JP2019217880A - Coupling device - Google Patents

Abstract

To provide a coupling device which can inhibit vibration.SOLUTION: A coupling device includes: a first member; a second member which rotates relative to the first member; a movable member which is supported by the first member so as to be slidable in a radial direction that is an orthogonal direction relative to a rotation axis of the second member; a driving member disposed at the outer side of the movable member in the radial direction; a first elastic member for pressing the movable member to the driving member; and a second elastic member for pressing the movable member to the second member.SELECTED DRAWING: Figure 20

Description

  The present invention relates to a coupling device.

  In an electric vehicle or a hybrid vehicle, wheels are driven by the power of a motor. When large power is transmitted to the wheel only by the motor, the size of the motor and peripheral devices increases. For this reason, a reduction mechanism is often combined with a motor. Patent Literatures 1 and 2 disclose examples of an in-wheel motor having a transmission mechanism. The efficiency of the in-wheel motors of Patent Literatures 1 and 2 is improved by realizing a first shift state and a second shift state in which the torque of the output shaft is smaller than that of the first shift state.

JP 2012-51540 A JP-A-2014-66320

  By the way, in a motorized vehicle, a brake and a clutch that do not use high-pressure oil pressure are required instead of a wet multi-plate clutch. The engagement type brake and clutch have backlash at the time of engagement. For this reason, vibration may occur at the time of switching between driving and regeneration of the electric vehicle.

  The present invention has been made in view of the above problems, and has as its object to provide a connecting device that can suppress vibration.

  In order to achieve the above object, a connecting device according to an embodiment of the present disclosure includes a first member, a second member that rotates with respect to the first member, and a diameter that is orthogonal to a rotation axis of the second member. A movable member supported by the first member so as to be slidable in the direction, a driving member disposed outside the movable member in the radial direction, and a first elastic member for pressing the movable member against the driving member. And a second elastic member for pressing the movable member against the second member.

  According to the coupling device of one embodiment of the present disclosure, the backlash between the movable member and the second member is reduced by the second elastic member. Accordingly, the coupling device can suppress the vibration.

  As a desirable mode of the above-mentioned connection device, a direction of expansion and contraction of the second elastic member is parallel to a direction of expansion and contraction of the first elastic member. Thereby, it is easy to set the elastic force of the first elastic member and the elastic force of the second elastic member.

  As a desirable mode of the above-mentioned connecting device, an elastic force is generated in the second elastic member in a state where the movable member is separated from the second member. Thereby, rattling of the second elastic member is suppressed.

  As a desirable mode of the above-mentioned connecting device, the elastic force of the second elastic member when the movable member is separated from the second member is the first elastic member when the movable member is in contact with the second member. Greater than the elastic force of Thus, the magnitude relationship between the elastic force of the first elastic member and the elastic force of the second elastic member is defined.

  As a desirable mode of the above-mentioned connecting device, a spring constant of the second elastic member is larger than a spring constant of the first elastic member. Thus, the second elastic member deforms after the first elastic member deforms.

  As a desirable mode of the above-mentioned connection device, the above-mentioned movable member has a cylinder which incorporates the above-mentioned 2nd elastic member, and penetrates the above-mentioned 1st elastic member. A first plunger, a roller in contact with the drive member, a second plunger connected to the roller and pressing the first plunger, and a second plunger provided on an inner peripheral surface of the cylinder, the second plunger of the first plunger. A stopper for restricting movement in the approaching direction, wherein a spring constant of the second elastic member is larger than a spring constant of the first elastic member, and the driving member has a convex surface, and a diameter corresponding to the convex surface. A cylinder disposed apart from the second member, the cylinder including an inner peripheral surface including a concave surface arranged outward in a direction, and a connection surface connecting the convex surface and the concave surface. When interacting with said roller is in contact with the connection surface.

  Thus, when the driving member rotates from a state where the roller contacts the concave surface, the roller rides on the connection surface. Thereby, the roller is pushed inward in the radial direction. The force applied to the roller is transmitted to the cylinder via the second plunger, the first plunger, and the second elastic member. Since the spring constant of the second elastic member is larger than the spring constant of the first elastic member, the first elastic member contracts before the second elastic member. The cylinder moves inward in the radial direction while the first elastic member contracts. When the drive member further rotates after the cylinder comes into contact with the second member, the roller further rides on the connection surface and approaches the convex surface. Thereby, the second elastic member contracts. As a result, the cylinder is pressed against the second member by the elastic force of the second elastic member. For this reason, the backlash between the cylinder and the second member is reduced. Therefore, the coupling device can suppress the vibration.

  According to the present disclosure, it is possible to provide a connection device that can suppress vibration.

FIG. 1 is a schematic diagram of the electric drive device of the embodiment. FIG. 2 is a schematic diagram illustrating a first low-speed mode of the embodiment. FIG. 3 is a schematic diagram illustrating a second low-speed mode of the embodiment. FIG. 4 is a schematic diagram illustrating a third low-speed mode of the embodiment. FIG. 5 is a schematic diagram illustrating a first high-speed mode of the embodiment. FIG. 6 is a schematic diagram illustrating a second high-speed mode of the embodiment. FIG. 7 is a schematic diagram illustrating a case where the clutch is in the engaged state in the third high-speed mode of the embodiment. FIG. 8 is a schematic diagram illustrating a case where the clutch is in the disengaged state in the third high-speed mode of the embodiment. FIG. 9 shows states of the first motor, the second motor, the brake, and the clutch in the first low-speed mode, the second low-speed mode, the third low-speed mode, the first high-speed mode, the second high-speed mode, and the third high-speed mode. FIG. FIG. 10 is a graph showing the relationship between the motor speed and the output torque in the first low-speed mode, the second low-speed mode, and the third low-speed mode. FIG. 11 is a graph showing a region where the efficiency is high in the relationship between the motor rotation speed and the output torque. FIG. 12 is a perspective view of the power transmission switching device of the embodiment. FIG. 13 is an exploded perspective view of the power transmission switching device according to the embodiment. FIG. 14 is a cross-sectional view of the power transmission switching device according to the embodiment. FIG. 15 is a perspective view of the movable member according to the embodiment. FIG. 16 is a cross-sectional view of the movable member according to the embodiment. FIG. 17 is a front view showing a part of the first connection device of the embodiment. FIG. 18 is an enlarged view of FIG. FIG. 19 is a front view showing a part of the connecting device of the embodiment. FIG. 20 is an enlarged view of FIG. FIG. 21 is a graph showing transition of the elastic force of the first elastic member and the second elastic member with respect to the rotation angle of the driving member. FIG. 22 is a perspective view illustrating a part of the clutch according to the embodiment. FIG. 23 is a cross-sectional view of the power transmission switching device when the clutch according to the embodiment is in the engaged state. FIG. 24 is an exploded perspective view of a connection device according to a modification. FIG. 25 is a perspective view showing a part of a connection device according to a modification. FIG. 26 is a perspective view showing a part of a connection device according to a modification. FIG. 27 is a front view showing a part of the connection device of the modified example. FIG. 28 is a sectional view taken along line AA of FIG. FIG. 29 is a perspective view of a lever according to a modification. FIG. 30 is a front view of a lever according to a modification. FIG. 31 is a front view of a lever according to a modification.

