JP6113676B2 - Multi-disc transmission and wheel drive device - Google Patents

Description

  The present invention relates to a multi-disc transmission and a wheel drive device.

  In Patent Document 1, a primary disk provided on the input shaft and a secondary disk provided on the output shaft are partially overlapped to provide a disk overlap area, and both disks are sandwiched between a pair of pressing rollers in this area. A multi-disc transmission that transmits the rotation of an input shaft to an output shaft by bringing them into contact is disclosed.

  In a multi-disc transmission, a shift is realized by changing a position where a pair of pressing rollers sandwich both discs. That is, if the position between the two disks is close to the input shaft, the gear ratio changes to the low side (large gear ratio side), and if close to the output shaft, the gear ratio changes to the high side (low gear ratio side). .

JP 2010-53995 A

  In the multi-disc transmission described in Patent Document 1, the pressing force between the pressing rollers is structurally determined by the selected shift stage, and therefore the pressing force cannot be adjusted according to the operating state of the transmission.

  The transmission torque generated by the pair of pressing rollers sandwiching both disks depends on the frictional force of both disks generated by the pressing force of the pressing rollers. Therefore, in order to transmit a large torque, a mechanism for increasing the pressing force of the pressing roller is required, which causes a problem that the transmission is enlarged.

  The present invention has been made in view of such technical problems, and an object of the present invention is to provide a multi-disc transmission capable of increasing the transmission torque without increasing the size of the multi-disc transmission.

According to an aspect of the present invention, there is provided a multi-disc transmission that includes an input shaft to which rotation from a power source is input, an output shaft that is disposed in parallel to the input shaft, and a primary that is provided on the input shaft. A disk, a secondary disk provided on the output shaft and partially overlapping the primary disk, a pair of pressing rollers disposed on both sides of the primary disk and the secondary disk, and a pair of pressing rollers, the input shaft and the output shaft The secondary disk is provided with a plurality of protrusions on the surface, and the primary disk is provided with a plurality of openings corresponding to the plurality of protrusions. hole is provided, the projection is constituted by a pin passing through the secondary disk in the thickness direction, and the primary disk by pressing rollers By clamping the cans Dali disc protrusions mechanically engaged is inserted into the hole, the rotation of the primary disk is characterized in that it is transferred to the secondary disk.

According to the above aspect, the torque is transmitted between the primary disk and the secondary disk not by friction but by mechanically engaging the protrusion and the hole . As a result, loss due to slippage in friction transmission can be greatly reduced, and the rigidity of each component and the pressing force of the pressing roller can be reduced. Therefore, the weight reduction, cost reduction, and efficiency improvement of the transmission can be achieved at the same time.

It is explanatory drawing of a vehicle provided with the wheel drive device of embodiment of this invention. It is explanatory drawing of the wheel drive device of embodiment of this invention. It is explanatory drawing of the wheel drive device of embodiment of this invention. It is explanatory drawing of the wheel drive device of embodiment of this invention. It is explanatory drawing of the primary disk and secondary disk of embodiment of this invention. It is explanatory drawing of the engaging part and projection part of embodiment of this invention. It is explanatory drawing of the projection part of embodiment of this invention. It is explanatory drawing of the projection part of embodiment of this invention. It is explanatory drawing of another example of the engaging part and projection part of embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is an explanatory diagram of a vehicle 4 including a wheel drive device 1 to which a multi-disc transmission according to an embodiment of the present invention is applied.

  The wheel drive device 1 according to the present embodiment is housed in a wheel 10 that constitutes the drive wheel 2 of the vehicle, and rotates the drive wheel 2 by the drive force of the motor 20 that is a drive force source. Let it run. The vehicle 4 is provided with a steering device 5 and controls the steering direction of the drive wheels 2. The wheel driving device 1 operates under the control of the control device 3 based on instructions from the driver such as the operation of the steering device 5 and the operation of the accelerator pedal 6 and the brake pedal 7.

  Although the vehicle 4 is provided with four wheels, it is sufficient that at least two wheels are configured as the drive wheels 2.

  2 to 4 are explanatory views showing the configuration of the wheel drive device 1 of the present embodiment.

