JP2011231893A - Engagement device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an engagement device that can reduce a drag loss while suppressing increase of the number of part items.SOLUTION: A brake 20A includes: an engagement connection 40 which connects a fixed member 22 and a first friction member 31 so as to be relatively movable and relatively non-rotatable with respect to an axial line Ax in a process that the members are shifted to an engagement position at which an interval X is narrowed from a releasing position at which the interval X is expanded, and separates the members in a process that the members are shifted to the releasing position from the engagement position; a spline connection 35 which connects a movable member 21 and a second friction member 32 so as to be relatively non-rotatable with respect to each other; and a snap ring 37 which holds the first friction member 31 at the movable member 21 together with the second friction member 32 when the first friction member 31 is separated from the fixed member 22 in a process that the members are shifted to the releasing position from the engagement position.

Description

  The present invention relates to an engagement device for engaging a plurality of friction members with each other.

  A friction brake having a pair of friction members, one of which is fixed and the other rotating, and hydraulically operated, and an electromagnetic force that is provided between the other rotatable friction member and the rotation member and switches between coupling and releasing And a meshing clutch that operates at the same time, and when the rotation of the rotating member is allowed, the meshing clutch is released to suppress the relative rotation between the pair of friction members and reduce drag loss. An engagement device incorporated in is known (Patent Document 1). In the engaging device, when the rotation of the rotating member is prevented, the rotating member and the other friction member are first coupled by the meshing clutch, and then the friction member is engaged by the friction brake. In addition, Patent Documents 2 and 3 exist as prior art documents related to the present invention.

JP 2009-127840 A JP 2009-2405 A JP 2009-234541 A

  The engaging device of Patent Document 1 requires an urging member such as a drive source and a return spring for each of the friction brake and the meshing clutch, so that the number of parts increases and the size of the device increases.

  Accordingly, an object of the present invention is to provide an engagement device that can reduce drag loss while suppressing an increase in the number of parts.

  The engaging device according to the present invention includes a first member and a second member which are arranged on a common axis and arranged so that at least one of them can move in the axial direction so that the interval in the axial direction changes, A first friction member and a second friction member disposed between the first member and the second member, wherein the first friction member and the second friction are at an engagement position where the interval is narrowed; The members are engaged with each other to restrain the first member and the second member, and the first friction member and the second friction member are engaged at a release position where the distance is wider than the engagement position. In the engagement device that releases the joint and releases the restraint between the first member and the second member, in the process of moving the first member and the first friction member from the release position to the engagement position Non-relatively movable in the axial direction And a second coupling means for coupling the second member and the second friction member in a relatively non-rotatable state, and a first coupling means for coupling in a process of shifting from the engagement position to the release position. Holding the first friction member on the second member together with the second friction member when the first friction member is separated by the first coupling means during the transition from the engagement position to the release position. Means (claim 1).

  According to this engagement device, the first member and the first friction member are utilized by using the operation of shifting from the engagement position to the release position or from the release position to the engagement position where the distance between the first member and the second member is narrowed. Since the first coupling means switches between coupling and decoupling with the first member, it is not necessary to prepare a separate drive source for coupling and decoupling the first member and the first friction member. When the first friction member is separated from the first member in the process of transition from the engagement position to the release position, the second friction member and the second friction member hold the second friction member. Relative rotation is suppressed. Therefore, drag loss can be reduced while suppressing an increase in the number of parts.

  There is no particular limitation on the driving source for shifting from the engagement position to the release position or from the release position to the engagement position. For example, these transitions can be performed using hydraulic pressure. Moreover, as one aspect of the engagement device of the present invention, electromagnetic driving is used to shift the first member and the second member from the release position to the engagement position by narrowing the distance between the first member and the second member. And an urging member that urges at least one of the first member and the second member in a direction in which the interval is widened (Claim 2). According to this aspect, it is possible to shift from the release position to the engagement position using the electromagnetic force, and to shift from the engagement position to the release position using the biasing force of the biasing member.

  In one aspect of the present invention, the first coupling means includes a circumferentially arranged tooth portion provided on the first member and a circumferentially arranged tooth portion provided on the first friction member, and these The tooth portion is configured as a meshing coupling portion that meshes with each other in the process of shifting from the release position to the engagement position, and the tooth portion provided on the first member and the tooth provided on the first friction member A taper surface extending while inclining radially inward in the axial direction may be formed on at least one of the parts (claim 3). According to this aspect, even if there is a slight axial deviation between the first member and the first friction member before the first member and the first friction member are abutted and the respective tooth portions are engaged, When these members are abutted by the tapered surface that follows the tooth base, each member is aligned on the axis. As a result, the coupling operation is ensured and the reliability of the engagement device is improved.

  As described above, according to the engagement device of the present invention, it is not necessary to prepare a separate drive source for coupling and disconnecting the first member and the first friction member, and the first friction member is the first friction member. When separated from the member, the second friction member is held by the second member and the relative rotation between the first friction member and the second friction member is suppressed, so that drag loss can be reduced while suppressing an increase in the number of parts.

The figure which showed typically the drive device of the vehicle in which the engagement apparatus which concerns on one form of this invention was integrated. It is sectional drawing which showed the detail of the brake which concerns on a 1st form, Comprising: The figure which showed the state of the releasing position. It is sectional drawing which showed the detail of the brake which concerns on a 1st form, Comprising: The figure which showed the state of the engagement position. The perspective view which showed the 1st friction member. It is sectional drawing which showed the detail of the brake which concerns on a 2nd form, Comprising: The figure which showed the state of the releasing position. It is sectional drawing which showed the detail of the brake which concerns on a 2nd form, Comprising: The figure which showed the state of the engagement position. It is explanatory drawing which showed the state which looked at the cam mechanism from the radial direction outer side, Comprising: The figure which showed the state in which the phase of a pair of cam member corresponded. It is explanatory drawing which showed the state which looked at the cam mechanism from the radial direction outer side, Comprising: The figure which showed the state which the phase of a pair of cam member shifted | deviated by relative rotation. It is sectional drawing which showed the detail of the brake which concerns on a 3rd form, Comprising: The figure which showed the state of the releasing position. It is sectional drawing which showed the detail of the brake which concerns on a 3rd form, Comprising: The figure which showed the state of the engagement position. The figure which showed typically the other example of the drive device which can apply the brake which concerns on each form, Comprising: The figure which showed the 1st example. The figure which showed typically the other example of the drive device which can apply the brake which concerns on each form, Comprising: The figure which showed the 2nd example. It is sectional drawing which showed the detail of the clutch which concerns on another form, Comprising: The figure which showed the state of the releasing position. It is sectional drawing which showed the detail of the clutch which concerns on another form, Comprising: The figure which showed the state of the engagement position. Explanatory drawing which showed the other example of the meshing coupling | bond part.