  Hereinafter, the present invention will be described in detail with reference to the drawings. The present invention is not limited by the following embodiments for carrying out the invention (hereinafter, referred to as embodiments). The components in the following embodiments include those that can be easily assumed by those skilled in the art, those that are substantially the same, and those that are in a so-called equivalent range. Furthermore, components disclosed in the following embodiments can be appropriately combined. Further, in the following embodiments, the same components as those described above are denoted by the same reference numerals, and overlapping description may be omitted as appropriate.

(Embodiment)
FIG. 1 is a schematic diagram of the electric drive device of the embodiment. FIG. 2 is a schematic diagram illustrating a first low-speed mode of the embodiment. FIG. 3 is a schematic diagram illustrating a second low-speed mode of the embodiment. FIG. 4 is a schematic diagram illustrating a third low-speed mode of the embodiment. FIG. 5 is a schematic diagram illustrating a first high-speed mode of the embodiment. FIG. 6 is a schematic diagram illustrating a second high-speed mode of the embodiment. FIG. 7 is a schematic diagram illustrating a case where the clutch is in the engaged state in the third high-speed mode of the embodiment. FIG. 8 is a schematic diagram illustrating a case where the clutch is in the disengaged state in the third high-speed mode of the embodiment. FIG. 9 shows states of the first motor, the second motor, the brake, and the clutch in the first low-speed mode, the second low-speed mode, the third low-speed mode, the first high-speed mode, the second high-speed mode, and the third high-speed mode. FIG.

  As shown in FIG. 1, the electric drive device 10 of the embodiment includes a first motor 11, a second motor 12, a first planetary gear mechanism 3, a second planetary gear mechanism 4, an output shaft 15, It includes a mechanism 101, an output shaft 18, a power transmission switching device 2, and a control device 19.

  The first motor 11 and the second motor 12 are arranged, for example, inside or around the wheel 100 of the vehicle. The first motor 11 and the second motor 12 are fixed to a case attached to the wheel 100. That is, the first motor 11 and the second motor 12 are in-wheel motors. The first motor 11 is connected to the first planetary gear mechanism 3. The second motor 12 is connected to the second planetary gear mechanism 4. In the following description, the direction along the axial direction of the first motor 11 is simply described as the axial direction. A direction orthogonal to the axial direction is simply described as a radial direction.

  As shown in FIG. 1, the first planetary gear mechanism 3 includes a first sun gear 31, a plurality of first pinion gears 33, a first ring gear 35, and a first carrier 34. The first sun gear 31 is connected to a shaft of the first motor 11. The first sun gear 31 includes a first sun gear shaft 30. The first sun gear shaft 30 may be fixed to the first sun gear 31 as a separate member, or may be formed integrally with the first sun gear 31. The first sun gear shaft 30 is connected to a shaft of the first motor 11. The first pinion gear 33 is arranged radially outward with respect to the first sun gear 31 and meshes with the first sun gear 31. The first ring gear 35 is disposed radially outward with respect to the first pinion gear 33 and meshes with the first pinion gear 33. The first carrier 34 is connected to the first pinion gear 33. The first carrier 34 supports the plurality of first pinion gears 33 so that each of the first pinion gears 33 can rotate. The first carrier 34 supports the plurality of first pinion gears 33 so as to revolve around the first sun gear 31. The first carrier 34 is connected to the output shaft 15. The output shaft 15 is connected to the wheel 100.

  As shown in FIG. 1, the second planetary gear mechanism 4 includes a second sun gear 41, a plurality of second pinion gears 43, a second ring gear 45, and a second carrier 44. The second sun gear 41 is connected to the first ring gear 35 and to the shaft of the second motor 12. The second sun gear 41 includes a second sun gear shaft 40. The second sun gear shaft 40 may be fixed to the second sun gear 41 as a separate member, or may be formed integrally with the second sun gear 41. The second sun gear shaft 40 is connected to a shaft of the second motor 12. As viewed from the axial direction, the center of the second sun gear shaft 40 overlaps the center of the first sun gear shaft 30. In the drawings, the second sun gear shaft 40 is shifted with respect to the first sun gear shaft 30 for convenience. The second pinion gear 43 is arranged radially outward with respect to the second sun gear 41, and meshes with the second sun gear 41. The second ring gear 45 is arranged radially outward with respect to the second pinion gear 43 and meshes with the second pinion gear 43. The second ring gear 45 is connected to the output shaft 15. The second carrier 44 is connected to the second pinion gear 43. The second carrier 44 supports the plurality of second pinion gears 43 so that each of the second pinion gears 43 can rotate. The second carrier 44 supports the plurality of second pinion gears 43 so as to revolve around the second sun gear 41.

  As shown in FIG. 1, the speed reduction mechanism 101 includes a small gear 16 and a large gear 17. The small gear 16 is connected to the output shaft 15. The large gear 17 meshes with the small gear 16. The number of teeth of the large gear 17 is larger than the number of teeth of the small gear 16. The large gear 17 is connected to an output shaft 18. The output shaft 18 is connected to the wheel 100. The output shaft 15 and the output shaft 18 are located on mutually different straight lines. The torque transmitted to the output shaft 15 is amplified by the speed reduction mechanism 101 and output from the output shaft 18.

  The power transmission switching device 2 includes a brake 6 (an example of a coupling device), a clutch 7, an actuator 5, and a housing 8. The brake 6 and the clutch 7 are driven by the actuator 5. The housing 8 is fixed to, for example, a case that supports the first motor 11 and the second motor 12.

  The brake 6 is disposed between the housing 8 (an example of a first member) and the second carrier 44 (an example of a second member). The brake 6 is in a fastening state in which the housing 8 and the second carrier 44 are fastened, or in a separated state in which the housing 8 and the second carrier 44 are separated. In the fastened state, the rotation (revolution) of the second carrier 44 is restricted. In the separated state, rotation (revolution) of the second carrier 44 is allowed.

  The clutch 7 is disposed between the second sun gear 41 and the second carrier 44. The clutch 7 is in an engaged state in which the second sun gear 41 and the second carrier 44 are engaged, or in a separated state in which the second sun gear 41 and the second carrier 44 are separated. In the fastened state, power is transmitted between the second sun gear 41 and the second carrier 44. In the separated state, the second sun gear 41 and the second carrier 44 rotate freely with respect to each other, and power is not transmitted between the second sun gear 41 and the second carrier 44.

  The control device 19 is a computer and includes, for example, a CPU (Central Processing Unit), a ROM (Read Only Memory), a RAM (Random Access Memory), an input interface, and an output interface. The control device 19 is, for example, an ECU (Electronic Control Unit) mounted on the vehicle. The control device 19 controls the first motor 11, the second motor 12, and the actuator 5.

  As shown in FIG. 9, the electric drive device 10 includes a first low speed mode, a second low speed mode, a third low speed mode, a first high speed mode, a second high speed mode, and a third high speed mode as driving modes. The control device 19 controls the first low-speed mode, the second low-speed mode, the third low-speed mode, the first high-speed mode, the second high-speed mode, and the third high-speed mode based on information obtained from various sensors provided on the vehicle. Switch.