  2 to 4 set the horizontal x-axis, the vertical y-axis, and the z-axis orthogonal to the x-axis y-axis, and show cross-sectional views in the x-axis plane, the y-axis plane, and the z-axis plane, respectively. .

  The wheel drive device 1 includes a wheel 10, a motor 20, a speed change mechanism 30, and a speed reduction mechanism 40.

  The wheel 10 includes a substantially cylindrical rim portion 10 a that holds a tire, and a disk-shaped disc portion 10 b that is attached to a rotation-side hub 15 via bolts 16. A drive device such as a motor 20 accommodated in the housing 12 is housed inside the wheel 10. The housing 12 has a substantially cylindrical shape that is slightly smaller than the inner diameter of the rim portion 10 a of the wheel 10, and is connected to a suspension (not shown) of the vehicle 4.

  The motor 20 is configured as an axial gap motor in which disk-shaped stators 21 and 22 having coils and a disk-shaped rotor 23 having permanent magnets are arranged side by side in the rotation axis direction. The rotation of the rotor 23 that rotates when the motor 20 is driven is input to the speed change mechanism 30 from the input shaft 31 fixed to the rotor 23.

  The input shaft 31 extends from the motor 20 into the housing 12, and the end of the input shaft 31 is rotatably supported at the center of the hub 15 coupled to the disk portion 10b of the wheel 10 via a bearing 12a. .

  The speed change mechanism 30 is configured such that a disk-shaped primary disk 32 fixed to the input shaft 31 and a disk-shaped secondary disk 34 fixed to the output shaft 33 are brought into contact with each other by a pressing mechanism 35, whereby the input shaft 31. This is a multi-disc transmission that transmits the rotation of the motor to the output shaft 33 so as to be variable.

  The speed reduction mechanism 40 includes an external gear output gear 33a provided on the output shaft 33 and an internal gear 14 meshing with the external gear output gear 33a, and the rotation output from the output shaft 33 is the internal gear. The speed is reduced by 14 and the reduced speed is transmitted to the wheel 10 via the hub 15.

  Next, each structure of the wheel drive device 1 will be described.

  The motor 20 is configured by sequentially arranging a stator 21, a rotor 23, and a stator 22 in the axial direction. The motor 20 has a substantially cylindrical shape whose outer periphery matches the inner diameter of the opening of the housing 12, and is fixed to the inner peripheral side of the housing 12.

  The rotor 23 is disposed between the stators 21 and 22 disposed with a gap in the axial direction, and rotates by the action of the magnetic field generated by these. Each of the stators 21 and 22 is provided with a plurality of coils in the circumferential direction. Each coil is wound around an axis parallel to the rotation axis of the motor 20. In the motor 20 of the present embodiment, the permanent magnet provided in the rotor 23 is configured as a ferrite magnet.

  The control device 3 rotates the rotor 23 by supplying a current corresponding to the amount of depression of the accelerator pedal 6 to the coils provided in the stators 21 and 22. As the rotor 23 rotates, the input shaft 31 rotates. The rotation of the input shaft 31 is input to the speed change mechanism 30.

  The transmission mechanism 30 includes a primary disk 32 fixed to the input shaft 31, a secondary disk 34 fixed to the output shaft 33, and a pressing mechanism 35.

  The primary disk 32 is configured by mounting two circular disks 32 a side by side in the axial direction of the input shaft, and rotates integrally with the input shaft 31. The two disks 32a are arranged at a predetermined interval. The outer peripheral end of the disk 32 a is disposed so as to be close to the output shaft 33.

  The secondary disk 34 is configured by attaching a single circular disk 34 a to the output shaft 33 and rotates integrally with the output shaft 33. The outer peripheral end of the disk 34 a is disposed so as to be close to the input shaft 31.

  The two disks 32a of the primary disk 32 are arranged so as to sandwich the disk 34a of the secondary disk 34. The primary disk 32 and the secondary disk 34 form a disk overlap region where a part of the disk overlaps between the input shaft 31 and the output shaft 33.

  In the disk overlap region, a gap is formed between the disk 32a of the primary disk 32 and the disk 34a of the secondary disk 34 in a state where the pressing force by the pressing mechanism 35 does not act. In a state in which the pressing force by the pressing mechanism 35 is applied, the primary disk 32 and the secondary disk 34 are elastically deformed to come into contact with each other to form a torque transmission contact portion. The primary disk 32 and the secondary disk 34 are configured to be mechanically engaged as will be described later, and the primary disk 32 and the secondary disk 34 are engaged with each other, whereby the primary disk 32 and the secondary disk 34 are changed to each other. Torque is transmitted.