(First form)
FIG. 1 schematically shows a vehicle drive device in which an engagement device according to an embodiment of the present invention is incorporated. The drive device 1A is a drive device applied to a so-called hybrid vehicle, and includes a first motor / generator 3 and a second motor / generator 4 in addition to the internal combustion engine 2 as drive sources. The power of the internal combustion engine 2 is input to the power split mechanism 7 via the input shaft 6. The power split mechanism 7A is configured as a single pinion type planetary gear mechanism having a sun gear S1, a ring gear R1, and a carrier C1 as rotational elements that can rotate differentially with each other. An output for transmitting power to the carrier C1 of the power split mechanism 7 via the input shaft 6, the first motor / generator 3 for the sun gear S1, and the drive gear (not shown) to the ring gear R1. The shafts 10 are connected to each other. A second motor / generator 4 is connected to the output shaft 10 via a transmission unit 11. Angle sensors 15 and 16 are provided on the motor shafts 13 and 14 for use in controlling the operation of the motor generators 3 and 4.

  The drive device 1A includes a fixed gear ratio mode in which the gear ratio of the power split mechanism 7 is fixed by locking the sun gear S1 to which the first motor / generator 3 is connected, and the rotation of the internal combustion engine 1 is decelerated, and the sun gear S1. Brake for switching between fixing and releasing the motor shaft 13 rotating integrally with the sun gear S1 to the case 18 in order to switch to a continuously variable transmission ratio mode in which the gear ratio of the power split mechanism 7 is changed steplessly by releasing the lock of 20A is provided. The engaging device according to the present embodiment is mounted on the driving device 1A as the brake 20A.

  2 and 3 are cross-sectional views showing details of the brake 20A. FIG. 2 shows the state of the release position, and FIG. 3 shows the state of the engagement position. The brake 20 </ b> A includes a movable member 21 and a fixed member 22 that are disposed on a common axis Ax. The movable member 21 is splined to the outer periphery of the motor shaft 13 while being allowed to move in the axis Ax direction within a predetermined range. Accordingly, the distance X between the movable member 21 and the fixed member 22 changes as the movable member 21 moves in the direction of the axis Ax. The motor shaft 13 is rotatably supported by the case 18 via a radial bearing 19.

  Movement of the movable member 21 to the side away from the fixed member 22 (left side in the figure) is restricted by a stopper (not shown). The movable member 21 is urged toward the side away from the fixed member 22 by the return spring 23, which is an urging member, that is, in the direction in which the interval X increases. The fixed member 22 also serves as an electromagnetic drive unit that draws the armature 21 a formed integrally with the movable member 21 by electromagnetic force, and is fixed to the case 18. The fixing member 22 includes an electromagnetic coil 25 that generates an electromagnetic force and a coil housing 26 that holds the electromagnetic coil 25 so as not to move. The coil housing 26 is formed with an inward flange portion 26a extending radially inward so as to approach the outer periphery of the motor shaft 13, and a pair of thrust bearings 27 are disposed on both sides of the inward flange portion 26a. Yes. The right thrust bearing 27 is positioned by a collar 28 mounted on the motor shaft 13, and the left thrust bearing 26 is positioned by a spring seat (not shown) that supports the return spring 23. Thereby, the thrust load generated when the motor shaft 13 rotates is received by the inward flange portion 26 a via the pair of thrust bearings 27.

  The brake 20 </ b> A further includes a first friction member 31 and a second friction member 32 arranged in a state of being sandwiched between the movable member 21 and the fixed member 22. Each of the friction members 31 and 32 has a hollow disk shape with a circular hole formed in the center, and each friction member 31 and 32 has an outer periphery of the hub portion 21b of the movable member 21 extending in the axis Ax direction. Is arranged. The first friction member 31 is disposed between the movable member 21 and the second friction member 32, and the second friction member 32 is disposed between the first friction member and the fixed member 22. The second friction member 32 is coupled to the movable member 21 by a spline coupling portion 35 in a state in which the second friction member 32 is relatively movable in the axis Ax direction and is not relatively rotatable. The spline coupling part 35 includes a tooth part 35a arranged on the outer periphery of the hub part 21b and a tooth part 35b arranged on the inner peripheral edge of the second friction member 32 and capable of meshing with the tooth part 35a. The movement of the second friction member 32 in the axis Ax direction is restricted by a snap ring 37 that is a retaining member attached to the outer periphery of the hub portion 21b.

  The first friction member 31 has a cylindrical protruding portion 38 extending from the outer peripheral portion thereof to the side parallel to the axis Ax direction and approaching the fixed member 22. The brake 20 </ b> A engages between the protrusion 38 and the fixing member 22 in order to connect the first friction member 31 to the fixing member 22 in the process of shifting from the release position of FIG. 2 to the engagement position of FIG. 3. Part 40 is provided. The meshing coupling portion 40 is provided at the distal end portion 38a of the protruding portion 38 and arranged in the circumferential direction, and the tooth portion 40b provided on the outer periphery of the fixing member 22 (coil housing 26) and meshed with the tooth portion 40a. Including. FIG. 4 is a perspective view showing the first friction member 31. As is clear from this figure, the tooth portion 40a formed on the protruding portion 38 is formed by machining a groove that crosses the distal end portion 38a in the thickness direction. As shown in FIGS. 2 and 3, the tooth portion 40 b provided in the fixing member 22 is formed with a tapered surface 41 that extends while inclining in the direction of the axis Ax. Thereby, even if there is some axial deviation between these members before the first friction member 31 and the fixing member 22 are abutted and the tooth portions 40a and 40b are engaged with each other, the tapered surface provided on the tooth portion 40b. When these members are abutted by 41, each member is aligned on the axis Ax. It is also possible to apply the same structure as the tapered surface 41 to the tooth portion 40a on the first friction member 31 side. Further, this structure can be provided on the tooth portion 40a instead of the tapered surface 41.

