Selectable clutch and separation mechanism

Abstract

A selectable clutch (100) is configured in such a manner that a first clutch mechanism is provided with a power transmission element (130) that transmits or interrupts power in both rotational directions between an input-side rotational element (110) and an output-side rotational element (120), and that a selector (150) that opens and closes the first clutch mechanism is coupled to the input-side rotational element (110) and the output-side rotational element (120) while being coupled to the input-side rotational element (110) and the output-side rotational element (120). And an input-side rotation element (110) connected to the input-side rotation element (110) by means of an engagement mechanism having a circumferential play capable of relative rotation within a prescribed rotation angle range with respect to the input-side rotation element (110). The separation mechanism (180) is configured such that the output-side rotating element (120) is connected to the auxiliary drive wheel axle (172), and the selector (150) is connected to the motor shaft of the auxiliary drive motor (177).

Description

TECHNICAL FIELD

[0001] The present application relates to a selectable clutch suitable for use as a decoupling clutch, and a decoupling mechanism provided with the selectable clutch. BACKGROUND

[0002] As a decoupling clutch for transmitting or cutting off power from an input shaft side to an output shaft side, for example, a ratchet type engagement clutch is known which links the input shaft side and the output shaft side by mechanical engagement.

[0003] As such a clutch, for example, a configuration is known in which recessed plates and slotted plates each having flat clutch surfaces are arranged so as to be relatively rotatable in a state in which the clutch surfaces face each other, and struts are arranged in each of a plurality of housing recesses formed on the clutch surface of the recessed plate, and a plurality of slots (engagement recesses) are formed on the clutch surface of the slotted plate (for example, refer to Patent Document 1 and Patent Document 2, etc.).

[0004] In this ratchet type clutch, each strut is forced toward the slotted plate side by a spring provided in the housing recess, and is configured so that, when the slotted plate is relatively rotated in the engagement direction with respect to the recessed plate, a portion of the strut engages with the engagement recess to become a state in which power can be transmitted, and when the slotted plate is relatively rotated in the opposite direction with respect to the recessed plate, the engagement of the strut with the engagement recess is released to become a state in which power cannot be transmitted.

[0005] Further, between the recessed plate and the slotted plate, a selection plate which is relatively rotatable with respect to the recessed plate is arranged, and by relative rotation of the selection plate, the state in which power can be transmitted and the state in which power cannot be transmitted can be switched.

[0006] Further, for example, a configuration provided with a ratchet mechanism is known (for example, refer to Patent Document 3 to Patent Document 7, etc.), the ratchet mechanism being configured by torque transmission members, i.e., a plurality of pawl members (ratchets), which are rotatably provided on the inner circumferential portion of an outer ring, and a tooth portion which is provided on the outer circumferential portion of an inner ring and engages with the pawl members.

[0007] For example, in the ratchet type clutch described in Patent Document 3, a plurality of first pawl members are provided which are forced toward the radially inner side by a spring, and a plurality of second pawl members are provided which are forced toward the radially inner side by a spring and differ in the circumferential direction from the first pawl members, the first pawl members being able to rotate the other side of the inner ring while locking the rotation of one side of the inner ring, and the second pawl members being able to lock the rotation of the other side of the inner ring while rotating one side of the inner ring.

[0008] Further, a ring-shaped switching plate is disposed adjacent to the inner ring in the direction of the central axis of the inner ring and coaxially with the inner ring, and by rotating the switching plate, the combination of the engaged state and the disengaged state of the first claw member and the second claw member with respect to the teeth of the inner ring can be changed.

[0009] Patent Literature

[0010] Patent Literature 1: Japanese Patent Application Laid-Open (Kokai) No. 2002-506958

[0011] Patent Literature 2: Japanese Patent Application Laid-Open (Kokai) No. 2019-516930

[0012] Patent Literature 3: Japanese Patent Application Laid-Open (Kokai) No. 2021-156432

[0013] Patent Literature 4: Japanese Patent Application Laid-Open (Kokai) No. 2022-190947

[0014] Patent Literature 5: Japanese Patent Application Laid-Open (Kokai) No. 2022-038806

[0015] Patent Literature 6: Japanese Patent Application Laid-Open (Kokai) No. 2022-047794

[0016] Patent Literature 7: Japanese Patent Application Laid-Open (Kokai) No. 2022-165688 SUMMARY

[0017] Further, the clutch described in each of the above patent literatures requires a dedicated driver, a selection mechanism such as a worm mechanism, a shift fork, or a cylindrical cam that links the clutch and the driver.

[0018] Therefore, the number of parts increases, the number of machining sites and assembly man-hours also increase, there is a problem that the manufacturing cost increases, and since a space for mounting the clutch in addition to the selection mechanism and the driver is required, there is a problem that the unit becomes large.

[0019] Further, when the operation mode of the switching clutch is switched, in addition to the control of the driving motor, the operation control of the driver is required, and there is a problem that the control easily becomes complicated.

[0020] The present application is made in view of the above circumstances, and the technical problem to be solved is to provide a selector-type clutch that does not require adjustment of the selector, can switch the operation mode with a simple structure, is easy to assemble, and can be miniaturized and long-lived.

[0021] Further, another technical problem to be solved by the present application is to provide a separation mechanism that can be miniaturized and simplified, and can smoothly and quickly switch the running state of a four-wheel drive vehicle.

