JP6511687B2 - Power transmission - Google Patents

Description

  The present invention relates to a power transmission device, and more particularly, to a power transmission device that operates to transmit torque from a drive shaft to a driven shaft while blocking torque from the driven shaft to the drive shaft.

  In some vehicles, the drive unit assists in opening and closing the door. For example, a drive unit mounted on a vehicle of this type is generally configured to rotate an output arm by driving a motor. The output arm is optionally connected to the door via a link. When the motor of the drive unit is driven, the output arm is rotated, and the door can be moved in the opening direction or the closing direction with respect to the vehicle body. For example, if the drive unit operates in a state where the striker and the latch are disengaged, the opening of the partially opened door is assisted, and the door can be opened with a small operation force. In addition, if the drive unit operates in the opposite direction to the above with the door open, it is possible to close the door without touching the hand, which is advantageous in terms of convenience.

  However, when the operator performs a manual operation while the door is moved by the drive unit, the operability may be impaired. That is, when the operator manually moves the door in the opening direction while the door is moved in the opening direction by the drive unit, the door is operated when the operation of the operator is faster than the moving speed of the door by the drive unit. I feel heavy opening operation. Similarly, even if the operator manually operates the door in the closing direction while the door is being moved in the closing direction by the driving unit, the door may be operated faster than the moving speed of the door by the driving unit. I feel heavy closing operation.

  For this reason, this type of drive unit is provided with an application of a power transmission device configured to cut off torque transmission to the door when fast operating force is applied while moving the door. ing. For example, Patent Document 1 discloses a first arm that protrudes in the radial direction when the drive shaft rotates in the first direction, and a second arm that protrudes in the radial direction when the drive shaft rotates in the second direction. And a power transmission device having a protrusion on an inner peripheral surface of a portion surrounding a periphery of the drive shaft in the driven shaft.

  In this power transmission device, when the drive shaft is rotated in the first direction, the radially projecting first arm abuts on the projection of the driven shaft, so that torque can be transmitted from the drive shaft to the driven shaft it can. Similarly, even when the drive shaft rotates in the second direction, the radially projecting second arm abuts on the projection of the driven shaft, so torque can be transmitted from the drive shaft to the driven shaft .

  On the other hand, when the drive shaft is rotating in the first direction, when the driven shaft rotates in the first direction at a speed exceeding this, it is caused to retract relative to the radially projecting first arm The protrusion of the driven shaft abuts on the first arm. Therefore, since the torque from the driven shaft to the drive shaft is cut off, the drive unit connected to the drive shaft does not become a load for the rotation of the driven shaft, and the driven shaft can be rotated by a small operating force. it can.

JP-A-9-273358

  In the power transmission device described in Patent Document 1, the first arm and the second arm are respectively provided with engagement pins, and these engagement pins are inserted into guide slots formed in the guide plate. By appropriately moving the guide slots according to the rotational direction of the drive shaft, the respective engagement pins project in the radial direction. Therefore, in order to smoothly operate the first arm and the second arm described in Patent Document 1, a high dimensional accuracy is required for the guide slot and the engagement pin for guiding the movement path of these arms. As a result, considering productivity, it is not necessarily preferable. In addition, the above-mentioned subject is not specific to the power transmission means of the drive unit which assists the opening and closing of the door, but switches between the state of transmitting the torque between the drive shaft and the driven shaft and the state of interrupting the torque. If there is, it can occur as well.

  An object of the present invention is, in view of the above-mentioned situation, to provide a power transmission which can improve operability without losing productivity.

