Clutch pressing mechanism

Abstract

To provide a pressing mechanism of a clutch capable of more reliably disengaging a clutch, in switching from a four-wheel driving state to a two-wheel driving state.SOLUTION: A pressing mechanism of a clutch is provided with: a first disc member 12 and a second disc member 13 which are coaxially disposed, relatively rotatable and movable in a rotating shaft direction; a first groove 12c formed on a first end face F12 directing the second disc member 13 of the first disc member 12, extending in a circumferential direction, and gradually changing in a depth from the first end face F12; a second groove 13c formed on a second end face F13 directing the first disc member 12 of the second disc member 13, extending in the circumferential direction, and gradually changing in a depth from the second end face F13; a spherical body 14 rolling between the first groove 12c and the second groove 13c; and an energization member 31 locked to the first disc member 12 at one end, locked to the second disc member 13 at the other end, and having energization force in a rotating direction of the rotating shaft.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a clutch pressing mechanism. [Background technology]

[0002] In a four-wheel drive vehicle based on a front-wheel drive system, power output from a power source located at the front of the vehicle is transmitted to a final drive unit mounted at the rear of the vehicle via a transmission, an auxiliary transmission connected to the transmission, and a propeller shaft. Driving in four-wheel drive mode offers greater driving stability than driving in front-wheel drive (two-wheel drive) mode, but is characterized by reduced fuel economy. Therefore, it is common practice to provide a power connection / disconnection device that connects and disconnects the power transmission path in order to switch between four-wheel drive and two-wheel drive as needed. Furthermore, when switching between four-wheel drive and two-wheel drive, sensors detect the behavior of the vehicle body and control the power interrupter to achieve more appropriate driving performance. The power interrupter may be installed in one of three ways: integrated with the auxiliary transmission, integrated with the final reduction gear, or disposed between the drive shaft that transmits power to the rear wheels and the final reduction gear.

[0003] For example, the power interrupter proposed in Patent Document 1 includes an input shaft, a plurality of first clutch discs that rotate integrally with the input shaft, a plurality of second clutch discs that are stacked alternately with the first clutch discs, an output shaft that rotates integrally with the second clutch discs, and a pressing mechanism that presses the first clutch discs and second clutch discs in the direction of the rotation axis. The pressing mechanism includes a pair of cam plates arranged coaxially to rotate relative to one another and to move axially. Grooves are formed on the surfaces of the cam plates that face each other. These grooves are circumferentially oriented and have gradually varying depths, and steel balls are placed in the grooves. One of the cam plates is attached so as to be biased against the other cam plate via a pressure plate. When the other cam plate is rotated by a motor, the steel balls roll from the deep region of the groove to the shallow region, causing one cam plate to move in the axial direction. One of the moving cam plates presses against a piston located at the end of the clutch disc, causing the first clutch disc and the second clutch disc to come into close contact with each other, thereby transmitting power. By controlling the amount of movement of one of the cam plates, it is possible to control the pressing force of the clutch, making it possible to transmit power to the rear wheels according to the running state of the vehicle. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 5896013 Summary of the Invention [Problem to be solved by the invention]

[0005] Incidentally, when switching from four-wheel drive to two-wheel drive, if one of the cam plates cannot return to its initial position, the first clutch disc and the second clutch disc will remain in close contact with each other. In other words, the clutch is unnecessarily engaged (this is called a dragging state), and the four-wheel drive state is maintained. In this dragging state, unnecessary power is transmitted to the rear wheels, resulting in reduced fuel efficiency. The present invention has been made in consideration of the above points, and aims to provide a clutch pressing mechanism that can more reliably release the clutch when switching from four-wheel drive to two-wheel drive. [Means for solving the problem]

