Selectable clutch

Abstract

A selectable clutch (100) according to the present invention is configured in such a manner that an outer ring-side spacer ring (120) and an inner ring-side spacer ring (130) are independently moved in the axial direction by a cylindrical cam (155) having a cam groove (155) formed on the circumferential surface thereof, and that operation modes can be switched, and the cam groove (155) has: a first follower guide region (L1) in which the outer ring-side spacer ring (120) and the inner ring-side spacer ring (130) are inserted into the first follower guide region (L1), and a second follower guide region (L2) in which the outer ring-side spacer ring (120) is inserted into the first follower guide region (L1); the first driven section (160) is connected with the outer ring side spacer ring (120), and the first driven section (160) is made to move in the axial direction. And a second driven section guide region (L2) including an inclined portion for moving a second driven section connected to the inner ring-side spacer ring (130) in the axial direction, one region being configured so as to include an inclined portion formed so as to be shifted in phase from the inclined portion of the other region in the circumferential direction, the second driven section guide region (L2) including an inclined portion for moving the second driven section in the axial direction, the second driven section being connected to the inner ring-side spacer ring (130).

Description

Technical Field

[0001] The present invention relates to a selectable clutch configured to be able to switch an operating mode. Background Art

[0002] As a selectable clutch, there is known a structure in which an operation mode is switched by moving an operation mode switching unit in the axial direction to tilt a cam as a power transmission member (for example, see Patent Document 1).

[0003] In the selectable clutch described in Patent Document 1, by tilting only one of the first cam and the second cam, which have different meshing directions relative to the outer ring and the inner ring, or by tilting both the first cam and the second cam, the following three action modes can be switched, namely: a two-way locking mode that can transmit power in both forward and reverse directions; a one-way locking mode that can transmit power in either forward or reverse directions; and a two-way idling mode that cuts off power transmission in both forward and reverse directions.

[0004] On the other hand, a switching mechanism using a cylindrical cam is known, for example, as a clutch switching mechanism. For example, Patent Document 2 describes a switching mechanism for a four-wheel drive vehicle drive force distribution device that connects an input shaft to a rear wheel output shaft via a sub-transmission mechanism. The sub-transmission mechanism comprises a planetary gear mechanism with a sun gear. The input shaft receives power from the engine via an automatic transmission or a manual transmission, and the rear wheel output shaft serves as a coaxial main output shaft. In this switching mechanism, a moving cylindrical cam, fixed to the output shaft of a driver that controls the moving mechanism of the sub-transmission mechanism, is rotated. A moving cam groove formed on its outer circumference guides a moving pin in the axial direction, allowing the moving pin to switch between an L position, in which the moving gear meshes with the clutch gear, and an H position, in which the sun gear is directly connected to the rear wheel output shaft.

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Application Laid-Open No. 2020-190255

[0007] Patent Document 2: Japanese Patent Application Laid-Open No. 2008-128262 Summary of the Invention

[0008] Moreover, there are many cases where the selectable clutch needs to be constructed to be able to switch between four action modes, namely, a two-way locking mode, a forward direction locking mode, a reverse direction locking mode, and a two-way idling mode. Therefore, the switching mechanism for switching the action mode of the selectable clutch is also required to be constructed to be able to switch the selectable clutch in four action modes.

[0009] However, in the above-mentioned selectable clutch, in the structure in which the shapes of the first cam and the second cam are changed to cause the first cam and the second cam to tilt in sequence, the one-way locking mode only realizes the action mode of either the forward direction locking mode or the reverse direction locking mode. In addition, there is a problem that the structure of the cam itself becomes complicated.

[0010] Regarding the switching mechanism, the switching mechanism described in the above-mentioned patent document 2 realizes simple linear motion of the driven section between two axial positions by the rotation of a cylindrical cam. Even if it is considered to be used as a driving source for the action mode switching unit on the selectable clutch described in the above-mentioned patent document 1, it cannot be constructed so as to be able to switch the selectable clutch among four action modes.

[0011] Furthermore, since the cylindrical cam, the input shaft, and the main output shaft of the switching mechanism described in Patent Document 2 are located on different rotation axes, when used as a switching mechanism for a selectable clutch, the radial size of the selectable clutch becomes larger.

[0012] The present invention is based on the above situation, and the technical problem to be solved is to provide a selective clutch that can smoothly switch the action mode and can switch the action mode according to the usage conditions, thereby realizing a highly functional clutch.

[0013] The present invention is a selectable clutch that can maintain a first cam and a second cam having different meshing directions relative to the outer ring and the inner ring by means of an outer ring side spacer and an inner ring side spacer provided between the outer ring and the inner ring, and has a switching mechanism for changing an action mode by forcibly tilting either or both of the first cam and the second cam, which can solve the above-mentioned problem by the following contents, namely, the outer ring side spacer and the inner ring side spacer are arranged to be able to move axially between a first axial position and a second axial position, the outer ring side spacer is constructed so that the first cam can change its posture between an engagement standby posture and an idling posture by moving between the first axial position and the second axial position, the idling posture being tilted away from the inner ring or the outer ring, and the inner ring side spacer is constructed so that the first cam can change its posture between an engagement standby posture and an idling posture by moving between the first axial position and the second axial position, the idling posture being tilted away from the inner ring or the outer ring, Moving between the first axial position and the second axial position can cause the second cam to change its posture between an engaged standby posture and an idling posture, wherein the idling posture is tilted away from the inner ring or the outer ring, and the switching mechanism comprises a cylindrical cam having a cam groove formed on the circumferential surface and a first driven section and a second driven section combined with the cylindrical cam, and while the first driven section is connected to the outer ring side spacer, the second driven section is connected to the inner ring side spacer, and the cam groove comprises: a first driven section guide area, including an inclined portion for moving the first driven section in the axial direction; and a second driven section guide area, including an inclined portion for moving the second driven section in the axial direction, an area on one side of the first driven section guide area and the second driven section guide area includes an inclined portion formed by shifting the circumferential phase with the inclined portion of the other area.

[0014] According to the invention according to claim 1, the cam groove formed in the cylindrical cam includes a first driven segment guide region including an inclined portion for axially moving the first driven segment, and a second driven segment guide region including an inclined portion for axially moving the second driven segment. The inclined portion in one of the first and second driven segment guide regions is circumferentially phase-shifted from the inclined portion in the other region. This allows the first and second driven segments to independently move in the axial direction. Therefore, by providing the first cam's posture control function to the outer ring spacer connected to the first driven segment, and the second cam's posture control function to the inner ring spacer connected to the second driven segment, the cam can be tilted simply by axially moving one or both of the outer ring spacer and the inner ring spacer, and the changed cam posture can be maintained. Consequently, the operating mode can be smoothly switched with a simple configuration, and the operating mode can be switched according to usage conditions, thereby achieving enhanced functionality.