  In order to achieve the above object, a power transmission device according to the present invention is interposed between a drive shaft and a driven shaft having a cylindrical portion surrounding the periphery of the drive shaft, and the drive relative to the device main body When the shaft rotates in the first direction and the second direction, torque is transmitted from the drive shaft to the driven shaft, while the driven shaft is the first shaft with respect to the apparatus main body. Power transmission device that operates to cut off the torque from the driven shaft to the drive shaft when rotated in the second direction and in the second direction, wherein both the drive shaft and the driven shaft are A recess is provided between the drive shaft and the cylindrical portion so as to be rotatable relative to one another and to form an accommodation space with the inner circumferential surface of the cylindrical portion, and the periphery of the recess is provided. The first crater at the end of the A roller and a clutch drum movably supporting the plate and the second clutch plate, a roller disposed in the housing space, and the roller being in contact with the inner circumferential surface of the cylindrical portion via the respective clutch plate And an individual clutch spring for urging the part, and a part of the cylindrical portion is provided with a protrusion protruding toward the inner peripheral side, and the first clutch plate and the second clutch plate The roller is allowed to move to the inner peripheral side by at least the protrusion of the protrusion when moving in a direction away from the inner circumferential surface of the cylindrical portion against the biasing force of the clutch spring. The drive shaft protrudes from the outer peripheral surface toward the inner peripheral surface of the driven shaft, and faces the first control unit facing the first clutch plate and the second clutch plate A cam member having two control units is provided, and in the state where the second control unit is separated from the second clutch plate when the drive shaft rotates in the first direction, the cam member The first control portion contacts the roller through the first clutch plate to rotate the clutch drum and the roller in the first direction, and the roller is projected from the cylindrical portion While the first control portion is separated from the first clutch plate when the drive shaft rotates in the second direction, the second control portion The clutch drum and the roller are rotated in the second direction by abutting on the roller through a clutch plate, and the roller is caused to abut on the projection of the cylindrical portion.

  Further, according to the present invention, in the above-described power transmission device, the first clutch plate and the second clutch plate are rotatably connected to each other via a common support shaft, and are directed toward the outer peripheral side. It is characterized in that it is disposed on the clutch drum via the support shaft in a state in which the interval gradually increases.

  Further, according to the present invention, in the above-described power transmission device, the clutch drum has the recess at a position shifted by 180 ° around the axis of the drive shaft, and clutch plates are respectively provided at both ends of the recess. The cam member is provided on the drive shaft at a position shifted by 180 ° around the axis, and each of the cam members is rotated when the drive shaft is rotated in the first direction. Contacting the first clutch plate disposed in each recess, and contacting the second clutch plate disposed in each recess when the drive shaft is rotated in the second direction It features.

  According to the present invention, the roller is brought into contact with the inner peripheral surface of the cylindrical portion through the first and second clutch plates by the biasing force of the clutch spring, and the cam member is either By contacting the clutch plate, torque is transmitted from the drive shaft to the driven shaft. On the other hand, when the driven shaft rotates at a speed exceeding this with respect to the rotation of the drive shaft, the projection of the cylindrical portion abuts against the roller and the clutch plate moves against the biasing force of the clutch spring. Since the roller moves to the inner circumferential side, the torque from the driven shaft to the drive shaft is cut off. Therefore, since a configuration for guiding the moving path is not required as in the prior art, it can be easily manufactured, and the operability can be improved without impairing the productivity.

FIG. 1 is a view conceptually showing the left side of a vehicle to which a power transmission apparatus according to an embodiment of the present invention is applied. FIG. 2 conceptually shows a connecting portion between the side door and the vehicle body of the vehicle shown in FIG. 1, and is an enlarged plan view of a state in which the side door is closed. FIG. 3 conceptually shows a connecting portion between the side door and the vehicle body of the vehicle shown in FIG. 1, and is an enlarged plan view of a state in which the side door is open. FIG. 4 is a side cross-sectional view of a hinge applied between the side door shown in FIG. 1 and the vehicle body. FIG. 5 shows the hinge shown in FIG. 4, in which (a) is an enlarged cross-sectional view of a state in which the needle bearing is accommodated in the groove of the hinge shaft, (b) is a needle bearing deviated from the hinge shaft FIG. 6 is an enlarged cross-sectional view of the state of FIG. FIG. 6 is a perspective view showing an appearance of a drive unit applied to the vehicle shown in FIG. FIG. 7 is a perspective view of a state in which the reduction gear of the drive unit shown in FIG. 6 is exposed. FIG. 8 is an exploded perspective view of the clutch mechanism of the drive unit shown in FIG. FIG. 9 is a perspective view showing an essential part of a clutch mechanism applied to the drive unit shown in FIG. FIG. 10 is a perspective view showing an essential part of a clutch mechanism applied to the drive unit shown in FIG. FIG. 11 is a view for showing the operation of the clutch mechanism applied to the drive unit shown in FIG. 6, in which the cam member is separated from the two clutch plates. FIG. 12 is a view showing a state where the electric motor is driven from the state shown in FIG. 11 and the control portion of the cam member abuts on one clutch plate and the roller abuts on the meshing surface of the driven shaft. FIG. 13 is a view showing a state in which the driven shaft is manually operated at a speed exceeding the cam member from the state shown in FIG. FIG. 14 is a view showing a state in which the driven shaft is further rotated from the state shown in FIG. 13 and the torque from the driven shaft to the electric motor side is cut off.

