130 and axially movable.

[0126] In this embodiment, if Fig. 22 As shown, the cam 180 has a garter spring installation groove 187 in the head portion 184. The garter spring installation groove 187 is configured such that the bottom surface is formed to extend parallel to the flat surface 186, and a garter spring as a force applying unit 190 is installed in a compressed state, thereby applying force to the cam 180 toward the inner ring 110. Therefore, the cam 180 is in a state of not contacting the outer ring 120 in the neutral posture.

[0127] In this embodiment, a guide groove portion 160 is provided in an end side area on the outer surface of the shaft portion 131 of the fixed spacer 130, and a pin component 140 is provided on the movable spacer 150 to move along the guide groove portion 160 as the movable spacer 150 moves axially.

[0128] like Fig. 20 As shown in FIG. 1 , the guide groove portion 160 is configured such that a guide groove 162 extending in the axial direction is formed on the outer surface of a mounting portion 161 protrudingly provided on the outer surface of the shaft portion 131 of the fixed spacer 130. The guide groove 162 includes: a phase restricting portion 163 extending linearly in the axial direction from one axial end edge of the fixed spacer 130; a first phase change allowing portion 164, which is continuous with the phase restricting portion 163 through a first continuous portion 166 extending obliquely in the normal rotation direction toward the other axial end side; and a second phase change allowing portion 165, which is continuous with the first phase change allowing portion 164 through a second continuous portion 167 formed in a manner that the groove width is increased toward the other axial end side.

[0129] When the pin member 140 is located at the phase restricting portion 163, the relative rotation of the movable cage 150 in both the forward and reverse directions with respect to the fixed cage 130 is prohibited, and the cam 180 is maintained in the neutral posture. Thus, the operation mode of the cam clutch 100 is maintained in the two-way simultaneous idling mode.

[0130] When the pin member 140 is located at the first phase change allowing portion 164, the movable spacer 150 moves relative to the fixed spacer 130 in the normal rotation direction, whereby the cam 180 is tilted, and at the same time, the phase change of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130 due to the relative rotation of the movable spacer 150 relative to the fixed spacer 130 is allowed. Thus, for example, when the outer ring 110 rotates in the normal rotation direction, the cam 180 is maintained in the meshing standby state so as to immediately start meshing with the inner ring 110 and the outer ring 120, and the operation mode of the cam clutch 100 is maintained in the one-way transmission mode in which the cam 180 can transmit torque in the normal rotation direction.

[0131] When the pin member 140 is located at the second phase change allowing portion 165, the phase change of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 of the fixed spacer 130 in both the forward and reverse directions is allowed due to the relative rotation of the movable spacer 150 relative to the fixed spacer 130. Therefore, even when the outer ring 120 rotates in either the forward or reverse direction, the cam 180 is maintained in the meshing standby state so as to start meshing with the inner ring 110 and the outer ring 120, and the operation mode of the cam clutch 100 is maintained in the bidirectional simultaneous transmission mode in which the cam 180 can transmit torque in either the forward or reverse direction.

[0132] Furthermore, in the second embodiment, for the sake of convenience, Fig.19 The counterclockwise direction is called the "forward direction", and the clockwise direction is called the "reverse direction".

[0133] In one end region between adjacent socket groups 152 on the shaft portion 151 of the movable spacer 150 , the pin member 140 is provided to protrude radially inwardly so that the tip end portion is inserted into the guide groove portion 160 .

[0134] In this embodiment, the phase synchronization unit 170 is configured such that when the movable spacer 150 moves toward the other axial end side in a manner that causes the pin member 140 to be located in the second phase change allowing portion 165, the movable spacer 150 is mechanically integrally joined to the outer ring 120 so that the movable spacer 150 rotates synchronously with the outer ring 120.

[0135] The phase synchronization unit 170 is composed of a chamfered portion 123 formed in a conical shape on the inner peripheral edge of one end of the outer ring 120 and a tapered portion 156 provided on one end side of the movable spacer 150. The outer peripheral surface of the outer flange portion 155 is formed in a manner inclined radially inward from one axial end side toward the other end side, thereby forming the tapered portion 156 of the movable spacer 150.