[0015] According to the invention according to claim 2, a cylindrical cam is formed by forming a cam groove on the circumferential surface of a cylindrical member. The first driven section is formed by an annular body with a follower protruding inward from the inner circumference, which engages with the cam groove. Furthermore, the second driven section is formed by an annular body with a follower protruding outward from the outer circumference, which engages with the cam groove. This allows the cylindrical cam, the first driven section, and the second driven section to be coaxially arranged with the outer and inner rings. This allows the radial dimensions of the selectable clutch to be miniaturized. Furthermore, since the first and second driven section guide areas can be arranged on the same circumference of the cylindrical cam, the axial dimensions of the selectable clutch can also be miniaturized. Furthermore, since power is transmitted coaxially, bending moment is virtually eliminated, thus avoiding performance degradation due to deformation. Furthermore, the use of a single shaft reduces the number of parts, the risk of failure, and the need for maintenance.

[0016] According to the invention involved in Technical Solution 3 of the present invention, by forming the first driven joint guide area and the second driven joint guide area with inclined portions which are staggered in phase in the circumferential direction at positions separated in the axial direction, the first driven joint and the second driven joint can each be moved independently in the axial direction, and the action mode can be switched according to the usage conditions, thereby achieving high functionality.

[0017] According to the invention involved in technical solution 4, since the first and second driven joints are prohibited from rotating with the rotation of the cylindrical cam, the first and second driven joints can be effectively moved axially by guiding the followers along the inclined portion of the cam groove to switch the operation mode.

[0018] According to the invention involved in technical solution 5, by limiting the freedom of circumferential movement of the outer ring side spacer ring and the inner ring side spacer ring, when the posture of the cam is changed, the "engagement" of the first cam and the second cam with the outer ring and the inner ring at the same time can be avoided, thereby achieving smooth movement and high responsiveness.

[0019] According to the invention according to claim 6 , the degree of freedom of the circumferential movement of the outer race side spacer and the inner race side spacer can be restricted with a simple configuration. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 It is an exploded perspective view showing a configuration example of a selectable clutch according to the first embodiment of the present invention.

[0021] Figure 2 yes Figure 1 A side view of the selectable clutch is shown.

[0022] Figure 3 yes Figure 2 AA line section view.

[0023] Figure 4 yes Figure 2 BB line cross-sectional view.

[0024] Figure 5 yes Figure 1 The selective clutch shown is a sectional perspective view cut along a plane including the rotation axis.

[0025] Figure 6A This is a perspective view showing the structure of the outer ring side spacer ring.

[0026] Figure 6B yes Figure 6A The partial expanded view of the outer ring side spacer is shown.

[0027] Figure 7A This is a perspective view showing the structure of the inner ring side spacer ring.

[0028] Figure 7B yes Figure 7A The partial expanded view of the inner ring side spacer is shown.

[0029] Figure 8A It is a perspective view showing the structure of a position regulating spacer ring.

[0030] Figure 8B yes Figure 8A A partial expanded view of the position limiting spacer ring is shown.

[0031] Figure 9 This is a development view showing the structure of a cylindrical cam.

[0032] Figure 10 It is a perspective view showing the structure of the first driven joint.

[0033] Figure 11 It is a perspective view showing the structure of the second driven joint.

[0034] Figure 12 It is a perspective view showing the structure of the casing.

[0035] Figure 13 This is a timing chart for explaining the operation of the cylindrical cam.

[0036] Figure 14 It is a schematic representation Figure 1 The illustrated schematic diagram shows the states of the first cam and the second cam when the selectable clutch is in the reverse direction lock mode.

[0037] Figure 15A Yes Figure 1 The illustrated side view shows the selectable clutch in the bidirectional freewheeling mode.

[0038] Figure 15B It is a schematic representation Figure 1 The diagram schematically shows the states of the first cam and the second cam when the selectable clutch is in the bidirectional freewheeling mode.

[0039] Figure 16A Yes Figure 1 A side view of the selectable clutch shown in the bidirectional locking mode.

[0040] Figure 16B It is a schematic representation Figure 1 The diagram schematically shows the states of the first cam and the second cam when the selectable clutch is in the bidirectional lock mode.

[0041] Figure 17A Yes Figure 1 The illustrated side view shows the selectable clutch in the forward rotation lock mode.

[0042] Figure 17B It is a schematic representation Figure 1 The diagram schematically shows the states of the first cam and the second cam when the selectable clutch is in the forward rotation direction lock mode.

[0043] Figure 18 This is a development view showing another configuration example of a cylindrical cam.

[0044] Figure 19 This is a timing chart for explaining the operation of the cylindrical cam.

[0045] Figure 20 It is a perspective view showing a configuration example of a selectable clutch according to a second embodiment of the present invention.

[0046] Figure 21 yes Figure 20 An exploded perspective view of the selectable clutch is shown.

[0047] Figure 22 This is a perspective view showing the structure of the outer ring side spacer ring.

[0048] Figure 23 This is a perspective view showing the structure of the inner ring side spacer ring.

[0049] Figure 24 It is a perspective view showing the structure of the first driven joint.

[0050] Figure 25 This is a development view showing the structure of a cylindrical cam.

[0051] Figure 26 This is a timing chart for explaining the operation of the cylindrical cam.

[0052] Explanation of symbols

[0053] 100, 200 - Selectable clutch; 101 - Outer ring; 102 - Outer ring raceway surface; 105 - Inner ring; 106 - Inner ring raceway surface; 110 - Cam; 110a - First cam; 110b - Second cam; 115 - Force-adding unit; 120, 220 - Outer ring side spacer; 121, 221 - Main body; 122, 222 - Outer flange; 222a - Groove; 123 - First cam holding portion; 123a - Guide space; 123b - First posture fixing space; 123c - Second posture fixing space; 124a - First opening width variable portion; 124b - Second opening width variable portion; 125 - Second cam holding portion ; 126-inner groove portion; 127-guide groove portion; 128-sliding groove portion; 130, 230-inner ring side spacer; 131, 231-body portion; 132-inner flange portion; 133-first cam holding portion; 134-second cam holding portion; 134a-guide space portion; 134b-first posture fixing space portion; 134c-second posture fixing space portion; 135a-first opening width variable portion; 135b-second opening width variable portion; 136-outer groove portion; 137-guide groove portion; 138-sliding groove portion; 239-outer flange portion; 239a-groove; 140-position limiting spacer; 141-circular ring portion; 142- Connecting portion; 143-recessed portion; 145-outer protrusion; 146-inner protrusion; 150, 250-switching mechanism; 151, 251-cylindrical cam; 152-shaft portion; 153-outer flange portion; 155, 255-cam groove; 156a, 256a-first straight portion; 156b, 256b-first inclined portion; 156c, 256c-second straight portion; 157a, 257a-first straight portion; 157b, 257b-first inclined portion; 157c, 257c-second straight portion; 157d, 257d-second inclined portion; 157e, 257e-third straight portion; 160, 260-first driven section; 1 61-base portion; 162-recess; 163-peripheral wall portion; 164-external teeth; 165, 265-first follower; 266-engaging portion; 267-arm portion; 268-bearing portion; 269-cylindrical cam through-hole; 170, 270-second follower section; 171-base portion; 172-extension portion; 173-internal teeth; 175, 275-second follower; 180-housing; 181-outer cylinder portion; 182-internal teeth; 185-inner cylinder portion; 186-external teeth; 187-notch portion; 190-retaining ring; 191-retaining ring; C1-rotation axis; C2-rotation drive shaft; L1-first follower section guide area; L2-second follower section guide area. DETAILED DESCRIPTION