  Hereinafter, preferred embodiments of a power transmission device according to the present invention will be described in detail with reference to the attached drawings.

  FIG. 1 shows a vehicle to which a power transmission device according to an embodiment of the present invention is applied. The vehicle illustrated here is a four-door four-wheeled vehicle provided with a front side door D and a rear side door D on both side surfaces of a vehicle body B, respectively. The front side door D and the rear side door D are, as shown in FIGS. 1 to 3, a door main body DM configured in a box shape by an outer panel OP and an inner panel IP, and a sash provided in a frame shape on the upper portion of the door main body DM. It comprises with DS. Each side door D is connected to the vehicle body B by the upper hinge 10 and the lower hinge 10 provided on the front surface DMF of the door body DM, and rotates around the hinge shaft 11 along the vertical direction. It is possible to open and close the boarding opening BO.

  As the upper hinge 10 and the lower hinge 10, as shown in FIGS. 4 and 5, one in which a check mechanism is built in between the outer hinge plate 12 and the inner hinge plate 13 is applied. That is, the hinge shaft 11 is attached to the outer hinge plate 12 in a state where relative rotation is restricted. A needle bearing 14 and a coil spring 15 are sequentially provided around the hinge shaft 11. The needle bearings 14 are arranged at equal intervals in the circumferential direction by the retainer 16 and are accommodated in grooves 11 a provided on the circumferential surface of the hinge shaft 11. The retainer 16 of the needle bearing 14 is engaged with the inner hinge plate 13. For example, in the state where the side door D is closed, as shown in FIG. 5A, the needle bearing 14 is accommodated in the groove 11a of the hinge shaft 11, and the state is maintained by the coil spring 15. When the side door D is opened from this state, the inner hinge plate 13 rotates with respect to the outer hinge plate 12. As a result, as shown in FIG. 5B, the needle bearing 14 held by the retainer 16 is coiled. It will be in the state where it deviated from slot 11a, expanding spring 15. When the rotation of the inner hinge plate 13 with respect to the outer hinge plate 12 progresses, the needle bearing 14 is accommodated in the groove 11a of the hinge shaft 11 again as shown in FIG. In order to be maintained, the rotation of the inner hinge plate 13 will be checked. The code | symbol 17 in a figure is a cover which covers the outer periphery of the coil spring 15. As shown in FIG.

  As shown in FIG. 1, a window glass G is disposed on the sash DS of the side door D. The window glass G is vertically movably disposed along the elevation guide WG by an elevation mechanism (not shown) disposed inside the door body DM, and closes the opening of the sash DS when it moves upward. It is possible. When the window glass G moves downward, the window glass G is sequentially accommodated inside the door body DM, and the opening of the sash DS can be opened.

  In each side door D, a drive unit 20 is provided inside the door body DM. The drive unit 20 is for assisting opening and closing of the side door D with respect to the vehicle main body B, and as shown in FIGS. 6-8, the electric motor 21, the first reduction gear 22, the rotation sensor 23, A second reduction gear 24 and a clutch mechanism 25 are provided.

  As shown in FIG. 7, the first reduction gear 22 is a planetary gear mechanism in which a gear (not shown) fixed to the output shaft 21 a of the electric motor 21 is configured as a sun gear. In this planetary gear mechanism, the carrier 22b of the planetary carrier 22a is fixed to the gear case 22c, and the rotation of the sun gear is decelerated and output from the ring gear 22d. The rotation sensor 23 magnetically detects the rotation angle and the rotation direction of the ring gear 22 d which is the output of the first reduction gear 22. The second reduction gear 24 is configured by connecting two sets of planetary gear mechanisms. The two sets of planetary gear mechanisms are configured to include the common fixed ring gear 24a, and the rotation of the sun gear 24b in the front stage connected to the ring gear 22d of the first reduction gear 22 is decelerated and transmitted to the planetary carrier 24c in the rear stage. Further, it is outputted from a second decelerating output shaft (drive shaft) 24d connected to the planetary carrier 24c. Although not clearly shown in the figure, in each of the first reduction gear 22 and the second reduction gear 24, the rotation axis of the sun gear and the second reduction output shaft 24d are extended with respect to the output shaft 21a of the electric motor 21. It is configured to be