[0006] In order to achieve the above object, a pressing mechanism for a clutch according to the present invention includes a first disk member and a second disk member that are coaxially arranged, rotatable relative to each other, and movable in a direction of a rotation axis; a first groove that is formed in a first end face of the first disk member that faces the second disk member, extends in a circumferential direction, and has a depth that gradually changes from the first end face; a second groove that is formed in a second end face of the second disk member that faces the first disk member, and extends in a circumferential direction, and has a depth that gradually changes from the second end face; a sphere that rolls between the first groove and the second groove; and an urging member that has one end engaged with the first disk member and the other end engaged with the second disk member, and has a urging force in a rotation direction of the rotation shaft. The biasing member is a spiral spring. [Effects of the Invention]

[0007] According to the present invention, it is possible to provide a clutch pressing mechanism that can more reliably release the clutch when switching from four-wheel drive to two-wheel drive. [Brief explanation of the drawings]

[0008] [Figure 1] 1 is a cross-sectional view of a power interrupter according to a first embodiment of the present invention. [Figure 2] 2A and 2B are a front view and an exploded perspective view of a ball cam shown in part II of FIG. 1. [Figure 3] FIG. 2 is a plan view showing a drive cam plate according to the first embodiment. [Figure 4] FIG. 2 is a plan view showing a driven cam plate according to the first embodiment. [Figure 5] 4 is a cross-sectional view taken along line VV in FIG. 3, showing the ball cam mechanism in a pressure release mode according to the first embodiment. [Figure 6] 4 is a cross-sectional view taken along line VV in FIG. 3, showing the ball cam mechanism in a pressing mode according to the first embodiment. [Figure 7] FIG. 5 is a cross-sectional view of a power interrupter according to a second embodiment of the present invention. [Figure 8] FIG. 10 is a plan view showing a drive cam plate according to a second embodiment. [Figure 9] FIG. 10 is a plan view showing a driven cam plate according to a second embodiment. [Figure 10] 10 is a cross-sectional view taken along line VV in FIG. 3, showing the ball cam mechanism in a pressure release mode according to the second embodiment. [Figure 11] 10 is a cross-sectional view taken along line VV in FIG. 3, showing the ball cam mechanism in a pressing mode according to the second embodiment. [Figure 12] FIG. 6 is a cross-sectional view of a power interrupter according to a third embodiment of the present invention. [Figure 13] FIG. 11 is a plan view showing a drive cam plate according to a third embodiment. [Figure 14] FIG. 11 is a plan view showing a driven cam plate according to a third embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0009] First Embodiment A power interrupter S according to a first embodiment of the present invention will be described in detail with reference to FIGS. In the description, the same elements are given the same reference numerals and redundant description will be omitted. The power interrupter S of this embodiment is mounted on a four-wheel drive vehicle based on front-wheel drive.

[0010] The power interrupter S transmits or interrupts power output from a power source (not shown), such as an engine, installed in the so-called engine room at the front of the vehicle body, to rear wheels (not shown). The power disconnecting device S is installed between the propeller shaft (55) and the differential gear DF ​​(final reduction gear). When the power interrupter S transmits power to the rear wheels, the vehicle becomes four-wheel drive, and when the power interrupter S interrupts the power, the vehicle becomes front-wheel drive (two-wheel drive). The power interrupter S of this embodiment includes a pressing mechanism S1 (a pressing mechanism for a clutch) and a clutch mechanism S2.

[0011] <Pressing mechanism> The pressing mechanism S1 (pressing mechanism of the clutch) is configured to apply a connecting force (pressing force) to the clutch mechanism S2 (see FIG. 1). The pressing mechanism S1 is disposed in a clutch housing CH which is the housing of the power interrupter S. The pressing mechanism S1 includes a ball cam 10, an actuator 20, a return means 30, and a pressure plate 40.

[0012] <Ball Cam> The ball cam 10 is a component for converting a rotational movement into a linear movement (see FIGS. 1 to 4). The ball cam 10 is configured to be selectively deformable into two forms: a pressure release form and a pressure form. The ball cam 10 includes a drive cam member 12 (first disk member), a driven cam member 13 (second disk member), and a cam ball 14 (sphere). The driving cam member 12 and the driven cam member 13 constitute a pair of cam members 11.