[0022] The present application is a selectable clutch provided with a first clutch mechanism provided with an input-side rotary element, an output-side rotary element, and a power transmission element that transmits or cuts off power in both rotary directions between the input-side rotary element and the output-side rotary element, and a selector that performs opening and closing actions of the first clutch mechanism, which can solve the problem by the selector being linked to the input-side rotary element by a fitting mechanism while being linked to an input shaft element of an input torque, the fitting mechanism having a circumferential play that can relatively rotate within a prescribed rotary angle range with respect to the input-side rotary element.

[0023] According to the present application related to the technical solution 1, the switching of the action mode of the selectable clutch can be performed only by the control of the magnitude and the rotary direction of the torque of the selector. Therefore, the driver, the transmission, the controller, the selection mechanism, and the like for driving the selector are not needed, and the adjustment work and the like of the selector mechanism are not needed, so that the reduction of the number of parts, the simplification and the miniaturization of the structure can be achieved, and the assembly can be facilitated and the reduction of the manufacturing cost can be achieved by the reduction of the machining sites and the reduction of the assembly man-hours. In addition, since the structure itself is simple and the switching control of the action mode is also simple, the generation of the failure and the inconvenience can be suppressed, and a selectable clutch that is maintenance-free and long-lived can be provided.

[0024] According to the present application related to the technical solution 2, the action mode of the selectable clutch can be switched to the one-way locking mode in which the transmission or the cut-off of the power can be performed by the second clutch mechanism by the first clutch mechanism being brought into the open state in which the transmission of the power in both rotary directions is cut off by the selector.

[0025] According to the present application related to the technical solution 3, the switching of the action mode of the selectable clutch can be practically performed only by the control of the magnitude and the rotary direction of the torque of the selector.

[0026] According to the present application related to the technical solution 4, since the rotary play can be generated by the gap between the fitting teeth of the outer ring and the fitting teeth of the selector, the switching of the action mode of the selectable clutch can be performed with a simple structure.

[0027] According to the application related to the present technical solution 5, since the first clutch mechanism is composed of a roller-ratchet type bidirectional clutch, torque transmission between the inner ring and the outer ring can be performed by sandwiching the roller in the circumferential direction with the notch portion and the support groove portion. Therefore, no torsion (elastic deformation) occurs during torque transmission, and the selectable clutch can be configured to have high rigidity. In addition, stable engagement can be achieved with a simple structure, miniaturization can be achieved, and more rollers can be arranged in a smaller space, thereby enabling high torque transmission. In addition, since the surface pressure acting on the roller and the wall surface portion sandwiching the roller can be reduced during torque transmission, the design can be performed using a cheap material resistant to impact breakage or wear, and since the roller itself rotates, engagement at the same position is less likely to occur, thereby improving durability and enabling long service life.

[0028] According to the application related to the present technical solution 6, since the second clutch mechanism is composed of a cam type one-way clutch, engagement and idling can be automatically switched according to the rotational speed of each of the outer ring and the inner ring, thereby ensuring high responsiveness and expected torque capacity.

[0029] According to the application related to the present technical solution 7, by controlling the rotation speed and the rotation direction of the auxiliary drive motor to switch the operation mode of the selectable clutch, the transmission or interruption of the power from the auxiliary drive motor to the auxiliary drive wheels can be switched during either of the forward travel and the reverse travel of the four-wheel drive vehicle, and the structure can be simplified and miniaturized. In addition, since the selectable clutch is configured to automatically switch engagement and idling according to the rotational speed of each of the outer ring and the inner ring, the switching of the travel state of the four-wheel drive vehicle can be smoothly and quickly performed. BRIEF DESCRIPTION OF DRAWINGS

[0030] Figure 1 is an exploded perspective view showing the configuration of the selectable clutch according to the embodiment of the present application.

[0031] Figure 2 is a partial cross-sectional perspective view showing the state of the selectable clutch shown in Figure 1 is a partial cross-sectional perspective view showing the state of the selectable clutch shown in

[0032] Figure 3 is a cross-sectional view taken from the other end side in the axial direction when a plane perpendicular to the rotation axis is cut when the operation mode of the selectable clutch is the bidirectional locking mode.

[0033] Figure 4 is a cross-sectional view taken from the other end side in the axial direction when a plane perpendicular to the rotation axis is cut when the operation mode of the selectable clutch is the bidirectional locking mode. Figure 3Fig. 6 is a sectional view taken along the axis of rotation of the selector of the selectable clutch shown in Fig. 1.

[0034] Figure 5 Fig. 7 is a sectional view taken along the axis of rotation of the selectable clutch shown in Fig. 1, when the selectable clutch is in the one-way lock mode.

[0035] Figure 6 Fig. 8 is a sectional view taken along the axis of rotation of the selectable clutch shown in Fig. 1, when the selectable clutch is in the one-way lock mode. Figure 1 Fig. 9 is a sectional view taken along the axis of rotation of the second clutch mechanism of the selectable clutch shown in Fig. 1.

[0036] Figure 7 Fig. 10 is a sectional view taken along the axis of rotation of the second clutch mechanism of the selectable clutch shown in Fig. 1. Figure 1 Fig. 11 is a plan view of the selector of the selectable clutch shown in Fig. 1.

[0037] Figure 8 Fig. 12 is a partial sectional perspective view of the first clutch mechanism of the selectable clutch shown in Fig. 1, when the selectable clutch is in the one-way lock mode.