[0054] Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[0055] (First embodiment)

[0056] like Figures 1 to 5 As shown, a selectable clutch 100 according to a first embodiment of the present invention comprises: an outer ring 101 and an inner ring 105 arranged to rotate coaxially relative to each other; a plurality of cams 110 arranged at intervals in the circumferential direction in the annular space between the outer ring raceway surface 102 and the inner ring raceway surface 106, for transmitting and interrupting torque between the outer ring 101 and the inner ring 105; and a biasing unit 115 for biasing each of the plurality of cams 110 so as to contact the outer ring 101 and the inner ring 105. The outer ring side spacer 120 and the inner ring side spacer 130 are arranged to rotate coaxially with the outer ring 101 or the inner ring 105 between the outer ring 101 and the inner ring 105, and hold each of the multiple cams 110; the position limiting spacer 140 is arranged between the outer ring side spacer 120 and the inner ring side spacer 130, and limits the circumferential movement freedom of the outer ring side spacer 120 and the inner ring side spacer 130; and the switching mechanism 150 switches the action mode of the selectable clutch 100. Figures 1 to 5 C1 is the axis of rotation.

[0057] Each of the plurality of cams 110 includes a first cam 110 a and a second cam 110 b having mutually different meshing directions with respect to the outer ring 101 and the inner ring 105 .

[0058] In this embodiment, the first cam 110a and the second cam 110b have the same outer shape, for example, and one end surface of the cam 110 is directed axially forward ( Figure 3 The cam arranged in a direction perpendicular to the drawing (toward the front side) is used as the first cam 110a, and the cam arranged with the other end surface of the cam 110 facing axially forward is used as the second cam 110b.

[0059] The first cam 110 a and the second cam 110 b are arranged alternately at equal intervals in the circumferential direction, for example.

[0060] The arrangement of the first cams 110a and the second cams 110b is not particularly limited. The first cams 110a and the second cams 110b may not be arranged alternately in the circumferential direction. Furthermore, the number of the first cams 110a and the number of the second cams 110b may be different.

[0061] The first cam 110a is configured to rotate the outer ring 101 in the forward direction ( Figure 3 in the clockwise direction) or rotate the inner ring 105 in the reverse direction ( Figure 3 The outer ring 101 and the inner ring 105 rotate in the counterclockwise direction.

[0062] The second cam 110 b is configured to mesh with the outer ring 101 and the inner ring 105 when the outer ring 101 rotates in the reverse direction or the inner ring 105 rotates in the forward direction.

[0063] The urging unit 115 is composed of, for example, a belt spring.

[0064] The urging means 115 may be any elastic body capable of urging the first cam 110 a and the second cam 110 b to contact the outer ring 101 and the inner ring 105 , and for example, a plurality of leaf springs or torsion springs may be used.

[0065] like Figure 6A As shown, the outer ring spacer 120 comprises an axially extending cylindrical main body 121 and an outer flange 122 formed at the rear end of the main body 121, projecting radially outward along the entire circumference. Alternately arranged circumferentially on the main body 121 are first cam retaining portions 123, which receive and retain the head portion of the first cam 110a; and second cam retaining portions 125, which receive and retain the head portion of the second cam 110b.

[0066] The first cam holding portion 123 of the outer ring side spacer 120 is configured to have an opening width varying portion in which the opening width continuously varies in the axial direction.

[0067] Specifically, if Figure 6B As shown, the first cam holding portion 123 includes: a guide space portion 123a, which is configured to have a constant opening width in the axial direction; a first posture fixing space portion 123b, which is configured to have an opening width smaller than that of the guide space portion 123a and is connected to the axial front side ( Figure 6B and the second posture fixing space portion 123c, is configured to have an opening width smaller than the guide space portion 123a, and the axial rear side of the guide space portion 123a ( Figure 6B The left side is connected.

[0068] The first posture fixing space portion 123b is connected to the guide space portion 123a through the first opening width changing portion 124a, and the first opening width changing portion 124a is formed so that the opening width continuously increases as it moves toward the axial rear. The second posture fixing space portion 123c is connected to the guide space portion 123a through the second opening width changing portion 124b, and the second opening width changing portion 124b is formed so that the opening width continuously increases as it moves toward the axial front.

[0069] The first opening width varying portion 124a is formed by adjusting the meshing direction ( Figure 6B The opening edge of the side is formed to protrude inward, and the second opening width changing portion 124b is formed by adjusting the engagement release direction ( Figure 6B The opening edge on the side (center is the lower direction) is formed to protrude inward.

[0070] The second cam holding portion 125 of the outer ring side spacer 120 is rectangular and is configured so that its opening width is constant in the axial direction.

[0071] The outer ring side spacer 120 is provided so as to be movable in the axial direction between a first axial position and a second axial position independently of the rotational movement of the outer ring 101 and the inner ring 105. When located in the first axial position, the first cam 110a is maintained in an engaged standby position, and when located in the second axial position, the first cam 110a is maintained in an idle rotation position, tilted away from the inner ring 105. This allows the first cam 110a to be tilted directly to change its position while maintaining the position of the second cam 110b.

[0072] In addition, the first cam retaining portion 123 of the outer ring side spacer 120 is not composed of a simple rectangular opening portion, but is composed of an irregular opening window with a narrowed opening width at both axial ends. This makes it possible to release small engagements caused by manufacturing errors, etc. with a smaller thrust, and by appropriately changing the opening shape of the first cam retaining portion 123, more action modes and their switching can be achieved.

[0073] On the inner surface of the main body portion 121 on the outer ring side spacer 120, an inner surface groove portion 126 extending in the axial direction is formed between the first cam retaining portion 123 and the second cam retaining portion 125 adjacent to the first cam retaining portion 123 in the meshing direction of the first cam 110a.

[0074] The inner groove portion 126 includes a guide groove portion 127 extending linearly from the axial rear end edge of the main body portion 121 to the axial front end edge, and a sliding groove portion 128 connected to the axial rear end portion of the guide groove portion 127. The sliding groove portion 128 is formed to extend circumferentially in the direction of engagement with the first cam 110a and is configured to allow circumferential movement of the outer protrusion 145 of the position regulating spacer 140, which will be described later, when the outer ring side spacer 120 is in a position where the first cam 110a is in an engagement standby position.

[0075] like Figure 7A As shown, the inner ring side spacer 130 has: a cylindrical main body portion 131 extending in the axial direction; and an inner flange portion 132 formed on the axial rear end portion of the main body portion 131 to protrude radially inward over the entire circumference.

[0076] The main body 13 is provided with a first cam holding portion 133 accommodating the foot portion of the first cam 110a and holding the first cam 110a and a second cam holding portion 134 accommodating the foot portion of the second cam 110b and holding the second cam 110b in an alternating arrangement in the circumferential direction.

[0077] like Figure 7B As shown, the first cam holding portion 133 of the inner race side spacer 130 is rectangular and is configured so that the opening width is constant in the axial direction.

[0078] The second cam holding portion 134 of the inner race side spacer 130 is configured to have an opening width varying portion in which the opening width continuously varies in the axial direction.

