JP5826618B2 - Clutch, motor and vehicle door opening and closing device - Google Patents

Description

  The present invention includes a mechanical clutch that is provided in a motor or the like serving as a drive source of a vehicle door opening and closing device, and that connects and disconnects a drive shaft and a driven shaft, a motor including the clutch, and a motor with the clutch. The present invention relates to a vehicle door opening and closing device.

  2. Description of the Related Art In recent years, some automobiles equipped with a sliding door that opens and closes an entrance / exit provided on the side of a vehicle body are equipped with a vehicle door opening / closing device that automatically opens and closes the sliding door by a driving force of a motor. In this vehicle door opening and closing device, it is required that the sliding door can be manually opened and closed. Therefore, for example, the vehicle door opening and closing device described in Patent Document 1 includes a mechanical clutch that enables automatic opening and closing and manual opening and closing in a motor serving as a drive source.

  The mechanical clutch described in Patent Document 1 includes a drive connecting portion that can rotate integrally with a drive shaft of a motor body, an intermediate plate that is held at a predetermined relative rotational position with respect to the drive connecting portion via a spring, And a driven shaft coupled to the door side and a driven cylindrical portion that can rotate integrally. Further, a roller member is disposed between the drive connecting portion and the intermediate plate in the radial direction and the driven cylindrical portion. This roller member is urged radially inward by a tension coil spring.

  In this clutch, when the motor main body is stopped, the roller member is disposed at a non-engagement position where the drive connecting portion and the driven cylindrical portion are not engaged in the rotation direction, and the initial state in which the drive shaft and the driven shaft are disconnected. It has become. Therefore, since the drive shaft and the driven shaft are disconnected and the drive shaft is not rotated, the door can be manually opened and closed easily.

  On the other hand, when the motor body is driven, the intermediate plate rotates with the rotation of the drive connecting portion, and the roller member circulates along with it. The roller member is moved outward in the radial direction by the centrifugal force at the time of rotation, and is disposed at an engagement position sandwiched between the intermediate plate and the driven cylindrical portion. In other words, the roller member is connected to connect the drive shaft and the driven shaft. Further, the roller member disposed at the engagement position is sandwiched between the drive connecting portion and the driven cylindrical portion that are rotated relative to the intermediate plate against the biasing force of the spring. That is, the drive connecting portion and the driven cylindrical portion are connected from the initial state where the drive shaft and the driven shaft are disconnected from each other to connect the drive shaft and the driven shaft. Then, since the drive connecting portion and the driven cylindrical portion are engaged in the rotation direction via the roller member, the driven cylindrical portion is rotated together with the drive connecting portion. As a result, the driven shaft is rotated, and the slide door connected to the driven shaft is automatically opened and closed.

  When the driving of the motor body is stopped, the drive connecting portion is rotated relative to the intermediate plate by the biasing force of the spring, and the holding of the roller member by the drive connecting portion and the driven cylindrical portion is released. That is, the drive connecting portion and the driven cylindrical portion are returned from the connected state to the initial state by the biasing force of the spring. Further, the roller member is moved radially inward by the urging force of the tension coil spring and is disposed at the non-engagement position. That is, the roller member returns from the connected state to the initial state by the urging force of the tension coil spring.

  If such a mechanical clutch is used, it is not necessary to carry out wiring for power feeding inside the motor as in the case of using an electromagnetic clutch, for example, and the internal structure of the motor becomes complicated. Is suppressed.

JP 2008-133951 A

  However, in the clutch described in Patent Document 1, a tension coil spring (biasing member) is used to return a mechanism composed of a roller member that moves between an engaged position and a non-engaged position from a connected state to an initial state. ) Is provided. In addition, a spring (biasing member) is provided in order to return the mechanism that clamps the roller member disposed at the engagement position between the drive connecting portion and the driven cylindrical portion from the connected state to the initial state. As described above, the drive shaft and the driven shaft are disconnected in the initial state when the drive shaft is not driven, while the drive shaft and the driven shaft are connected to each other when the drive shaft is driven. If each of the urging members for returning to the initial state is arranged one by one, there is a problem that the number of parts increases.

  The present invention has been made in view of such circumstances, and an object thereof is to provide a clutch capable of reducing the number of urging members, a motor including the clutch, and a vehicle door opening / closing device. is there.

In order to solve the above problem, the invention according to claim 1 is in an initial state in which the drive shaft and the driven shaft are disconnected when the drive shaft is not driven, while the drive shaft is driven when the drive shaft is driven from the drive shaft side. A plurality of mechanisms connected to the driven shaft, wherein the driven shaft is disconnected from the drive shaft when the drive shaft is not driven, while the drive shaft and the driven are driven when driven from the drive shaft side; a clutch operable to connect the shaft, in the clutch having a biasing member that exerts a biasing force so as to return the at least two of the mechanism to the initial state of the plurality of said mechanisms, said drive A drive-side rotator provided to be rotatable integrally with the shaft; a driven-side rotator provided to be rotatable integrally with the driven shaft; and the drive-side rotator and the driven-side rotator in the radial direction. Toru And a non-engagement position where the drive-side rotator and the driven-side rotator are not engaged with each other in the rotational direction, and radially outward from the non-engagement position. A power transmission member that is moved between an engagement position that engages the drive side rotation body and the driven side rotation body in a rotation direction; and the power transmission member that is engaged and the engagement position is not engaged. The power transmission member is moved from the disengaged position by the cam portion in accordance with the relative rotation of the guide member having a cam portion that guides the movement of the power transmission member between the joint position and the driving side rotating body. A cam mechanism for guiding to the engagement position, a holding mechanism for holding the power transmission member at the engagement position by the guide member moved radially outward by the centrifugal force generated by rotating with the driving side rotating body, The power transmission disposed at the engagement position. At least two of three mechanisms of a clamping mechanism that clamps a member between the driving side rotating body and the driven side rotating body, and the biasing member is configured to move the power when the driving side rotating body is stopped. The gist thereof is to urge at least two of the at least two mechanisms so as to dispose the transmission member at the disengaged position .

  According to the configuration, the biasing member exerts a biasing force so as to return at least two mechanisms to the initial state, and therefore, when a biasing member for returning each of the plurality of mechanisms to the initial state is provided. As compared with the above, the number of urging members can be reduced. As a result, the number of parts can be reduced. Furthermore, the structure of the clutch can be simplified and the assembling property can be improved.

  According to this configuration, the urging member includes at least two of the cam mechanism, the holding mechanism, and the clamping mechanism so that the power transmission member is disposed in the non-engagement position when the driving side rotating body is stopped, that is, in the initial state. It is energized to be in a state. Therefore, the number of urging members for returning at least two of the cam mechanism, the holding mechanism, and the clamping mechanism to the initial state can be reduced. Further, when the clutch includes a cam mechanism, when the driving side rotating body and the guide member are rotated together at the start of the rotational driving of the driving side rotating body, the power transmission member held by the driving side rotating body and The cam portion of the guide member is rotated together. When the drive side rotating body and the guide member rotate together, the power transmission member is guided by the cam portion and moves from the non-engagement position to the engagement position. Thus, since the movement of the power transmission member is performed in a state in which the movement direction is regulated by the cam portion, the power transmission member stably moves from the non-engagement position to the engagement position while being guided by the cam portion. Is done. Accordingly, it is possible to improve the reliability of the operation of connecting the driving side rotating body and the driven side rotating body. Further, when the clutch includes a holding mechanism, the power transmission member is held at the engagement position by the guide member that is moved radially outward by the centrifugal force when the driving side rotating body is driven to rotate. Therefore, since the state where the driving side rotating body and the driven side rotating body are connected via the power transmission member is stably maintained, the driving side rotating body is stably stabilized from the driving side rotating body via the power transmission member. The rotational driving force can be transmitted. Further, since the power transmission member is held at the engagement position by the guide member, a frictional force or the like is generated to maintain the state where the driving side rotating body and the driven side rotating body are connected when the driving side rotating body is driven to rotate. There is no need to provide a separate means. Therefore, it is suppressed that the structure and operation | movement of a clutch are complicated. In addition, when the clutch includes a clamping mechanism, the power transmission member arranged at the engagement position is clamped by the driving side rotating body and the driven side rotation body, so that the power transmission member is arranged at the engagement position. It is easy to maintain, and the rotational driving force can be stably transmitted from the driving side rotating body to the driven side rotating body.