[0038] Figure 9 Fig. 13 is a sectional view taken along the axis of rotation of the first clutch mechanism of the selectable clutch shown in Fig. 1, when the selectable clutch is in the one-way lock mode.

[0039] Figure 10 Fig. 14 is a sectional view taken along the axis of rotation of the first clutch mechanism of the selectable clutch shown in Fig. 1, when the selectable clutch is in the one-way lock mode. Figure 9 Fig. 15 is a sectional view taken along the axis of rotation of the first clutch mechanism of the selectable clutch shown in Fig. 1, when the selectable clutch is in the one-way lock mode.

[0040] Figure 11 Fig. 16 is a sectional view taken along the axis of rotation of the selectable clutch shown in Fig. 1, when the selectable clutch is in the one-way lock mode.

[0041] Figure 12 Fig. 17 is a mode diagram showing an application example of the separation mechanism according to the present application.

[0042] Figure 13 Fig. 18 is a diagram showing the relationship between the running state of a four-wheel drive vehicle and the rotational speed of an auxiliary drive wheel axle and the rotational speed of a motor shaft of an auxiliary drive motor.

[0043] Explanation of symbols

[0044] 100 - Selectable clutch; 110 - Outer ring (input side rotating element); 111 - 1st cylindrical portion; 112 - Tooth; 113 - Notch portion; 115 - 2nd cylindrical portion; 116 - Track surface; 120 - Inner ring (output side rotating element); 121 - Large diameter cylindrical portion; 122 - Support groove portion; 125 - Small diameter cylindrical portion; 126 - Track surface; 127 - Peripheral groove; 128 - Shaft portion; 130 - Roller; 131 - Elastic member mounting groove; 135 - Elastic member; 140 - Cam clutch unit; 141 - Partition ring; 142 - Cam; 143 - Concentric holding member (roller); 144 - Force applying member; 150 - Selector; 151 - Peripheral wall portion; 152 - Tooth (engaging mechanism); 153 - End wall portion; 154 - Shaft portion; 155 - Control plate portion; 156 - Tooth portion; 157 - Roller holding portion; 158 - Roller holding groove; 159 - Cam surface; 160 - Retainer; 170 - Drive wheel; 171 - Auxiliary drive wheel; 172 - Auxiliary drive wheel axle; 175 - Battery; 176 - Main drive motor; 177 - Auxiliary drive motor; 180 - Disengaging mechanism; C - Rotational axis. DETAILED DESCRIPTION

[0045] Hereinafter, a selectable clutch according to one embodiment of the present application will be described based on the drawings.

[0046] As shown in Figures 1 to 6 , the selectable clutch 100 according to the present embodiment is provided with a 1st clutch mechanism composed of a roller-ratchet type bidirectional clutch and a 2nd clutch mechanism composed of a cam type unidirectional clutch.

[0047] The selectable clutch 100 is provided with: an outer ring 110 as an input side rotating element; an inner ring 120 as an output side rotating element, which is disposed so as to be relatively rotatable on the same axis as the outer ring 110; a plurality of rollers 130 as power transmission elements in the 1st clutch mechanism; a cam clutch unit 140, which constitutes a power transmission element in the 2nd clutch mechanism; and a selector 150, which performs switching operation of the opening and closing operation of the 1st clutch mechanism, i.e., switching operation of the operation mode between an on state (locked mode) in which the 1st clutch mechanism is capable of transmitting power in two rotational directions and an off state (freewheeling mode) in which power transmission in both rotational directions is cut off. The outer ring 110 and the inner ring 120 are configured to be common to the 1st clutch mechanism and the 2nd clutch mechanism.

[0048] The outer ring 110 has a 1st cylindrical portion 111 and a 2nd cylindrical portion 115 which is coaxial with the 1st cylindrical portion 111 and continuous with an axial end of the 1st cylindrical portion 111.

[0049] The first cylindrical portion 111 is configured to have an outer diameter larger than that of the second cylindrical portion 115 and an inner diameter smaller than that of the second cylindrical portion 115. Thus, an axial one end portion of the first cylindrical portion 111 protrudes toward the radially inner side from the inner peripheral surface of the second cylindrical portion 115, thereby dividing the inside of the outer ring 110 in the axial direction. In the present embodiment, the inside of the first cylindrical portion 111 is a space in which a large-diameter cylindrical portion 121 of a later-described inner ring 120 is arranged. Further, the inside of the second cylindrical portion 115 is a space in which a cam clutch unit is arranged, and the inner peripheral surface of the second cylindrical portion 115 constitutes a track surface 116 that contacts a cam 142 of the cam clutch unit 140.

[0050] On the inner peripheral surface of the first cylindrical portion 111, a plurality of notch portions 113 configured to accommodate the rollers 130 and corresponding to the respective rollers 130 are formed at positions arranged at regular intervals in the circumferential direction.

[0051] In the present embodiment, the notch portions 113 are constituted by grooves having a cross-sectional shape, for example, a shape in which an isosceles trapezoid and a circle contacting two equal sides of the isosceles trapezoid are combined, and are formed so as to extend toward the radially outer side.

[0052] The inner ring 120 has a large-diameter cylindrical portion 121 whose axial one end is closed, a small-diameter cylindrical portion 125 coaxially positioned with the large-diameter cylindrical portion 121 and connected to the axial one end of the large-diameter cylindrical portion 121, and a shaft portion 128 provided so as to extend in the axial direction from an end wall of the large-diameter cylindrical portion 121 on the rotational axis C and protrude toward the axial outer side from an open end of the small-diameter cylindrical portion 125.