[0079] Specifically, the second cam holding portion 134 includes: a guide space portion 134a, which is configured to have a constant opening width in the axial direction; a first posture fixing space portion 134b, which is configured to have an opening width smaller than that of the guide space portion 134a and is connected to the axial front side ( Figure 7B and the second posture fixing space portion 134c, is configured to have an opening width smaller than the guide space portion 134a, and the axial rear side of the guide space portion 134a ( Figure 7B The left side is connected.

[0080] The first posture fixing space portion 134b is connected to the guide space portion 134a through the first opening width changing portion 135a, and the first opening width changing portion 135a is formed so that the opening width continuously increases as it moves toward the axial rear. The second posture fixing space portion 134c is connected to the guide space portion 134a through the second opening width changing portion 135b, and the second opening width changing portion 135b is formed so that the opening width continuously increases as it moves toward the axial front.

[0081] The first opening width varying portion 135a is formed by adjusting the meshing direction ( Figure 7B The opening edge of the side is formed to protrude inward, and the second opening width changing portion 135b is formed by adjusting the engagement release direction ( Figure 7B The opening edge on the side (center is the upper direction) is formed to protrude inward.

[0082] The inner ring side spacer 130 is provided so as to be movable in the axial direction between a first axial position and a second axial position independently of the rotational movement of the outer ring 101 and the inner ring 105. When located in the first axial position, the second cam 110b is maintained in an engaged standby position, and when located in the second axial position, the second cam 110b is maintained in an idle rotation position, tilted away from the inner ring 105. This allows the second cam 110b to be tilted directly to change its position while maintaining the position of the first cam 110a.

[0083] In addition, the second cam retaining portion 134 of the inner ring side spacer 130 is not a simple rectangular opening portion, but is composed of a special-shaped opening window with a narrowed opening width at both axial ends. This makes it possible to release small engagements caused by manufacturing errors, etc. with a smaller thrust. At the same time, by appropriately changing the opening shape of the second cam retaining portion 134, more action modes and their switching can be achieved.

[0084] On the outer surface of the main body portion 131 on the inner ring side spacer 130, an outer groove portion 136 extending in the axial direction is formed between the second cam retaining portion 134 and the first cam retaining portion 133 adjacent to the second cam retaining portion 134 in the disengagement direction of the second cam 110b.

[0085] The outer groove portion 136 includes a guide groove portion 137 extending linearly from the axial front end edge to the axial rear end edge of the main body portion 131, and a sliding groove portion 138 connected to the axial front end portion of the guide groove portion 137. The sliding groove portion 138 is formed to extend circumferentially in the direction of engagement with the second cam 110b, and is configured to allow circumferential movement of the inward protrusion 146 of the position regulating spacer 140, which will be described later, when the inner race side spacer 130 is in a position where the second cam 110b is in an engagement standby position.

[0086] Furthermore, as described above, the selectable clutch 100 of this embodiment is configured to include the position limiting spacer 140 for limiting the degree of freedom of circumferential movement of the outer and inner spacers 120, 130. This allows the degree of freedom of circumferential movement of the outer and inner spacers 120, 130 relative to the position limiting spacer 140 to be adjusted to an appropriate degree of freedom corresponding to each operating mode, thereby maintaining the first and second cams 110a, 110b in their appropriate postures.

[0087] like Figure 8A and Figure 8BAs shown, the position limiting spacer 140 is composed of a pair of annular portions 141 arranged side by side in the axial direction and a plurality of connecting portions 142 that connect the annular portions 141 in the axial direction at predetermined intervals. Notches 143 capable of accommodating each of the first cam 110a and the second cam 110b are formed in the spaces between adjacent connecting portions 142. The notches 143 are arranged at equal intervals along the circumferential direction.

[0088] The position limiting spacer ring 140 includes: an outer protrusion 145, which is arranged on the axial front end portion in a manner protruding radially outward and is slidably engaged with the inner surface groove portion 126 of the outer ring side spacer ring 120; and an inner protrusion 146, which is arranged on the axial rear end portion in a manner protruding radially inward and is slidably engaged with the outer surface groove portion 136 of the inner ring side spacer ring 130.

[0089] The switching mechanism 150 includes a cylindrical cam 151 , a first driven joint 160 and a second driven joint 170 coupled to the cylindrical cam 151 , and a housing 180 for accommodating the first driven joint 160 and the second driven joint 170 .

[0090] Also like Figure 9 As shown, the cylindrical cam 151 in this embodiment has a cam groove 155 formed on the circumferential surface of the cylindrical component, and has: a cylindrical shaft portion 152; and an outer flange portion 153, which is formed on the axial rear end portion of the shaft portion 152 in a manner extending radially outward along the entire circumference, and is used to appropriately transmit power from the drive source.

[0091] like Figure 5 As shown, with the shaft 152 inserted between the outer race side spacer 120 and the inner race side spacer 130, the cylindrical cam 151 is positioned on the rotation axis C1, thereby achieving radial miniaturization of the selectable clutch 100. Furthermore, because power is transmitted coaxially, bending moment is virtually eliminated, thus avoiding performance degradation due to deformation. Furthermore, the use of a single shaft reduces the number of parts, minimizing the risk of failure and the need for maintenance.

[0092] The cam groove 155 has: a first driven joint guide area L1, including an inclined portion that engages with the first follower 165 of the first driven joint 160 to move the first driven joint 160 in the axial direction; and a second driven joint guide area L2, including an inclined portion that engages with the second follower 175 of the second driven joint 170 to move the second driven joint 170 in the axial direction.

[0093] The first driven joint guide area L1 and the second driven joint guide area L2 are arranged on the same circumference of the cylindrical cam 151 at positions opposing each other with the rotation axis C1 interposed therebetween, thereby also achieving miniaturization of the axial structure of the selective clutch 100 .

[0094] The first driven joint guide area L1 has: a first straight portion 156a, which is formed on the axial front side so as to extend in the circumferential direction; a first inclined portion 156b, which is formed so as to extend obliquely toward the axial rear side and is connected to the first straight portion 156a; and a second straight portion 156c, which is formed on the axial rear side so as to extend in the circumferential direction and is connected to the first inclined portion 156b.

[0095] The second driven joint guide area L2 has: a first straight portion 157a, which is formed on the axial front side so as to extend in the circumferential direction; a first inclined portion 157b, which is formed so as to extend obliquely toward the axial rear side and is connected to the first straight portion 157a; a second straight portion 157c, which is formed on the axial rear side so as to extend in the circumferential direction and is connected to the first inclined portion 157b; a second inclined portion 157d, which is formed so as to extend obliquely toward the axial front side and is connected to the second straight portion 157c; and a third straight portion 157e, which is formed on the axial front side so as to extend in the circumferential direction and is connected to the second inclined portion 157d.

[0096] like Figure 10 As shown, the first driven joint 160 is an annular body including an annular base portion 161 and a first follower 165 that engages with the cam groove 155 of the cylindrical cam 151 .