  By forming a torque transmission contact portion between the primary disk 32 and the secondary disk 34, rotation is transmitted from the input shaft 31 to the output shaft 33. By moving the torque transmission contact portion in the radial direction of the primary disk 32 and the secondary disk 34 in the disk overlapping region, the rotation of the input shaft 31 can be transmitted to the output shaft 33 in a variable speed manner. In FIG. 3, an axis connection line O indicated by a thick dotted line connects the axis of the input shaft 31 and the output shaft 33 and is orthogonal to the input shaft 31 and the output shaft 33. The torque transmission contact portion is formed on the shaft connection line O.

  The pressing mechanism 35 includes a pressing roller mechanism 130, a disc clamping mechanism 131, a pressing force adjusting mechanism 132, and a speed change actuator 133.

  The pressing roller mechanism 130 includes a pressing roller 140, a holding portion 141, a pressing roller shaft 142, a guide block 149, a guide block 150, and a guide block shaft 151.

  The pair of pressing roller mechanisms 130 are arranged on both sides of the primary disk 32 and the secondary disk 34 and are attached to the guide block 149. The guide block 149 is attached between the two guide blocks 150 attached to the inner periphery of the housing 12 and is slidably attached to a plurality of guide block shafts 151 extending in the direction of the axis connection line O.

  As shown in FIG. 4, the disk clamp mechanism 131 includes a front clamp arm 167 and a rear clamp arm 168. The front clamp arm 167 and the rear clamp arm 168 are each slidably attached with a guide portion 146 on the lower side of the pressing roller mechanism 130. The front clamp arm 167 and the rear clamp arm 168 are moved in a direction in which the primary disk 32 and the secondary disk 34 are clamped with each other by the pressing force adjusting mechanism 132, thereby pressing the pressing roller 140 against the disk.

  The pressing force adjusting mechanism 132 moves the front clamp arm 167 and the rear clamp arm 168 in a direction to sandwich the primary disk 32 and the secondary disk 34 by the operation of the actuator 190. By operating the actuator 190 in response to a command signal from the control device 3, the pressing roller 140 is pressed against the disk side. Thereby, the primary disk 32 and the secondary disk 34 are elastically deformed and brought into contact with each other to form a torque transmission contact portion, and the rotation of the input shaft 31 is transmitted to the output shaft 33.

  The speed change actuator 133 includes an electric motor 134 and a sliding mechanism 135, and the electric motor 134 is operated in response to a command signal from the control device 3 to advance and retract the sliding mechanism 135, and the pressing connected to the sliding mechanism 135. The roller mechanism 130 is moved along the axial connection line O. As a result, the pressing roller 140 of the pressing roller mechanism 130 is moved in the direction of the axis connection line O to form a torque transmission contact portion at a position corresponding to the target gear ratio.

  An external gear 33a is provided at the end of the output shaft 33 on the disk portion 10b side. The external gear output gear 33 a meshes with the internal gear 14 fixed to the hub 15 coupled to the wheel 10 to rotate the internal gear 14.

  The external tooth output gear 33a meshes with an idler gear 51 that is provided on the inner peripheral side of the internal gear 14 and is rotatably provided coaxially with the input shaft 31. The internal gear 14 and the idler gear 51 have the same rotation shaft, and there is an interval between the external gear 33a and the external gear 33a. The idler gear 51 is pivotally supported via a bearing 51 a so as to be rotatable with respect to the output shaft 33.

  Between the internal gear 14 and the idler gear 51, a pinion 61a having substantially the same shape as that of the external gear 33a is engaged with a position different from that of the external gear 33a. The pinion 61 a is provided on the disk portion 10 b side of the counter shaft 61.

  The external gear 33a of the output shaft 33 is provided at one point in the circumferential equal division point of the internal gear 14, and the pinion 61a of the counter shaft 61 is provided at another point in the circumferential equal division point of the internal gear 14. In the present embodiment, the external tooth output gear 33a and the pinion 61a are arranged in the diameter direction of the internal gear 14 with the input shaft 31 as the center, but more pinions 61a and counter shafts may be arranged.