According to a second aspect of the present invention, in the clutch according to the first aspect , the clutch mechanism includes at least the cam mechanism and the holding mechanism, and the urging member has the power transmission member moved to the non-engagement position side. The gist of the invention is to urge the guide member so as to rotate the drive-side rotator and the guide member together, and to urge the guide member radially inward.

According to this configuration, the urging member can easily return both the cam mechanism and the holding mechanism to the initial state only by urging the guide member.
According to a third aspect of the present invention, in the clutch according to the second aspect , the cam portion includes a first guide portion for arranging the power transmission member at the non-engagement position, and the first guide portion. A second guide portion provided on the outer side in the radial direction for guiding the power transmission member to the engagement position, and a cam extending from the first guide portion to the second guide portion and slidingly contacting the power transmission member And the biasing member biases the cam surface in the radial direction.

  According to this configuration, the biasing member biases the guide member in the radial direction by biasing the cam surface that guides the movement of the power transmission member from the non-engagement position to the engagement position in the radial direction. In addition, the guide member can be biased in the rotational direction. Therefore, in order to return the two mechanisms of the cam mechanism and the holding mechanism to the initial state, it is not necessary to newly add a configuration for applying the urging force of the urging member to the two mechanisms. As a result, the clutch configuration is prevented from being complicated.

The invention described in claim 4 is the clutch according to claim 3 , wherein the biasing member biases the power transmission member radially inward.
According to this configuration, since the power transmission member is a component related to all the mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism, by urging the power transmission member with the urging member, a new component can be obtained. Even if it is not added, the biasing force of the biasing member can be easily applied to the cam mechanism, the holding mechanism, and the clamping mechanism via the power transmission member.

According to a fifth aspect of the present invention, in the clutch according to any one of the second to fourth aspects, the power transmission member includes the clamping mechanism, the driving side rotating body, and the driven side rotating body. The gist of the invention is that it includes an auxiliary biasing member that biases the driving side rotating body so that the clamping is released.

  According to this configuration, the holding mechanism releases the holding of the power transmission member by the driving side rotating body and the driven side rotating body by the biasing force of the auxiliary biasing member, that is, the initial state by the biasing force of the auxiliary biasing member. Will be restored. Therefore, the urging member only needs to have an urging force sufficient to return the cam mechanism and the holding mechanism to the initial state, so that the urging force of the urging member can be kept small. Therefore, it is possible to reduce the size of the urging member, and consequently to reduce the size of the clutch.

According to a sixth aspect of the present invention, in the clutch according to the fifth aspect , the drive-side rotator is provided with a wedge surface that is provided so as to be able to rotate integrally with the drive shaft and is capable of contacting the power transmission member from a rotation direction. And a second rotating body that is provided so as to be rotatable relative to the first rotating body and holds the power transmission member in a radial direction and rotates integrally with the power transmission member. The side rotating body includes a transmission surface for sandwiching the power transmission member together with the wedge surface, and the auxiliary biasing member is interposed between the first rotating body and the second rotating body, When the rotational driving of the single rotating body is stopped, the first rotating body is rotated immediately before the second rotating body so as to release the holding of the power transmission member by the wedge surface and the transmitting surface. The first rotating body is urged to rotate in the opposite direction to It has as its gist that.

  According to this configuration, when the rotation of the first rotating body is stopped, the first rotating body is rotated so that the first rotating body rotates in the direction opposite to the immediately preceding rotating direction with respect to the second rotating body. By urging with the auxiliary urging member, the wedge surface can be easily separated from the transmission surface. Therefore, the clamping mechanism can be easily returned to the initial state by the biasing force of the auxiliary biasing member.

According to a seventh aspect of the present invention, in the clutch according to the sixth aspect of the present invention, either the first rotating body or the second rotating body is accommodated while compressing the auxiliary biasing member having elasticity. An auxiliary biasing member housing portion in which at least a part of the opening is closed by either one of the first rotating body and the second rotating body is formed, and the first rotating body or the second rotating body has And an insertion path for inserting the auxiliary biasing member into the auxiliary biasing member receiving portion from the outside of the first rotating body and the second rotating body that are communicated with the auxiliary biasing member receiving portion and assembled to each other. Its gist is that it is formed.

  According to this configuration, the auxiliary urging member can be inserted into the auxiliary urging member accommodating portion through the insertion path in a state where the first rotator and the second rotator are assembled with each other. Therefore, the auxiliary biasing member can be assembled through the insertion path into the auxiliary biasing member accommodating portion in a state where at least a part of the opening is closed by either one of the first rotating body and the second rotating body. The auxiliary urging member assembled to the auxiliary urging member housing portion is prevented from coming out of the auxiliary urging member housing portion from the opening of the auxiliary urging member housing portion. As a result, the assembling property of the auxiliary biasing member can be improved. Also, when the other components of the clutch are assembled after the auxiliary urging member is assembled to the auxiliary urging member housing, the auxiliary urging member is prevented from coming off, improving the assembly of the clutch. it can.

According to an eighth aspect of the present invention, in the clutch according to the seventh aspect , in the insertion path, the auxiliary biasing member is compressed between the first rotating body and the second rotating body when the clutch is operated. However, the gist is that the auxiliary biasing member is formed so that the end in the expansion / contraction direction does not reach the insertion path.

  According to this configuration, even if the auxiliary biasing member is compressed between the first rotating body and the second rotating body during the operation of the clutch and the auxiliary biasing member is shortened in the expansion / contraction direction, the auxiliary biasing force is increased. Since the end of the member in the expansion / contraction direction does not reach the insertion path, the auxiliary biasing member is prevented from being caught by the insertion path during operation of the clutch.

According to a ninth aspect of the present invention, in the clutch according to the seventh or eighth aspect of the present invention, the expansion / contraction of the auxiliary urging member disposed in the auxiliary urging member accommodating portion is formed on the inner peripheral surface of the insertion path. The gist is that a guide surface inclined with respect to the direction is formed.

  According to this configuration, when the auxiliary urging member is inserted into the insertion path along the guide surface from one end portion in the expansion / contraction direction of the auxiliary urging member, the auxiliary urging member becomes one end in the expansion / contraction direction of the auxiliary portion control member. Until the portion comes into contact with the inner peripheral surface of the auxiliary urging member accommodating portion, the auxiliary urging member accommodating portion is inserted into the auxiliary urging member accommodating portion while being inclined with respect to the expansion / contraction direction of the auxiliary urging member within the auxiliary urging member accommodating portion. . Therefore, after the one end portion in the expansion / contraction direction of the auxiliary urging member abuts on the inner peripheral surface of the auxiliary urging member accommodating portion, the portion inserted into the auxiliary urging member accommodating portion from the insertion path in the auxiliary urging member is: It becomes possible to enter the inner side of the auxiliary biasing member accommodating portion along the inner peripheral surface of the auxiliary biasing member accommodating portion. Therefore, the auxiliary biasing member can be assembled to the auxiliary biasing member accommodating portion without being inserted into the insertion path in a compressed state. As a result, the assembling property of the auxiliary biasing member is further improved.