  In the release position shown in FIG. 2, the second friction member 32 is retained by the snap ring 37, and the first friction member 31 is held between the movable member 21 and the second friction member 32. The Therefore, the friction members 31 and 32 are held by the movable member 21 and are rotated, and relative rotation between the friction members 31 and 32 does not occur unless the change in the rotation speed of the movable member 21 is large. When power is supplied to the electromagnetic coil 25 to excite the brake 20A from the release position in FIG. 2, the movable member 21 integrated with the armature 21a is drawn toward the fixed member 22 by the magnetic force, and the interval X is increased. It narrows. Then, the protruding portion 38 of the first friction member 31 abuts against the fixed member 22, and the first friction member 31 and the fixed member 22 are coupled to each other in a state in which the first friction member 31 and the fixed member 22 are relatively movable in the axis Ax direction and are not relatively rotatable. Since the first friction member 31 is prevented from rotating when meshing by the meshing coupling portion 40 is started, the frictional force generated between these members while the first friction member 31 and the second friction member 32 rotate relative to each other. As a result, deceleration of the movable member 21 (motor shaft 13) starts. Further, when the movable member 21 moves in the direction of the axis Ax and the engagement of the engagement coupling portion 40 proceeds, the friction members 31 and 32 are sandwiched between the movable member 21 and the fixed member 22 by the electromagnetic force generated by the electromagnetic coil 25. Thereby, the frictional force generated between these members increases, the friction members 31 and 32 are engaged with each other, the rotation of the movable member 21 is stopped, and the engagement position shown in FIG.

  3, when the power supply to the electromagnetic coil 25 is stopped, the movable member 21 moves away from the fixed member 22 by the elastic force of the return spring 23, that is, in the direction in which the interval X increases. To start. As described above, the first friction member 31 is held by the movable member 21 together with the second friction member 32 by the second friction member 32 being prevented from coming off by the snap ring 37. Accordingly, since the first friction member 31 moves in the same direction by the movement of the movable member 21, the engagement of the engagement coupling portion 40 is released and the first friction member 31 is separated from the fixed member 22. And it moves to the release position of FIG.

  As described above, according to the brake 20A, the movement of the first friction member 31 and the fixing member 22 between the engagement position in FIG. 3 and the release position in FIG. 2 or from the release position to the engagement position is performed. Since coupling and decoupling are switched at the meshing coupling unit 40, it is not necessary to prepare a separate drive source for coupling and decoupling. When the first friction member 31 is separated from the fixed member 22 in the transition process from the engagement position to the release position, the snap ring 37 is held by the movable member 21 together with the second friction member 32. Therefore, the first friction member 31 is movable at the release position. Even if the member 21 rotates, the relative rotation between the first friction member 31 and the second friction member 32 is suppressed. Therefore, drag loss can be reduced while suppressing an increase in the number of parts. In this embodiment, the fixed member 22 corresponds to the first member according to the present invention, the movable member 21 corresponds to the second member according to the present invention, and the snap ring 37 corresponds to the holding means according to the present invention. Further, the meshing coupling part 40 functions as a first coupling means according to the present invention, and the spline coupling part 35 functions as a second coupling means according to the present invention.

(Second form)
Next, a second embodiment of the present invention will be described with reference to FIGS. In the following, the same reference numerals are attached to the same members as those in the first embodiment, and the description thereof is omitted. 5 and 6 are cross-sectional views showing details of the brake as the engagement device according to the second embodiment, FIG. 5 shows the state of the release position, and FIG. 6 shows the state of the engagement position. .

  The brake 20B is applied to the drive device 1A (FIG. 1) similarly to the first embodiment. The brake 20B is provided with a cam mechanism 50 for assisting an engaging force by an electromagnetic force or for achieving a self-locking for holding the engagement without the electromagnetic force. The cam mechanism 50 includes a pair of cam members 51 and 52 arranged in the direction of the axis Ax, and a cam ball 53 interposed between the cam members 51 and 52. V-shaped grooves 55 and 56 for holding the cam balls 53 are formed on the opposing surfaces of the cam members 51 and 52.

  7 and 8 are explanatory views showing a state in which the cam mechanism 50 is viewed from the outside in the radial direction. As shown in these drawings, each V-shaped groove 55, 56 is formed in a V shape, and the depth is gradually reduced with respect to the rotation direction of the motor shaft 13 (upward or downward in the figure). Has been. As shown in FIGS. 5 and 6, the fixed cam member 51 located on the left side of the pair of cam members 51 and 52 is fixed to the motor shaft 13 and rotates integrally with the motor shaft 13. The other movable cam member 52 is combined with the fixed cam member 51 so that it can rotate relative to the fixed cam member 51 and the motor shaft 13 and can move in the direction of the axis Ax. When the pair of cam members 51 and 52 change from the state in which the phases shown in FIGS. 5 and 7 coincide with each other to the state in FIG. Changes to a shallow position of the V-shaped grooves 55 and 56, so that a thrust F that moves the movable cam member 52 away from the fixed cam member 51 is generated. The thrust F can be used to assist the engagement force due to electromagnetic force, and the torque input to the fixed cam member 51 and the geometrical conditions of the cam ball 53 and the V-shaped grooves 55 and 56 are appropriately set. By doing so, self-locking can be realized.

  The brake 20 </ b> B has a fixed member 58 disposed on the common axis Ax with the movable cam member 52. As the movable cam member 52 moves in the direction of the axis Ax, the interval X between the movable cam member 52 and the fixed member 53 changes. The movable cam member 52 is biased by a return spring 59 that is a biasing member on the side away from the fixed member 58, that is, on the side where the interval X is widened. The fixed member 58 is also fixed to the case 18 as an electromagnetic drive unit that pulls the armature 52a integral with the movable cam member 52 by electromagnetic force. The fixing member 58 includes an electromagnetic coil 61 that generates electromagnetic force and a coil housing 62 that holds the electromagnetic coil 61 so as not to move. The coil housing 62 is formed with an inward flange portion 62 a extending radially inward so as to approach the outer periphery of the motor shaft 13. The inward flange portion 62 a receives the thrust load generated when the motor shaft 13 rotates through the thrust bearing 27 as in the first embodiment.