[0013] The drive cam member 12 (first disk member) is configured as a disk-shaped member supported by the clutch housing CH in a state where it can rotate around the rotation axis AX. The drive cam member 12 has a shaft hole 12a, spur teeth 12b, and a drive cam groove 12c.

[0014] The shaft hole 12a is formed as a circular hole that penetrates the plate surface at the center of the disk shape. The shaft hole 12a is disposed so that its center is concentric with the rotation axis AX.

[0015] The spur teeth 12b are formed on the outer periphery of the drive cam member 12 and are constituted by the teeth of a spur gear. The drive cam member 12 is provided with the spur teeth 12b, and functions as a gear that rotates around the rotation axis AX.

[0016] The drive cam groove 12c (first groove) is formed on the plate surface F12 (first end surface) of the drive cam member 12 that faces the driven cam member 13. The drive cam groove 12c, together with a driven cam groove 13c and a cam ball 14, which will be described later, constitute a cam structure. The drive cam groove 12c has an arc shape that curves in the circumferential direction around the rotation axis AX.

[0017] The drive cam groove 12c is designed so that the depth of the groove gradually increases from one end to the other end in the circumferential direction. Three such drive cam grooves 12c are arranged at equal angular intervals (120 degree intervals) around the rotation axis AX.

[0018] The driven cam member 13 (second disk member) is made up of a plate-shaped member supported by the clutch housing CH in a state in which it is movable along the direction of the rotation axis AX. Furthermore, the driven cam member 13 is disposed so that its plate surface faces the plate surface of the driving cam member 12 . The driven cam member 13 includes a locking claw 13b and a driven cam groove 13c.

[0019] The locking pawl 13b is formed on the outer periphery of the driven cam member 13 and is composed of a segment that projects radially outward from the rotation axis AX. The locking pawl 13b is disposed in a pawl groove (not shown) formed in the clutch housing CH so as to be movable along the direction of the rotation axis AX while engaging in a circumferential direction around the rotation axis AX. Three such locking pawls 13b are arranged on the outer periphery of the driven cam member 13 at equal angular intervals (120 degree intervals) around the rotation axis AX.

[0020] The driven cam groove 13c (second groove) is formed in a portion of the plate surface F13 (second end surface) of the driven cam member 13 that faces the drive cam groove 12c. The driven cam groove 13c has an arc shape that curves in the circumferential direction around the rotation axis AX.

[0021] The driven cam groove 13c is formed so that the depth of the groove gradually increases from one end to the other end in the circumferential direction. Three such driven cam grooves 13c are arranged at equal angular intervals (120 degree intervals) around the rotation axis AX.

[0022] The cam ball 14 (sphere) is made of a hard sphere that is not deformed by the pressing pressure. The cam ball 14 is disposed so as to be able to roll in both the drive cam groove 12c and the driven cam groove 13c.

[0023] <Actuator> Next, the configuration of the actuator 20 will be described (see FIG. 1). The actuator 20 is configured to apply a rotational force to the driving cam member 12 that constitutes the ball cam 10 . The actuator 20 includes a motor 21 and an idler gear 22 .

[0024] The motor 21 is controlled so as to be selectively switched between forward and reverse rotation. When the motor 21 rotates forward, the drive cam member 12 rotates in a direction (connection direction) in which the drive cam member 12 changes from the pressure release state to the pressure state. When the motor 21 rotates in the reverse direction, the drive cam member 12 rotates in a direction (connection releasing direction) in which the drive cam member 12 changes from the pressing state to the pressing release state.

[0025] The idler gear 22 is in mesh with the motor 21 and also in mesh with the spur teeth 12 b of the drive cam member 12 . The idler gear 22 transmits the rotational force of the motor 21 to the drive cam member 12 while reducing the rotational speed.

[0026] <Return method> Next, the configuration of the return means 30 will be described (see FIGS. 1 to 6). The return means 30 is configured to apply a biasing force for returning the ball cam 10 from the pressing state to the pressing-released state. The return means 30 includes a compression coil spring 31a (biasing member 31), a drive-side spring accommodating portion 32, a driven-side spring accommodating portion 33, a drive-side spring end support portion , and a driven-side spring end support portion .