Invention according to claim 1 0, in the clutch of claim 9, the inner peripheral surface of the insertion path, the insertion of the outer opening opposite the auxiliary biasing member accommodating portion in the insertion path The assisting means is arranged such that the distance between the inner opening and the outer opening becomes smaller toward the inner opening on the side of the auxiliary biasing member accommodating portion in the road. The gist thereof is that a pair of guide surfaces inclined with respect to the extending and contracting direction of the auxiliary biasing member disposed in the biasing member accommodating portion is formed.

  According to this configuration, the pair of guide surfaces are inclined in different directions with respect to the expansion / contraction direction of the auxiliary biasing member in the auxiliary biasing member housing portion. Therefore, the auxiliary biasing member can be inserted into the auxiliary biasing member accommodating portion through the insertion path along one of the two directions along each guide surface. Accordingly, the assembly direction of the auxiliary biasing member is further improved because the auxiliary biasing member is not limited to one direction.

The invention of claim 1 1, in the clutch according to claim 1 0, the inner peripheral surface of the insertion path, the mutual spacing As the direction from the outer opening toward said inner opening A pair of the guide surfaces inclined with respect to the expansion and contraction direction of the auxiliary biasing member disposed in the auxiliary biasing member accommodating portion so as to be narrowed, and a pair of guide surfaces closer to the inner opening than the pair of guide surfaces Along with the guide surface, with respect to the expansion and contraction direction of the auxiliary urging member disposed in the auxiliary urging member accommodating portion so that the interval between the inner opening portion and the outer opening portion becomes narrower toward the outer opening portion. The gist of the present invention is that a pair of inclined surfaces are formed.

  According to this configuration, the pair of inclined surfaces are formed at the end portion on the inner opening side of the insertion path so as to be aligned with the pair of guide surfaces. Further, the pair of inclined surfaces are arranged in a direction in which the auxiliary urging member disposed in the auxiliary urging member accommodating portion expands and contracts such that the interval between the inclined surfaces decreases from the inner opening toward the outer opening. Is inclined. Therefore, when the auxiliary biasing member is inserted into the auxiliary biasing member accommodating portion through the insertion path along one of the pair of guide surfaces, the auxiliary biasing member is hardly caught by the inner opening. . Therefore, the auxiliary biasing member can be more smoothly inserted into the auxiliary biasing member accommodating portion.

Section 1 2 according to the invention is claimed in clutch according to claim 1 1, with one of the inclined surface is formed substantially parallel to the one the guide surface of the opposite side, the other of said inclined surfaces facing Its gist is that it is formed substantially parallel to the other guide surface on the side.

  According to this configuration, when the auxiliary urging member is inserted into the auxiliary urging member accommodating portion through the insertion path along one of the pair of guide surfaces, the auxiliary urging member becomes the inner opening. It becomes difficult to get caught. Therefore, the auxiliary biasing member can be more smoothly inserted into the auxiliary biasing member accommodating portion.

The invention according to claim 1 3, in the clutch according to any one of claims 7 to 1 2, wherein the auxiliary biasing member accommodating portion, of the first rotating body and the second rotary member It has an arc-shaped groove shape extending in the rotation direction, and the gist thereof is that the insertion path is formed on the outer side in the radial direction of the auxiliary biasing member accommodating portion.

  According to this configuration, when the auxiliary biasing member accommodating portion is formed in an arc shape extending along the rotation direction of the first rotating body and the second rotating body, the radial biasing inner end portion of the auxiliary biasing member accommodating portion is formed. Also, the end portion on the radially outer side in the auxiliary biasing member accommodating portion tends to be longer in the circumferential direction. Therefore, by forming the insertion path on the radially outer side of the auxiliary urging member accommodating portion, the insertion path communicates with the auxiliary urging member accommodating portion than when forming the insertion path on the radially inner side of the auxiliary urging member accommodating portion. The range in which the insertion path can be formed is widened.

The invention described in claim 1 4, in the clutch according to claim 1 3, wherein the auxiliary biasing member is made of a compression coil spring, wherein the second rotary member, said auxiliary biasing member accommodating portion, A return accommodating portion connected to the auxiliary biasing member accommodating portion and having a radial width narrower than that of the auxiliary biasing member accommodating portion is formed on both sides in the circumferential direction of the auxiliary biasing member accommodating portion, and the first rotation The body has a pair of return convex portions inserted into the return accommodating portion and interposing the auxiliary biasing member therebetween, and at both ends in the circumferential direction of the auxiliary biasing member accommodating portion, the return accommodating portion A first pressing surface that extends along the radial direction on the outer side in the radial direction and is pressed against the auxiliary biasing member, and extends along the radial direction on the inner side in the radial direction with respect to the return accommodating portion and presses against the auxiliary biasing member And a second pressing surface that is longer in the radial direction than the first pressing surface. That is has the gist thereof.

  According to this configuration, when the auxiliary biasing member made of the compression coil spring is inserted into the arc-shaped auxiliary biasing member housing portion extending along the rotation direction of the first rotating body and the second rotating body, the auxiliary biasing member The amount of compression in the inner peripheral portion is larger than that in the outer peripheral portion. Accordingly, the auxiliary biasing member has a greater force toward the inner peripheral portion than the outer peripheral portion, so that the outer side in the radial direction becomes longer in the circumferential direction in the auxiliary biasing member housing portion. Try to move on. Therefore, the auxiliary urging member is stabilized in the auxiliary urging member accommodating portion by forming the second pressing surface provided on the radially inner side longer in the radial direction than the first pressing surface provided on the radially outer side. Can be accommodated.

Invention according to claim 1 5, in the clutch according to any one of claims 2 to 1 4, the driven-side rotating member, the driving side rotational disposed on the outer periphery of the driving-side rotator A cylindrical side wall portion facing the body in the radial direction, and the inner peripheral surface of the side wall portion is wider in the rotational direction than the power transmission member and is moved radially outward by the cam mechanism. A first engagement recess that can be engaged in the rotational direction by inserting a power transmission member, and the power transmission member that is formed and inserted on the bottom surface of the first engagement recess is more radial than the first engagement recess. The gist of the invention is that a second engaging recess that is arranged outside and engages with the power transmission member so as not to move relative to the rotation direction is formed.

  According to this configuration, since the first engaging recess is wider in the rotational direction than the power transmission member, when the power transmission member is moved radially outward by the cam mechanism at the start of rotational driving of the driving side rotating body. In addition, the power transmission member is easily inserted into the first engagement recess. Therefore, the drive-side rotator and the driven-side rotator can be engaged in the rotation direction via the power transmission member in a short time after the drive of the drive-side rotator is started. Further, when the power transmission member is inserted into the second engagement recess, the power transmission member and the driven-side rotator cannot be moved relative to each other in the rotational direction. Therefore, even when a reverse load, which is a load in the same direction as the rotation direction of the driving side rotating body, is applied to the driven side rotating body, the driving side rotating body and the driven side rotating body are connected via the power transmission member. Can be maintained in the rotational direction. Therefore, the rotational driving force can be stably transmitted from the driving side rotating body to the driven side rotating body.

Invention according to claim 1 6, in the clutch of claim 1 5, wherein the second engagement recess being formed at both ends of the rotational direction of the bottom surface of the first engaging recess This is the gist.

According to this configuration, the power transmission member can be inserted into the second engagement recess regardless of the rotation direction of the drive-side rotator.
The invention according to claim 1 7, in the clutch according to claim 1 5 or claim 1 6, wherein the second engagement recess is formed in the central portion of the rotational direction of the bottom surface of the first engaging recess The gist of this is.