  The brake 20 </ b> B further includes a first friction member 63 and a second friction member 64 that are disposed between the movable cam member 51 and the fixed member 58. As in the first embodiment, the main parts of the friction members 63 and 64 are formed in a hollow disk shape with a circular hole formed in the center. The first friction member 63 is disposed between the second friction member 64 and the fixed member 58, and the outer periphery of the first friction member 63 abuts against the inner peripheral surface of the protrusion 66 that protrudes from the second friction member 64 in the axis Ax direction. It is supported. The second friction member 64 is coupled to the fixed member 58 by a spline coupling portion 67 so as to be relatively movable in the axis Ax direction and not to be relatively rotatable. The spline coupling portion 67 includes a tooth portion 67a arranged on the outer periphery of the coil housing 62 and a tooth portion 67b arranged at the tip end portion of the protruding portion 66 of the second friction member 64 and capable of meshing with the tooth portion 67a. The movement of the second friction member 64 in the axis Ax direction is restricted by a stopper 68 fixed to the inner peripheral surface of the case 18.

  The brake 20B is coupled between the first friction member 63 and the movable cam member 52 in order to couple the first friction member 63 to the movable cam member 52 in the process of shifting from the release position of FIG. 5 to the engagement position of FIG. An intervening meshing coupling part 70 is provided. The meshing coupling part 70 includes a tooth part 70 a arranged on the inner peripheral edge of the first friction member 63 and a tooth part 70 b provided on the outer periphery of the hub part 52 b of the movable cam member 52 and capable of meshing with the tooth part 70 a. Further, the tooth portion 70b provided on the movable cam member 52 is formed with a tapered surface 71 extending while inclining in the direction of the axis Ax, and the first friction member is formed by the tapered surface 71 as in the first embodiment. The shaft misalignment between the movable cam member 52 and the movable cam member 52 can be eliminated when the meshing coupling portion 70 is meshed. A structure similar to that of the tapered surface 71 can be applied to the tooth portion 70 a, and the structure can be provided on the tooth portion 70 a instead of the tapered surface 71.

  In the release position shown in FIG. 5, the second friction member 64 is retained by the stopper 68, and the first friction member 63 is held between the fixed member 58 and the second friction member 64. At the same time, the first friction member 63 abuts against the protrusion 66 of the second friction member 64 and is supported. Therefore, the friction members 63 and 64 are kept stationary together with the fixing member 58, and relative rotation between the friction members 63 and 64 does not occur. When electric power is supplied to the electromagnetic coil 61 and excited to operate the brake 20B from the release position of FIG. 5, the movable cam member 52 integral with the armature 52a is attracted to the fixed member 58 side by the magnetic force, and the interval X Narrows. Then, the movable cam member 52 comes into contact with the first friction member 63, and the first coupling member 70 is coupled to the first friction member 63 and the movable cam member 52 so as to be relatively movable in the direction of the axis Ax but not relatively rotatable. Since the first friction member 63 rotates integrally with the movable cam member 52 when the engagement by the engagement coupling portion 70 is started, the frictional force generated between these members while the first friction member 63 and the second friction member 64 rotate relative to each other. As a result, deceleration of the movable cam member 52 (motor shaft 13) starts. Further, when the movable cam member 52 moves in the direction of the axis Ax and the engagement of the engagement coupling portion 70 proceeds, the friction members 63 and 64 are sandwiched between the movable cam member 52 and the fixed member 58 by the electromagnetic force generated by the electromagnetic coil 61. It is. Then, relative torque is generated between the cam members 51 and 52 by the torque input to the fixed cam member 51 of the cam mechanism 50, and the force for sandwiching the friction members 63 and 64 is assisted by the thrust obtained thereby. As a result, the frictional force generated between these members increases, the friction members 63 and 64 are engaged with each other, and the rotation of the movable cam member 52 is stopped to shift to the engagement position in FIG.

  6, when the power supply to the electromagnetic coil 61 is stopped, the movable cam member 52 is moved away from the fixed member 58 by the elastic force of the return spring 59, that is, in the direction in which the interval X is widened. Start moving. However, when the cam mechanism 50 has a self-lock function, even if the power supply to the electromagnetic coil 61 is stopped, the cam mechanism 50 is maintained in the engaged position unless the self-lock is released. When the opposite direction torque is input to the fixed cam member 51 and the self-lock is released, the movable cam member 52 starts moving in the axis Ax direction by the elastic force of the return spring 59. As described above, since the second friction member 64 is prevented from coming off by the stopper 68, the engagement of the engagement coupling portion 40 is released by the movement of the movable cam member 52 in the axis Ax direction, and the first friction member 63 is moved to the movable cam. It is separated from the member 52. And it moves to the release position of FIG.

  As described above, according to the brake 20B, as in the first embodiment, the first friction is performed using the movement from the engagement position in FIG. 6 to the release position in FIG. 5 or from the release position to the engagement position. Since the coupling and decoupling of the member 63 and the movable cam member 52 are switched by the meshing coupling portion 70, it is not necessary to prepare a separate drive source for the coupling and decoupling. When the first friction member 63 is separated from the movable cam member 52 in the process of transition from the engagement position to the release position, the stopper 18 holds the second friction member 64 together with the second friction member 64. The relative rotation between the first friction member 63 and the second friction member 64 is suppressed. Therefore, drag loss can be reduced while suppressing an increase in the number of parts. In this embodiment, the movable cam member 52 corresponds to the first member according to the present invention, the fixed member 58 corresponds to the second member according to the present invention, and the stopper 68 corresponds to the holding means according to the present invention. Further, the meshing coupling part 70 functions as a first coupling means according to the present invention, and the spline coupling part 67 functions as a second coupling means according to the present invention.