[0027] The compression coil spring 31a (biasing member 31) has one end supported by a drive-side spring end support portion 34 of the drive cam member 12, and the other end supported by a driven-side spring end support portion 35 of the driven cam member 13. That is, the compression coil spring 31a is installed so that its central axis A31a is inclined obliquely with respect to the plate surface. Therefore, the distance between the driving cam member 12 and the driven cam member 13 increases, and the inclination of the central axis A31a increases. The component of the restoring force of the compressed compression coil spring 31 a in the direction of the rotation axis AX acts as a biasing force for attracting the driven cam member 13 to the driving cam member 12 .

[0028] The drive-side spring accommodating portion 32 is configured to accommodate the compression coil spring 31a. The drive-side spring accommodating portion 32 is configured as a groove-shaped recess that opens into the plate surface of the drive cam member 12 that faces the driven cam member 13 . The drive-side spring accommodating portion 32 is disposed radially outside the drive cam groove 12c. The drive-side spring accommodating portion 32 is curved in an arc shape along the circumferential direction around the rotation axis AX.

[0029] The driven-side spring accommodating portion 33, together with the driving-side spring accommodating portion 32, is configured to accommodate the compression coil spring 31a. The driven-side spring accommodating portion 33 is configured as a groove-shaped recess that opens to a portion of the plate surface of the driven cam member 13 that faces the drive-side spring accommodating portion 32 . The driven-side spring accommodating portion 33 has an arc shape that curves in the circumferential direction around the rotation axis AX. The driven-side spring accommodating portion 33 and the driving-side spring accommodating portion 32 form a space having a generally rectangular cross section.

[0030] The drive-side spring end support portion 34 (one end support portion) is configured to support one end of the compression coil spring 31a (biasing member 31) housed in the drive-side spring housing portion 32 on the drive cam member 12. The drive-side spring end support portion 34 is provided at the end of the drive-side spring accommodating portion 32 on the side that receives the repulsive force of the compressed compression coil spring 31a. Three such drive-side spring accommodating portions 32 are arranged at equal angular intervals (120-degree intervals) around the rotation axis AX.

[0031] The driven-side spring end support portion 35 (other end support portion) is configured to support the other end of the compression coil spring 31a (biasing member 31) housed in the driven-side spring housing portion 33 on the driven cam member 13. The driven-side spring end support portion 35 is provided at the end of the driven-side spring accommodating portion 33 on the side that receives the repulsive force of the compressed compression coil spring 31a. Three such driven-side spring accommodating portions 33 are arranged at equal angular intervals (120-degree intervals) around the rotation axis AX. That is, a total of three compression coil springs 31a are arranged at equal angular intervals along the circumferential direction.

[0032] <Pressure Plate> The pressure plate 40 serves as an output part of the pressing mechanism S1 and moves in the longitudinal direction of the vehicle along the axial direction of the rotation axis AX (see FIG. 1). The pressure plate 40 is arranged so as to be able to abut against the rear surface of the output-side friction plate 54 which is located at the rearmost position. The pressure plate 40 is supported by the driven cam member 13 via a thrust bearing 41 in a state in which it can rotate around the rotation axis. As a result, in the pressing mechanism S1 in the pressing mode, the pressure plate 40 applies a pressing force to the output-side friction plate 54 described below, and rotates together with the output-side friction plate 54 around the rotation axis AX.

[0033] <Clutch mechanism> Next, the clutch mechanism S2 will be described (see FIG. 1). The clutch mechanism S2 is configured to connect and disconnect power depending on the strength of the pressing force applied by the pressing mechanism S1. The clutch mechanism S2 includes a clutch case 51, an output shaft 52, an input side friction plate 53, and an output side friction plate .

[0034] The clutch case 51 is supported in the clutch housing CH so as to be rotatable about a rotation axis AX. The clutch case 51 includes a connecting portion 51a, an input side spline 51b, and a pressure wall 51c.