[0136] The inclination angle of the inclined surface of the tapered portion 156 with respect to the rotation axis is formed to be larger than the inclination angle of the inclined surface of the chamfered portion 123 of the outer ring 120 with respect to the rotation axis.

[0137] In the cam clutch 100 according to the second embodiment, first, Fig.24A As shown, when the movable spacer 150 is fixed relative to the fixed spacer 130 at the axial position of the phase limiting portion 163 of the pin member 140 in the guide groove portion 160, the relative movement of the movable spacer 150 in both the positive and negative directions relative to the fixed spacer 130 is prohibited, and the socket portion 153 in the movable spacer 150 and the socket portion 133 in the fixed spacer 130 are kept in the same phase. In this state, as shown in FIG. Fig. 24B As shown, all cams 180 are kept away from the raceway surface 121 of the outer ring 120. Therefore, the operation mode of the cam clutch 100 is a two-way simultaneous idling mode in which the torque transmission between the inner ring 110 and the outer ring 120 is cut off.

[0138] like Fig.25A As shown, when the movable spacer 150 is moved toward the other end side in the axial direction and fixed at the axial position of the first phase change allowing portion 164 of the guide groove portion 160 of the pin member 140, the phase change of the socket portion 153 in the movable spacer 150 relative to the socket portion 133 in the fixed spacer 130 in the forward rotation direction is allowed. Fig.25B As shown, the cam 180 tilts in the meshing direction of the forward rotation direction. Thus, the operation mode of the cam clutch 100 is switched to a one-way transmission mode capable of transmitting torque in the forward rotation direction.

[0139] like Fig.26A As shown, when the movable spacer 150 is further moved to the other axial end side and fixed at the axial position of the second phase change allowing portion 165 of the pin member 140 located in the guide groove portion 160, the movable spacer 150 is maintained in a state where relative movement in both positive and negative directions relative to the fixed spacer 130 is allowed. At this time, the tapered portion 156 of the movable spacer 150 contacts and engages with the chamfered portion 123 of the outer ring 120, and the movable spacer 150 and the outer ring 120 are mechanically integrally joined.

[0140] In this state, when the outer ring 120 rotates in the forward direction, Fig.26B As shown in FIG. 1 , the movable spacer 150 rotates integrally with the outer ring 120 and presses the head portion 184 of the cam 180. As a result, the cam 180 tilts in the meshing direction in the forward direction and meshes with the inner ring 110 and the outer ring 120, transmitting torque in the forward direction. On the other hand, when the outer ring 120 rotates in the reverse direction, as shown in FIG. Fig.26CAs shown, the movable spacer 150 rotates integrally with the outer ring 120 and presses the head portion 184 of the cam 180. As a result, the cam 180 tilts in the meshing direction of the reverse direction and meshes with the inner ring 110 and the outer ring 120, and transmits torque in the reverse direction. In this way, the pin member 140 is in the state of the second phase change allowance portion 165 of the guide groove portion 160, so that the cam 180 can be actively tilted according to the rotation direction of the outer ring 120 of the rotating wheel as the input side, and the operation mode of the cam clutch 100 is switched to a bidirectional simultaneous transmission mode that can transmit torque in both the forward and reverse directions.

[0141] Therefore, according to the cam clutch 100 involved in the above-mentioned second embodiment, it is basically possible to obtain the same effect as the cam clutch 100 involved in the first embodiment. In addition, since the phase synchronization unit 170 is configured to mechanically integrate the movable spacer 150 and the outer ring 120, it is possible to avoid slippage on the joint surface between the movable spacer 150 and the outer ring 120 due to the change in the posture of the cam 180, and at the same time, it is possible to avoid the action mode becoming unstable due to, for example, the adsorption of wear powder.

[0142] In the cam clutch 100 involved in the above-mentioned first embodiment and the cam clutch 100 involved in the second embodiment, although the structure in which the cam 180 is in a neutral posture due to the force applied by the force unit 190 is described, the cam 180 can also be constructed to be in an inclined posture contacting the inner ring 110 and the outer ring 120 due to the force applied by the force unit 190.