(Third form)
Next, a third embodiment of the present invention will be described with reference to FIGS. In the following, the same reference numerals are attached to the same members as those in the first embodiment, and the description thereof is omitted. 9 and 10 are cross-sectional views showing details of the brake as the engagement device according to the third embodiment. FIG. 9 shows the state of the release position, and FIG. 10 shows the state of the engagement position. .

  The brake 20C is applied to the drive device 1A (FIG. 1) similarly to the first embodiment, and is provided with a cam mechanism 80 similar to the cam mechanism 50 according to the second embodiment. The cam mechanism 80 has a pair of cam members 81 and 82 arranged in the direction of the axis Ax, and a cam ball 83 interposed between the cam members 81 and 82. V-shaped grooves 85 and 86 for holding the cam balls 83 are formed on the opposing surfaces of the cam members 81 and 82. These V-shaped grooves 85 and 86 have the same shape as that shown in FIGS.

  Of the pair of cam members 81, 82, the fixed cam member 81 located on the left side of the figure is fixed to the motor shaft 13 and rotates integrally with the motor shaft 13. The other movable cam member 82 is combined with the fixed cam member 81 so as to be able to rotate relative to the fixed cam member 81 and the motor shaft 13 and to move in the direction of the axis Ax. The cam mechanism 80 also has the same function as described above. That is, the cam mechanism 80 can generate a thrust force that moves the movable cam member 52 away from the fixed cam member 51 using the relative rotation between the cam members 81 and 82. The thrust can be used to assist the engaging force by the electromagnetic force, and the torque input to the fixed cam member 81 and the geometric conditions of the cam ball 83 and the V-shaped grooves 85 and 86 are appropriately determined. Self-locking can be realized by setting.

  The brake 20 </ b> C has a fixed member 88 disposed on the common axis Ax with the movable cam member 82. As the movable cam member 82 moves in the direction of the axis Ax, the interval X between the movable cam member 82 and the fixed member 88 changes. The movable cam member 82 is urged by a return spring 89, which is an urging member, on the side away from the fixed member 88, that is, on the side where the interval X increases. The fixed member 88 also serves as an electromagnetic drive unit that draws the armature 82a integral with the movable cam member 52 by electromagnetic force, and is fixed to the case 18. The fixing member 88 includes an electromagnetic coil 91 that generates an electromagnetic force and a coil housing 92 that holds the electromagnetic coil 91 so as not to move. The coil housing 92 is formed with an inward flange portion 92 a extending radially inward so as to approach the outer periphery of the motor shaft 13. The inward flange portion 92 a receives the thrust load generated when the motor shaft 13 rotates through the thrust bearing 27 as in the first embodiment. The fixed member 88 is coupled to the base of the inward flange portion 92a and has a cylindrical protrusion 92b extending from the base toward the side approaching the movable cam member 82 along the axis Ax direction. .

  The brake 20 </ b> C further includes a first friction member 93 and a second friction member 94 that are disposed between the movable cam member 82 and the fixed member 88. As in the first embodiment, the main parts of the friction members 93 and 94 are formed in a hollow disk shape in which a circular hole is formed in the center. The first friction member 93 is disposed between the second friction member 94 and the fixed member 88, and the second friction member 94 is disposed between the movable cam member 82 and the first friction member 93. The friction members 93 and 94 are held on the outer periphery of the protruding portion 92 b of the fixing member 88. The second friction member 94 is coupled to the fixed member 88 (projecting portion 92b) by a spline coupling portion 97 so as to be relatively movable in the direction of the axis Ax but not to be relatively rotatable. The spline coupling part 97 includes a tooth part 97a arranged on the outer periphery of the projecting part 92b and a tooth part 97b arranged on the inner peripheral edge of the second friction part 94 and capable of meshing with the tooth part 97a. The movement of the second friction member 94 in the axis Ax direction is restricted by a snap ring 98 that is a retaining member attached to the outer periphery of the protrusion 92b.

  The brake 20C connects the first friction member 93 to the movable cam member 82 in the process of shifting from the release position of FIG. 9 to the engagement position of FIG. An intervening meshing coupling part 100 is provided. The meshing coupling part 100 includes a tooth part 100a arranged on the outer peripheral edge of the first friction member 93 and a tooth part 100b provided on the outer peripheral end part 82b of the movable cam member 82 and capable of meshing with the tooth part 100a. Further, the tooth portion 100b provided on the movable cam member 82 is formed with a tapered surface 101 extending while being inclined in the direction of the axis Ax, and the first friction member is formed by the tapered surface 101 as in the first embodiment. The misalignment of the movable cam member 82 and the movable cam member 82 can be eliminated when the meshing coupling portion 100 is meshed. Note that a structure similar to that of the tapered surface 101 can be applied to the tooth portion 100 a, and the structure can be provided on the tooth portion 100 a instead of the tapered surface 101.

  The brake 20C operates in the same manner as the brake 20B according to the second embodiment. That is, in the release position shown in FIG. 9, the second friction member 94 is prevented from coming off by the snap ring 98, and the first friction member 93 is sandwiched between the fixed member 88 and the second friction member 94. Retained. Therefore, the friction members 93 and 94 are kept stationary together with the fixing member 58, and relative rotation between the friction members 93 and 94 does not occur. When electric power is supplied to the electromagnetic coil 91 and excited to operate the brake 20C from the release position of FIG. 9, the movable cam member 82 integrated with the armature 82a is attracted to the fixed member 88 side by the magnetic force, and the interval X Narrows. Then, the movable cam member 82 comes into contact with the first friction member 93, and the first friction member 93 and the movable cam member 82 are coupled to each other in a state in which the first friction member 93 and the movable cam member 82 are relatively movable in the axis Ax direction and are not relatively rotatable. When the engagement by the engagement coupling portion 100 is started, the first friction member 93 rotates integrally with the movable cam member 82. Therefore, the frictional force generated between these members while the first friction member 93 and the second friction member 94 rotate relative to each other. As a result, deceleration of the movable cam member 82 (motor shaft 13) starts. Further, when the movable cam member 82 moves in the direction of the axis Ax and the engagement of the engagement coupling portion 100 proceeds, the friction members 93 and 94 are sandwiched between the movable cam member 82 and the fixed member 88 by the electromagnetic force generated by the electromagnetic coil 91. It is. The torque input to the fixed cam member 81 of the cam mechanism 80 causes relative rotation between the cam members 81 and 82, and the thrust that is obtained thereby assists the force for sandwiching the friction members 93 and 94. As a result, the frictional force generated between these members is increased, the friction members 93 and 94 are engaged with each other, and the rotation of the movable cam member 82 is stopped to shift to the engagement position in FIG.