  A bearing 17 is provided on the inner peripheral side of the housing 12 and on the disk portion 10b side, and the internal gear 14 is supported by the bearing 17 so as to be rotatable from the outer periphery. The internal gear 14 is fixed to the hub 15. The hub 15 is rotatably supported by the housing 12 via the internal gear 14 and the bearing 17. The disk portion 10 b of the wheel 10 is coupled to the hub 15 via a bolt 16.

  An oil seal 18 is provided between the hub 15 and the housing 12. The oil seal 18 prevents the lubricating oil from scattering from the bearing 17 and the like to the wheel 10 and the outside thereof.

  The secondary disk 34 fixed to the output shaft 33 is provided with a brake device 72. The brake device 72 imparts rotational resistance by clamping the disk 34 a of the secondary disk 34, and brakes the rotation of the output shaft 33. A braking force is applied to the vehicle by braking the rotation of the output shaft 33.

  The brake device 72 gives a braking force by sandwiching the secondary disk 34 and controls the braking force of the wheel driving device 1 according to an instruction from the control device 3 according to, for example, the amount of depression of the brake pedal by the driver.

  As described above, the wheel drive device 1 according to the present embodiment shifts the output of the motor 20 by the speed change mechanism 30, and the wheel 10 via the internal gear 14 provided on the inner side of the wheel 10 with the speed-changed rotation. It is the structure which is transmitted to Thus, by transmitting the rotation to the wheel 10 by the internal gear 14, the rotation to the wheel 10 can be transmitted with a large reduction ratio, and the space in the inner diameter portion of the internal gear 14 is driven by the wheel. Since it can use for the component of the apparatus 1, the depth of a component can be formed flat, and the size and weight of the wheel drive device 1 can be reduced.

  Next, the structure of the primary disk 32 and the secondary disk 34 of this embodiment is demonstrated.

  FIG. 5 is an explanatory diagram of the disk 32a of the primary disk 32 and the disk 34a of the secondary disk 34 of the present embodiment.

  In the present embodiment, the protrusion 34 is provided on the disk 34 a of the secondary disk 34, and the engaging part 102 corresponding to the protrusion 101 is provided on the disk 32 a of the primary disk 32.

  By pressing the primary disk 32 and the secondary disk 34 by the pressing roller 140, the protrusion 101 of the disk 34a is engaged with the engaging part 102 of the disk 32a. The rotation of the primary disk 32 is transmitted to the secondary disk 34 in a state where the engaging part 102 and the protruding part 101 are engaged.

  In this embodiment, with such a configuration, the primary disk 32 and the secondary disk 34 transmit torque by mechanically engaging the protrusion 101 and the engaging portion 102 instead of friction. As a result, the actuator 190 and the elastic member of the pressing force adjusting mechanism 132 that adjusts the pressing force of the pressing roller 140 can be reduced in size, so that the transmission torque can be increased without increasing the size of the speed change mechanism 30.

  FIG. 6 is an explanatory diagram of the engaging portion 102 of the disk 32a and the protrusion 101 of the disk 34a of the present embodiment.

  The protruding portion 101 is configured to protrude from the surface of the disk 34a by a pin 111 provided through the disk 34a. The pin 111 has a substantially cylindrical shape, and chamfered portions 101a are formed at both ends.

  The engaging portion 102 is configured by a through hole formed in the disk 32a. The engaging portion 102 is formed by a hole whose diameter is increased in accordance with the surface toward the disk 34 a and has a shape corresponding to the chamfered portion 101 a at the end of the protruding portion 101.

  The protrusions 101 and the engaging portions 102 are regularly formed at predetermined radial positions in the circumferential direction of the disc 32a and the disc 34a. By engaging the protrusion 101 and the engaging portion 102 in the torque transmission contact portion, the gear ratio between the primary disk 32 and the secondary disk 34 is changed from the lowest to the highest.

  More specifically, when the pressing roller 140 sandwiches and presses the primary disk 32 and the secondary disk 34, the primary disk 32 is elastically deformed, and the engaging portion 102 of the disk 32a in the torque transmission contact portion The protrusion 101 of the disk 34a is engaged. At a place other than the torque transmission contact portion that is the pressing position of the pressing roller 140, the protruding portion 101 is separated from the engaging portion 102.