[0143] For example, Fig. 27 As shown, the bottom surface of the clamp spring installation groove 187 of such a cam 180 is formed to extend radially outwardly from one side toward the other side, and by installing the clamp spring as the force applying unit 190, the inner ring side meshing surface 183 of the cam 180 and the outer ring side meshing surface 185 on one side receive force and are in an inclined posture contacting the inner ring 110 and the outer ring 120. In this example, although the clamp spring installation groove 187 is formed in the head portion 184, it can also be a structure in which the clamp spring installation groove 187 is formed in the foot portion 182. In addition, the clamp spring installation groove 187 can be formed to make the cam 180 in an inclined posture capable of transmitting torque in the forward direction, or it can be formed to make the cam 180 in an inclined posture capable of transmitting torque in the reverse direction, and any formation method can be used.

[0144] In the cam clutch using such a cam 180, when the operation mode is the bidirectional simultaneous idling mode, the pin member 140 is fixed at the axial position of the phase restricting portion 163 of the guide groove portion 160, so that the cam 180 is in a state of maintaining a neutral posture (refer to Fig. 24B ).

[0145] When the cam clutch is in the one-way transmission mode, the pin member 140 is fixed in the axial position of the first phase change allowing portion 164 of the guide groove portion 160, and the movable spacer 150 is kept in a state where the phase change in the positive rotation direction relative to the fixed spacer 130 is allowed. Fig.28A As shown in FIG. 1 , the cam 180 is held in a tilted posture rotating in the meshing direction in the forward rotation direction by the force applied by the force applying unit. Fig.28A As shown by the solid arrow in FIG. 1 , the followability of the tilting action of the cam 180 in the meshing direction accompanying the normal rotation direction rotation of the outer ring 120 can be improved.

[0146] In addition, when the cam clutch is in the bidirectional simultaneous transmission mode, the pin member 140 is fixed in the axial position of the second phase change allowing portion 165 of the guide groove portion 160, and the movable spacer 150 is kept in a state where relative movement in both the forward and reverse directions relative to the fixed spacer 130 is allowed. Fig.28B As shown, the cam 180 is held in the tilted posture in which it rotates in the meshing direction of the reverse direction due to the biasing force of the biasing unit.

[0147] At this time, since the movable spacer 150 is integrally connected with the outer ring 120, Fig.28B As shown by the solid arrow in FIG. 1 , as the outer ring 120 rotates in the positive direction, the cam 180 tilts in the meshing direction and meshes with the inner ring 110 and the outer ring 120. Fig.28B As shown by the hollow arrow in , as the outer ring 120 rotates in the reverse direction, the cam 180 tilts in the meshing direction and meshes with the inner ring 110 and the outer ring 120 .

[0148] The cam clutch according to the second embodiment may also be configured to switch the operation mode among four operation modes.

[0149] For example, Fig.29 As shown, the cam clutch corresponding to four operation modes can be realized by using the fixed spacer 130 having the following structure, that is, the guide grooves are respectively provided in the one end side region and the other end side region on the outer surface of the shaft portion 131, and the first phase change allowing portion 164 in the one guide groove portion 160a and the first phase change allowing portion 164 in the other guide groove portion 160b keep the movable spacer 150 in a state where it can move within a predetermined range in different directions relative to the fixed spacer 130. When such a fixed spacer 130 is used, the structure of the movable spacer is that the first pin member 140a and the second pin member 140b are respectively provided in the one end side region and the other end side region on the inner surface of the shaft portion.

[0150] In a cam clutch having such a fixed spacer 130, when the operating mode is a bidirectional simultaneous idling mode, the first pin component 140a and the second pin component 140b are in a state where they are respectively located at the phase limiting portion 163 in the guide groove portion 160a on one side and the phase limiting portion 163 in the guide groove portion 160b on the other side.