  When the power supply to the electromagnetic coil 91 is stopped in the state of the engagement position in FIG. 10, the movable cam member 82 is moved away from the fixed member 88 by the elastic force of the return spring 89, that is, in the direction in which the interval X is widened. Start moving. However, when the cam mechanism 80 has a self-lock function, even if the power supply to the electromagnetic coil 91 is stopped, the cam mechanism 80 is maintained in the engaged position unless the self-lock is released. When the opposite direction torque is input to the fixed cam member 81 and the self-lock is released, the movable cam member 82 starts moving in the direction of the axis Ax by the elastic force of the return spring 89. As described above, since the second friction member 94 is prevented from coming off by the snap ring 98, the engagement of the engagement coupling portion 100 is released by the movement of the movable cam member 82 in the axis Ax direction, and the first friction member 93 is movable. The cam member 82 is separated. And it moves to the release position of FIG.

  As described above, according to the brake 20C, as in the first embodiment, the first friction is performed using the movement from the engagement position in FIG. 10 to the release position in FIG. 9 or from the release position to the engagement position. Since the coupling and decoupling of the member 93 and the movable cam member 82 are switched by the meshing coupling portion 100, it is not necessary to prepare a separate drive source for the coupling and decoupling. When the first friction member 93 is separated from the movable cam member 82 in the transition process from the engagement position to the release position, the snap ring 89 holds the second friction member 94 together with the second friction member 94. The relative rotation between the first friction member 93 and the second friction member 94 is suppressed. Therefore, drag loss can be reduced while suppressing an increase in the number of parts. In this embodiment, the movable cam member 82 corresponds to the first member according to the present invention, the fixed member 88 corresponds to the second member according to the present invention, and the snap ring 98 corresponds to the holding means according to the present invention. Further, the meshing coupling part 100 functions as a first coupling means according to the present invention, and the spline coupling part 97 functions as a second coupling means according to the present invention.

(Other forms)
However, this invention is not limited to the said form, It can implement with a various form within the range of the summary of this invention. The brakes 20A to 20C as the engagement devices of the above embodiments are applied to the drive device 1A shown in FIG. 1, but there is no particular limitation on the application targets. 11 and 12 are diagrams schematically showing another example of a drive device to which the brakes 20A to 20C can be applied. In the following, the same members as those in FIG.

  The drive device 1B according to the first example shown in FIG. 11 is a drive device applied to a hybrid vehicle. The power split mechanism 7B provided in the drive device 1B is configured by combining two sets of planetary gear mechanisms 8a and 8b. One first planetary gear mechanism 8a is configured as a single pinion type planetary gear mechanism, and includes a sun gear S21, a ring gear R21, and a carrier C21 as rotational elements that can rotate differentially with respect to each other. The other second planetary gear mechanism 8b is configured as a double pinion type planetary gear mechanism, and includes a sun gear S22, a ring gear R22, and a carrier C22 as rotational elements that can rotate differentially with respect to each other. In the power split mechanism 7B, the carrier C21 of the first planetary gear mechanism 8a and the ring gear R22 of the second planetary gear mechanism 8b are coupled, and the ring gear R21 of the first planetary gear mechanism 8a and the second planetary gear mechanism 8b It is configured by being connected to the carrier C22. The internal combustion engine 2 is connected to the carrier C21, the first motor / generator 3 is connected to the sun gear S1, and the output shaft 10 is connected to the carrier C22. One of the brakes 20A to 20C described above is provided between the sun gear S22 and the case 18 in order to selectively realize the fixed gear ratio mode and the continuously variable gear ratio mode by switching between fixing and releasing the sun gear S22. Can do. The drive device 1B is provided with an angle sensor 17 for detecting the rotational position of the sun gear S22 of the power split mechanism 7B.

  The drive apparatus 1C according to the second example shown in FIG. 12 is a drive apparatus applied to a hybrid vehicle. The driving devices 1A and 1B described above are for a vehicle having an FR layout, whereas the driving device 1C is for a vehicle having an FF layout. The power split mechanism 7C provided in the drive device 1C is configured as a single pinion type planetary gear mechanism having a sun gear S31, a ring gear R32, and a carrier C31, which are rotational elements capable of differentially rotating with each other. The internal combustion engine 2 is connected to the carrier C31 of the power split mechanism 7C, the first motor / generator 3 is connected to the sun gear S31, and the output unit 5 is connected to the ring gear R31. The output unit 5 rotates integrally with the ring gear R31, a first intermediate gear 5b that meshes with the output gear 5a, and rotates integrally with the first intermediate gear 5b and meshes with the ring gear 9a of the differential gear 9. Second intermediate gear 5c. In order to selectively realize the fixed gear ratio mode and the continuously variable gear ratio mode by switching between fixing and releasing the sun gear S31 of the power split mechanism 7C, the brakes 20A to 20C described above are interposed between the sun gear S31 and the case 18. Either can be provided. The power of the second motor / generator 4 is transmitted to the output unit 5 via a speed change mechanism 12 configured as a planetary gear mechanism. The speed change mechanism 12 includes a sun gear S32 connected to the second motor / generator 4, a ring gear R32 coupled integrally with the output gear 5a, and a carrier C32 fixed to the case 18.

  In each of the above embodiments, the engaging device of the present invention is implemented as a brake. However, the engaging device of the present invention can also be implemented as a clutch for intermittently transmitting power between two rotating elements. 13 and 14 are cross-sectional views showing the main part of another embodiment in which the engaging device of the present invention is implemented as a clutch. FIG. 13 shows the state of the released position, and FIG. 14 shows the state of the engaged position. Show.