  According to this configuration, after the power transmission member is inserted into the first engagement recess, the power transmission member rotates with respect to the driven-side rotator until the power transmission member is inserted into the second engagement recess. It is possible to reduce the amount to be performed.

The invention according to claim 18 is the clutch according to any one of claims 2 to 17 , wherein the cam portion is a cam groove into which the power transmission member is inserted. It is said.

  According to this configuration, when the urging member urges the power transmission member radially inward, the power transmission member presses the inner peripheral surface of the cam groove radially inward. Therefore, the guide member can be easily moved radially inward by the urging force of the urging member, so that the holding mechanism can be easily returned to the initial state. Further, since the cam portion is a cam groove, the configuration of the guide member is prevented from being complicated.

The invention according to claim 19, in the clutch according to claim 1 8, the cam groove, relative rotation between said power transmitting member and the cam groove when the rotation driving of the driving side rotational member is stopped The gist of the invention is that a relative rotation blocking means for blocking the rotation is provided.

  According to this configuration, even when the guide member tries to rotate relative to the power transmission member by the inertial force acting on the guide member when the rotational drive of the drive side rotator is stopped, the power transmission member is driven by the relative rotation blocking means. And the relative rotation of the cam groove are prevented. Therefore, since the power transmission member is prevented from relatively moving in the cam groove after the driving of the driving side rotating body is stopped, the driving side rotating body and the driven side rotating body are engaged in the rotational direction. It can be released quickly. In addition, since the power transmission member can be prevented from relatively moving in the cam groove and colliding with the inner peripheral surface of the cam groove after the rotation drive of the drive side rotator is stopped, It is possible to prevent the generation of a collision sound with the peripheral surface and to suppress the impact load from being applied to the power transmission member and the guide member.

The invention of claim 2 0, in the clutch according to claim 19, wherein the cam groove includes a first guide portion for positioning said power transmission member to the disengaged position, the first guide portion A second guide part that is provided in a position shifted in the rotational direction and radially outside the first guide part and guides the power transmission member to the engagement position, and from the first guide part to the second A cam surface extending to the guide portion and to which the power transmission member is slidably contacted, and the relative rotation preventing means is recessed in the cam surface, and the power transmission member is at least when the rotation of the drive side rotating body is stopped. Its gist is that it is a blocking recess that fits and engages in a relatively non-rotatable manner.

According to this configuration, the blocking recess formed by recessing the cam surface has a simple shape. Therefore, the relative rotation preventing means can be easily provided in the cam groove.
The invention described in claim 2 1, in a clutch according to claim 2 0, wherein the biasing member is biasing the power transmission member radially inward, with the rotation of the driving-side rotator When the guide member moves radially outward due to the centrifugal force generated by rotating the power guide member, the power transmission member is held in the engagement position by the guide member in the second guide groove. The first guide portion in the cam groove of the guide member disposed radially inward within the radial movement range of the guide member. A portion of the cam surface that is adjacent to the first guide portion in the radial direction has a diameter so that the power transmission member that is inserted into the portion and disposed at the non-engagement position has a depth that does not engage with the blocking recess. It is formed to be recessed in the direction It has as its gist that.

  According to this configuration, the power transmission member does not engage with the blocking recess when the power transmission member is disposed in the non-engagement position, and therefore, when the drive side rotating body starts to rotate, the first guide portion to the second guide portion. It can be easily moved in the cam groove. Further, when the guide member moves radially outward due to the centrifugal force generated by the rotation of the driving side rotating body, the power transmission member is held in the engagement position while being held at the engagement position by the guide member. Is relatively moved from the second guide part to the first guide part. Therefore, it is possible to engage the power transmission member with the blocking recess that is adjacent to the first guide portion in the radial direction during the rotation of the drive-side rotator.

The invention according to claim 2 2, in the clutch according to any one of claims 2 to 2 1, the driving-side rotating member and the phase body rotatably provided, the guide member said guide member The gist of the present invention is to provide a holding case capable of guiding the movement in the radial direction so as to be capable of guiding and rotating integrally with the guide member.

  According to this configuration, since the radial movement of the guide member is guided by the holding case, the holding mechanism functions well. In addition, the guide member receives the urging force of the urging member when the drive side rotating body is stopped, and moves radially inward while being guided by the holding case. Therefore, the holding mechanism can be smoothly returned to the initial state. Is called.

The invention according to claim 2 3, in the clutch according to any one of claims 1 to 2 2, wherein at the start of the rotation of the driving-side rotator, the inertial force acting on the guide member The gist of the invention is that the drive-side rotating body and the guide member are relatively rotated by the guide member rotating later than the drive-side rotating body.

  According to this configuration, at the start of the rotational drive of the drive-side rotator, the drive-side rotator and the guide member are rotated together using the inertial force acting on the guide member. Therefore, it is not necessary to separately provide a means for rotating the driving side rotating body and the guide member together in order to move the power transmission member from the non-engaging position to the engaging position.

The invention of claim 2 4, wherein a motor body having a drive shaft that is driven to rotate, the driven shaft which is rotated by the rotational driving force of being disposed on the drive shaft coaxially with the drive shaft a speed reduction mechanism and outputting the decelerated rotation of the drive shaft, a motor and a clutch according to any one of claims 1 to 2 3 arranged between the driven shaft and the drive shaft The gist is that.

According to this configuration, the motor is provided with a clutch in which the number of urging members is reduced. Therefore, since the number of parts constituting this motor is reduced, the manufacturing cost is reduced. Further, since the clutch is provided between the drive shaft of the motor main body and the driven shaft constituting the speed reduction mechanism, the clutch is provided in the motor before the rotational driving force of the drive shaft is decelerated. Therefore, the load applied to each component constituting the clutch can be kept small, and the clutch can be miniaturized. Therefore, it is possible to reduce the size of the motor provided with this clutch. The miniaturized motor can be easily installed in a narrow space such as the inside of the slide door. Further, by providing the clutch before being decelerated in the motor, a centrifugal force acting on the guide member is likely to be generated. Therefore, it is advantageous when the clutch is configured to move the guide member radially outward by centrifugal force as in the clutch according to claim 1 .

The invention according to claim 2 5, a vehicle door opening and closing device configured to open and close operation by the driving force of the motor according to claim 2 4 door for opening and closing an opening provided in a vehicle, the When a command to automatically open and close the door is generated, the drive shaft is connected to the driven shaft by the clutch together with the driving of the motor body, and the door is automatically opened and closed. The gist of the invention is to provide a vehicle door opening / closing device in which the driven shaft is disconnected from the drive shaft to reduce the operating load when the door is manually opened and closed.

  According to this configuration, the motor used as the drive source is provided with the clutch in which the number of urging members is reduced. Therefore, the number of parts constituting the vehicle door opening / closing device is reduced, and thus the manufacturing cost is reduced.

  According to the present invention, it is possible to provide a clutch capable of reducing the number of urging members, a motor including the clutch, and a vehicle door opening / closing device.