[0097] A recess 162 is formed on the front end face of the base portion 161, and the recess 162 is configured to accommodate the outer flange portion 122 of the outer ring side spacer 120. When the rear face of the outer flange portion 122 abuts against the bottom face of the recess 162, the outer ring side spacer 120 can be connected to the first driven joint 160 by embedding a C-shaped retaining ring 190 with a portion of the circular plate cut away into the inner circumferential surface of the circumferential wall portion 163 that divides the recess 162.

[0098] Furthermore, a plurality of external teeth 164 are formed on the outer peripheral surface of the base portion 161 so as to be arranged at predetermined intervals in the circumferential direction, and a follower insertion hole is formed that extends through the base portion 161 in the thickness direction.

[0099] The first follower 165 is inserted into the follower insertion hole so that the tip portion thereof protrudes radially inward from the inner peripheral surface of the base portion 161 .

[0100] like Figure 11 As shown, the second driven joint 170 is an annular body including an annular base portion 171 and a second follower 175 that engages with the cam groove 155 of the cylindrical cam 151 .

[0101] On the front end face of the base portion 171, a thin-walled cylindrical extension portion 172 is formed in such a way that its inner circumference is connected to the inner circumference of the base portion 171. When the rear face of the inner flange portion 132 on the inner ring side spacer 130 is in contact with the front end face of the base portion 171, the inner ring side spacer 130 can be connected to the second driven joint 170 by embedding a C-shaped retaining ring 191 with a part of the circular plate cut off on the outer circumference of the extension portion 172.

[0102] Furthermore, a plurality of internal teeth 173 are formed on the inner peripheral surface of the base portion 171 so as to be arranged at predetermined intervals in the circumferential direction, and a follower insertion hole is formed that penetrates and extends in the thickness direction of the base portion 171 .

[0103] The second follower 175 is inserted into the follower insertion hole so that its tip portion protrudes radially outward from the outer peripheral surface of the base portion 171 .

[0104] like Figure 12 As shown, the housing 180 is formed in a double cylindrical shape with a closed rear end, and has a rotation stopper that prohibits the housing 180 from rotating together with the cylindrical cams 151 of the first driven joint 160 and the second driven joint 170 .

[0105] The anti-rotation portion is composed of internal teeth 182 formed on the inner circumference of the outer cylindrical portion 181 of the housing 180 and external teeth 186 formed on the outer circumference of the inner cylindrical portion 185. Internal teeth 182 are spline-engaged with external teeth 164 of the first driven joint 160, while external teeth 186 are spline-engaged with internal teeth 173 of the second driven joint 170. This prevents the first and second driven joints 160 and 170 from rotating in response to the rotation of the cylindrical cam 151. Therefore, by guiding the first and second driven joints 165 and 175 along the inclined portion of the cam groove 155, the first and second driven joints 160 and 170 can be reliably moved in the axial direction to switch the operating mode of the selectable clutch 100. Although the anti-rotation portion in this embodiment is configured such that the first driven joint 160 and the second driven joint 170 are spline-coupled to the housing 180 , the first driven joint 160 and the second driven joint 170 may be coupled to the housing 180 by key coupling or other methods.

[0106] The outer cylinder portion 181 is formed with a cutout portion 187 that exposes a portion of the outer flange portion 153 of the cylindrical cam 151 to the outside, thereby enabling the power from the driving source to be appropriately transmitted to the cylindrical cam 15 .

[0107] On the switching mechanism 150, as shown in FIG. Figure 13 As shown, when the outer ring side spacer 120 and the inner ring side spacer 130 are both located at the first axial position P1 (refer to Figure 2), the first follower 165 of the first driven joint 160 and the second follower 175 of the second driven joint 170 are respectively located on the second straight portion 156c of the first driven joint guide area L1 and the second straight portion 157c of the second driven joint guide area L2 ( Figure 13 Area A in the ). Figure 13 The broken line shown by the solid line represents the relationship between the circumferential phase of the first follower 165 relative to the cam groove 155 and the axial position of the outer ring side spacer 120, and the broken line shown by the dotted line represents the relationship between the circumferential phase of the second follower 175 relative to the cam groove 155 and the axial position of the inner ring side spacer 130.

[0108] At this moment, if Figure 14 As shown, the first cam 110a maintains an idle position tilted so that the inner ring-side engaging surface is separated from the inner ring raceway surface 106, while the second cam 110b maintains an engagement standby position in contact with the outer ring 101 and the inner ring 105. This allows the second cam 110b to immediately engage with the outer ring 101 and the inner ring 105 upon application of torque to the outer ring 101 or the inner ring 105. Consequently, the selective clutch 100 is in the reverse direction lock mode (Mode A1) that prohibits relative rotation of the inner ring 105 with respect to the outer ring 101 in the reverse direction.

[0109] When the cylindrical cam 151 is rotated in the forward direction, the first follower 165 is guided along the second straight portion 156c of the first follower joint guide area L1, and the outer ring side spacer 120 is maintained at the first axial position P1 ( Figure 13 On the other hand, the second follower 175 is guided along the first inclined portion 157b of the second follower joint guide area L2, and the second follower joint 170 and the inner ring side spacer 130 connected thereto move axially forward ( Figure 13 Then, the second follower 175 is guided along the first straight portion 157a, thereby Figure 15A As shown, the inner ring side spacer 130 is located at the second axial position P2 ( Figure 13 Area C in the

[0110] At this moment, if Figure 15B As shown, the second opening width variable portion 135b on the second cam holding portion 134 of the inner race side spacer 130 presses the foot portion of the second cam 110b, causing the second cam 110b to tilt in the disengagement direction. Since the first cam holding portion 133 of the inner race side spacer 130 is formed into a rectangular shape with a constant opening width in the axial direction, the first cam 110a maintains an idle position.

[0111] Thus, the operation mode of the selectable clutch 100 is switched from the reverse direction locking mode (Mode A1) to the bidirectional freewheeling mode (Mode A2) that allows relative rotation of the outer ring 101 and the inner ring 105 in both the forward and reverse directions.

[0112] Furthermore, when the cylindrical cam 151 is rotated in the reverse direction, the first follower 165 is guided along the first inclined portion 156b of the first follower joint guide region L1, and the first follower joint 160 and the outer ring side spacer ring 120 connected thereto move axially forward ( Figure 13 Then, the first follower 165 is guided along the first straight portion 156a, thereby Figure 16A As shown, the outer ring side spacer 120 is located at the second axial position P2 ( Figure 13 On the other hand, the second follower 175 is guided along the second straight portion 157c of the second follower joint guide region L2, maintaining the inner ring side spacer 130 at the first axial position P1 ( Figure 13 Area D and Area E).

[0113] At this moment, if Figure 16B As shown, the second opening width variable portion 124b on the first cam retaining portion 123 of the outer race side spacer 120 presses the head portion of the first cam 110a, causing the first cam 110a to tilt toward the meshing direction. Since the second cam retaining portion 125 on the outer race side spacer 120 is formed into a rectangular shape with a constant opening width in the axial direction, the second cam 110b maintains its meshing standby position.

[0114] As a result, the operation mode of the selectable clutch 100 is switched from the reverse direction locking mode (Mode A1) to the bidirectional locking mode (Mode A3) which prohibits relative rotation of the outer ring 101 and the inner ring 105 in both the forward and reverse directions.