[0053] The inner ring 120 is insertable from the axial other end side of the outer ring 110, and the large-diameter cylindrical portion 121 of the inner ring 120 is arranged on the partition wall portion that divides the inside of the outer ring 110. The small-diameter cylindrical portion 125 of the inner ring 120 is positioned inside the second cylindrical portion 115 of the outer ring 110, and the outer peripheral surface constitutes a track surface 126 that contacts the cam 142 in the cam clutch unit 140. The large-diameter cylindrical portion 121 of the inner ring 120 has the other end surface positioned on the axial one end side more than the other end surface of the outer ring 110 in a state where the outer peripheral surface thereof and the inner peripheral surface of the first cylindrical portion 111 of the outer ring 110 are close to and oppose each other. The shaft portion 128 is connected to an output shaft member (not shown) that outputs a torque.

[0054] On the outer circumferential surface of the large-diameter cylindrical portion 121 of the inner ring 120, a plurality of support grooves 122 are formed at predetermined intervals in the circumferential direction, extending in the axial direction. Although in this embodiment, six rollers 130 are arranged at predetermined intervals in the circumferential direction, the number of support grooves 122 is formed to be greater than the number of rollers 130. The number of rollers 130 is not particularly limited, and the spacing between them does not have to be equal.

[0055] In this embodiment, the support groove 122 is formed by a groove with a cross-sectional shape, such as an arc, that can accommodate a portion of the circumferential surface of the roller 130 and support the roller 130. The opening edge of the support groove 122 may also be, for example, a C-shaped or R-shaped chamfer.

[0056] A peripheral groove 127 is formed on the outer peripheral surface of one axial end of the small-diameter cylindrical portion 125. By installing a retaining ring 160 into the peripheral groove 127, an anti-disengagement mechanism can be formed to prevent the cam clutch unit 140 from disengaging axially.

[0057] Each of the multiple rollers 130 is configured to protrude axially outward from the other end of the first cylindrical portion 111 on the outer ring 110 when it is received in the recess 113, and an elastic member mounting groove 131 extending circumferentially is formed on the circumferential surface of the protruding portion.

[0058] like Figure 5 As shown, the axial movement of each of the multiple rollers 130 is restricted by the partition portion on the outer ring 110 and the selector 150.

[0059] In this embodiment, the elastic member 135 is common to all of the plurality of rollers 130, and is, for example, constituted by a ring-shaped clamp spring. The elastic member 135 may also be constituted by, for example, a strip spring.

[0060] The elastic member 135 is mounted radially outward in the elastic member mounting groove 131 of the roller 130 so as to exert a spring force on each roller 130 radially inward toward the support groove 122. That is, the elastic member 135 is configured to retain the roller 130 on the inner ring 120 side and apply force to the roller 130 so as to keep the first clutch mechanism in the engaged state.

[0061] The first clutch mechanism, in a state where the roller 130 is held in the support groove portion 122 of the inner ring 120, when the outer ring 110 or the inner ring 120 rotates, then regardless of the direction of rotation, the roller 130 is pinched in the circumferential direction by the notch portion 113 and the support groove portion 122, and power transmission between the outer ring 110 and the inner ring 120 is performed. On the other hand, by making the roller 130 a state of being housed in the notch portion 113 of the outer ring 110, regardless of the direction of rotation of the outer ring 110 or the inner ring 120, idling is performed.

[0062] The cam clutch unit 140 has: a spacer ring 141 disposed coaxially with the outer ring 110 and the inner ring 120 between the second cylindrical portion 115 of the outer ring 110 and the small-diameter cylindrical portion 125 of the inner ring 120; a plurality of cams 142 and a plurality of concentric holding members 143 held swingably by the spacer ring 141 and disposed in an annular space between the second cylindrical portion 115 of the outer ring 110 and the small-diameter cylindrical portion 125 of the inner ring 120 in a circumferentially aligned manner; and a force applying member 144 applying force to each of the plurality of cams 142 so as to be in contact with the outer ring 110 and the inner ring 120. The concentric holding members 143 are composed of cylindrical rollers having annular spring mounting grooves in the axial center portions. The force applying member 144 is composed of, for example, an annular spring mounted into a mounting groove provided on the outer ring side peripheral surface of the cam 142 from the radially outer side.

[0063] On the second clutch mechanism, from a stationary state, when the inner ring 120 is rotated in one circumferential direction (for example, the clockwise direction in FIG. 6) from the one axial end side, or from a stationary state, when the outer ring 110 is rotated in the other circumferential direction (for example, the counterclockwise direction in FIG. 6), the cams 142 are swung in the meshing direction, and the cams 142 mesh with the outer ring 110 and the inner ring 120 to perform power transmission between the outer ring 110 and the inner ring 120. Further, when the outer ring 110 and the inner ring 120 are rotated at the same speed in the same direction, the cams 142 mesh with the outer ring 110 and the inner ring 120 to perform power transmission between the outer ring 110 and the inner ring 120. Figure 6 Figure 6 On the second clutch mechanism, from a stationary state, when the inner ring 120 is rotated in one circumferential direction (for example, the clockwise direction in FIG. 6) from the one axial end side, or from a stationary state, when the outer ring 110 is rotated in the other circumferential direction (for example, the counterclockwise direction in FIG. 6), the cams 142 are swung in the meshing direction, and the cams 142 mesh with the outer ring 110 and the inner ring 120 to perform power transmission between the outer ring 110 and the inner ring 120. Further, when the outer ring 110 and the inner ring 120 are rotated at the same speed in the same direction, the cams 142 mesh with the outer ring 110 and the inner ring 120 to perform power transmission between the outer ring 110 and the inner ring 120.