Sectional drawing of a motor with a clutch. The schematic block diagram of a sliding door opening / closing apparatus. Sectional drawing (CC sectional drawing in FIG. 6) of the clutch of 1st Embodiment. The disassembled perspective view of the clutch of 1st Embodiment. The disassembled perspective view of the clutch of 1st Embodiment. Sectional drawing (AA sectional drawing in FIG. 3) of the clutch of 1st Embodiment. Sectional drawing (BB sectional drawing in FIG. 3) of the clutch of 1st Embodiment. Sectional drawing of the clutch of 1st Embodiment. Sectional drawing of the clutch of 1st Embodiment. Sectional drawing of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. (A) And (b) is sectional drawing of the clutch of 1st Embodiment. The disassembled perspective view of the clutch of 2nd Embodiment. Sectional drawing of the clutch of 2nd Embodiment (EE sectional drawing in FIG. 17). Sectional drawing (DD sectional drawing in FIG. 16) of the clutch of 2nd Embodiment. Sectional drawing of the clutch of 2nd Embodiment. (A) is sectional drawing of the clutch of 2nd Embodiment, (b) is sectional drawing of the clutch of 2nd Embodiment (FF sectional drawing in FIG. 17). (A) And (b) is sectional drawing of the clutch of 2nd Embodiment. (A) And (b) is sectional drawing of the clutch of 2nd Embodiment. The disassembled perspective view of the clutch of 3rd Embodiment. (A) And (b) is sectional drawing of the clutch of 3rd Embodiment. Sectional drawing (GG sectional drawing in Fig.23 (a)) of the clutch of 3rd Embodiment. Sectional drawing of the clutch of 3rd Embodiment. Sectional drawing of the clutch of 3rd Embodiment. Sectional drawing of the clutch of 4th Embodiment. Sectional drawing of the clutch of 5th Embodiment. (A) And (b) is sectional drawing of the clutch of 5th Embodiment. Sectional drawing of the clutch of 5th Embodiment. Sectional drawing of the clutch of 5th Embodiment. (A) And (b) is sectional drawing of the clutch of 5th Embodiment. Sectional drawing of the clutch of 6th Embodiment. Sectional drawing of the clutch of 6th Embodiment. Sectional drawing of the clutch of another form. Sectional drawing of the clutch of another form. The perspective view of the clutch of another form except a driven side rotary body.

(First embodiment)
A first embodiment of the present invention will be described below with reference to the drawings.
As shown in FIG. 2, the motor 11 of the present embodiment shown in FIG. 1 is used as a drive source for a slide door opening / closing device 1 mounted on an automobile. The slide door opening / closing device 1 is disposed in a slide door 3 that is slidable along the side surface of the vehicle body 2. The slide door 3 is supported by a connector 5 connected to a guide rail 4 provided on the vehicle body 2. The connector 5 moves along the guide rail 4 by winding and feeding out the wire cable 6 by driving the motor 11. The sliding door 3 opens and closes the entrance / exit 2a formed in the vehicle body 2 by the movement of the connector 5.

  As shown in FIG. 1, the motor 11 is a so-called geared motor including a motor body 12 and a speed reduction unit 13. The motor body 12 includes a yoke housing 14, a pair of magnets 15, an armature 16, a brush holder 17, and a pair of brushes 18.

  The yoke housing 14 has a bottomed cylindrical shape, and a pair of magnets 15 are fixed to the inner peripheral surface thereof. A bearing 19 is provided at the center of the bottom of the yoke housing 14, and the bearing 19 pivotally supports the base end portion of the rotating shaft 20 (drive shaft) of the armature 16 disposed inside the yoke housing 14. ing.

  A flange portion 14b extending outward in the radial direction is formed in the opening portion 14a of the yoke housing 14, and the flange portion 14b is connected and fixed to a gear housing 31 of the speed reduction portion 13 described later. In this fixing, the flange portion 14b is fixed to the gear housing 31 with the screw 21 in a state where the brush holder 17 is interposed between the flange portion 14b and the opening portion 31a of the gear housing 31.

  In the yoke housing 14, the brush holder 17 holds a bearing 22 that pivotally supports a portion on the tip side of the rotary shaft 20 and a pair of brushes 18 that are in sliding contact with a commutator 23 fixed to the rotary shaft 20. ing. Further, in the brush holder 17, a portion protruding outside the yoke housing 14 and the gear housing 31 is a connector portion 17 a to which a vehicle body side connector (not shown) extending from the vehicle body side is connected, and the connection of the connector portion 17 a. A plurality of terminals 24 are exposed in the recess 17b. These terminals 24 are inserted into the brush holder 17 and are electrically connected to a rotation sensor (a hall element 42 described later) provided in the motor 11, the brush 18, and the like. When the vehicle body side connector is connected to the connector portion 17a, the controller 25 and the motor 11 provided on the vehicle body side are electrically connected. As a result, power supply and output of sensor signals and the like can be performed between the motor 11 and the controller 25.

The speed reduction unit 13 includes a gear housing 31, a speed reduction mechanism 34 including a worm shaft 32 (driven shaft) and a worm wheel 33, an output shaft 35, and a clutch 50.
The gear housing 31 includes an opening 31a facing the opening 14a of the yoke housing 14, and the brush holder 17 is interposed between the openings 14a and 31a. The gear housing 31 is formed with a clutch housing portion 31b that is recessed from the opening 31a of the gear housing 31 in the axial direction. Further, the gear housing 31 accommodates a worm wheel 33 that is connected to the substantially cylindrical shaft accommodating cylinder portion 31c and extends in the axial direction from the bottom of the clutch accommodating portion 31b and accommodates the worm shaft 32, and is connected to the shaft accommodating cylinder portion 31c. A substantially circular wheel housing portion 31d is formed.

  Bearings 36 and 37 are disposed at both ends in the axial direction of the shaft accommodating cylinder portion 31c. The worm shaft 32 is coaxial with the rotary shaft 20 in a state where the tip end portion is supported by the bearing 37 (that is, the central axes of the rotary shaft 20 and the worm shaft 32 coincide with each other). As in the case of the shaft housing cylinder portion 31c. A worm portion 32 a having a screw tooth shape is formed at a substantially central portion in the axial direction of the worm shaft 32. A thrust receiving ball 38 and a thrust receiving plate 39 for receiving the thrust load of the worm shaft 32 are disposed at the end of the shaft accommodating cylinder portion 31c on the distal end side of the worm shaft 32.

  A ring-shaped sensor magnet 41 magnetized in the circumferential direction between the worm portion 32 a and the portion supported by the bearing 37 in the worm shaft 32 is mounted so as to rotate integrally with the worm shaft 32. Has been. A hall element 42 that detects a change in the magnetic field associated with the rotation of the sensor magnet 41 is disposed in a portion of the shaft housing cylinder portion 31 c that faces the outer peripheral surface of the sensor magnet 41. The Hall element 42 is a signal for detecting rotation information such as the rotation speed and rotation speed of the worm shaft 32, and outputs a rotation detection signal that is a signal corresponding to a change in the magnetic field accompanying the rotation of the sensor magnet 41. . The controller 25 detects the opening / closing position and opening / closing speed of the slide door 3 based on the rotation detection signal.

  A disc-shaped worm wheel 33 that meshes with the worm portion 32a of the worm shaft 32 is rotatably accommodated in the wheel accommodating portion 31d. An output shaft 35 is fixed to the central portion of the worm wheel 33 in the radial direction so as to rotate integrally with the worm wheel 33. As shown in FIG. 2, a drive pulley (not shown) on which the wire cable 6 for opening and closing the slide door 3 is engaged is connected to the output shaft 35 so as to rotate integrally.

  As shown in FIG. 1, the clutch housing portion 31 b houses a mechanical clutch 50 that is disposed between the worm shaft 32 and the rotating shaft 20 and connects and disconnects the worm shaft 32 and the rotating shaft 20. Has been. As shown in FIG. 4, the clutch 50 includes a driving side rotating body 51, two roller members 52, two return springs 53, a holding case 54, two guide members 55, and a driven side rotating body 56.