[0115] When the cylindrical cam 151 is rotated in the reverse direction, the first follower 165 is guided along the first straight portion 156a of the first driven joint guide area L1, and the outer ring side spacer 120 is maintained in the second axial position P2 (area F and area G in Figure 13). On the other hand, the second follower 175 is guided along the second inclined portion 157d of the second driven joint guide area L2, and the second driven joint 170 and the inner ring side spacer 130 connected thereto move toward the axial front ( Figure 13 Then, the second follower 175 is guided along the third straight portion 157e, thereby Figure 17A As shown, the inner ring side spacer 130 is located at the second axial position P2 ( Figure 13 region G in the .

[0116] At this moment, if Figure 17B As shown, the second opening width varying portion 135b on the second cam retaining portion 134 of the inner race side spacer 130 presses the foot portion of the second cam 110b, causing the second cam 110b to tilt in the disengagement direction. Since the first cam retaining portion 133 of the inner race side spacer 130 is formed into a rectangular shape with a constant opening width in the axial direction, the first cam 110a is maintained in the engaged standby position.

[0117] As a result, the operation mode of the selectable clutch 100 is switched from the bidirectional locking mode (Mode A3) to the forward rotation locking mode (Mode A4) that prohibits the inner race 105 from rotating relative to the outer race 101 in the forward direction.

[0118] Moreover, according to the above-mentioned selectable clutch 100, since the cam groove 155 formed on the cylindrical cam 151 has: a first driven joint guide area L1, including a first inclined portion 156b that causes the first driven joint 160 to move in the axial direction; and a second driven joint guide area L2, including a first inclined portion 157b and a second inclined portion 157d that causes the second driven joint 170 to move in the axial direction, and the area on one side of the first driven joint guide area L1 and the second driven joint guide area L2 includes an inclined portion that is staggered in phase with the inclined portion of the other area in the circumferential direction, the first driven joint 160 and the second driven joint 170 can each move in the axial direction independently. Therefore, by providing the first cam 110a's posture control function to the outer spacer ring 120 connected to the first driven joint 160, and providing the second cam 110b's posture control function to the inner spacer ring 130 connected to the second driven joint 170, the cam 110 can be tilted and the changed posture of the cam 110 can be maintained simply by axially moving one or both of the outer spacer ring 120 and the inner spacer ring 130. This allows for smooth switching of operating modes with a simple configuration, and allows for switching of operating modes according to usage conditions, resulting in enhanced functionality.

[0119] Although the selective clutch configured to switch between four operating modes has been described above, it may also be configured to switch between three operating modes, for example, a bidirectional locking mode, a bidirectional freewheeling mode, and a forward locking mode or a reverse locking mode.

[0120] For example, Figure 18As shown, the cylindrical cam 151 constituting the switching mechanism in the selective clutch of this construction is constructed so that the first driven section guide area L1 in the cam groove 155 has: a first straight portion 156a, formed on the axial front side portion in a manner extending in the circumferential direction; a first inclined portion 156b, formed in a manner extending obliquely toward the axial rear side and connected to the first straight portion 156a; and a second straight portion 156c, formed on the axial rear side portion in a manner extending in the circumferential direction and connected to the first inclined portion 156b.

[0121] In addition, the second driven joint guide area L2 in the cam groove 155 is constructed to have: a first straight portion 157a, which is formed on the axial front side portion in a manner extending in the circumferential direction; a first inclined portion 157b, which is formed in a manner extending obliquely toward the axial rear side and is connected to the first straight portion 157a; and a second straight portion 157c, which is formed on the axial rear side portion in a manner extending in the circumferential direction and is connected to the first inclined portion 157b.

[0122] The first inclined portion 156 b in the first driven joint guide region L1 and the first inclined portion 157 b in the second driven joint guide region L2 are formed so as to be shifted in phase in the circumferential direction from each other.

[0123] In the switching mechanism with such a cylindrical cam 151, Figure 19 As shown, when the outer ring side spacer 120 and the inner ring side spacer 130 are simultaneously located at the first axial position P1, the first follower 165 of the first driven joint 160 and the second follower 175 of the second driven joint 170 are respectively located on the second straight portion 156c of the first driven joint guide area L1 and the second straight portion 157c of the second driven joint guide area L2 ( Figure 19 At this time, the first cam 110a is held in an idle position, and the second cam 110b is held in an engaged standby position. Therefore, the operation mode of the selective clutch 100 is a reverse direction locking mode (Mode A1) that prohibits relative rotation of the inner race 120 with respect to the outer race 110 in the reverse direction.

[0124] When the cylindrical cam 151 is rotated in the forward direction, the first follower 165 is guided along the second straight portion 156c of the first follower joint guide area L1, and the outer ring side spacer 130 is maintained at the first axial position P1 ( Figure 19 On the other hand, the second follower 175 is guided along the first inclined portion 157b of the second follower joint guide area L2, and the second follower joint 170 and the inner ring side spacer 130 connected thereto move axially forward ( Figure 19Then, the second follower 175 is guided along the first straight portion 157a, whereby the inner ring side spacer 130 is located at the second axial position P2 ( Figure 13 As a result, the first cam 110a is maintained in the idle position, and the second cam 110b tilts from the engaged standby position to the idle position. Consequently, the operation mode of the selectable clutch 100 is switched from the reverse direction locking mode (Mode A1) to the bidirectional idle mode (Mode A2) that allows relative rotation of the outer ring 101 and the inner ring 105 in both the forward and reverse directions.

[0125] Furthermore, when the cylindrical cam 151 is rotated in the reverse direction, the first follower 165 is guided along the first inclined portion 156b of the first follower joint guide region L1, and the first follower joint 160 and the outer ring side spacer ring 120 connected thereto move axially forward ( Figure 19 Then, the first follower 165 is guided along the first straight portion 156a, whereby the outer ring side spacer 120 is located at the second axial position P2 ( Figure 19 On the other hand, the second follower 175 is guided along the second straight portion 157c of the second follower joint guide region L2, and the inner ring side spacer 130 maintains the state of being located at the first axial position P1 ( Figure 19 As a result, the first cam 110a tilts from the idle position to the engaged standby position, while the second cam 110b maintains the engaged standby position. Consequently, the operation mode of the selectable clutch 100 switches from the reverse direction locking mode (Mode A1) to the bidirectional locking mode (Mode A3) that prohibits relative rotation of the outer ring 101 and the inner ring 105 in both the forward and reverse directions.

[0126] (Second embodiment)

[0127] Figure 20 1 is a perspective view showing a configuration example of a selectable clutch according to a second embodiment of the present invention. Figure 21 yes Figure 20 An exploded perspective view of the selectable clutch is shown.

[0128] The selectable clutch 200 according to the second embodiment has substantially the same structure as the selectable clutch 100 according to the first embodiment, except for the different structure of the switching mechanism. For convenience, the same symbols are given to the same components as those of the selectable clutch 100 according to the first embodiment, and the description is omitted.