[0064] ​On the other hand, the 2nd clutch mechanism idles by swinging the cam 142 to the disengagement direction from the state of rest when the inner ring 120 rotates in the other circumferential direction from the state of rest or when the outer ring 110 rotates in one circumferential direction from the state of rest. Further, the 2nd clutch mechanism idles and cuts the power transmission between the outer ring 110 and the inner ring 120 when the rotation speed of the inner ring 120 is greater than the rotation speed of the outer ring 110 in the state where the outer ring 110 and the inner ring 120 rotate in one circumferential direction together or when the rotation speed of the outer ring 110 is greater than the rotation speed of the inner ring 120 in the state where the outer ring 110 and the inner ring 120 rotate in the other circumferential direction together.

[0065] In the present embodiment, the selector 150 is configured to switch the operation mode of the selectable clutch 100 between a bidirectional lock mode which is capable of transmitting power in both rotation directions and a unidirectional lock mode which is capable of transmitting power in one direction. Specifically, the operation mode of the selectable clutch 100 becomes the bidirectional lock mode by bringing the 1st clutch mechanism into the on state which is capable of transmitting power in both rotation directions by the selector 150, and the operation mode of the selectable clutch 100 becomes the unidirectional lock mode by bringing the 1st clutch mechanism into the off state which cuts the power transmission in both rotation directions by the selector 150.

[0066] The selector 150 has a circumferential wall portion 151 which is cylindrical and has the same outer diameter as the 1st cylindrical portion 111 of the outer ring 110, an end wall portion 153 which closes the other end of the circumferential wall portion 151 in the axial direction, a shaft portion 154 which extends outward in the axial direction from the outside of the end wall portion 153 on the rotation axis C, and a control plate portion 155 which is provided on the inner face of the end wall portion 153 on the radially inner side of each roller 130.

[0067] The selector 150 is linked to the outer ring 110 by a fitting mechanism which has a circumferential play which enables relative rotation within a prescribed rotation angle range with respect to the outer ring 110, and the shaft portion 154 is linked to an input shaft element (not shown) to which a torque is input.

[0068] The engagement mechanism is configured to transmit power by engaging the plurality of engagement teeth 152 provided on one end portion of the peripheral wall portion 151 of the selector 150 with the plurality of engagement teeth 112 provided on the other end portion of the first cylindrical portion 111 of the outer ring 110 by rotation of the selector 150. The engagement teeth 152 of the selector 150 are configured to have a gap between the engagement teeth 112 on the outer ring 110 when in contact with one of the engagement teeth 112. Thus, a rotational play occurs when the selector 150 rotates, and the rotational amount of the play does not transmit power to the outer ring 110, so that the operation mode of the selectable clutch 100 can be switched by relative rotation of the selector 150 with respect to the outer ring 110.

[0069] As shown in Figure 7 , the control plate portion 155 has a plurality of tooth portions 156 formed at equal intervals in the circumferential direction on the outer circumferential surface of the circular plate-shaped base portion, and has a roller holding portion 157 between adjacent tooth portions 156 for holding the rollers 130 when the operation mode of the selectable clutch 100 is the bidirectional lock mode, and has a roller holding groove 158 on the circumferential surface of each tooth portion 156 for holding the rollers 130 when the operation mode of the selectable clutch 100 is the unidirectional lock mode. The outer circumferential surface of the control plate portion 155 between the roller holding portion 157 and the roller holding groove 158 is a cam surface 159 whose distance from the rotational axis C to the circumferential surface gradually increases in the circumferential direction from the roller holding portion 157 toward the roller holding groove 158 when viewed from the one end side in the axial direction.

[0070] When the engagement teeth 152 of the selector 150 are in contact with the engagement teeth 112 of the outer ring 110 on the one side in the circumferential direction (clockwise direction) when viewed from the other end side in the axial direction on the above-described selectable clutch 100, as shown in Figures 2 to 5 , each roller 130 is in a state of being held in the support groove portion 122 of the inner ring 120 and the roller holding portion 157 of the selector 150. Thus, the first clutch mechanism is configured to be able to transmit power in both rotational directions between the outer ring 110 and the inner ring 120 in the on state, and the operation mode of the selectable clutch 100 is the bidirectional lock mode.

[0071] When the selector 150 is rotated in the other direction in the circumferential direction so as to bring the engagement teeth 152 into contact with the engagement teeth 112 of the outer ring 110 on the other side in the circumferential direction (counterclockwise direction) when viewed from the other end side in the axial direction, as shown in Figures 8 to 11As shown, the roller 130 moves radially outward against the elastic force of the elastic member 135 by the action of the cam surface 159 of the control plate portion 155, and is received in the recess 113 of the outer ring 110. At this time, since the selector 150 is connected to the outer ring 110 through an engagement mechanism with clearance in the circumferential direction, the selector 150 rotates relative to the outer ring 110, and power is not transmitted from the selector 150 to the outer ring 110. As a result, the first clutch mechanism is in an open state where the power transmission in both rotational directions between the outer ring 110 and the inner ring 120 is cut off, and the operating mode of the selectable clutch 100 is switched to a one-way locking mode constituted by the second clutch mechanism.