  With this configuration, the primary disk 32 has a predetermined radial position (first radial position) and the secondary disk 34 has a predetermined radial position (second radial position) engaged by the protrusion 101 and the engaging portion 102. Thus, the rotation of the input shaft 31 is transmitted from the primary disk 32 to the secondary disk 34 at a speed ratio set by the ratio between the first radial position and the second radial position. By changing the position of the pressing roller 140 on the axial connection line O in the radial direction, the position where the protrusion 101 and the engaging portion 102 are engaged is changed, and the gear ratio is changed.

  FIG. 7 is an explanatory diagram showing the positional relationship between the engaging portion 102 of the disk 32a and the protrusion 101 of the disk 34a according to the present embodiment.

  The engaging portions 102 are formed at predetermined intervals in the circumferential direction at predetermined radial positions from the center of the input shaft 31 of the primary disk 32. Similarly, the protrusions 101 are also formed at predetermined intervals in the circumferential direction at predetermined radial positions from the center of the output shaft 33 of the secondary disk 34.

  A predetermined gear ratio is realized by engaging the engaging portion 102 and the protruding portion 101 formed at predetermined radial positions of the primary disk 32 and the secondary disk 34.

  Here, in this embodiment, as shown in FIG. 7, a predetermined gear ratio is realized by engagement of a pair of engaging portions 102 and projections 101 that are offset in the radial direction with respect to the predetermined gear ratio. To do.

  In FIG. 7, the thick one-dot chain line indicates a predetermined gear ratio, and a set of engaging portions 102 and a set of protrusions 101 are arranged in a staggered manner in the radial direction with respect to the predetermined gear ratio. With such a configuration, when the primary disk 32 and the secondary disk 34 are pressed by the pressing roller 140, a plurality of the engaging portions 102 and the protruding portions 101 are simultaneously engaged as shown by the broken lines, and sequentially engaged by rotation. Repeat joining and leaving.

  With this configuration, a larger torque can be transmitted when the pressing force of the pressing roller 140 is the same as compared with the case where one engaging portion 102 and one protrusion 101 are engaged. . Further, when the transmission torque is the same, the pressing force of the pressing roller 140 can be small.

  FIG. 8 is an explanatory diagram showing the positions of the engaging portion 102 of the disk 32a and the protrusion 101 of the disk 34a according to this embodiment.

  Further, in the present embodiment, in order to smoothly move the pressing roller 140 and change the gear ratio, the engaging portion 102 and the protruding portion 101 are aligned in a row in the radial direction in the shaft center connection line O. A shift area V is provided.

  In the speed change area V, even when the pressing roller 140 keeps pressing the primary disk 32 and the secondary disk 34, the pressing roller 140 moves to move to the engaging portion 102 and the protruding portion 101 corresponding to the adjacent gear ratio. can do.

  The pressing roller 140 reaches the speed change area V every time the primary disk 32 rotates once. When shifting, the control device 3 moves the pressing roller 140 by the shift actuator 133 at the timing when the pressing roller 140 is positioned in the shift area V. At this time, since the pressing roller 140 can immediately hold the engaging portion 102 and the protruding portion 101 that are adjacent in the radial direction, the gear ratio can be changed while the torque is transmitted.

  Next, a modification of the embodiment of the present invention will be described.

  FIG. 9 is an explanatory diagram of the engaging portion 102 of the disk 32a and the protrusion 101 of the disk 34a according to a modification of the present embodiment.

  As shown in FIG. 6, the primary disk 32 and the secondary disk 34 are provided with the engaging portion 102 and the protruding portion 101, respectively, and these are engaged by the pressing roller 140. The pressing roller 140 presses the secondary disk 34 while elastically deforming the disk 32a of the primary disk 32.

  At this time, the engaging portion 102 to be engaged and the engaging portion 102 adjacent to the protruding portion 101 may come into contact with the distal end portion of the protruding portion 101. When the engaging portion 102 and the protruding portion 101 that are not engaged come into contact with each other, abnormal noise and vibration are caused.