  As shown in FIG. 9, in the first low-speed mode, the first motor 11 is driven, the second motor 12 is not driven, the brake 6 is engaged, and the clutch 7 is disengaged. In the second low-speed mode, the first motor 11 is not driven, the second motor 12 is driven, the brake 6 is engaged, and the clutch 7 is disengaged. In the third low-speed mode, both the first motor 11 and the second motor 12 are driven, the brake 6 is engaged, and the clutch 7 is disengaged. In the first high-speed mode, the first motor 11 is driven, the second motor 12 is not driven, and the brake 6 is in the separated state. In the first high-speed mode, the clutch 7 is in the engaged state. In the second high-speed mode, the first motor 11 is not driven, the second motor 12 is driven, and the brake 6 is in the separated state. In the second high-speed mode, the clutch 7 is engaged. In the third high-speed mode, both the first motor 11 and the second motor 12 are driven, and the brake 6 is in the separated state. In the third high-speed mode, the clutch 7 is in the engaged state or the disengaged state (either is possible).

  As shown in FIG. 2, in the first low-speed mode, the first motor 11 outputs a torque Ta. No torque is output from the second motor 12. The shaft of the second motor 12 idles. The torque Ta is input to the first sun gear 31. In the first planetary gear mechanism 3, the torque Ta is distributed to the torque T1 and the torque T2. The torque T1 is transmitted from the first carrier 34 to the output shaft 15. The torque T2 is transmitted to the second sun gear 41 via the first ring gear 35. The torque T2 becomes the torque T3 via the second pinion gear 43 and the second ring gear 45. The torque T3 is transmitted to the output shaft 15. The torque T3 merges with the torque T1. The torque T4 transmitted to the output shaft 15 is the sum of the torque T1 and the torque T3.

  The reduction ratio (first reduction ratio) of the first planetary gear mechanism 3 is defined as i1. The number of teeth of the first sun gear 31 is Zs1. The number of teeth of the first ring gear 35 is defined as Zr1. At this time, the first reduction ratio (i1) is represented by the following equation (1).

  i1 = Zr1 / Zs1 (1)

  The reduction ratio (second reduction ratio) of the second planetary gear mechanism 4 is defined as i2. The number of teeth of the second sun gear 41 is Zs2. The number of teeth of the second ring gear 45 is defined as Zr2. At this time, the second reduction ratio (i2) is represented by the following equation (2).

  i2 = Zr2 / Zs2 (2)

  The reduction ratio (overall reduction ratio) of the electric drive device 10 in the first low-speed mode is defined as I1. The overall reduction ratio in the first low-speed mode refers to the ratio of the rotation speed of the first motor 11 to the rotation speed of the output shaft 15. At this time, the overall reduction ratio (I1) is expressed by the following equation (3). For example, when the first reduction ratio (i1) is 2.5 and the second reduction ratio (i2) is 1.8, the overall reduction ratio (I1) is 8.

  I1 = i1 (1 + i2) +1 (3)

  The torque T4 output to the output shaft 15 is represented by the following equation (4). For example, when the first reduction ratio (i1) is 2.5 and the second reduction ratio (i2) is 1.8, the torque T4 is eight times the torque Ta.

  T4 = {i1 (1 + i2) +1} Ta (4)

  As shown in FIG. 3, in the second low-speed mode, the torque Tb is output from the second motor 12. No torque is output from the first motor 11. The shaft of the first motor 11 idles. The torque Tb is input to the second sun gear 41. The torque Tb becomes the torque T5 via the second pinion gear 43 and the second ring gear 45. The torque T5 is transmitted to the output shaft 15. The torque T5 is represented by the following equation (5).

  T5 = i2 × Tb (5)

  As shown in FIG. 4, in the third low-speed mode, the first motor 11 outputs the torque Ta, and the second motor 12 outputs the torque Tb. The torque Ta is input to the first sun gear 31. In the first planetary gear mechanism 3, the torque Ta is distributed to the torque T1 and the torque T2. The torque T1 is transmitted from the first carrier 34 to the output shaft 15. The torque T2 is transmitted to the second sun gear 41 via the first ring gear 35. The torque T2 merges with the torque Tb to become a torque T6. The torque T6 becomes the torque T7 via the second pinion gear 43 and the second ring gear 45. The torque T7 is transmitted to the output shaft 15. The torque T7 merges with the torque T1. The torque T8 transmitted to the output shaft 15 is the sum of the torque T1 and the torque T7. The torque T8 is represented by the following equation (6).

  T8 = {i1 (1 + i2) +1} Ta + i2 × Tb (6)

  As shown in FIG. 5, in the first high-speed mode, the first motor 11 outputs a torque Ta. No torque is output from the second motor 12. The shaft of the second motor 12 idles. The torque Ta is input to the first sun gear 31. In the first high-speed mode, the brake 6 is in the separated state, and the second carrier 44 is not fixed to the housing 8. Thus, the second planetary gear mechanism 4 does not receive a reaction force from the housing 8. In the first high-speed mode, the clutch 7 is in the engaged state, and the first ring gear 35, the second sun gear 41, and the second carrier 44 are integrated via the second sun gear shaft 40. Accordingly, the first ring gear 35, the second sun gear 41, and the second carrier 44 rotate integrally, and the first planetary gear mechanism 3 and the second planetary gear mechanism 4 rotate integrally. I have.

  In this state, the torque Ta input to the first sun gear 31 is distributed to the torque Ta1 and the torque Ta2 by the first pinion gear 33. The torque Ta1 is transmitted to the output shaft 15 via the first carrier 34. The torque Ta2 is transmitted to the output shaft 15 via the first ring gear 35 and the second planetary gear mechanism 4 that rotates integrally with the first ring gear 35. The torque Ta1 and the torque Ta2 merge at the output shaft 15 to become the torque Ta. Thus, in the first high-speed mode, the torque Ta is transmitted from the first motor 11 to the output shaft 15. In the first high-speed mode, the rotation speed of the output shaft 15 matches the rotation speed of the first motor 11.

  As shown in FIG. 6, in the second high-speed mode, the torque Tb is output from the second motor 12. No torque is output from the first motor 11. The shaft of the first motor 11 idles. The torque Tb is input to the second sun gear 41. In the second high-speed mode, the brake 6 is in the separated state, and the second carrier 44 is not fixed to the housing 8. Thus, the second planetary gear mechanism 4 does not receive a reaction force from the housing 8. In the second high-speed mode, the clutch 7 is in the engaged state, and the first ring gear 35, the second sun gear 41, and the second carrier 44 are integrated via the second sun gear shaft 40. Accordingly, the first ring gear 35, the second sun gear 41, and the second carrier 44 rotate integrally, and the first planetary gear mechanism 3 and the second planetary gear mechanism 4 rotate integrally. I have.