[0072] The aforementioned selectable clutch 100 can, for example, be applied to a separation mechanism for switching the driving state of a four-wheel drive vehicle between a four-wheel drive (4WD) state and a two-wheel drive (2WD) state, wherein one of the left and right front wheels and the left and right rear wheels of the four-wheel drive vehicle is a drive wheel driven by the driving force of the main drive motor, and the other is an auxiliary drive wheel driven by the driving force of the auxiliary motor. Figure 12 An application example with a separation mechanism is shown.

[0073] In this example, the left and right front wheels are drive wheels 170 driven by the driving force of the main drive motor 176, and the left and right rear wheels are auxiliary drive wheels 171 driven by the driving force of the auxiliary drive motor 177. Symbol 175 represents the battery that supplies power to the main drive motor 176 and the auxiliary drive motor 177.

[0074] The separation mechanism 180 has the aforementioned selectable clutch 100 and is configured to freely engage or disengage the transmission of driving force between the auxiliary drive motor 177 and the auxiliary drive wheel 171.

[0075] When the rotation of the auxiliary drive wheel axle 172 is in the forward direction, the shaft portion 128 of the inner ring 120 of the selectable clutch 100 is connected to the output shaft element, i.e., the auxiliary drive wheel axle 172, via a suitable connecting component (not shown), so that the inner ring 120 can rotate in the other circumferential direction (e.g., when referring to...). Figure 6 At that time, it is Figure 6 The selector 150 rotates counterclockwise, and at the same time, the shaft 154 of the selector 150 is connected to the motor shaft of the input element, namely the auxiliary drive motor 177, via a suitable connecting component not shown.

[0076] The following explains the switching action of the driving state of a four-wheel drive vehicle.

[0077] Figure 13 This is a graph showing the relationship between the driving state of a four-wheel drive vehicle and the rotational speeds of the auxiliary drive wheel axles and the auxiliary drive motor shaft. Figure 13In this case, the broken line indicates a change in the rotational speed of the auxiliary drive wheel axle 172, and the solid line indicates a change in the rotational speed of the motor shaft of the auxiliary drive motor 177. In addition, the rotational speed of the auxiliary drive wheel axle 172 is synchronized with the rotational speed of the motor shaft of the main drive motor 176.

[0078] When the vehicle is accelerated in the 2WD forward travel (in the section A in FIG. 6), the control selector 150 is controlled so as to bring the first clutch mechanism into the disengaged state (refer to FIG. 5). The selectable clutch 100 is brought into the one-way lock mode. Although the inner ring 120 coupled to the auxiliary drive wheel axle 172 rotates in the circumferential direction in the other direction, the cam 142 for the second clutch mechanism swings in the disengagement direction, and thus the second clutch mechanism idles. Therefore, the power from the auxiliary drive wheel axle 172 is not transmitted to the outer ring 110, and in addition, since the first clutch mechanism is in the disengaged state and the auxiliary drive motor 177 is stopped, the selector 150 and the outer ring 110 are in the stationary state (stopped). Figure 13 Figures 8 to 11 When the vehicle is accelerated in the 2WD forward travel (in the section A in FIG. 6), the control selector 150 is controlled so as to bring the first clutch mechanism into the disengaged state (refer to FIG. 5). The selectable clutch 100 is brought into the one-way lock mode. Although the inner ring 120 coupled to the auxiliary drive wheel axle 172 rotates in the circumferential direction in the other direction, the cam 142 for the second clutch mechanism swings in the disengagement direction, and thus the second clutch mechanism idles. Therefore, the power from the auxiliary drive wheel axle 172 is not transmitted to the outer ring 110, and in addition, since the first clutch mechanism is in the disengaged state and the auxiliary drive motor 177 is stopped, the selector 150 and the outer ring 110 are in the stationary state (stopped).

[0079] When the vehicle is accelerated in the 2WD forward travel (in the section A in FIG. 6), the control selector 150 is controlled so as to bring the first clutch mechanism into the disengaged state (refer to FIG. 5). The selectable clutch 100 is brought into the one-way lock mode. Although the inner ring 120 coupled to the auxiliary drive wheel axle 172 rotates in the circumferential direction in the other direction, the cam 142 for the second clutch mechanism swings in the disengagement direction, and thus the second clutch mechanism idles. Therefore, the power from the auxiliary drive wheel axle 172 is not transmitted to the outer ring 110, and in addition, since the first clutch mechanism is in the disengaged state and the auxiliary drive motor 177 is stopped, the selector 150 and the outer ring 110 are in the stationary state (stopped). Figure 13 When the vehicle is accelerated in the 2WD forward travel (in the section A in FIG. 6), the control selector 150 is controlled so as to bring the first clutch mechanism into the disengaged state (refer to FIG. 5). The selectable clutch 100 is brought into the one-way lock mode. Although the inner ring 120 coupled to the auxiliary drive wheel axle 172 rotates in the circumferential direction in the other direction, the cam 142 for the second clutch mechanism swings in the disengagement direction, and thus the second clutch mechanism idles. Therefore, the power from the auxiliary drive wheel axle 172 is not transmitted to the outer ring 110, and in addition, since the first clutch mechanism is in the disengaged state and the auxiliary drive motor 177 is stopped, the selector 150 and the outer ring 110 are in the stationary state (stopped).