  The clutch mechanism 25 is interposed between the second decelerating output shaft 24d and the driven shaft 26 serving as the final output shaft as shown in FIG. 8, and torque is applied to the driven shaft 26 when the second decelerating output shaft 24d is rotated. While blocking the torque to the second decelerating output shaft 24d when the driven shaft 26 rotates. In the present embodiment, a clutch case 251 configured by a plate-shaped upper case 251a and a cylindrical lower case 251b, and a clutch drum 252 housed in the clutch case 251, a cam member 253, and a driven shaft 26 are provided. The clutch mechanism 25 is configured.

  The clutch drum 252 has a cylindrical base 252a and a large outer diameter flange 252b provided at one end of the base 252a, and can be rotated inside the clutch case 251 with the axis of the base 252a as the center of rotation. Housed in As apparent from the figure, a coil spring 254 is disposed between the flange 252b of the clutch drum 252 and the bottom wall of the lower case 251b. The coil spring 254 restricts the movement of the clutch drum 252 in the axial direction by urging the clutch drum 252 against the upper case 251a via the flange 252b.

  As shown in FIGS. 9 and 10, the clutch drum 252 is provided with recesses 252c at two circumferential surfaces of the base 252a. The recesses 252c have openings at positions mutually offset by 180 ° along the circumferential direction, and each have two clutch plates 271, 272 and a roller 28 inside.

  The clutch plates 271 and 272 are rotatably connected between the base end edges of each other via a support shaft 273. The two clutch plates 271 and 272 are arranged such that the support shaft 273 extends along the axial center of the base 252a and the distance between the tip end portions of the clutch plates 271 and 272 gradually increases toward the outer periphery of the base 252a. It is arrange | positioned by the recessed part 252c of the clutch drum 252 via. The clutch plates 271 and 272 are provided with contact pieces 271a and 272a at respective leading end edges, and a clutch spring 274 is provided between them. The contact pieces 271 a and 272 a are disc-like portions provided so as to be bent in a direction away from each other from a part of tip end portions of the clutch plates 271 and 272. The contact pieces 271 a and 272 a contact the inner peripheral surface of the base 252 a when the clutch plates 271 and 272 rotate in the direction approaching each other with the support shaft 273 as a center, and the two clutch plates 271 , 272 function to define a minimum depression angle. The clutch spring 274 is a torsion spring provided to bias the clutch plates 271 and 272 in the direction of closing each other and to press the respective contact pieces 271a and 272a against the inner peripheral surface of the base 252a. In the clutch spring 274, the support shaft 273 of the clutch plates 271 and 272 penetrates through the cylindrically wound portion, and the respective spring ends contact the back surface of the clutch plates 271 and 272 facing the inner peripheral side of the base 252a. It is arranged to be in contact.

  As shown in FIGS. 8 and 10, the roller 28 has a cylindrical shape having a substantially constant outer diameter over the entire length, and is in contact with the surface of the clutch plates 271 and 272 facing the outer peripheral side of the base 252a. It is arranged. As shown in FIG. 11, when the contact pieces 271a and 272a of the clutch plates 271 and 272 are in contact with the inner peripheral surface of the base 252a, a part of the roller 28 is on the outer peripheral side than the outer peripheral surface of the base 252a. Each dimension is set so as to protrude into the When the peripheral surface of the roller 28 is pressed toward the center of the base 252a against the biasing force of the clutch spring 274 from this state, the clutch plates 271 and 272 center the support shaft 273 as shown by the solid line in FIG. As a result, it is possible to rotate to the inner peripheral side of the base 252a, and to reduce the amount of projection of the roller 28 from the outer peripheral surface of the base 252a.