[0035] The connecting portion 51 a is provided at the front end portion of the clutch case 51 . The connecting portion 51a is connected to the rear end of the propeller shaft (55), and receives rotation from an engine (not shown).

[0036] The input spline 51b is provided on the inner peripheral surface of the clutch case 51 at the rear portion thereof. The input side spline 51b allows the input side friction plate 53 to move along the axial direction of the rotation axis AX while engaging with the input side spline 51b in the circumferential direction around the rotation axis AX.

[0037] The pressure wall 51c is disposed at the front end of the input side spline 51b. The pressure wall 51c is formed on a plane perpendicular to the rotation axis AX. The pressure wall 51c restricts the movement of the input side friction plate 53 in the direction of the rotation axis AX.

[0038] The output shaft 52 protrudes rearward from the rear opening of the clutch housing CH and is fitted into the housing of the differential device DF, and its rear end is connected to the drive pinion gear D1 of the differential device DF, which transmits rotation to the rear wheels (not shown), thereby transmitting the rotation. The output shaft 52 is supported by the clutch housing CH in a state in which it can rotate about a rotation axis AX.

[0039] The output shaft 52 is provided with a shaft spline 52a. The axial spline 52a engages with the output side friction plate 54 in the circumferential direction around the rotation axis AX, while allowing movement along the axial direction of the rotation axis AX.

[0040] The input side friction plate 53 has a disk shape with a circular through hole opening in the center. The input side friction plate 53 is disposed in the clutch case 51 with input side engagement pieces 53a formed on the outer periphery engaged with the input side splines 51b. That is, the input side friction plate 53 is arranged so as to be movable in the direction of the rotation axis AX within the clutch case 51 and to rotate together with the clutch case 51 . A plurality of input side friction plates 53 are stacked and arranged along the rotation axis direction.

[0041] The output side friction plate 54 has a disk shape with a circular through hole opening in the center. The output side friction plate 54 is supported by the output shaft 52 in a state in which an output side engagement piece 54a formed on the inner periphery is engaged with the shaft spline 52a. That is, the output-side friction plate 54 is arranged so as to be movable on the outer periphery of the output shaft 52 in the direction of the rotation axis AX and to rotate together with the output shaft 52 . The same number of output-side friction plates 54 as the input-side friction plates 53 are alternately stacked on the output shaft 52 along the direction of the rotation axis AX.

[0042] <Function of the power interrupter> Next, the operation of the power interrupter S of this embodiment will be described. The power disconnecting device S can selectively change its state between a disconnected state and a connected state. [Unlinked state] In the power interrupter S in the disconnected state, the pressing mechanism S1 is in the pressure release state. The pressing mechanism S1 is constantly subjected to a biasing force by the compression coil spring 31a (biasing member 31) of the return means 30. Therefore, in the pressure release state, the pressing mechanism S1 is held in a state in which the driven cam member 13 is closest to the driving cam member 12.

[0043] Furthermore, the pressure plate 40 moves back and forth along the rotation axis AX together with the driven cam member 13, and is therefore spaced apart from the output-side friction plate 54. Therefore, no pressing force is applied to bring the input side friction plate 53 and the output side friction plate 54 into close contact with each other. In other words, the power disconnecting device S is in a disconnected state in which power is not transmitted to the rear wheels.

[0044] [Connection status] In the power interrupter S in the connected state, the pressing mechanism S1 in the pressing form is in the pressing form. In the pressing mode, the pressing mechanism S1 causes the ball cam 10 to push the driven cam member 13 forward against the biasing force of the compression coil spring 31a. Therefore, in the pressed state, the driven cam member 13 is held at a position furthest from the driving cam member 12.

[0045] Additionally, the pressure plate 40 moves together with the driven cam member 13 toward the front of the vehicle. As the pressure plate 40 moves toward the front of the vehicle, the input side friction plate 53 and the output side friction plate 54 are sandwiched between the pressure plate 40 and the pressure wall 51c and are brought into pressure contact with each other. As a result, the rotation of the clutch case 51 is transmitted to the output shaft 52 . In other words, the power disconnecting device S is in a connected state in which power is transmitted to the rear wheels.