[0080] Figure 13 When the vehicle is accelerated in the 2WD forward travel (in the section A in FIG. 6), the control selector 150 is controlled so as to bring the first clutch mechanism into the disengaged state (refer to FIG. 5). The selectable clutch 100 is brought into the one-way lock mode. Although the inner ring 120 coupled to the auxiliary drive wheel axle 172 rotates in the circumferential direction in the other direction, the cam 142 for the second clutch mechanism swings in the disengagement direction, and thus the second clutch mechanism idles. Therefore, the power from the auxiliary drive wheel axle 172 is not transmitted to the outer ring 110, and in addition, since the first clutch mechanism is in the disengaged state and the auxiliary drive motor 177 is stopped, the selector 150 and the outer ring 110 are in the stationary state (stopped).

[0081] When the vehicle is accelerated in the 2WD forward travel (in the section A in FIG. 6), the control selector 150 is controlled so as to bring the first clutch mechanism into the disengaged state (refer to FIG. 5). The selectable clutch 100 is brought into the one-way lock mode. Although the inner ring 120 coupled to the auxiliary drive wheel axle 172 rotates in the circumferential direction in the other direction, the cam 142 for the second clutch mechanism swings in the disengagement direction, and thus the second clutch mechanism idles. Therefore, the power from the auxiliary drive wheel axle 172 is not transmitted to the outer ring 110, and in addition, since the first clutch mechanism is in the disengaged state and the auxiliary drive motor 177 is stopped, the selector 150 and the outer ring 110 are in the stationary state (stopped). Figure 13 When the vehicle is accelerated in the 2WD forward travel (in the section A in FIG. 6), the control selector 150 is controlled so as to bring the first clutch mechanism into the disengaged state (refer to FIG. 5). The selectable clutch 100 is brought into the one-way lock mode. Although the inner ring 120 coupled to the auxiliary drive wheel axle 172 rotates in the circumferential direction in the other direction, the cam 142 for the second clutch mechanism swings in the disengagement direction, and thus the second clutch mechanism idles. Therefore, the power from the auxiliary drive wheel axle 172 is not transmitted to the outer ring 110, and in addition, since the first clutch mechanism is in the disengaged state and the auxiliary drive motor 177 is stopped, the selector 150 and the outer ring 110 are in the stationary state (stopped).

[0082] ​​When the 2WD forward deceleration or braking is performed (in the section E of Figure 13 , the 1st clutch mechanism and the 2nd clutch mechanism also maintain the freewheeling state.

[0083] When the four-wheel drive vehicle is caused to travel backward from a stopped state (in the section F of Figure 13 , first, the selector 150 is controlled so as to bring the 1st clutch mechanism into the engaged state (refer to Figures 2 to 5 ). Specifically, by performing reverse rotation driving of the motor shaft of the auxiliary drive motor 177, the selector 150 is relatively rotated in one circumferential direction with respect to the outer ring 110, and the pawl 152 of the selector 150 comes into abutment with the pawl 112 of the outer ring 110 on the one circumferential direction side. Thus, the 1st clutch mechanism is switched to the engaged state. After the 1st clutch mechanism is switched to the engaged state, the auxiliary drive motor 177 is stopped.

[0084] Next, when the main drive motor 176 and the auxiliary drive motor 177 are caused to perform reverse rotation driving together (in the section G of Figure 13 , in the 2nd clutch mechanism, the outer ring 110 rotates together with the selector 150. Thus, since the rollers 130 are pinched in the circumferential direction by the notch portions 113 and the support groove portions 122, the outer ring 110 meshes with the inner ring 120, and it is possible to transmit the driving force of the auxiliary drive motor 177 to the auxiliary drive wheels 171. Thus, the four-wheel drive vehicle travels backward in the 4WD state.

[0085] Then, by stopping the auxiliary drive motor 177, the travel state of the four-wheel drive vehicle is switched to the 2WD state (in the section H of Figure 13 ). By stopping the auxiliary drive motor 177, the power transmission from the auxiliary drive motor 177 to the auxiliary drive wheels 171 is cut off, but since the 2nd clutch mechanism maintains the meshing, it is possible to transmit the driving force of the auxiliary drive wheels 171 to the auxiliary drive motor 177 (regenerative function). In this example, although the rotational speed of the motor shaft of the main drive motor 176 decreases (deceleration of the four-wheel drive vehicle) at the same time as the auxiliary drive motor 177 is stopped, even if the rotational speed of the inner ring 120 decreases due to the decrease in the rotational speed of the auxiliary drive wheel shaft 172, the 1st clutch mechanism maintains the meshing.

[0086] Then, after the four-wheel drive vehicle is stopped (in the section I of Figure 13 , when the four-wheel drive vehicle is caused to travel forward in the 2WD state, for example, the selector 150 is controlled so as to bring the 1st clutch mechanism into the disengaged state (refer to Figures 8 to 11). Specifically, by performing forward rotation drive of the motor shaft of the auxiliary drive motor 177, the selector 150 is relatively rotated in the other circumferential direction with respect to the outer ring 110, and the pawl 152 of the selector 150 is brought into abutment with the pawl 112 of the outer ring 110 on the other circumferential direction side. Thus, the first clutch mechanism is switched to the disengaged state. After switching to the disengaged state of the first clutch mechanism, the auxiliary drive motor 177 is stopped.