  In this state, the torque Tb input to the second sun gear 41 is distributed to the torque Tb1 and the torque Tb2 by the second sun gear shaft 40. The torque Tb1 is transmitted to the output shaft 15 via the second planetary gear mechanism 4 that rotates integrally with the first ring gear 35. The torque Tb2 is transmitted to the output shaft 15 via the first ring gear 35 and the first carrier 34. The torque Tb1 and the torque Tb2 join at the output shaft 15 to form a torque Tb. Thus, in the second high-speed mode, the torque Tb is transmitted from the second motor 12 to the output shaft 15. In the second high-speed mode, the rotation speed of the output shaft 15 matches the rotation speed of the second motor 12.

  As shown in FIG. 7, in the third high-speed mode, the torque Ta is output from the first motor 11, and the torque Tb is output from the second motor 12. As described above, in the third high-speed mode, the brake 6 is in the disengaged state, and the clutch 7 is in the engaged state or the disengaged state (either is possible).

  As shown in FIG. 7, when the clutch 7 is in the engaged state in the third high-speed mode, the first ring gear 35, the second sun gear 41, and the second carrier 44 are integrated via the second sun gear shaft 40. Accordingly, the first ring gear 35, the second sun gear 41, and the second carrier 44 rotate integrally, and the first planetary gear mechanism 3 and the second planetary gear mechanism 4 rotate integrally. I have. In this state, the torque Ta output from the first motor 11 is distributed by the first pinion gear 33 to the torque Ta1 and the torque Ta2. The torque Ta1 is transmitted to the output shaft 15 via the first carrier 34. The torque Ta2 is transmitted to the output shaft 15 via the first ring gear 35 and the second planetary gear mechanism 4 that rotates integrally with the first ring gear 35. The torque Tb output from the second motor 12 is distributed by the second sun gear 41 to the torque Tb1 and the torque Tb2. The torque Tb1 is transmitted to the output shaft 15 via the second planetary gear mechanism 4 that rotates integrally with the first ring gear 35. The torque Tb2 is transmitted to the output shaft 15 via the first ring gear 35 and the first carrier 34. The torque Ta1, the torque Ta2, the torque Tb1, and the torque Tb2 merge on the output shaft 15 to form a torque T9, which is transmitted to the output shaft 15.

  On the other hand, as shown in FIG. 8, when the clutch 7 is in the disengaged state in the third high-speed mode, the second sun gear shaft 40 and the second carrier 44 are not integrated, and the second carrier 44 also receives a reaction force from the housing 8. Absent. Thereby, the second planetary gear mechanism 4 does not transmit power. Therefore, the torque Tb output from the second motor 12 is transmitted to the first ring gear 35 but is not transmitted to the second ring gear 45. The torque Ta output from the first motor 11 is also transmitted to the first carrier 34 but is not transmitted to the second ring gear 45. The torque Ta output from the first motor 11 and the torque Tb output from the second motor 12 merge at the first pinion gear 33 to become a torque T9, which is transmitted to the output shaft 15.

  As described above, in the third high-speed mode, the torque Ta and the torque Tb merge and become the torque T9 regardless of whether the clutch 7 is engaged or disengaged. The torque T9 is represented by the following equation (7). In the third high-speed mode, the ratio of the rotation speed of the second motor 12 to the rotation speed of the first motor 11 is constant. In the third high-speed mode, the rotation speed of the output shaft 15 depends on the ratio of the rotation speed of the second motor 12 to the rotation speed of the first motor 11.

  T9 = Ta1 + Ta2 + Tb1 + Tb2 = Ta + Tb (7)

  FIG. 10 is a graph showing the relationship between the motor speed and the output torque in the first low-speed mode, the second low-speed mode, and the third low-speed mode. FIG. 11 is a graph showing a region where the efficiency is high in the relationship between the motor rotation speed and the output torque. The output torque means a torque output to the output shaft 15. FIG. 11 shows the relationship between the motor rotation speed and the output torque in a general motor.

  As shown in FIG. 10, the relationship between the motor speed and the output torque in the first low-speed mode, the second low-speed mode, and the third low-speed mode is different from each other. A region R indicated by a broken line in FIG. 11 is a region where the efficiency of the motor tends to increase. In the electric drive device 10 of the embodiment, the drive mode can be switched among the first low-speed mode, the second low-speed mode, the third low-speed mode, the first high-speed mode, the second high-speed mode, and the third high-speed mode. The area corresponding to the area R becomes relatively large. Therefore, according to the electric drive device 10, the efficiency is easily improved.

  As shown in FIG. 9, the electric drive device 10 has a parking mode. In the parking mode, the first motor 11 and the second motor 12 stop respectively. Further, the brake 6 is brought into the engaged state, and the clutch 7 is brought into the engaged state. As a result, the first planetary gear mechanism 3 and the second planetary gear mechanism 4 are fastened to the housing 8 and cannot rotate. Therefore, the electric drive device 10 can lock the rotation of the output shaft 15.

  The in-wheel motors disclosed in Patent Documents 1 and 2 described above combine two motors and a plurality of planetary gear mechanisms, and can switch between a low-speed mode with a large reduction ratio and a high-speed mode with a small reduction ratio. ing. In the in-wheel motors disclosed in Patent Documents 1 and 2, the high-speed mode is set in a state where one element of the planetary gear mechanism and the fixed member are not fastened. Even if only one motor is driven in this state, the planetary gear mechanism cannot receive the reaction force. Therefore, the in-wheel motors disclosed in Patent Documents 1 and 2 need to drive two motors in the high-speed mode.

  On the other hand, in the electric drive device 10 of the embodiment, the clutch 7 engages the second sun gear 41 and the second carrier 44, so that the operation by one motor is possible even when the brake 6 is in the separated state. And The electric drive device 10 can drive the vehicle by driving only one of the first motor 11 and the second motor 12 when the required traveling power is small during high-speed traveling. As described above, the electric drive device 10 can select the optimal number of motors in accordance with the operation state even at the time of high-speed running, and thus can improve the efficiency.

  FIG. 12 is a perspective view of the power transmission switching device of the embodiment. FIG. 13 is an exploded perspective view of the power transmission switching device according to the embodiment. FIG. 14 is a cross-sectional view of the power transmission switching device according to the embodiment. FIG. 15 is a perspective view of the movable member according to the embodiment. FIG. 16 is a cross-sectional view of the movable member according to the embodiment. Drawing 17 is a front view showing a part of connection device of an embodiment. FIG. 18 is an enlarged view of FIG. FIG. 19 is a front view showing a part of the connecting device of the embodiment. FIG. 20 is an enlarged view of FIG. FIG. 21 is a graph showing transition of the elastic force of the first elastic member and the second elastic member with respect to the rotation angle of the driving member. FIG. 22 is a perspective view illustrating a part of the clutch according to the embodiment. FIG. 23 is a cross-sectional view of the power transmission switching device when the clutch according to the embodiment is in the engaged state.

  As shown in FIG. 12, the power transmission switching device 2 includes a control ring 21, an actuator 5, a brake 6 (an example of a coupling device), and a clutch 7. The control ring 21 is an annular member and has a plurality of teeth on an outer peripheral surface. That is, the control ring 21 is an external gear.

  As shown in FIG. 12, the actuator 5 includes a gear 55. The gear 55 is fixed to the shaft 52 and rotates together with the shaft 52. The gear 55 meshes with the control ring 21. Therefore, when the motor 51 is driven, the control ring 21 rotates.