  As shown in FIG. 8, the cam member 253 is connected to the second decelerating output shaft 24d, and includes two control parts 253a. The control portion 253a protrudes in the radial direction from a position shifted by 180 ° with respect to the second decelerating output shaft 24d, and through an insertion hole (not shown) provided on the flange 252b of the clutch drum 252 It is inserted in the inside of base 252a, and it is arranged so that the back of clutch plates 271 and 272 may be countered. As shown in FIG. 11, when the contact pieces 271a and 272a of the clutch plates 271 and 272 are in contact with the inner peripheral surface of the base 252a, the control unit 253a of the cam member 253 performs all the clutch plates 271. , 272 are dimensioned so as to be separated from the back surface. When the cam member 253 is rotated toward one side with respect to the clutch drum 252 from this state, as shown in FIG. 12, on the back surface of one clutch plate 272, each control portion 253a is disposed in each recess 252c. While in contact with the other, the back surface of the other clutch plate 271 disposed in the individual recess 252c is maintained in a separated state. Similarly, when the cam member 253 is rotated toward the other with respect to the clutch drum 252, each control portion 253a abuts on the back surface of the other clutch plate 271 disposed in the respective recess 252c, while the respective recess is A state of being separated from the back surface of one clutch plate 272 disposed at 252c is maintained.

  The driven shaft 26 has a cylindrical shape, and is integrally formed with a meshing cylindrical portion (cylindrical portion) 261 whose one end is a closed end and an output portion 262 having a square pole shape provided at the closed end of the meshing cylindrical portion 261 The base portion 252a of the clutch drum 252 is accommodated inside the meshing cylinder portion 261, and the output portion 262 is accommodated inside the clutch case 251 in a state where the output portion 262 is exposed to the outside from the hole of the lower case 251b. As shown in FIG. 11, arc-shaped surfaces 261 a and meshing surfaces (projections) 261 b are alternately provided along the circumferential direction on the inner peripheral surface of the meshing cylindrical portion 261. The arc-shaped surface 261 a is a surface that forms an arc having an inner diameter larger than the maximum protrusion amount of the roller 28 in contact with the clutch plates 271 and 272. On the other hand, the meshing surface 261b is a flat surface that linearly connects the arced surfaces 261a to each other, and the maximum projection of the roller 28 in which the distance from the axial center of the meshing cylinder 261 contacts the clutch plates 271 and 272 It is formed to be smaller in size than the amount. However, the projection dimension d of the meshing surface 261 b is set smaller than the movable distance of the roller 28 to the inner circumferential side when the clutch plates 271 and 272 rotate to the inner circumferential side of the base 252 a about the support shaft 273. It is

  In the drive unit 20 configured as described above, for example, when the electric motor 21 is driven in the forward direction, the rotation of the output shaft 21a is decelerated through the first reduction gear 22 and the second reduction gear 24, and the second reduction output shaft 24d Rotate towards. When the second decelerating output shaft 24d rotates toward one side, in the clutch mechanism 25, as shown in FIG. 12, the back surface of one clutch plate 272 provided with the control portion 253a of the cam member 253 in each recess 252c. While the clutch drum 252 rotates toward one side via one clutch plate 272, and the respective rollers 28 rotate toward one side. When the roller 28 rotates in one direction, the circumferential surface of the roller 28 is in contact with the meshing surface 261 b of the meshing cylinder 261 positioned in the direction of travel.

  Here, the clutch plate 272 rotating the roller 28 is in a state where the control portion 253a of the cam member 253 is in contact with the back surface thereof. Therefore, the clutch plate 272 does not rotate to the inner peripheral side with respect to the base 252 a of the clutch drum 252, and the peripheral surface of the roller 28 is maintained in contact with the meshing surface 261 b of the meshing cylinder 261. As a result, when the second decelerating output shaft 24 d rotates, torque is transmitted to the driven shaft 26 via the cam member 253, the clutch plate 272, the roller 28 and the meshing cylinder portion 261.

  On the other hand, when the driven shaft 26 is rotated by the electric motor 21, when the driven shaft 26 is rotated in the same direction at a speed exceeding the clutch drum 252, as shown in FIG. Contacts the circumferential surface of the roller 28, and the roller 28 rotates with the driven shaft 26 with respect to the clutch drum 252. Here, the control portion 253 a of the cam member 253 is not in contact with the back surface of the clutch plate 271 positioned in the traveling direction of the roller 28. Therefore, when the roller 28 abuts, as shown in FIG. 14, the clutch plate 271 rotates in the inner peripheral side so as to separate the contact piece 271a from the inner peripheral surface of the base 252a, and the roller 28 takes the base 252a. Move toward the center of the inner radius. As a result, since the amount of projection of the roller 28 from the outer peripheral surface of the clutch drum 252 decreases, the meshing surface 261 b of the meshing cylinder 261 passes through the roller 28, and torque is transmitted to the clutch drum 252. There is no. Even when the electric motor 21 is driven reversely, torque is transmitted to the driven shaft 26 by the rotation of the second decelerating output shaft 24 d as described above. It is also the same as described above that torque is not transmitted from the driven shaft 26 to the clutch drum 252 even if the driven shaft 26 is rotated at a speed exceeding the clutch drum 252 from this state.