The drive-side rotator 51 includes a first drive plate 61, a second drive plate 62 disposed so as to overlap the first drive plate 61, and two connecting springs 63.
The first drive plate 61 has a substantially disc shape, and has a cylindrical drive-side shaft coupling portion 61 a that protrudes in the axial direction at the center in the radial direction. A shaft coupling recess 61b is formed in the radial central portion of the drive side shaft coupling portion 61a (that is, the radial central portion of the first drive plate 61). The shaft coupling recess 61b extends along the axial direction from the axial end surface on the second driving plate 62 side in the driving side shaft coupling portion 61a toward the axial end surface on the driven side rotating body 56 side in the first driving plate 61. The shape seen from the axial direction forms a two-sided width shape. Then, as shown in FIG. 3, the tip of the rotating shaft 20 has a two-sided width shape corresponding to the shaft connecting recess 61b, and when the tip of the rotating shaft 20 is inserted into the shaft connecting recess 61b, The first drive plate 61 is engaged with the distal end portion of the rotation shaft 20 in the rotation direction, and can rotate integrally with the rotation shaft 20. In addition, the connected rotating shaft 20 and the first drive plate 61 are coaxial (the respective central axes coincide with each other). A ball housing hole 61c is formed at the bottom of the shaft coupling recess 61b. A spherical thrust receiving ball 71 that receives a thrust load between the rotary shaft 20 and the driven rotary body 56 is accommodated in the ball accommodation hole 61c.

  As shown in FIGS. 4 and 6, two control grooves 61 d are formed on the outer peripheral edge portion of the first drive plate 61. The two control grooves 61d are formed at two locations in the first drive plate 61 that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment). Each control groove 61d is recessed radially outward from the outer peripheral edge of the first drive plate 61, thereby opening radially outward. Each control groove 61d penetrates the first drive plate 61 in the axial direction and is open on both sides in the axial direction.

  The central portion in the circumferential direction of each control groove 61d is a non-engaging recess 61e that is deeply recessed in the radial direction. The inner peripheral surface of the non-engaging recess 61e is parallel to the axial direction and curved in an arc shape. By forming the non-engaging recess 61e, a pair of engaging recesses 61f that are shallower in the radial direction than the non-engaging recess 61e are formed on both sides of each control groove 61d in the circumferential direction of the non-engaging recess 61e. Is formed. The inner peripheral surface of each engaging recess 61f is a wedge surface 61g that is parallel to the axial direction and curved in an arc shape. The curvature of each wedge surface 61g is equal to the curvature of the inner peripheral surface of the non-engaging recess 61e, and the center of curvature of each wedge surface 61g is more than the center of curvature of the inner peripheral surface of the non-engaging recess 61e. 61 is located radially outside. Further, when viewed from the axial direction of the first drive plate 61, each control groove 61d is axisymmetric with a straight line (not shown) extending in the radial direction passing through the center in the circumferential direction of each control groove 61d as an axis of symmetry. .

  Further, two pairs of return convex portions 61 h are formed to project from the end surface of the first drive plate 61 in the axial direction on the second drive plate 62 side. The pair of return convex portions 61h are two locations that are equiangularly spaced in the circumferential direction (180 ° spacing in the present embodiment) in the first drive plate 61, and are between the control grooves 61d that are adjacent in the circumferential direction. Each is formed at a position. The pair of return convex portions 61h are formed at a distance in the circumferential direction of the first drive plate 61 and have a substantially rectangular parallelepiped shape protruding in the axial direction.

  As shown in FIGS. 3 and 5, the second drive plate 62 has a disk shape. The second drive plate 62 includes a disc-shaped guide portion 62a and a substantially disc-shaped accommodation portion 62b that protrudes from the guide portion 62a toward the first drive plate 61 along the axial direction. The guide part 62a and the accommodating part 62b are formed coaxially. In addition, the outer diameter of the guide portion 62 a is formed larger than the outer diameter of the first drive plate 61, and the outer diameter of the housing portion 62 b is formed to be equal to the outer diameter of the first drive plate 61. An insertion hole 62c penetrating in the axial direction is formed in the radial center of the second drive plate 62. The insertion hole 62c has a circular shape when viewed from the axial direction, and the inner diameter thereof is set to be approximately equal to the outer diameter of the drive side shaft coupling portion 61a.

  As shown in FIGS. 5 and 6, a pair of spring accommodating recesses 62d is formed on the outer peripheral side of the insertion hole 62c in the accommodating portion 62b. The two spring accommodating recesses 62d are formed by recessing the accommodating portion 62b in the axial direction from the axial end surface of the accommodating portion 62b on the first drive plate 61 side. The two spring accommodating recesses 62d have an arc shape surrounding the insertion hole 62c, and have a symmetrical shape with the insertion hole 62c interposed therebetween. The connecting springs 63 are accommodated in the spring accommodating recesses 62d, respectively. Each connection spring 63 is a compression coil spring.

  In addition, a pair of return recesses 62e are formed on both sides of each spring accommodating recess 62d in the circumferential direction. That is, two pairs of return recesses 62e are formed in the accommodating portion 62b. The return recesses 62e paired on both sides in the circumferential direction of each spring accommodating recess 62d are formed by recessing the accommodating portion 62b in the axial direction from the axial end surface of the accommodating portion 62b on the first drive plate 61 side. Yes. The radial width of each return recess 62e is narrower than the radial width of the spring accommodating recess 62d and is substantially equal to the radial width of the return convex portion 61h. The circumferential width of each return recess 62e is formed longer than the circumferential width of the return convex portion 61h. Furthermore, the axial depth of each return recess 62e is formed to be equal to the axial depth of the spring accommodating recess 62d and substantially equal to the axial length of the return protrusion 61h. Further, the internal space of the spring accommodating recess 62d and the internal space of the return recesses 62e on both sides in the circumferential direction are connected.

  In the accommodating part 62b, there are two places between the return recesses 62e adjacent to each other in the circumferential direction, and two places that are equiangularly spaced in the circumferential direction (180 ° interval in the present embodiment) in the accommodating part 62b. Guide recesses 62f are respectively formed. Each guide recess 62f is formed by recessing the accommodating portion 62b along the radial direction from the outer peripheral edge of the accommodating portion 62b. Each guide recess 62f opens outward in the radial direction and penetrates the accommodating portion 62b in the axial direction. In the present embodiment, each guide recess 62f has a U shape whose shape viewed from the axial direction opens radially outward. Further, the circumferential width of each guide recess 62f is formed substantially equal to the circumferential width of the non-engaging recess 61e.

  The guide portion 62a is formed with insertion engagement portions 62g at two locations adjacent to the two guide recess portions 62f in the axial direction. The two insertion engaging portions 62g are formed at equiangular intervals in the circumferential direction (180 ° intervals in the present embodiment). Each insertion engagement portion 62g is formed by recessing the guide portion 62a in the axial direction from the end surface of the guide portion 62a opposite to the housing portion 62b in the axial direction. Further, as shown in FIGS. 3 and 6, each insertion engagement portion 62g is radially outer than the guide recess 62f (accommodating portion 62b) from a position adjacent to the radially inner end of the guide recess 62f in the axial direction. It has a groove shape extending along the radial direction to a position that is radially outward from the outer peripheral edge. The circumferential width of each insertion engaging portion 62g is formed to be narrower than the circumferential width of the guide recess 62f. A portion of each insertion engaging portion 62g adjacent to the guide recess 62f in the axial direction passes through the guide portion 62a in the axial direction and communicates with the guide recess 62f. A portion of each insertion engagement portion 62g that is radially outward from the guide recess 62f is not recessed through the guide portion 62a in the axial direction.