  As shown in FIG. 12, the housing 8 includes a first plate 85 and a second plate 86. The first plate 85 and the second plate 86 are connected by bolts or the like. As shown in FIG. 13, the first plate 85 includes a substantially cylindrical attachment portion 851.

  As shown in FIG. 14, the brake 6 includes a driving member 61, a movable member 63, a first elastic member 67, and a second elastic member 68.

  The drive member 61 is an annular member that rotates together with the control ring 21. The driving member 61 is fixed to the control ring 21 so as not to rotate relative to the control ring 21. As shown in FIGS. 17 and 19, the inner diameter of the driving member 61 differs (not constant) depending on the position in the circumferential direction. The driving member 61 is a cam ring. The inner peripheral surface 610 of the driving member 61 includes a convex surface 611, a concave surface 612, and a connection surface 613. The convex surface 611 is located radially inward of the concave surface 612. The convex surface 611 and the concave surface 612 are respectively arranged at equal intervals in the circumferential direction. For example, in the embodiment, the inner peripheral surface 610 includes three convex surfaces 611 arranged at equal intervals in the circumferential direction, and three concave surfaces 612 arranged at equal intervals in the circumferential direction. A concave surface 612 is arranged between the two convex surfaces 611. That is, the convex surfaces 611 and the concave surfaces 612 are alternately arranged. The connection surface 613 connects the convex surface 611 and the concave surface 612.

  As shown in FIG. 14, the movable member 63 faces the outer peripheral surface of the second carrier 44. The movable member 63 is arranged inside the driving member 61 in the radial direction. As shown in FIG. 16, the movable member 63 includes a cylinder 631, a first plunger 632, a second plunger 636, a roller 637, and a stopper 633.

  As shown in FIG. 16, the cylinder 631 is a substantially cylindrical member having one end closed and the other end opened. As shown in FIG. 14, the cylinder 631 radially penetrates a hole 8510 of the mounting portion 851. The cylinder 631 is guided in the radial direction by the hole 8510. The circumferential movement of the cylinder 631 is restricted by the housing 8. That is, the cylinder 631 does not rotate relative to the housing 8.

  As shown in FIG. 16, the cylinder 631 includes a main body 631a, a tapered portion 631b, and a flange 631c. The main body 631a is substantially cylindrical. The tapered portion 631b is arranged at an inner end of the main body 631a in the radial direction. The tapered portion 631b becomes thinner toward the tip. The tapered portion 631b faces the concave portion 441 of the second carrier 44. The flange portion 631c is disposed at an outer end of the main body portion 631a in the radial direction.

  The first plunger 632 is disposed inside the cylinder 631. The first plunger 632 is movable in the radial direction. The first plunger 632 includes a base 632a and a protrusion 632b. The base 632a extends along the inner peripheral surface of the cylinder 631, and has a substantially columnar shape. The protruding portion 632b protrudes radially outward from the base 632a.

  As shown in FIG. 16, the second plunger 636 is disposed at a radially outer end of the cylinder 631. The second plunger 636 is connected to the roller 637 and can push the first plunger 632. The second plunger 636 includes a base 636a, a flange 636b, and a roller support 636c. The base 636a extends along the inner peripheral surface of the cylinder 631, and has a substantially columnar shape. At least a part of the base 636a is disposed inside the cylinder 631. The flange portion 636b has a substantially disk shape and faces the end surface of the cylinder 631. The roller support 636c is disposed on the opposite side of the flange 636b from the base 636a. The roller support section 636c rotatably supports the roller 637. The roller 637 contacts the inner peripheral surface 610 of the driving member 61.

  The stopper 633 is a member that restricts the movement of the first plunger 632. The stopper 633 is substantially annular. The stopper 633 is disposed inside the cylinder 631. The stopper 633 is disposed between the base 632a of the first plunger 632 and the base 636a of the second plunger 636. The protrusion 632 b of the first plunger 632 penetrates the stopper 633. When the base 632a of the first plunger 632 contacts the stopper 633, the movement of the first plunger 632 is restricted.

  The first elastic member 67 is a member for pressing the movable member 63 against the driving member 61. The first elastic member 67 applies a radial outward force to the movable member 63. As shown in FIG. 15, the first elastic member 67 is, for example, a coil spring. One end of the first elastic member 67 contacts the mounting portion 851. The other end of the first elastic member 67 contacts the flange 631c of the cylinder 631. The cylinder 631 penetrates the first elastic member 67. The first elastic member 67 expands and contracts in the radial direction.

  The second elastic member 68 is a member for pressing the movable member 63 against the second carrier 44. The second elastic member 68 is disposed inside the cylinder 631. As shown in FIG. 15, the second elastic member 68 is, for example, a coil spring. One end of the second elastic member 68 contacts the bottom surface of the cylinder 631. The other end of the second elastic member 68 is in contact with the base 632a of the first plunger 632. The second elastic member 68 expands and contracts in the radial direction. The direction of expansion and contraction of the second elastic member 68 is the same as the direction of expansion and contraction of the first elastic member 67. The spring constant of the second elastic member 68 is larger than the spring constant of the first elastic member 67.

  As shown in FIG. 17, when the roller 637 contacts the concave surface 612, the cylinder 631 is positioned outside the concave portion 441 of the second carrier 44. Therefore, in the state shown in FIG. 17, the second carrier 44 can freely rotate with respect to the housing 8. That is, the brake 6 is in the separated state. In the state shown in FIG. 17, there is a gap between the flange portion 631c of the first plunger 632 and the flange portion 636b of the second plunger 636 as shown in FIG. In the state shown in FIG. 17, the base 632a of the first plunger 632 contacts the stopper 633. In the state shown in FIG. 17, the protrusion 632b of the first plunger 632 contacts the second plunger 636.

  In FIG. 21, the rotation angle of the driving member 61 in the state shown in FIG. 17 is 0 °. As shown in FIG. 21, in the state of FIG. 17, an elastic force is generated in the first elastic member 67 and the second elastic member 68. That is, a preload is applied to the first elastic member 67 and the second elastic member 68. The elastic force F1 of the first elastic member 67 in the state shown in FIG. 17 is equal to the reaction force that the roller 637 receives from the concave surface 612. The elastic force F3 of the second elastic member 68 in the state shown in FIG. 17 is larger than the elastic force F1. Since one end of the second elastic member 68 contacts the bottom surface of the cylinder 631 and the other end of the second elastic member 68 contacts the stopper 633, the elastic force F3 is canceled by the cylinder 631. Therefore, in the state shown in FIG. 17, the elastic force of the second elastic member 68 does not affect the operation of the first elastic member 67. By adjusting only the elastic force of the first elastic member 67, the reaction force that the roller 637 receives from the concave surface 612 can be set. Therefore, it is easy to set the reaction force that the roller 637 receives from the concave surface 612.