  As shown in FIGS. 13 and 14, the clutch 120 is configured as an electromagnetic clutch, and is mounted between the input shaft 105 and the output shaft 106 of the power transmission device that rotates around a common axis Ax1. Each of the input shaft 105 and the output shaft 106 is rotatably supported by the case 107 via a bearing (not shown). The clutch 120 is provided with a cam mechanism 130 in order to assist the engagement force by the electromagnetic force or to achieve self-locking that maintains the engagement without the electromagnetic force. The cam mechanism 130 includes a pair of cam members 131 and 132 arranged in the direction of the axis Ax1, and a cam ball 133 interposed between the cam members 131 and 132. V-shaped grooves 135 and 136 for holding the cam balls 133 are formed on the opposing surfaces of the cam members 131 and 132. These V-shaped grooves 135 and 136 have the same shape as that shown in FIGS.

  Of the pair of cam members 131 and 132, the fixed cam member 131 located on the left side of the figure is fixed to the input shaft 105 and rotates integrally with the input shaft 105. The other movable cam member 132 is combined with the fixed cam member 131 so as to be able to rotate relative to the fixed cam member 131 and the input shaft 105 and to move in the direction of the axis Ax1. As the movable cam member 132 moves in the direction of the axis Ax1, the interval X1 between the movable cam member 132 and the output shaft 106 changes. The movable cam member 132 is urged by a return spring 137 that is an urging member on the side away from the output shaft 106, that is, on the side where the interval X1 is widened.

  The cam mechanism 130 also has the same function as the above-described mechanisms. That is, the cam mechanism 130 can generate a thrust force that moves the movable cam member 132 in a direction away from the fixed cam member 131 using the relative rotation between the cam members 131 and 132. The thrust can be used to assist the engagement force by the electromagnetic force, and the torque input to the fixed cam member 131 and the geometric conditions of the cam ball 133 and the V-shaped grooves 135 and 136 can be appropriately set. Self-locking can be realized by setting. The clutch 120 includes an electromagnetic drive unit 138 that draws the armature 132a integrated with the movable cam member 132 toward the side closer to the output shaft 106 in the direction of the axis Ax1 using electromagnetic force. The electromagnetic drive unit 138 includes an electromagnetic coil 141 that generates electromagnetic force, and a coil housing 142 that holds the electromagnetic coil 141 so as not to move and is fixed to the case 107.

  The clutch 120 further includes a first friction member 143 and a second friction member 144 disposed between the movable cam member 132 and the output shaft 106. Similar to the above-described embodiments, the main portions of the friction members 143 and 144 are formed in a hollow disk shape in which a circular hole is formed in the central portion. The friction members 143 and 144 are held on the outer periphery of the output shaft 106. The second friction member 144 is coupled to the output shaft 106 by a spline coupling portion 147 so as to be relatively movable in the direction of the axis Ax1 and not relatively rotatable. The spline coupling portion 147 includes a tooth portion 147a arranged on the outer periphery of the output shaft 106 and a tooth portion 147b arranged on the inner peripheral edge of the second friction member 144 and capable of meshing with the tooth portion 147a. The movement of the second friction member 144 in the direction of the axis Ax1 is restricted by a snap ring 148 that is a retaining member attached to the outer periphery of the output shaft 106. Further, the movement of the first friction member 143 toward the coil housing 142 is restricted by the stopper 149 so as not to contact the coil housing 142 of the electromagnetic drive unit 138.

  The clutch 120 is coupled between the first friction member 143 and the movable cam member 132 in order to couple the first friction member 143 to the movable cam member 132 in the process of shifting from the release position of FIG. 13 to the engagement position of FIG. An intervening meshing joint 150 is provided. The meshing coupling part 150 includes a tooth part 150a arranged on the outer peripheral edge of the first friction member 143 and a tooth part 150b provided on the outer peripheral end part 132b of the movable cam member 132 and capable of meshing with the tooth part 150a. Further, the tooth portion 150b provided on the movable cam member 132 is formed with a tapered surface 151 that extends while inclining in the direction of the axis Ax1, and the tapered surface 151 causes the first friction member 143 to be the same as the above-described embodiments. And the misalignment of the movable cam member 132 can be eliminated when the meshing coupling portion 150 is meshed. Note that the same structure as the tapered surface 151 can be applied to the tooth portion 150 a, and the structure can be provided on the tooth portion 150 a instead of the tapered surface 151.

  In the release position shown in FIG. 13, the second friction member 144 is retained by the snap ring 148, and the first friction member 143 is held between the stopper 149 and the second friction member 144. . Therefore, the friction members 143 and 144 are rotated with the output shaft 106, and relative rotation between the friction members 143 and 144 does not occur. When electric power is supplied to the electromagnetic coil 141 and excited at the release position in FIG. 13, the movable cam member 132 integrated with the armature 132a is drawn toward the output shaft 106 by the magnetic force, and the interval X1 is narrowed. Then, the movable cam member 132 comes into contact with the first friction member 143, and the first friction member 143 and the movable cam member 132 are coupled to each other in a state in which the first friction member 143 and the movable cam member 132 are relatively movable in the axis Ax1 direction and are not relatively rotatable. Since the first friction member 143 rotates integrally with the movable cam member 132 (the input shaft 105) when the engagement by the engagement coupling portion 150 is started, these members are rotated while the first friction member 143 and the second friction member 144 are relatively rotated. The differential rotation between the input shaft 105 and the output shaft 106 starts to decrease due to the frictional force generated therebetween. Further, when the movable cam member 132 moves in the direction of the axis Ax1 and the engagement of the engagement coupling portion 150 proceeds, the second friction member 144 is brought into contact with the stopper 149 by the electromagnetic force generated by the electromagnetic coil 91. Is sandwiched between the first friction member 143 and the movable cam member 132. Then, relative torque is generated between the cam members 131 and 132 by the torque input to the fixed cam member 131 of the cam mechanism 130, and the force for sandwiching the second friction member 144 is assisted by the thrust obtained thereby. As a result, the frictional force generated between these members increases, and the friction members 143 and 144 are engaged with each other, so that the movable cam member 132 (output shaft 105) and the output shaft 106 can rotate together as shown in FIG. Transition to the engaged position.