[0129] Also like Figure 22As shown, the main body 221 of the outer race side spacer 220 in this embodiment is formed to have a larger axial dimension than the main body 121 of the outer race side spacer 120 in the selectable clutch 100 according to the first embodiment. The first cam retaining portion 123, the second cam retaining portion 125, and the inner surface groove portion 126 are formed in the axially forward portion of the main body 221, and the first driven joint mounting portion is formed in the axially rearward end portion of the main body 221.

[0130] The first driven joint mounting portion is formed by forming a groove 222 a extending over the entire circumference in the circumferential direction on the outer peripheral surface of the outer flange portion 222 provided at the rear end portion of the main body portion 221 .

[0131] Also like Figure 23 As shown, the inner ring side spacer 230 in this embodiment is formed with a first cam retaining portion 133, a second cam retaining portion 134 and an outer groove portion 136 on the axial front side portion of the main body portion 231, and a second driven joint mounting portion is formed on the axial rear end portion.

[0132] The second driven joint mounting portion is formed by forming a groove 239 a extending over the entire circumference on the outer peripheral surface of the outer flange portion 239 provided at the rear end portion of the main body portion 231 .

[0133] The axial dimension of the main body portion 231 is formed to be larger than the main body portion 221 of the outer ring side spacer 220, so that in the assembled state, the rear end side portion protrudes rearward from the rear end surface of the outer ring side spacer 220, and thus, the second driven joint mounting portion on the inner ring side spacer 230 is separated from the first driven joint mounting portion on the outer ring side spacer 220 and is located on the axial rear side.

[0134] The first driven joint 260 and the second driven joint 270 in the switching mechanism 250 of the present embodiment have the same configuration, and therefore the description of the configuration of the second driven joint 270 will be omitted.

[0135] Also like Figure 24 As shown, the first driven joint 260 includes an engaging portion 266 and a bearing portion 268 .

[0136] The engaging portion 266 is formed in a C-shape with a portion of a circular ring cut away, and has a pair of arms 267. The arms 267 are elastically deformed to expand, thereby engaging with the first driven joint mounting portion of the outer ring spacer 220. The engaging portion of the second driven joint 270 is configured to engage with the second driven joint mounting portion of the inner ring spacer 230.

[0137] The bearing portion 268 is formed continuously with the engaging portion 266, extending radially outward relative to the center of the engaging portion 266. It includes a cylindrical cam through-hole 269 configured to rotatably allow the cylindrical cam 251 to pass through. A follower insertion hole is formed in the bearing portion 268, opening into the inner circumference of the cylindrical cam through-hole 269. A rod-shaped first follower 265 is positioned in the follower insertion hole with its tip protruding inward from the inner circumference of the cylindrical cam through-hole 269. A rod-shaped second follower 275 is positioned in the second follower joint 270 with its tip protruding inward from the inner circumference of the cylindrical cam through-hole.

[0138] The cylindrical cam 251 in the switching mechanism 250 of this embodiment has a cam groove 255 formed on the peripheral surface of a cylindrical member. Figure 20 As shown, the cylindrical cam 251 is passed through the cylindrical cam through hole 269 of the first driven section 260 connected to the outer ring side spacer 220 and the cylindrical cam through hole of the second driven section 270 connected to the inner ring side spacer 230, and is combined with the first driven section 260 and the second driven section 270 by the engagement of the first follower 265 of the first driven section 260 and the second follower 275 of the second driven section 270 with the cam groove 255, and is configured to be able to rotate forward and reverse around the rotating drive axis C2 extending parallel to the rotation axis C1.

[0139] Also like Figure 25 As shown, the cam groove 255 includes a first driven joint guide area L1 including an inclined portion that engages with the first follower 265 of the first driven joint 260 to cause the first driven joint 260 to move in the axial direction; and a second driven joint guide area L2 including an inclined portion that engages with the second follower 275 of the second driven joint 270 to cause the second driven joint 270 to move in the axial direction. In this embodiment, the second driven joint guide area L2 is formed at a position spaced axially rearward relative to the first driven joint guide area L1.

[0140] The first driven joint guide area L1 has: a first straight portion 256a, which is formed in a manner extending in the circumferential direction; a first inclined portion 256b, which is formed in a manner extending obliquely toward the axial front side and is connected to the first straight portion 256a; and a second straight portion 256c, which is formed in a manner extending in the circumferential direction and is connected to the first inclined portion 256b.

[0141] The second driven joint guide area L2 has: a first straight portion 257a, which is formed in a manner extending in the circumferential direction; a first inclined portion 257b, which is formed in a manner extending obliquely toward the axial front side and is connected to the first straight portion 257a; a second straight portion 257c, which is formed in a manner extending in the circumferential direction and is connected to the first inclined portion 257b; a second inclined portion 257d, which is formed in a manner extending obliquely toward the axial rear side and is connected to the second straight portion 257c; and a third straight portion 257e, which is formed on the axial rear side so as to extend in the circumferential direction and is connected to the second inclined portion 257d.

[0142] In the cam groove 255, the first inclined portion 256b in the first driven joint guide area L1 and the first inclined portion 257b and the second inclined portion 257d in the second driven joint guide area L2 are formed by staggering the circumferential phases of each other, thereby enabling the first driven joint 260 and the second driven joint 270 to move independently in the axial direction.

[0143] In the switching mechanism 250, as Figure 26 As shown, when the outer ring side spacer 220 and the inner ring side spacer 230 are both located at the first axial position P1 (refer to Figure 20 ), the first follower 265 of the first driven joint 260 and the second follower 275 of the second driven joint 270 are respectively located on the first straight portion 256a of the first driven joint guide area L1 and the first straight portion 257a of the second driven joint guide area L2 ( Figure 26 Area A in the ). Figure 26 The broken line shown by the solid line represents the relationship between the circumferential phase of the first follower 265 relative to the cam groove 255 and the axial position of the outer ring side spacer 220, and the broken line shown by the dotted line represents the relationship between the circumferential phase of the second follower 275 relative to the cam groove 255 and the axial position of the inner ring side spacer 230.

[0144] At this point, the first cam 110a maintains an idle rotation posture, tilted so that the inner ring-side engagement surface is separated from the inner ring raceway surface 106, while the second cam 110b maintains an engagement standby state, in contact with the outer ring 101 and the inner ring 105. This allows the application of torque to the outer ring 101 or the inner ring 105 to immediately initiate engagement of the second cam 110b with the outer ring 101 and the inner ring 105. Consequently, the selective clutch 200 is in reverse direction lock mode (Mode B1), which prohibits reverse rotation of the inner ring 105 relative to the outer ring 101.

[0145] When the cylindrical cam 251 is rotated in the clockwise direction (positive direction) as viewed from the axial front side, the first follower 265 is guided along the first straight portion 256a of the first follower joint guide area L1, and the outer ring side spacer 220 maintains the state of being located at the first axial position P1 ( Figure 26 On the other hand, the second follower 275 is guided along the first inclined portion 257b of the second follower joint guide area L2, and the second follower joint 270 and the inner ring side spacer 230 connected thereto move axially forward ( Figure 26 Then, the second follower 275 is guided along the second straight portion 257c, whereby the inner ring side spacer 220 becomes located at the second axial position P2 ( Figure 26 Area C in the

[0146] At this point, the second opening width varying portion 135b on the second cam retaining portion 134 of the inner race side spacer 230 presses the foot portion of the second cam 110b, causing the second cam 110b to tilt in the disengagement direction and shift to an idle position. Because the first cam retaining portion 133 of the inner race side spacer 230 is formed into a rectangular shape with a constant opening width in the axial direction, the first cam 110a maintains an idle position.