  Therefore, in the modification shown in FIG. 9, the protruding portion 101 is provided so that no protruding portion 101 other than the engaging protruding portion 101 protrudes on the surface of the disk 34 a of the secondary disk 34 provided with the protruding portion 101. The elastic member 120 made of resin having the same thickness as the height was provided.

  The elastic member 120 has such a thickness that the non-engaged protrusion 101 does not protrude from the surface of the disk 34 a, that is, the surface of the elastic member 120, and the engagement portion 102 and the protrusion 101 are pressed against the pressing roller 140. When it is pressed, the engaging portion 102 and the protruding portion 101 are engaged by elastically deforming so that only the protruding portion 101 protrudes.

  With such a configuration, the protruding portion 101 is not projected by the elastic member 120 at a position other than the engaging portion 102 and the protruding portion 101 to be engaged, so that the contact between the engaging portion 102 and the protruding portion 101 is prevented. Abnormal noise and vibration due to contact between the engaging portion 102 and the protruding portion 101 can be prevented.

  As described above, the present embodiment is provided on the input shaft 31 to which the rotation from the motor 20 that is a power source is input, the output shaft 33 that is arranged in parallel to the input shaft 31, and the input shaft 31. A primary disk 32, a secondary disk 34 provided on the output shaft 33 and partially overlapping the primary disk 32, a pair of pressing rollers 140 disposed on both sides of the primary disk 32 and the secondary disk 34, and a pair of This is a multi-disc transmission including a speed change actuator 133 that moves the pressing roller 140 between the input shaft 31 and the output shaft 33.

  In the multi-disc transmission of this embodiment, one of the primary disk 32 and the secondary disk 34 is provided with a plurality of protrusions 101 on the surface, and either the primary disk 32 or the secondary disk 34 is provided on the other. Is provided with a plurality of engaging portions 102 corresponding to the plurality of protruding portions 101, and the protruding portion 101 and the engaging portion 102 are engaged with each other by sandwiching the primary disk 32 and the secondary disk 34 by the pressing roller 140. Thus, the rotation of the primary disk 32 is transmitted to the secondary disk 34.

  In the multi-disc transmission of this embodiment, with such a configuration, the primary disc 32 and the secondary disc 34 are not frictioned, and the projection 101 and the engaging portion 102 are mechanically engaged to generate torque. introduce. As a result, the actuator 190 and the elastic member of the pressing force adjusting mechanism 132 that adjusts the pressing force of the pressing roller 140 can be reduced in size, so that the transmission torque can be increased without increasing the size of the speed change mechanism 30. This effect corresponds to claims 1 and 8.

  In particular, in the present embodiment, since a large torque can be transmitted with two primary disks 32 and one secondary disk 34, the size and weight of the multi-disk transmission can be reduced without increasing the number of disks. .

  In the multi-disc transmission according to the present embodiment, the protrusions 101 and the engaging portions 102 respectively provided at the first predetermined radial position of the primary disk 32 and the second predetermined radial position of the secondary disk 34 are engaged. Thus, the rotation of the primary disk 32 is transmitted to the secondary disk 34 at a gear ratio corresponding to the first and second predetermined radial positions.

  With such a configuration, the target gear ratio can be obtained only with a simple configuration of the protrusion 101 and the engagement portion 102, so that the weight is reduced compared to the gear type or belt type gear ratio. The transmission torque can be increased without increasing the size of the speed change mechanism 30. This effect corresponds to claim 2.

  In the multi-disc transmission according to the present embodiment, a plurality of protrusions 101 and engaging portions 102 can be simultaneously engaged by disposing the engaging portions 102 and the engaging portions 102 in a staggered manner. With such a configuration, a large torque can be transmitted. This effect corresponds to the third aspect.

  In the multi-disc transmission according to the present embodiment, the primary disc 32 and the secondary disc 34 are provided with a shift area V in which the protruding portions 101 and the engaging portions 102 are arranged in the radial direction. Since the pressing roller 140 is moved when the pressing roller 140 is in the speed change area, the speed ratio can be changed while torque is transmitted when the speed ratio is changed. This effect corresponds to claim 4.