  As shown in FIG. 17, when the driving member 61 rotates from a state where the roller 637 is in contact with the concave surface 612, the roller 637 rides on the connection surface 613. Thus, the roller 637 is pushed inward in the radial direction. The force applied to the roller 637 is transmitted to the cylinder 631 via the second plunger 636, the first plunger 632, and the second elastic member 68. Since the spring constant of the second elastic member 68 is larger than the spring constant of the first elastic member 67, the first elastic member 67 contracts before the second elastic member 68. While the first elastic member 67 contracts, the cylinder 631 moves inward in the radial direction. Then, the tip (tapered portion 631b) of the cylinder 631 contacts the bottom surface of the concave portion 441 of the second carrier 44. As a result, the cylinder 631 cannot move inward in the radial direction. The second carrier 44 is fastened to the housing 8 by fitting the cylinder 631 into the recess 441. Thereby, the rotation of the second carrier 44 is restricted. That is, the brake 6 is brought into the engaged state.

  When the tip of the cylinder 631 contacts the bottom surface of the concave portion 441 of the second carrier 44, the roller 637 contacts the connection surface 613. When the driving member 61 further rotates after the tip of the cylinder 631 contacts the bottom surface of the concave portion 441 of the second carrier 44, the roller 637 further rides on the connection surface 613 and approaches the convex surface 611. Thereby, the roller 637 is further pushed inward in the radial direction. The second plunger 636 moves relatively to the cylinder 631, and pushes the first plunger 632 radially inward. For this reason, the second elastic member 68 contracts. As a result, the cylinder 631 is pressed against the bottom surface of the recess 441 by the elastic force of the second elastic member 68. Since the backlash between the cylinder 631 and the concave portion 441 is reduced, vibration is suppressed. When the driving member 61 further rotates, the roller 637 contacts the convex surface 611 as shown in FIG. As a result, the engaged state of the brake 6 is maintained.

  In FIG. 21, the rotation angle of the drive member 61 when the roller 637 rides on the connection surface 613 from the concave surface 612 is A1. The rotation angle of the driving member 61 when the tip of the cylinder 631 contacts the bottom surface of the concave portion 441 of the second carrier 44 is A2. The rotation angle of the drive member 61 when the roller 637 rides on the convex surface 611 from the connection surface 613 is A3. The elastic force of the first elastic member 67 increases in rotation angle between A1 and A2, and thereafter becomes constant. The elastic force of the second elastic member 68 has a constant rotation angle from A1 to A2, increases from A2 to A3, and then becomes constant.

  In the state shown in FIG. 19, the first elastic member 67 and the second elastic member 68 are compressed. The cylinder 631 is pushed outward in the radial direction by the elastic force F2 of the first elastic member 67 (see FIG. 21). The cylinder 631 is pushed toward the recess 441 by the elastic force F4 of the second elastic member 68 (see FIG. 21). When the driving member 61 rotates from the state shown in FIG. 19, first, the first plunger 632 contacts the stopper 633 by the elastic force of the second elastic member 68. Thereafter, the cylinder 631 moves radially outward by the elastic force of the first elastic member 67 and separates from the recess 441. As described above, the tapered portion 631b becomes thinner toward the tip. Thus, when the tapered portion 631b is pressed against the inner wall of the concave portion 441, the tapered portion 631b receives a radially outward reaction force from the inner wall of the concave portion 441. For this reason, the cylinder 631 is easily detached from the concave portion 441.

  As shown in FIG. 21, the elastic force F3 of the second elastic member 68 when the cylinder 631 is separated from the second carrier 44 is the elastic force of the first elastic member 67 when the cylinder 631 is in contact with the second carrier 44. It is larger than F2. That is, the minimum value of the elastic force of the second elastic member 68 is larger than the maximum value of the elastic force of the first elastic member 67.

  As shown in FIG. 14, the clutch 7 includes a pin holding member 71, a bearing 72, a pin 73, a hub 79, a second cam ring 75, a bearing 77, and a retaining ring 78.

  The pin holding member 71 is an annular member that rotates together with the control ring 21. In the embodiment, the pin holding member 71 is integrated with the driving member 61. That is, the pin holding member 71 is the driving member 61. The pin holding member 71 is supported by the second plate 86 via a bearing 72. The pin 73 protrudes from the inner peripheral surface of the pin holding member 71. The pin 73 rotates together with the pin holding member 71. For example, a plurality of pins 73 are arranged at equal intervals in the circumferential direction.

  As shown in FIG. 14, the hub 79 is attached to the second sun gear 41. The hub 79 includes a plurality of teeth 791 provided on the inner peripheral surface and a plurality of teeth 792 provided on the outer peripheral surface. The teeth 791 are, for example, splines and mesh with the teeth of the second sun gear 41. The hub 79 can slide in the axial direction with respect to the second sun gear 41. The teeth 792 are splines and mesh with the teeth on the inner peripheral surface of the second carrier 44 when the hub 79 overlaps the second carrier 44 in the radial direction.

  As shown in FIG. 14, the second cam ring 75 is attached to a hub 79 via a bearing 77. The second cam ring 75 is rotatable relative to the hub 79. The retaining ring 78 is a member for positioning the bearing 77. The second cam ring 75, the bearing 77, and the hub 79 can slide integrally in the axial direction. As shown in FIG. 22, the second cam ring 75 includes a cam groove 750 on the outer peripheral surface. The pin 73 fits into the cam groove 750. As shown in FIG. 22, the cam groove 750 includes a convex portion 751, a concave portion 752, and a connecting portion 753. The convex portion 751 is located on the opposite side of the concave portion 752 from the second carrier 44. The convex portions 751 and the concave portions 752 are respectively arranged at equal intervals in the circumferential direction. For example, the cam groove 750 includes three convex portions 751 arranged at equal intervals in the circumferential direction, and three concave portions 752 arranged at equal intervals in the circumferential direction. A concave portion 752 is arranged between the two convex portions 751. That is, the convex portions 751 and the concave portions 752 are arranged alternately. The connecting portion 753 connects the convex portion 751 and the concave portion 752. When the cam groove 750 moves with respect to the pin 73, the second cam ring 75 slides in the axial direction.

  When the pin 73 is in the recess 752, the hub 79 is located outside the second carrier 44. The teeth 792 of the hub 79 do not mesh with the second carrier 44. Therefore, the second carrier 44 and the second sun gear 41 can freely rotate with respect to each other. That is, the clutch 7 is in the disengaged state. On the other hand, when the pin 73 is on the convex portion 751, the hub 79 overlaps with the second carrier 44. The teeth 792 of the hub 79 mesh with the second carrier 44. Therefore, the second carrier 44 and the second sun gear 41 are fastened. That is, the clutch 7 is brought into the engaged state.

  Hereinafter, the rotation angle of the control ring 21 is simply described as a rotation angle. In the embodiment, each time the rotation angle changes by 30 °, the combination of the state of the brake 6 and the state of the clutch 7 changes. For example, the rotation angle when the brake 6 is engaged and the clutch 7 is engaged is 0 °. When the rotation angle is 30 °, the brake 6 is in the engaged state and the clutch 7 is in the disengaged state. When the rotation angle is 60 °, the brake 6 is in the disengaged state and the clutch 7 is in the disengaged state. When the rotation angle is 90 °, the brake 6 is in the disengaged state and the clutch 7 is in the engaged state. When the rotation angle is 120 °, the brake 6 is engaged and the clutch 7 is engaged, and the rotation angle returns to 0 °. For this reason, the power transmission switching device 2 can realize the seven modes shown in FIG.