[0147] Therefore, the operation mode of the selectable clutch 200 is switched from the reverse direction locking mode (Mode B1) to the bidirectional freewheeling mode (Mode B2) that allows relative rotation of the outer ring 101 and the inner ring 105 in both the forward and reverse directions.

[0148] When the cylindrical cam 251 is further rotated in the forward direction, the first follower 265 is guided along the first inclined portion 256b of the first follower section guide area L1, and the first follower section 260 and the outer ring side spacer ring 220 connected thereto move axially forward ( Figure 26 Then, the first follower 265 is guided along the second straight portion 256c, whereby the outer ring side spacer 220 becomes located at the second axial position P2 ( Figure 26 On the other hand, the second follower 275 is guided along the second straight portion 257c of the second follower joint guide region L2, and the inner ring side spacer 230 maintains the state of being located at the second axial position P2 ( Figure 26 Area D and Area E).

[0149] At this point, the second opening width variable portion 124b on the first cam retaining portion 123 of the outer race-side spacer 220 presses against the head portion of the first cam 110a, causing the first cam 110a to tilt in the meshing direction and shift to the meshing standby position. Since the second cam retaining portion 125 on the outer race-side spacer 220 is formed into a rectangular shape with a constant opening width in the axial direction, the second cam 110b remains in an idle position.

[0150] Therefore, the operation mode of the selectable clutch 200 is switched from the two-way freewheeling mode (Mode B2) to the forward rotation locking mode (Mode B3) that prohibits the relative rotation of the inner ring 105 with respect to the outer ring 101 in the forward rotation direction.

[0151] When the cylindrical cam 251 is further rotated in the forward direction, the first follower 265 is guided along the second straight portion 256c of the first follower joint guide area L1, and the outer ring side spacer 220 maintains the state of being located at the second axial position P2 ( Figure 26 On the other hand, the second follower 275 is guided along the second inclined portion 257d of the second follower joint guide area L2, and the second follower joint 270 and the inner ring side spacer 230 connected thereto move axially rearward ( Figure 26 Then, the second follower 275 is guided along the third straight portion 257e, whereby the inner ring side spacer 230 becomes located at the first axial position P1 ( Figure 26 region G in the .

[0152] At this point, the second opening width varying portion 135b of the second cam holding portion 134 of the inner race side spacer 230 presses the foot portion of the second cam 110b, causing the second cam 110b to tilt in the meshing direction and shift to the meshing standby position. Since the first cam holding portion 133 of the inner race side spacer 230 is formed into a rectangular shape with a constant opening width in the axial direction, the first cam 110a remains in the meshing position.

[0153] Therefore, the operation mode of the selectable clutch 200 is switched from the forward rotation lock mode (Mode B3) to the bidirectional lock mode (Mode B4) which prohibits relative rotation of the outer ring 101 and the inner ring 105 in both the forward and reverse directions.

[0154] The selectable clutch according to the second embodiment is not limited to being capable of switching between four operating modes, and may be capable of switching between three operating modes, for example, a bidirectional locking mode, a bidirectional freewheeling mode, and a forward locking mode or a reverse locking mode.

[0155] Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the scope of the present invention described in the claims.

[0156] While the above embodiment describes a configuration in which the selectable clutch operates in the reverse direction locking mode when the outer and inner spacers are in the first axial position, the relationship between the selectable clutch operation mode and the axial position of the outer and inner spacers is not particularly limited. For example, the selectable clutch operation mode may be in the forward direction locking mode, the bidirectional locking mode, or the reverse direction locking mode when the outer and inner spacers are in the first axial position.

Claims

1. A selectable clutch comprising: an outer ring-side spacer ring and an inner ring-side spacer ring disposed between an outer ring and an inner ring, which retain a first cam and a second cam having different meshing directions with respect to the outer ring and the inner ring; and a switching mechanism for changing an operating mode by forcibly tilting one or both of the first cam and the second cam, characterized in that: The outer ring side spacer ring and the inner ring side spacer ring are arranged to be movable in the axial direction between a first axial position and a second axial position. The outer ring side spacer is configured to change the posture of the first cam between an engagement standby posture and an idle posture by moving between the first axial position and the second axial position, wherein the idle posture is tilted away from the inner ring or the outer ring. The inner ring side spacer is configured to change the posture of the second cam between an engagement standby posture and an idle posture by moving between the first axial position and the second axial position, wherein the idle posture is tilted away from the inner ring or the outer ring. The switching mechanism includes a cylindrical cam having a cam groove formed on its circumferential surface and a first driven section and a second driven section coupled to the cylindrical cam, wherein the first driven section is connected to the outer ring side spacer, and the second driven section is connected to the inner ring side spacer. The cam groove has: a first driven joint guide area, including an inclined portion that causes the first driven joint to move in the axial direction; and a second driven joint guide area, including an inclined portion that causes the second driven joint to move in the axial direction, and the area on one side of the first driven joint guide area and the second driven joint guide area includes an inclined portion that is formed by shifting the circumferential phase with the inclined portion of the other area.

2. The selectable clutch according to claim 1, characterized in that: The cylindrical cam has the cam groove formed on the circumferential surface of the cylindrical member. The first driven joint is an annular body, and is provided with a first follower that engages with the cam groove in a manner protruding radially inward from the inner peripheral surface. The second driven joint is an annular body and is provided with a second follower that engages with the cam groove in a manner protruding radially outward from the outer peripheral surface. The cylindrical cam, the first driven joint, the second driven joint, the outer ring, and the inner ring are arranged coaxially.

3. The selectable clutch according to claim 1, characterized in that: The cylindrical cam is formed with the first driven joint guide area and the second driven joint guide area at positions separated in the axial direction on the peripheral surface of the cylindrical member. The cylindrical cam is arranged on a shaft extending parallel to the rotational axes of the inner ring and the outer ring.

4. The selectable clutch according to claim 2, characterized in that: The switching mechanism includes a housing for accommodating the cylindrical cam, the first driven joint, and the second driven joint. The housing includes a rotation-stopping portion that prevents the first driven joint and the second driven joint from rotating together with the cylindrical cam.

5. The selectable clutch according to claim 1, characterized in that: A position restricting ring is disposed between the outer ring side spacer and the inner ring side spacer to restrict the degree of freedom of circumferential movement of the outer ring side spacer and the inner ring side spacer.

6. The selectable clutch according to claim 5, characterized in that: The outer ring side spacer has an inner surface groove portion extending in the axial direction on the inner surface, The inner ring side spacer has an outer groove portion extending in the axial direction on the outer surface. The position limiting spacer ring has an outer protrusion on one axial end portion, the outer protrusion is arranged to protrude radially outward and is slidably engaged with the inner surface groove of the outer ring side spacer ring, and has an inner protrusion on the other axial end portion, the inner protrusion is arranged to protrude radially inward and is slidably engaged with the outer surface groove of the inner ring side spacer ring.

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