  For the above-described vehicle, as shown in FIG. 1, the clutch mechanism 25 is at the lower side, and the output shaft 21 a of the electric motor 21 is in the extending direction of the hinge shaft 11. The drive unit 20 is attached. The position where the drive unit 20 is attached is the space A between the front face DMF to which the hinge 10 is attached and the lifting guide WG inside the door body DM. As shown in FIG. 2, the driven shaft 26 of the drive unit 20 is connected to the pillar P of the vehicle main body B via the output arm 30 fixed to the output portion 262 and the open / close link arm 31. The open / close link arm 31 is connected to the vehicle body B at a portion between the upper hinge 10 and the lower hinge 10.

  As described above, when the electric motor 21 of the drive unit 20 is driven, torque is transmitted to the driven shaft 26. Therefore, for example, if the drive unit 20 is operated in a state in which the striker and the latch are disengaged, as shown in FIG. 3, the opening of the side door D opened halfway is assisted, which is small. It becomes possible to open the side door D by the operating force. Further, when the drive unit 20 is operated in the opposite direction to the above with the side door D opened, as shown in FIG. 2, the side door D can be closed without touching the hand.

  During these operations, according to the drive unit 20, when the side door D is manually operated in the same direction at a speed exceeding the opening / closing speed of the side door D by the electric motor 21, as described above, the driven shaft Since the torque transmission from 26 to the electric motor 21 side is interrupted, the load on the drive unit 20 does not occur, and the situation that the open / close operation of the side door D does not feel heavy is not caused. Moreover, since the open / close link arm 31 is connected to the vehicle body B at a portion between the upper hinge 10 and the lower hinge 10, there is no possibility that the open / close link arm 31 may be twisted at the time of operation . Furthermore, in the drive unit 20 housed in the side door D, only the open / close link arm 31 is exposed to the outside from the front face DMF of the side door D, and there is no influence on the living space of the vehicle. There is no loss of sexuality.

  As described above, according to the drive unit 20, the urging force of the clutch spring 274 causes the roller 28 to abut on the arc-shaped surface 261a of the meshing cylinder portion 261 via the clutch plates 271 and 272, and the second decelerating output shaft 24d When the motor rotates, the control portion 253a of the cam member 253 abuts on any of the clutch plates 271 and 272, and the roller 28 abuts on the meshing surface 261ab of the meshing cylindrical portion 261 to follow the second decelerating output shaft 24d. The torque is transmitted to the shaft 26. On the other hand, when the driven shaft 26 rotates at a speed exceeding this with respect to the rotation of the second decelerating output shaft 24 d, the meshing surface 261 b of the meshing cylindrical portion 261 abuts on the roller 28 to bias the clutch spring 274. The clutch plates 271 and 272 move against it and the roller 28 moves to the inner peripheral side, so that the torque from the driven shaft 26 to the second decelerating output shaft 24d is cut off. Therefore, since a configuration for guiding the moving path is not required as in the prior art, it can be easily manufactured, and the operability can be improved without impairing the productivity.

  Moreover, in the vehicle to which the drive unit 20 described above is applied, the drive unit 20 can be accommodated in advance inside the door body DM in the process of assembling and manufacturing the side door D. Therefore, in the main vehicle assembly and manufacturing line, after attaching the side door D to the vehicle main body B, only work for wiring connection with the vehicle main body B side is required, and the production efficiency can be improved. It will be possible.

  After the side door D is closed or after the side door D is opened, the electric motor 21 is rotated in the reverse direction for a preset time, and the control portion 253a of the cam member 253 controls which clutch plate 271, 272 It is controlled to return to the state shown in FIG. For example, when the clutch mechanism 25 is stopped in the state shown in FIG. 12, when the side door is manually operated in the direction in which the meshing cylinder 261 rotates counterclockwise, the control portion of the cam member 253 on the clutch plate 272 The roller 253 can not move to the inner circumferential side because the contact 253 a is in contact. As a result, the torque transmission from the driven shaft 26 to the electric motor 21 is not interrupted, and there is a possibility that the electric motor 21 may become a load when performing the manual operation. Therefore, in the drive unit 20, the electric motor 21 is rotated in the reverse direction to stop the clutch mechanism 25 in the state shown in FIG.