[0046] [Coupling operation (front-wheel drive → four-wheel drive)] The coupling operation causes the power coupling / disconnecting device S to transition from a disengaged state to a coupled state. In the connecting operation, first, the motor 21 operates in the normal direction with respect to the ball cam 10 in the pressure release state, and the drive cam member 12 rotates in the connecting direction via the idler gear 22 . As the drive cam member 12 rotates in the connecting direction while compressing the compression coil spring 31a, the cam ball 14 moves from a wide, deep portion to a narrow, shallow portion within the drive cam groove 12c and the driven cam groove 13c.

[0047] The cam ball 14 moves within the drive cam groove 12c and the driven cam groove 13c, and pushes the driven cam member 13 away from the drive cam member 12 (from the rear to the front of the vehicle) (pressing mode). The driven cam member 13 being pushed forward pushes the pressure plate 40 forward via the thrust bearing 41 . The pushed-out pressure plate 40 presses the output-side friction plate 54 and the input-side friction plate 53 forward.

[0048] Then, the output-side friction plate 54 and the input-side friction plate 53 are pressed against each other between the pressure plate 40 and the pressure wall 51c, and the transition of the power connection / disconnection device S to the connected state is completed. In this state, when a rotational force is applied to the clutch case 51 , the input side friction plate 53 and the output side friction plate 54 rotate while remaining connected, and the rotation of the propeller shaft is transmitted to the output shaft 52 . This switches the vehicle from front-wheel drive to four-wheel drive.

[0049] [Uncoupling operation (four-wheel drive to front-wheel drive)] The uncoupling operation causes the power disconnector S to transition from a coupled state to a uncoupled state. In the disconnection operation, the motor 21 operates in the reverse direction relative to the ball cam 10 in the pressing state, and the drive cam member 12 rotates in the disconnection direction via the idler gear 22. When the drive cam member 12 rotates in the direction of disconnection, the cam ball 14 moves from a narrow, shallow portion to a wide, deep portion within the drive cam groove 12c and the driven cam groove 13c.

[0050] When the cam ball 14 moves from a shallow portion to a deep portion within the drive cam groove 12c and the driven cam groove 13c, the driven cam member 13 moves closer to (retracts from) the drive cam member 12 due to the biasing force of the compression coil spring 31a. Then, as the driven cam member 13 moves backward, the pressure plate 40 moves away from the output side friction plate 54 (pressure release state). As a result, the pressure contact between the input side friction plate 53 and the output side friction plate 54 is released, and the transition of the power connection / disconnection device S to the disconnected state is completed.

[0051] Next, the effects of this embodiment will be described. The pressing mechanism S1 constituting the power interrupter S of this embodiment is provided with a return means 30 for urging the movement of the ball cam 10 from the pressing state to the pressing release state. The return means 30 has a compression coil spring 31 a as a biasing member, one end of which is supported by the drive cam member 12 and the other end of which is supported by the driven cam member 13 .

[0052] With this configuration, the compression coil spring 31a is compressed in the pressed state and disposed obliquely with respect to the plate surface of the drive cam member 12 (see FIGS. 5 and 6). Then, the restoring force of the compression coil spring 31a quickly returns the drive cam member 12 to the disconnected state, the pressing force of the driven cam member 13 against the clutch mechanism S2 is released, and the transmission of power is released.

[0053] This makes it possible to more reliably release the pressure contact between the input side friction plate 53 and the output side friction plate 54 (disconnect). Therefore, when switching from four-wheel drive to two-wheel drive, unnecessary power transmission is suppressed, and a decrease in fuel efficiency can be suppressed.

[0054] In this embodiment, the drive-side spring accommodating portion 32 and the driven-side spring accommodating portion 33 are groove-shaped, but are not limited to this form. For example, the driving cam member 12 and the driven cam member 13 may be formed as elongated holes curved in an arc shape that penetrate through the plate thickness direction, and similar effects can be obtained. Furthermore, since the compression coil spring 31a can be installed after the driving cam member 12 and the driven cam member 13 are stacked together, the assembly workability can be improved.