[0151] When the other end side of the axis ( Fig.29 When the movable spacer is moved (on the left side of the cam clutch 100), and the movable spacer is fixed relative to the fixed spacer 130 at the axial position of the first phase change allowing portion 164 in the guide groove portion 160a on one side of the first pin member 140a, the phase change of the socket portion in the movable spacer relative to the socket portion in the fixed spacer in the forward direction is allowed. As a result, the working mode of the cam clutch 100 is switched to a one-way transmission mode capable of transmitting torque in the forward direction. In addition, the second pin member 140b is in a state of being disengaged from the guide groove portion 160b on the other side.

[0152] On the other hand, when the axial end side ( Fig.29 When the movable spacer is moved (on the right side of the cam clutch 100), and the movable spacer is fixed relative to the fixed spacer 130 at the axial position of the first phase change allowing portion 164 in the guide groove portion 160b on the other side of the second pin member 140b, the phase change of the socket portion in the movable spacer relative to the socket portion in the fixed spacer in the reverse direction is allowed. As a result, the working mode of the cam clutch 100 is switched to a one-way transmission mode capable of transmitting torque in the reverse direction. In addition, the first pin member 140a is in a state of being disengaged from the guide groove portion 160a on one side.

[0153] In the fixed spacer 130, the guide groove portion 160a on one side and the guide groove portion 160b on the other side respectively have a second phase change allowing portion 165, so that the working mode can be smoothly switched from a unidirectional transmission mode that can transmit torque in the forward direction to a bidirectional simultaneous transmission mode, or from a unidirectional transmission mode that can transmit torque in the reverse direction to a bidirectional simultaneous transmission mode.

[0154] At this time, at the other axial end side, if a chamfered portion is also formed on the outer ring and a tapered portion is provided on the movable spacer, when the second pin member 140b is located in the second phase change allowing portion 165 and the working mode is a bidirectional simultaneous transmission mode, the movable spacer can rotate synchronously with the outer ring.

[0155] In addition, even if the guide groove portion is configured to include a third phase change allowing portion, a cam clutch that can correspond to four operating modes can be realized. In this case, the third phase change allowing portion is configured to keep the movable spacer 150 in a state of moving within a prescribed range in a direction opposite to the moving direction of the movable spacer 150 when the pin member 140 is located in the first phase change allowing portion 164.

[0156] For example, Fig.30 As shown, the third phase change allowing portion 168 may be formed to be continuous with the other end side of the second phase change allowing portion 165 .

[0157] As mentioned above, although embodiment of this invention is described in detail, this invention is not limited to the said embodiment, Various design changes are possible without departing from the scope of this invention described in a claim.

[0158] For example, in the first embodiment described above, an example is described in which the inner ring is used as a rotating wheel on the input side and the outer ring is used as a rotating wheel on the output side, but the inner ring may be used as a rotating wheel on the output side and the outer ring may be used as a rotating wheel on the output side. Thus, the cam may be configured to be separated from the outer ring in a neutral posture, or the cam may be configured to be separated from the inner ring and the outer ring in a neutral posture. Furthermore, the spacer located on the inner ring side may be used as a fixed spacer, the spacer located on the outer ring side may be used as a movable spacer, and the magnet as a phase synchronization unit may be provided on the spacer on the outer ring side. Similarly, in the second embodiment described above, the inner ring may be used as a rotating wheel on the input side and the outer ring may be used as a rotating wheel on the output side. Thus, the cam may be configured to be separated from the inner ring in a neutral posture, or the cam may be configured to be separated from the inner ring and the outer ring in a neutral posture. Furthermore, the spacer located on the inner ring side may be configured as a movable spacer, the spacer located on the outer ring side may be configured as a fixed spacer, and the phase synchronization unit may be configured as a structure in which the movable spacer is mechanically integrated with the inner ring.

[0159] In addition, in the first embodiment described above, a structure in which a pin member is provided on the fixed spacer and a guide groove portion is provided on the movable spacer is described, but it is also possible to configure such that the guide groove portion is provided on the inner surface of the shaft portion of the fixed spacer, and the pin member protruding radially outward is provided on the outer surface of the movable spacer. Similarly, in the second embodiment described above, it is also possible to configure such that the guide groove portion is provided on the inner surface of the movable spacer, and the pin member protruding radially outward is provided on the outer surface of the fixed spacer.