  When the power supply to the electromagnetic coil 141 is stopped in the engagement position of FIG. 14, the movable cam member 132 is moved away from the output shaft 106 by the elastic force of the return spring 137, that is, in the direction in which the interval X1 is widened. Start moving. However, when the cam mechanism 130 has a self-lock function, even if the power supply to the electromagnetic coil 141 is stopped, the cam mechanism 130 is maintained in the engaged position unless the self-lock is released. When the torque in the opposite direction is input to the fixed cam member 131 and the self-lock is released, the movable cam member 132 starts to move in the direction of the axis Ax1 by the elastic force of the return spring 137. As described above, since the second friction member 144 is prevented from coming off by the snap ring 148, the engagement of the engagement coupling portion 150 is released by the movement of the movable cam member 132 in the axis Ax1 direction, and the first friction member 143 is movable. The cam member 132 is separated. And it moves to the release position of FIG.

  As described above, according to the clutch 120, as in each of the above-described embodiments, the first friction member is utilized by using the movement from the engagement position in FIG. 14 to the release position in FIG. 13 or from the release position to the engagement position. Since the coupling and decoupling of 143 and the movable cam member 132 are switched by the meshing coupling unit 150, it is not necessary to prepare a separate drive source for the coupling and decoupling. When the first friction member 143 is separated from the movable cam member 132 in the transition process from the engagement position to the release position, the snap ring 148 holds the second friction member 144 together with the second friction member 144. The relative rotation between the first friction member 143 and the second friction member 144 is suppressed. Therefore, drag loss can be reduced while suppressing an increase in the number of parts. In this embodiment, the movable cam member 132 corresponds to the first member according to the present invention, the output shaft 107 corresponds to the second member according to the present invention, and the snap ring 148 corresponds to the holding means according to the present invention. Further, the meshing coupling part 150 functions as a first coupling means according to the present invention, and the spline coupling part 147 functions as a second coupling means according to the present invention.

  The meshing coupling portions 40, 70, 100 applied to the brakes 20A to 20C and the clutch 120 according to the above embodiments are not limited to the configuration shown in FIG. For example, these coupling portions can be changed to the form shown in FIG. 15 to function as the first coupling portion according to the present invention. FIG. 15 is an explanatory view showing another form of the meshing coupling portion. The coupling portion Co of this form is configured as a spline coupling portion that is chamfered so that the tooth portions Tp that mesh with each other taper toward the end in the direction of the axis Ax ′. Even if the coupling portion Co is replaced with the coupling portion 40 or the like of each of the above forms, the same effects as those of the above embodiments can be obtained.

  In each of the above embodiments, the spline coupling portions 35, 67, 97, and 147 that allow the second friction member to move in the axial direction are used as the second coupling means. However, the second friction member moves in the axial direction. It is not essential to implement the present invention. Therefore, the second friction member may be fixed to the second member using a coupling means such as welding. Thus, when the 2nd friction member is fixed to the 2nd member, the 2nd friction member will also serve as a holding means concerning the present invention.

  The brakes 20 </ b> A to 20 </ b> C and the clutch 120 use electromagnetic force as their driving force source, but the present invention can also be implemented in a form driven by hydraulic or other driving sources.

20A Brake (engagement device)
21 Movable member (second member)
22 Fixed member (first member, electromagnetic drive)
23 Return spring (biasing means)
31 1st friction member 32 2nd friction member 35 Spline coupling | bond part (2nd coupling means)
37 Snap ring (holding means)
40 Intermeshing coupling part (first coupling means)
41 Tapered surface 20B Brake (engagement device)
52 Movable cam member (first member)
58 Fixed member (second member, electromagnetic drive)
59 Return spring (biasing means)
63 1st friction member 64 2nd friction member 67 Spline coupling | bond part (2nd coupling means)
68 Stopper (holding means)
70 meshing joint (first coupling means)
71 Tapered surface 20C Brake (engagement device)
82 Movable cam member (first member)
88 Fixed member (second member, electromagnetic drive)
89 Return spring 93 First friction member 94 Second friction member 97 Spline connecting portion (second connecting means)
98 Snap ring (holding means)
100 meshing joint (first coupling means)
101 Tapered surface 106 Output shaft (second member)
120 Clutch (engagement device)
132 Movable cam member (first member)
138 Electromagnetic drive portion 143 First friction member 144 Second friction member 147 Spline coupling portion (second coupling means)
148 Snap ring (holding means)
150 meshing joint (first coupling means)
151 Tapered surface Ax, Ax1 Axis Co Coupling part X, X1 spacing

Claims (3)

A first member and a second member which are arranged on a common axis and arranged so that at least one of them can move in the axial direction so that an interval in the axial direction changes, the first member and the second member A first friction member and a second friction member disposed between the first friction member and the first friction member and the second friction member engaged with each other at an engagement position where the distance is narrowed. The first member and the second member are constrained, and the first friction member and the second friction member are disengaged at a release position where the distance is wider than the engagement position. In the engagement device for releasing the restraint between the member and the second member,
The first member and the first friction member are coupled to each other in a state in which the first member and the first friction member are relatively movable in the axial direction and are not relatively rotatable in the process of moving from the release position to the engagement position, and from the engagement position to the release position. A first coupling means for separating in the process of moving to
A second coupling means for coupling the second member and the second friction member in a relatively non-rotatable state;
Holding the first friction member on the second member together with the second friction member when the first friction member is separated by the first coupling means during the transition from the engagement position to the release position. Means,
An engagement device comprising:   Using an electromagnetic force to narrow the distance between the first member and the second member to shift from the release position to the engagement position; and at least one of the first member and the second member The engagement device according to claim 1, further comprising a biasing member that biases one side in a direction in which the interval widens. The first coupling means includes a circumferentially arranged tooth portion provided on the first member and a circumferentially arranged tooth portion provided on the first friction member, and these tooth portions are disposed at the release position. Configured as a meshing coupling portion that meshes with each other in the process of shifting from the engagement position to the engagement position,
The taper surface which inclines inclining toward the said axial direction is formed in at least one of the said tooth part provided in the said 1st member, and the said tooth part provided in the said 1st friction member. Or the engagement apparatus of 2.

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