  In the first drive plate 61 and the second drive plate 62 as described above, a pair of return convex portions 61h are inserted into a pair of return concave portions 62e, and the drive side shaft connecting portion 61a is inserted into the insertion hole 62c. Are overlapped in the axial direction so as to be inserted into the. In the drive-side rotator 51, the first drive plate 61 and the second drive plate 62 are arranged on the same axis (so that their center axes coincide with each other). Further, the coupling springs 63 are arranged between the pair of return convex portions 61 h, whereby the first drive plate 61 and the second drive plate 62 are coupled in the rotational direction via the coupling springs 63. . The first drive plate 61 and the second drive plate 62 can rotate relative to each other while resisting the urging force of the coupling spring 63 with the center axis of each other as the center of rotation. The first drive plate 61 and the second drive plate 62 are held at a predetermined relative rotational position by the urging force of the connection spring 63. In the present embodiment, the connection spring 63 has a relative rotational position between the first drive plate 61 and the second drive plate 62, a circumferential position of the control groove 61d (non-engaging recess 61e), and a circumferential direction of the guide recess 62f. The first drive plate 61 (returning convex portion 61h) is urged so as to be held at a neutral position where the position matches. Therefore, as shown in FIG. 6, when the rotary shaft 20 is not driven, when the driving side rotary body 51 is viewed from the axial direction, the circumferential center of the two control grooves 61 d and the circumferential direction of the two guide recesses 62 f are displayed. The center matches.

  As shown in FIGS. 3, 5, and 6, each roller member 52 is formed integrally with a connecting portion 52a, a power transmission portion 52b formed integrally with the connecting portion 52a, and the connecting portion 52a. And a cam engaging portion 52c.

  The connecting portion 52a has a plate shape in which the shape seen from the axial direction forms a track shape. The width of the connecting portion 52a in the short direction is formed to be substantially equal to the width in the circumferential direction of the guide recess 62f. Further, the longitudinal width of the connecting portion 52a is formed to be substantially equal to the radial length of the guide recess 62f. Then, both end surfaces of the connecting portion 52a in the longitudinal direction have an arc shape having the same curvature as the inner peripheral surface of the non-engaging recess 61e. Furthermore, the thickness of the connecting portion 52a is formed substantially equal to the axial width of the guide recess 62f (that is, the axial thickness of the accommodating portion 62b).

  The power transmission portion 52b is one end surface in the thickness direction (axial direction) of the connecting portion 52a, and one end portion in the longitudinal direction of the connecting portion 52a (end portion on the radially outer side when assembled as the clutch 50). It extends along the thickness direction (axial direction) of the connection part 52a from the part which becomes. The power transmission portion 52b has a cylindrical shape, and the axial length thereof is formed substantially equal to the axial length of the control groove 61d. In addition, the curvature of the cylindrical outer peripheral surface of the power transmission portion 52b is equal to the curvature of the inner peripheral surface of the non-engaging recess 61e and the wedge surface 61g.

  The cam engaging portion 52c is the other end surface in the thickness direction (axial direction) of the connecting portion 52a, and the other end portion in the longitudinal direction of the connecting portion 52a (the radially inner end when assembled as the clutch 50). Part) is extended along the thickness direction (axial direction) of the connecting part 52a. The cam engagement portion 52c is formed in a columnar shape having a smaller diameter than the power transmission portion 52b, and the axial length thereof is longer than the axial thickness of the guide portion 62a. A flat biasing surface 52d is formed at the base end of the cam engagement portion 52c. The urging surface 52d is parallel to the axial direction and faces one end side in the longitudinal direction of the connecting portion 52a (that is, the end portion side in the longitudinal direction on the side where the power transmission portion 52b is formed in the connecting portion 52a). Yes.

  The two roller members 52 as described above are inserted into the two control grooves 61d of the first drive plate 61 with the power transmission portions 52b inserted into the two guide recesses 62f of the second drive plate 62, respectively. The connecting portion 52a is assembled to the drive side rotating body 51 so as to be inserted. Further, the two roller members 52 are arranged with respect to the drive side rotating body 51 so that the cam engagement portions 52c are inserted into the two insertion engagement portions 62g of the second drive plate 62, respectively. The connecting portion 52a inserted into the guide recess 62f has a longitudinal direction that coincides with the radial direction and a thickness direction that coincides with the axial direction. Further, in each roller member 52, the cam engagement portion 52c is located radially inward of the power transmission portion 52b, and the urging surface 52d faces the radially outer side. Each roller member 52 slides the outer peripheral surface of the coupling portion 52a on the inner peripheral surface of the guide recess 62f, and at the same time slides the outer peripheral surface of the cam engagement portion 52c on the inner peripheral surface of the insertion engaging portion 62g. It is possible to move in the radial direction with respect to the drive-side rotator 51. Therefore, the roller member 52 is guided to move in the radial direction by the guide recess 62f and the insertion engagement portion 62g, while the circumferential movement with respect to the second drive plate 62 is restricted by the guide recess 62f and the insertion engagement portion 62g. Is done. Further, the roller member 52 is engaged with the second drive plate 62 in the rotation direction by the coupling portion 52a being disposed in the guide recess 62f and the cam engagement portion 52c being inserted into the insertion engagement portion 62g. The second drive plate 62 and the second drive plate 62 can rotate together.

  Each insertion engagement portion 62g houses a return spring 53 at a position on the radially outer side of the cam engagement portion 52c. The return spring 53 of this embodiment is a compression coil spring. Each return spring 53 abuts against a biasing surface 52d formed on the cam engagement portion 52c, and biases the roller member 52 radially inward along the radial direction.

  As shown in FIGS. 3, 5 and 7, the holding case 54 includes a disc-shaped cover portion 54a, an insertion portion 54b formed integrally with the cover portion 54a, and the cover portion 54a and the insertion portion 54b. And a pair of guide holding portions 54c formed integrally.

  The cover portion 54a has an outer diameter equal to the outer diameter of the guide portion 62a of the second drive plate 62. And the cylindrical insertion part 54b is formed in the center part of the radial direction of this cover part 54a. The insertion portion 54b extends along the axial direction from the axial end surface of the cover portion 54a on the second drive plate 62 side, and is formed coaxially with the cover portion 54a. The outer diameter of the insertion portion 54b is formed to be equal to the outer diameter of the drive side shaft coupling portion 61a. Further, the insertion hole 54d formed in the central portion in the radial direction of the insertion portion 54b penetrates the insertion portion 54b and the cover portion 54a in the axial direction, and the inner diameter of the insertion hole 54d is equal to the outer diameter of the rotating shaft 20. It is formed approximately equally. The holding case 54 rotates the center axis of the drive-side rotating body 51 with respect to the drive-side rotating body 51 by inserting the distal end portion of the insertion portion 54b into the insertion hole 62c of the second drive plate 62 from the guide portion 62a side. It is assembled as a center so that it can rotate. Further, the holding case 54 is coaxial with the drive-side rotator 51 (the center axes of the holding cases 54 coincide with each other). The rotating shaft 20 is inserted into the shaft coupling recess 61 b of the first drive plate 61 through the insertion hole 54 d of the holding case 54.

  The pair of guide holding portions 54c are equiangularly spaced (180 ° intervals in this embodiment) in the circumferential direction on the outer peripheral surface of the insertion hole 54d on the axial end surface of the cover portion 54a on the second drive plate 62 side. After extending radially outward from each of these two locations along the radial direction, they extend to both sides in the circumferential direction along the outer peripheral edge of the cover portion 54a. Each guide holding portion 54c is substantially T-shaped when viewed from the axial direction. By forming the guide holding portion 54c as described above, the holding case 54 is formed with holding recesses 54e at two locations between the two guide holding portions 54c and on both sides in the diameter direction of the insertion portion 54b. ing. Each holding recess 54e opens to the radially outer side and one side in the axial direction (second drive plate 62 side).