[0160] Furthermore, as long as the phase synchronization unit can rotate the movable spacer in synchronization with the inner ring or the outer ring, it may be formed by, for example, a friction plate or a spring.

[0161] In addition, as long as the cam is configured to be meshable in either the forward or reverse directions, it is not necessary to be formed in a bilaterally symmetrical manner.

[0162] In addition, the arrangement of the socket portions in the fixed spacer and the movable spacer is not limited to the above-mentioned embodiment, but can be appropriately changed according to the number of cams (torque capacity) to be installed.

[0163] The urging means is not particularly limited as long as it is an elastic body that can urge the plurality of cams toward the outer ring, and may be composed of a plurality of leaf springs, a plurality of torsion springs, or the like.

Claims

1. A cam clutch comprising: an inner ring and an outer ring, which are arranged to be relatively rotatable on the same axis; a fixed spacer, which has socket portions arranged at predetermined intervals in the circumferential direction and is fixed to the inner ring or the outer ring; a movable spacer, which has socket portions arranged at predetermined intervals in the circumferential direction and is configured to be relatively rotatable relative to the fixed spacer; a plurality of cams, which are configured to be held by the fixed spacer and the movable spacer, so as to be arranged along the circumferential direction between the inner ring and the outer ring, relative to a neutral posture that does not contact either or both of the inner ring and the outer ring, and can mesh with the inner ring and the outer ring even when tilted in either direction; and a force applying unit, which applies force in a manner that the plurality of cams are in a neutral posture or in an inclined posture that contacts the inner ring and the outer ring, characterized in that: The movable spacer is arranged to be movable in the axial direction. A guide groove portion is provided on one of the fixed spacer and the movable spacer in a manner extending in the axial direction, and a pin member is provided on the other of the fixed spacer and the movable spacer in a manner moving along the guide groove portion as the movable spacer moves in the axial direction. The guide groove portion includes: a phase limiting portion, which is configured to be able to maintain the movable spacer in a state where the socket portion of the movable spacer is in the same phase as the socket portion of the fixed spacer; a first phase change allowing portion, which is configured to be able to maintain the movable spacer in a state where it can move within a specified range in either a positive or negative direction relative to the fixed spacer; and a second phase change allowing portion, which is configured to be able to maintain the movable spacer in a state where it can move within a specified range in both positive and negative directions relative to the fixed spacer.

2. The cam clutch according to claim 1, characterized in that: The guide groove portion is formed so that the first phase change allowing portion is located between the phase restricting portion and the second phase change allowing portion.

3. The cam clutch according to claim 1, wherein the guide groove is provided in one end side region and the other end side region in the axial direction, respectively. The first phase change allowing portion in one guide groove portion and the first phase change allowing portion in the other guide groove portion are configured to hold the movable spacer in a state movable within a predetermined range in different directions relative to the fixed spacer.

4. The cam clutch according to claim 1 is characterized in that the guide groove portion also includes a third phase change allowing portion, which is configured to maintain the movable spacer in a state where it can move within a specified range in a direction opposite to the moving direction of the movable spacer when the pin member is located in the first phase change allowing portion.

5. The cam clutch according to claim 1, characterized in that: The movable spacer includes a phase synchronization unit that rotates the movable spacer in synchronization with the inner ring or the outer ring when the movable spacer moves in the axial direction so that the pin member is located in the second phase change allowing portion.

6. The cam clutch according to claim 5, characterized in that: The phase synchronization unit is composed of a magnet.

7. The cam clutch according to claim 5, characterized in that: The phase synchronization unit is composed of a tapered portion that is provided on the movable spacer and can come into contact and mesh with the inner ring or the outer ring by axial movement.

8. The cam clutch according to claim 1, characterized in that: The plurality of cams are configured to rotate by the biasing force of the biasing unit and to be in an inclined posture.

Images