[0055] Second Embodiment Next, a power interrupter S according to a second embodiment of the present invention will be described with reference to FIGS. In the description, the same elements as those in the first embodiment are denoted by the same reference numerals, and duplicated descriptions will be omitted. In the power interrupter S of this embodiment, the biasing member 31 constituting the return means 30 is changed from the compression coil spring 31a to a tension coil spring 31b.

[0056] In accordance with this change, the shapes of the drive-side spring end support portion 34 and the driven-side spring end support portion 35 have been changed to protrusions that hook the ends of the springs. Furthermore, the drive-side spring accommodating portion 32 and the driven-side spring accommodating portion 33 are not provided for each spring, but are each provided as a single recess capable of accommodating all of the tension coil springs 31b.

[0057] When the motor 21 rotates in the coupling direction, the drive cam member 12 rotates while pulling the tension coil spring 31b, and transitions to the pressing form. When transitioning from the pressing state to the pressing release state, the restoring force of the tension coil spring 31b along the direction of the rotation axis AX quickly returns the driving cam member 12 to the disconnected state, the pressing force of the driven cam member 13 against the clutch mechanism S2 is released, and the transmission of power is released, just like in the first embodiment. As described above, the power interrupter S of this embodiment can provide the same effects as those of the first embodiment.

[0058] Third Embodiment Next, a power interrupter S according to a third embodiment of the present invention will be described with reference to FIGS. In the description, the same elements as those in the first embodiment are denoted by the same reference numerals, and duplicated descriptions will be omitted. In the power interrupter S of this embodiment, the biasing member 31 constituting the return means 30 is changed from the compression coil spring 31a to a spiral spring 31c.

[0059] The spiral spring 31c is arranged so as to be wound around the driving cam groove 12c and the driven cam groove 13c at radially outer portions thereof, with the center of the spiral being concentric with the rotation axis AX. In accordance with this change, the shapes of the drive-side spring end support portion 34 and the driven-side spring end support portion 35 have been changed to protrusions that hook the ends of the springs. The spiral spring 31c has an inner end (one end) hooked and supported by the driving side spring end support portion 34, and an outer end (the other end) hooked and supported by the driven side spring end support portion 35.

[0060] When the pressing mechanism S1 changes from the pressing release state to the pressing state, the driven cam member 13 moves toward the front of the vehicle, and the outer end of the spiral spring 31c is pulled toward the front of the vehicle. When the driven cam member 13 is transformed from the pressing state to the pressing release state, the restoring force of the pulled outer end portion returning to the rear of the vehicle acts as a biasing force for moving the driven cam member 13 backward. As described above, the power interrupter S of this embodiment can provide the same effects as those of the first embodiment. [Explanation of symbols]

[0061] S1 Pressing mechanism S Power interrupter 12 Drive cam member (first disk member) 12c Drive cam groove (first groove) 13 Follower cam member (second disc member) 13c Follower cam groove (second groove) 14 Come Ball (Sphere) 31 biasing member 31a Compression coil spring (coil spring) 31b Tension coil spring (coil spring) 31c Spiral spring 55 Propulsion shaft AX Rotation Axis S2 clutch mechanism DF differential gear (final reduction gear)

Claims

1. a first disk member and a second disk member that are coaxially arranged, relatively rotatable, and movable in the direction of the rotation axis; a first groove formed in a first end surface of the first disk member facing the second disk member, extending in a circumferential direction, and having a depth gradually changing from the first end surface; a second groove formed in a second end surface of the second disk member facing the first disk member, extending in a circumferential direction, and having a depth gradually changing from the second end surface; a sphere that rolls between the first groove and the second groove; a biasing member having one end fixed to the first disk member and the other end fixed to the second disk member, and having a biasing force in a rotational direction of the rotation shaft; Equipped with The biasing member is a spiral spring. Clutch pressing mechanism.

2. Located between the propeller shaft and the final drive The clutch pressing mechanism according to claim 1.

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