  In the embodiment described above, the clutch mechanism 25 including two sets of the clutch plates 271 and 272 and the roller 28 is illustrated, but the present invention is not limited to this, and one set of the clutch plate and the roller is provided. The clutch mechanism may be configured by providing three or more sets. Further, although the clutch plates 271 and 272 rotate around the support shaft 273 to allow the roller 28 to move toward the inner peripheral side, the movement mode of the clutch plate does not necessarily have to be a rotation. For example, the roller may be configured to be allowed to move to the inner circumferential side by parallel movement. In the embodiment described above where the clutch plates 271 and 272 are rotatably provided, the base end edges of the common support shaft 273 are rotatably connected to each other, but individual support Of course, the clutch plate may be rotated about the shaft.

24d second decelerating output shaft 25 clutch mechanism 26 driven shaft 28 roller 252 clutch drum 252a base 252b flange 252c recessed portion 253 cam member 253a control portion 254 coil spring 261 meshing cylinder portion 261a arcuate surface 261b meshing surface 271, 272 clutch plate 271a, 272a Contact piece 273 Support shaft 274 Clutch spring

Claims (3)

When it intervenes between the drive shaft and the driven shaft having a cylindrical portion surrounding the periphery of the drive shaft and the drive shaft rotates in the first direction and the second direction with respect to the apparatus main body In each case, torque is transmitted from the drive shaft to the driven shaft, and when the driven shaft is rotated in the first direction and the second direction with respect to the device main body, In a power transmission device operable to cut off a torque from the driven shaft to the drive shaft,
Disposed between the drive shaft and the cylindrical portion in such a manner as to be relatively rotatable with respect to both the drive shaft and the driven shaft, and a storage space is formed between the drive shaft and the inner peripheral surface of the cylindrical portion And a clutch drum movably supporting a first clutch plate and a second clutch plate at portions that are both ends along the circumferential direction of the recess,
A roller disposed in the housing space;
And an individual clutch spring for urging the roller into contact with the inner peripheral surface of the cylindrical portion through the respective clutch plates, and a part of the cylindrical portion is directed to the inner peripheral side. Provide a protruding protrusion,
When the first clutch plate and the second clutch plate move in a direction away from the inner peripheral surface of the cylindrical portion against the biasing force of the clutch spring, the first clutch plate and the second clutch plate are at least as much as the protrusion of the protrusion The roller is allowed to move to the inner peripheral side,
The drive shaft protrudes from the outer peripheral surface toward the inner peripheral surface of the driven shaft, and a first control unit facing the first clutch plate and a second control unit facing the second clutch plate Provide a cam member with
When the drive shaft rotates in the first direction, the first control unit performs the first clutch while the cam member is separated from the second clutch plate when the drive shaft rotates in the first direction. The clutch drum and the roller are rotated in the first direction by coming into contact with the roller via a plate, and the roller is brought into contact with the projection of the cylindrical portion, while the drive shaft is moved When rotating in two directions, the second control unit contacts the roller via the second clutch plate in a state where the first control unit is separated from the first clutch plate A power transmission device, wherein the clutch drum and the roller are rotated in the second direction, and the roller is brought into contact with the projection of the cylindrical portion.   The first clutch plate and the second clutch plate are rotatably connected to each other via a common support shaft, and the distance between the first clutch plate and the second clutch plate is gradually increased toward the outer peripheral side via the support shaft. The power transmission device according to claim 1, wherein the power transmission device is disposed on the clutch drum. The clutch drum has the recess at a position shifted by 180 ° around the axis of the drive shaft, and clutch plates are supported at portions serving as both ends of the recess,
The drive shaft is provided with the cam member at a position shifted by 180 ° around the shaft center,
Each of the cam members abuts on the first clutch plate disposed in each recess when the drive shaft rotates in the first direction, and the drive shaft rotates in the second direction. The power transmission device according to claim 1 or 2, wherein the power transmission device is in contact with the second clutch plate disposed in each of the recessed portions in the case where it is used.

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