  In addition, the brake 6 is only an example of a connection device. The housing 8 is just an example of a first member. The second carrier 44 is merely an example of the second member. For example, the coupling device may fasten the housing 8 and other components of the second planetary gear mechanism 4 or fasten the housing 8 and other components of the first planetary gear mechanism 3. The coupling device may be used as the clutch 7. Further, the connecting device does not necessarily have to be used in the electric drive device 10. The connection device can be widely applied to a device that can fasten and separate the first member and the second member.

  The drive member 61 is not limited to a cam ring. The cam ring is merely an example of the driving member 61. For example, the driving member 61 may be a linear motion mechanism or the like connected to the movable member 63.

  As described above, the coupling device (the brake 6) includes the first member (the housing 8), the second member (the second carrier 44) that rotates with respect to the first member, and the rotation axis Z of the second member. A movable member 63 supported by the first member so as to be slidable in a radial direction that is a direction perpendicular to the movable member 63, a driving member 61 disposed outside the movable member 63 in the radial direction, and pressing the movable member 63 against the driving member 61. And a second elastic member 68 for pressing the movable member 63 against the second member.

  In an electric vehicle or a hybrid electric vehicle, a brake and a clutch that do not use high-pressure hydraulic pressure are required instead of a multi-plate clutch. When an engagement type brake and clutch are used, the device can be simplified and the drag torque in the disengaged state can be reduced because no hydraulic pressure is used, as compared with a wet multi-plate clutch. However, in the engagement type brake and clutch, backlash exists in the engaged state. For this reason, vibration may occur when switching between the driving of the electric drive device 10 and the regeneration (when the direction of the torque is reversed) or the like.

  On the other hand, in the connecting device (brake 6) of the present embodiment, the backlash between the movable member 63 and the second member (second carrier 44) is reduced by the second elastic member 68. Accordingly, the coupling device (brake 6) can suppress vibration.

  In the connecting device of the present embodiment, the direction of expansion and contraction of the second elastic member 68 is parallel to the direction of expansion and contraction of the first elastic member 67. This makes it easy to set the elastic force of the first elastic member 67 and the elastic force of the second elastic member 68.

  In the connection device of the present embodiment, an elastic force is generated in the second elastic member 68 in a state where the movable member 63 is separated from the second member. Thereby, rattling of the second elastic member 68 is suppressed.

  In the connection device of the present embodiment, the elastic force F3 of the second elastic member 68 when the movable member 63 is separated from the second member is determined by the elasticity of the first elastic member 67 when the movable member 63 is in contact with the second member. Greater than the force F2. Thus, the magnitude relationship between the elastic force of the first elastic member 67 and the elastic force of the second elastic member 68 is defined.

  In the connection device of the present embodiment, the spring constant of the second elastic member 68 is larger than the spring constant of the first elastic member 67. Thereby, the second elastic member 68 is deformed after the first elastic member 67 is deformed.

  In the connecting device according to the present embodiment, the movable member 63 includes the second elastic member 68 and penetrates the first elastic member 67, and the movable member 63 is in contact with the second elastic member 68 and is movable with respect to the cylinder 631. A first plunger 632, a roller 637 in contact with the driving member 61, a second plunger 636 connected to the roller 637 and pressing the first plunger 632, and a second plunger provided on the inner peripheral surface of the cylinder 631. A stopper 633 for restricting movement in a direction approaching the two plungers 636. The spring constant of the second elastic member 68 is larger than the spring constant of the first elastic member 67. The driving member 61 includes an inner peripheral surface 610 including a convex surface 611, a concave surface 612 arranged radially outward with respect to the convex surface 611, and a connection surface 613 connecting the convex surface 611 and the concave surface 612. When the cylinder 631 separated from the second member contacts the second member, the roller 637 contacts the connection surface 613.

  Thus, when the driving member 61 rotates from a state where the roller 637 is in contact with the concave surface 612, the roller 637 rides on the connection surface 613. Thus, the roller 637 is pushed inward in the radial direction. The force applied to the roller 637 is transmitted to the cylinder 631 via the second plunger 636, the first plunger 632, and the second elastic member 68. Since the spring constant of the second elastic member 68 is larger than the spring constant of the first elastic member 67, the first elastic member 67 contracts before the second elastic member 68. While the first elastic member 67 contracts, the cylinder 631 moves inward in the radial direction. When the drive member 61 further rotates after the cylinder 631 contacts the second member, the roller 637 further rides on the connection surface 613 and approaches the convex surface 611. Thereby, the second elastic member 68 contracts. As a result, the cylinder 631 is pressed against the second member by the elastic force of the second elastic member 68. For this reason, the backlash between the cylinder 631 and the second member is reduced. Therefore, the coupling device can suppress the vibration.

  If the stopper 633 is not provided, the elastic force of the first elastic member 67 and the elastic force of the second elastic member 68 act on the cylinder 631 and balance when the roller 637 is in contact with the concave surface 612. Therefore, no reaction force from the driving member 61 is applied to the cylinder 631. Further, since the first elastic member 67 contracts by the elastic force of the second elastic member 68, the cylinder 631 may move radially inward. For this reason, there is a possibility that the fastening state is switched from the separated state unintentionally. In order to transmit the reaction force from the driving member 61 to the cylinder 631, the elastic force of the first elastic member 67 may be made larger than the elastic force of the second elastic member 68. However, since the cylinder 631 moves radially inward after only the second elastic member 68 has contracted, the movable member 63 is no longer pressed against the second member, and vibration is not suppressed.

  On the other hand, in the present embodiment, when the second elastic member 68 comes into contact with the stopper 633, both elastic forces of the second elastic member 68 in two directions act on the cylinder 631. Therefore, the elastic force of the second elastic member 68 is canceled by the cylinder 631. Therefore, the elastic force of the second elastic member 68 does not affect the operation of the first elastic member 67. By adjusting only the elastic force of the first elastic member 67, the reaction force received by the roller 637 from the driving member 61 can be set. Therefore, it is easy to set the reaction force that the roller 637 receives from the driving member 61. In addition, by setting the elastic force of the second elastic member 68 to be sufficiently large with respect to the elastic force of the first elastic member 67, fine dimensional control or individual difference between the first elastic member 67 and the second elastic member 68 can be achieved. Eliminates management. This reduces the cost of manufacturing the coupling device.

(Modification)
FIG. 24 is an exploded perspective view of a connection device according to a modification. FIG. 25 is a perspective view showing a part of a connection device according to a modification. FIG. 26 is a perspective view showing a part of a connection device according to a modification. FIG. 27 is a front view showing a part of the connection device of the modified example. FIG. 28 is a sectional view taken along line AA of FIG. FIG. 29 is a perspective view of a lever according to a modification. FIG. 30 is a front view of a lever according to a modification. FIG. 31 is a front view of a lever according to a modification. Note that the same components as those described in the above-described embodiment are denoted by the same reference numerals, and redundant description will be omitted.

  As shown in FIG. 24, the brake 6A of the modified example includes a driving member 61A, a movable member 63A, a first elastic member 67A, a lever 9, and a second elastic member 68A.