[0087] Thus, according to the separation mechanism 180 according to the present application, by controlling the rotation speed and the rotation direction of the auxiliary drive motor 177, the operation mode of the selectable clutch 100 is switched, and in either the forward travel or the reverse travel of the four-wheel drive vehicle, the power transmission or the cutoff from the auxiliary drive motor 177 to the auxiliary drive wheels 171 can be switched, and the structure can be simplified and downsized. Moreover, since the selectable clutch 100 is configured to automatically switch between engagement and idling in accordance with the rotation speeds of the outer ring 110 and the inner ring 120, the switching of the travel state of the four-wheel drive vehicle can be smoothly and quickly performed.

[0088] Although the embodiments of the present application have been described above, the present application is not limited to the above-described embodiments, and various design changes can be made within the scope of the present application described above.

[0089] For example, although the configuration in which the support groove portion is formed on the outer circumferential surface of the inner ring and the notched portion is formed on the inner circumferential surface of the outer ring, and the elastic member is arranged to apply force to the roller in the radially outward direction has been described for the first clutch mechanism, the configuration can also be such that the support groove portion is formed on the inner circumferential surface of the outer ring and the notched portion is formed on the outer circumferential surface of the inner ring. In this configuration, the control plate portion of the selector can be annular on the radially outward side of the roller. Furthermore, the elastic member can also be configured such that the elastic member is arranged to apply force to the roller in the radially outward direction.

[0090] Furthermore, although the configuration in which the first clutch mechanism is constituted by a roller ratchet type clutch and the second clutch mechanism is constituted by a cam type clutch has been described in the above-described embodiments, the first clutch mechanism is not limited to the roller ratchet type clutch, and as long as the configuration is such that the power transmission and the cutoff can be switched, the first clutch mechanism can also be constituted by a cam type, a plate type, or a pawl type clutch, for example. Furthermore, the second clutch mechanism is not limited to the cam type clutch, and as long as the configuration is such that the second clutch mechanism is constituted by a one-way clutch, the second clutch mechanism can also be constituted by a roller type or a ratchet type clutch, for example.

Claims

1. A selectable clutch, comprising: a first clutch mechanism including an input-side rotary element, an output-side rotary element, and a power transmission element that transmits or cuts off power in both rotary directions between the input-side rotary element and the output-side rotary element; and a selector that performs opening and closing operations of the first clutch mechanism, characterized in that the selector is linked to the input-side rotary element by a coupling mechanism having a circumferential play that allows relative rotation within a prescribed rotary angle range with respect to the input-side rotary element while being linked to an input shaft element that inputs a torque.

2. The selectable clutch according to claim 1, characterized in that it further comprises a second clutch mechanism that transmits or cuts off power between the input-side rotary element and the output-side rotary element, and the second clutch mechanism is configured by a one-way clutch.

3. The selectable clutch according to claim 1, characterized in that the selector is configured to be able to switch between an on state in which the power transmission element is able to transmit power from the input-side rotary element to the output-side rotary element, and an off state in which the power transmission element cuts off transmission of power from the input-side rotary element to the output-side rotary element, by relative rotation of the selector with respect to the input-side rotary element.

4. The selectable clutch according to claim 1, characterized in that the coupling mechanism is configured to transmit power by engaging ratchets provided on each of the input-side rotary element and the selector.

5. The selectable clutch according to claim 1, characterized in that the input-side rotary element and the output-side rotary element are each configured by an outer ring and an inner ring that are provided to be able to relatively rotate on the same axis, the power transmission element is configured by a plurality of rollers provided in a circumferential direction between the outer ring and the inner ring in a state in which the rollers are urged in a radial direction by an elastic member, a notch portion configured to be able to accommodate the rollers is formed on one of an inner peripheral surface of the outer ring and an outer peripheral surface of the inner ring, and a support groove portion that supports the rollers is formed on the other of the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring, the selector includes a control plate portion that is located on the outer ring side or the inner ring side of the rollers and on which a plurality of tooth portions are formed on an inner peripheral surface or an outer peripheral surface, a peripheral surface between the tooth portions on the control plate portion is a cam surface in which a distance from a rotary axis to the peripheral surface gradually increases or gradually decreases in a circumferential direction, and the control plate portion is configured to be able to move the rollers in a radial direction by relative movement of the selector with respect to the outer ring.

6. The selectable clutch according to claim 2, characterized in that the input-side rotary element and the output-side rotary element are each configured by an outer ring and an inner ring that are provided to be able to relatively rotate on the same axis. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ The second clutch mechanism is configured such that a plurality of cams are held swingably in a spacer ring disposed between the outer ring and the inner ring in a state in which the cams are forced to rotate in the engaging direction by a force applying member.

7. A separation mechanism that switches a running state of a four-wheel drive vehicle between a four-wheel running state and a two-wheel running state, one of left and right front wheels and left and right rear wheels of the four-wheel drive vehicle being a drive wheel that is driven by a drive force of a main drive motor, and the other being an auxiliary drive wheel that is driven by a drive force of an auxiliary drive motor, characterized by comprising: The selectable clutch according to claim 2, The selector is linked to a motor shaft of the auxiliary drive motor while the output-side rotating element of the selectable clutch is linked to an auxiliary drive wheel axle, and is configured to freely connect and disconnect the transmission of the drive force between the auxiliary drive motor and the auxiliary drive wheel.

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