  In the multi-disc transmission of the present embodiment, the protrusion 101 is configured by the pin 111 that penetrates the secondary disc 34 in the plate thickness direction, so that the processing becomes easier as compared with the case where the disc surface is processed three-dimensionally. The cost of the speed change mechanism 30 can be reduced. This effect corresponds to the fifth aspect.

  The multi-disc transmission according to the present embodiment includes an elastic member 120 on the surface of the secondary disk, and the elastic member 120 is compressed by sandwiching the primary disk 32 and the secondary disk 34 by the pressing roller 140, and is engaged with the protrusion 101. The joint portion 102 is engaged. The elastic member 120 is configured to have substantially the same thickness as the height at which the protruding portion 101 protrudes from the surface of the secondary disk 34.

  With such a configuration, since the protrusion 101 is not projected by the elastic member 120 at a position other than the engagement portion 102 and the protrusion 101 engaged by the pressing roller 140, the contact between the engagement portion 102 and the protrusion 101. Is prevented, and abnormal noise and vibration due to contact between the engaging portion 102 and the protruding portion 101 can be prevented. This effect corresponds to claims 6 and 7.

  The embodiment of the present invention has been described above, but the above embodiment is merely a part of an application example of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. is not.

  In the present embodiment, the primary disk 32 includes the engaging portion 102, and the secondary disk 34 includes the protruding portion 101. However, the primary disk 32 includes the protruding portion 101, and the secondary disk 34 includes the engaging portion 102. Good.

DESCRIPTION OF SYMBOLS 1 Wheel drive device 3 Control apparatus 10 Wheel 20 Motor 30 Transmission mechanism (multi disk transmission)
DESCRIPTION OF SYMBOLS 31 Input shaft 32 Primary disk 33 Output shaft 34 Secondary disk 72 Brake device 101 Protrusion part 101a Chamfer part 102 Engagement part 111 Pin 120 Elastic member 130 Pressing roller mechanism 131 Disc clamp mechanism 132 Pressing force adjustment mechanism 133 Speed change actuator 140 Pressing roller 190 Actuator

Claims (7)

A multi-disc transmission,
An input shaft to which rotation from a power source is input;
An output shaft disposed parallel to the input shaft;
A primary disk provided on the input shaft;
A secondary disk provided on the output shaft and partially overlapping the primary disk;
A pair of pressing rollers disposed on both sides of the primary disk and the secondary disk;
A speed change actuator that moves the pair of pressing rollers between the input shaft and the output shaft;
With
The secondary disk is provided with a plurality of protrusions projecting on the surface, and the primary disk is provided with a plurality of holes that open corresponding to the plurality of protrusions,
The protrusion is constituted by a pin that penetrates the secondary disk in the plate thickness direction,
By sandwiching the primary disk and the secondary disk by the pressing roller, the protrusion is inserted into the hole and mechanically engaged, and rotation of the primary disk is transmitted to the secondary disk. A featured multi-disc transmission. The multi-disc transmission according to claim 1,
By engaging the projections and the holes provided at the first predetermined radial position of the primary disk and the second predetermined radial position of the secondary disk, respectively, the first and second predetermined radial positions are engaged. A multi-disc transmission characterized in that the rotation of the primary disc is transmitted to the secondary disc by a gear ratio corresponding to a radial position of the disc. The multi-disc transmission according to claim 1 or 2,
The multi-disc transmission is characterized in that the rotation of the primary disc is transmitted to the secondary disc by simultaneously engaging a plurality of the protrusions and the hole portions. The multi-disc transmission according to any one of claims 1 to 3,
The primary disk and the secondary disk are provided with a speed change area in which the protrusion and the hole are arranged in a radial direction,
The multi-disc transmission, wherein the speed change actuator moves the pressing roller when the pressing roller is in the speed change area. The multi-disc transmission according to claim 1,
An elastic member is provided on the surface of the secondary disk,
The multi-disk transmission , wherein the elastic member is compressed by sandwiching the primary disk and the secondary disk by the pressing roller, and the protrusion and the hole engage with each other . The multi-disc transmission according to claim 5,
The multi-disk transmission according to claim 1, wherein the elastic member has a thickness that is substantially the same as a height at which the protrusion protrudes from the surface of the secondary disk . A wheel drive device comprising the multi-disc transmission according to any one of claims 1 to 6, wherein the power source is a motor disposed inside or near the wheel.

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