  The driving member 61A includes a lever fixing portion 615. The lever fixing portion 615 is provided on the outer peripheral surface of the driving member 61A. The lever 9 is attached to the lever fixing portion 615.

  The movable member 63A includes a pin 635. The pin 635 is a rod-shaped member that penetrates the hole 8510 of the mounting portion 851 in the radial direction. The pin 635 is, for example, a solid member. The pin 635 is guided in the radial direction by the hole 8510. Pin 635 does not rotate relative to housing 8. The pin 635 rotatably supports the roller 637.

  The first elastic member 67A is a member for pressing the movable member 63A against the drive member 61A. The first elastic member 67A applies a radial outward force to the movable member 63A. As shown in FIG. 24, the first elastic member 67A is, for example, a coil spring. One end of the first elastic member 67A is in contact with the mounting portion 851. The other end of the first elastic member 67A contacts the pin 635. The pin 635 penetrates the first elastic member 67A. The first elastic member 67A expands and contracts in the radial direction.

  The lever 9 is a member for rotating the driving member 61A. The lever 9 is driven by, for example, an actuator. As shown in FIGS. 25 and 26, the lever 9 includes a cover 93, a rod 91, and a pin 99.

  As shown in FIGS. 25 and 26, the cover 93 is attached to the lever fixing portion 615 by a pin 99. The cover 93 is rotatable with respect to the lever fixing portion 615. The pin 99 is retained by a snap pin (R pin) 98.

  As shown in FIG. 31, the rod 91 passes through the cover 93. As shown in FIG. 29, the rod 91 includes a protrusion 911 and a protrusion 912. The protrusion 912 is arranged on the opposite side of the cover 93 from the protrusion 911.

  The second elastic member 68A is a member for pressing the movable member 63A against the second carrier 44. The second elastic member 68A is arranged on the outer periphery of the rod 91. The second elastic member 68A is, for example, a coil spring. One end of the second elastic member 68 </ b> A contacts the cover 93. The other end of the second elastic member 68A is in contact with the protrusion 911. The second elastic member 68A expands and contracts in the axial direction of the rod 91. The spring constant of the second elastic member 68A is larger than the spring constant of the first elastic member 67A.

  When the roller 637 contacts the concave surface 612, an elastic force is generated in the first elastic member 67A and the second elastic member 68A. That is, a preload is applied to the first elastic member 67A and the second elastic member 68A.

  When the rod 91 of the lever 9 is pushed toward the cover 93, the protrusion 911 pushes the cover 93 via the second elastic member 68A. Thereby, the driving member 61A rotates. When the driving member 61A rotates from a state where the roller 637 is in contact with the concave surface 612, the roller 637 rides on the connection surface 613. The roller 637 is pushed inward in the radial direction. Since the spring constant of the second elastic member 68A is larger than the spring constant of the first elastic member 67A, the first elastic member 67A contracts before the second elastic member 68A. The pin 635 moves radially inward while the first elastic member 67A contracts. Then, the tip of the pin 635 contacts the bottom surface of the concave portion 441 of the second carrier 44. This makes it impossible to move the pin 635 inward in the radial direction. The second carrier 44 is fastened to the housing 8 by fitting the pin 635 into the recess 441. Thereby, the rotation of the second carrier 44 is restricted. That is, the brake 6 is brought into the engaged state.

  When the tip of the pin 635 contacts the bottom surface of the concave portion 441 of the second carrier 44, the roller 637 contacts the connection surface 613. When the driving member 61A further rotates after the tip of the pin 635 contacts the bottom surface of the concave portion 441 of the second carrier 44, the roller 637 further rides on the connecting surface 613 and approaches the convex surface 611. As a result, the second elastic member 68A contracts. As a result, the pin 635 is pressed against the bottom surface of the recess 441 by the elastic force of the second elastic member 68A. Since the backlash between the pin 635 and the concave portion 441 is reduced, the vibration is suppressed. When the driving member 61A further rotates, the roller 637 comes into contact with the convex surface 611 as shown in FIG. As a result, the engaged state of the brake 6 is maintained.

  The elastic force of the second elastic member 68A when the pin 635 is away from the second carrier 44 is larger than the elastic force of the first elastic member 67A when the pin 635 is in contact with the second carrier 44. That is, the minimum value of the elastic force of the second elastic member 68A is larger than the maximum value of the elastic force of the first elastic member 67A.

Reference Signs List 10 electric drive device 100 wheel 101 reduction mechanism 11 first motor 12 second motor 15, 18 output shaft 16 small gear 17 large gear 19 control device 2 power transmission switching device 21 control ring 30 first sun gear shaft 31 first sun gear 33 1 pinion gear 34 1st carrier 35 1st ring gear 4 2nd planetary gear mechanism 40 2nd sun gear shaft 41 2nd sun gear 43 2nd pinion gear 44 2nd carrier (2nd member)
441 recess 45 second ring gear 5 actuator 51 motor 52 shaft 55 gear 6, 6A brake (connecting device)
61, 61A Drive member 610 Inner peripheral surface 611 Convex surface 612 Concave surface 613 Connection surface 615 Lever fixing portion 63, 63A Movable member 631 Cylinder 632 First plunger 633 Stopper 636 Second plunger 637 Roller 67, 67A First elastic member 68, 68A 2 elastic member 7 clutch 71 pin holding member 73 pin 75 second cam ring 750 cam groove 751 convex portion 752 concave portion 753 connecting portion 77 bearing 78 retaining ring 79 hub 8 housing (first member)
85 first plate 851 mounting part 8510 hole 86 second plate

Claims (6)

A first member;
A second member that rotates with respect to the first member;
A movable member supported by the first member so as to be slidable in a radial direction that is a direction orthogonal to a rotation axis of the second member;
A driving member disposed outside the movable member in the radial direction;
A first elastic member for pressing the movable member against the driving member;
A second elastic member for pressing the movable member against the second member;
A coupling device comprising: The connecting device according to claim 1, wherein a direction of expansion and contraction of the second elastic member is parallel to a direction of expansion and contraction of the first elastic member. The connecting device according to claim 1, wherein an elastic force is generated in the second elastic member in a state where the movable member is separated from the second member. The elastic force of the second elastic member when the movable member is separated from the second member is greater than the elastic force of the first elastic member when the movable member is in contact with the second member. The coupling device according to claim 1. The connection device according to claim 1, wherein a spring constant of the second elastic member is larger than a spring constant of the first elastic member. The movable member,
A cylinder containing the second elastic member and penetrating the first elastic member;
A first plunger in contact with the second elastic member and movable with respect to the cylinder;
A roller in contact with the driving member,
A second plunger connected to the roller and pushing the first plunger;
A stopper provided on the inner peripheral surface of the cylinder, for restricting movement of the first plunger in a direction approaching the second plunger;
With
A spring constant of the second elastic member is larger than a spring constant of the first elastic member;
The driving member includes an inner peripheral surface including a convex surface, a concave surface arranged outside in the radial direction with respect to the convex surface, and a connection surface connecting the convex surface and the concave surface,
The connection device according to claim 1, wherein the roller is in contact with the connection surface when the cylinder that has been separated from the second member contacts the second member.

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