  A pair of regulating convex portions 54g is formed in the opening portion 54f that opens to the outside in the radial direction of each holding concave portion 54e. In each holding recess 54e, a pair of restricting projections 54g protrudes toward the inside of the guide recess 62f so as to narrow the circumferential width of the holding recess 54e. And the front-end | tip surface of the regulation convex part 54g which makes a pair is the guide surface 54h which makes mutually parallel in the circumferential direction. Each guide surface 54h is formed in parallel with the straight line (not shown) passing through the center of the holding case 54 and passing through the center in the circumferential direction of the guide recess 62f while being parallel to the axial direction.

  The guide members 55 are accommodated in the two holding recesses 54e, respectively. Each guide member 55 is a weight having a weight on which an inertial force acts. The axial thickness of each guide member 55 is formed to be equal to the axial width of the holding recess 54e. The end surface on the radially inner side of each guide member 55 has a shape corresponding to the bottom surface 54k on the radially inner side of the holding recess 54e (that is, the surface constituted by the outer peripheral surface of the insertion portion 54b and the side surface of the guide holding portion 54c). I am doing. Further, locking projections 55a are formed to project from both end faces of each guide member 55 in the circumferential direction. Each locking projection 55a is formed at the end on the bottom surface 54k side of the holding recess 54e on both end surfaces in the circumferential direction of each guide member 55, and faces the regulation projection 54g. Further, both the circumferential end surfaces of each guide member 55 and the portions on the radially outer side (the opening 54 f side of the holding recess 54 e) than the locking projection 55 a are planar guided surfaces 55 b. Yes. The two guided surfaces 55b formed on each guide member 55 are parallel to the axial direction and parallel to each other. Further, in each guide member 55, the interval between the two guided surfaces 55b is formed substantially equal to the interval between the guide surfaces 54h forming a pair in each holding recess 54e. Further, the radially outer end surface 55c of each guide member 55 has an arc shape with the same curvature as the outer peripheral surface of the cover portion 54a.

  Such a guide member 55 is disposed between a pair of guide surfaces 54 h in the holding recess 54 e and is held by the holding case 54. Each guide member 55 is movable in the radial direction while bringing the guided surface 55b into sliding contact with the guide surface 54h. Accordingly, the guide member 55 is guided to move in the radial direction by the guide surface 54h, while the guide surface 54h restricts the movement in the circumferential direction with respect to the holding case 54. Furthermore, the guide member 55 can rotate integrally with the holding case 54 around the central axis of the holding case 54. Each guide member 55 is disposed on the innermost radial direction within the movement range of the guide member 55 when the radially inner end face is in contact with the bottom surface 54k of the holding recess 54e. Each guide member 55 is movable outward in the radial direction until the locking projection 55a abuts on the regulation projection 54g. Each guide member 55 is arranged on the outermost radial direction within the movement range when the locking projection 55a is in contact with the regulation projection 54g. Each guide member 55 has the center of curvature of the radially outer end surface 55c coincides with the center of the holding case 54 when the locking projection 55a abuts on the regulation projection 54g.

  Each guide member 55 is formed with a cam groove 55d. As shown in FIG. 7, the cam groove 55 d has a groove shape extending substantially along the circumferential direction of the holding case 54 (or the second drive plate 62), and penetrates each guide member 55 in the axial direction. . Further, the cam groove 55d extends from the central portion in the circumferential direction (substantially the same as the longitudinal direction of the cam groove 55d) so as to go outward in the radial direction toward both ends in the circumferential direction. The width (width in the short direction) is formed to be substantially equal to the outer diameter of the cam engaging portion 52c of the roller member 52. In the cam groove 55d of each guide member 55, the center in the circumferential direction (longitudinal direction) is the first guide portion P1, and both end portions in the circumferential direction (longitudinal direction) are the second guide portions P2. . The first guide portion P1 is located at the center of the guide member 55 in the circumferential direction. In a state where each guide member 55 is accommodated in the holding recess 54e, the first guide portion P1 is located on the innermost radial direction in the cam groove 55d, while the second guide portion P2 is located on the outermost radial direction in the cam groove 55d. Located in.

  Further, when viewed from the axial direction, the cam groove 55d of the present embodiment is formed in line symmetry with a straight line (not shown) extending in the radial direction passing through the first guide portion P1 as an axis of symmetry. Each cam groove 55d has an arc shape that swells radially outward from the first guide portion P1 to the second guide portion P2. And the shape which looked at the cam groove 55d from the axial direction has comprised the substantially V shape opened to a radial direction outer side. Furthermore, the cam groove 55d is provided with a pair of cam surfaces S facing in the radial direction (the short direction of the cam groove 55d). The cam surface S is an inner peripheral surface of the cam groove 55d and extends from the first guide portion P1 to the second guide portions P2 on both sides in the circumferential direction (longitudinal direction).

  As shown in FIGS. 3 and 7, the cam grooves 55d of the two guide members 55 respectively accommodated in the two holding recesses 54e are provided on the tip side portions of the cam engaging portions 52c of the two roller members 52, respectively. Has been inserted. By inserting the cam engagement portion 52c into the cam groove 55d, the roller member 52 is engaged with the cam groove 55d, and the movement along the longitudinal direction of the cam groove 55d with respect to the guide member 55 is guided. The movement of the cam groove 55d in the width direction is restricted. When the guide member 55 held by the holding case 54 and the drive-side rotator 51 are rotated relative to each other about the center axis of the drive-side rotator 51, the roller member 52 and the guide member 55 (cam groove 55d) are rotated. ) And relative rotation. Then, the roller member 52 is guided by the insertion engagement portion 62g according to the radial position of the guide member 55 by the cam mechanism including the cam groove 55d and the cam engagement portion 52c, and the drive-side rotator 51 in the radial direction. Is moved along. At this time, the roller member 52 is guided to move in the radial direction by the outer peripheral surface of the cam engaging portion 52c being in sliding contact with the cam surface S.

  As described above, the clutch 50 includes the cam groove 55d formed in the guide member 55 and the roller member 52 that engages with the cam groove 55d. As the guide member 55 and the drive-side rotator 51 rotate relative to each other, the clutch 50 is provided. And a cam mechanism for guiding the movement of the roller member 52 in the radial direction by the cam groove 55d. As shown in FIGS. 6 and 7, the cam engagement is performed by the relative rotation between the drive side rotating body 51 and the guide member 55 in a state where the guide member 55 is disposed at the innermost radial direction within the radial movement range. When the portion 52c is disposed in the first guide portion P1 of the cam groove 55d, the power transmission portion 52b is disposed in the non-engaging recess 61e and is radially innermost in the radial movement range. Placed in. The arrangement position of the roller member 52 at this time corresponds to a non-engaging position where the driving side rotating body 51 and a driven side rotating body 56 described later are not engaged in the rotation direction. In the cam mechanism, the roller engagement member 52 is disengaged by disposing the cam engagement portion 52c in the first guide portion P1 of the cam groove 55d of the guide member 55 disposed on the innermost radial direction as described above. The state of being arranged at the alignment position is an initial state in which the rotary shaft 20 and the worm shaft 32 are disconnected.

  On the other hand, as shown in FIG. 8, the cam engagement portion is driven by the relative rotation of the drive side rotating body 51 and the guide member 55 in a state where the guide member 55 is disposed on the innermost radial direction within the radial movement range. When 52c is disposed in the second guide portion P2 of the cam groove 55d, as shown in FIG. 11A, the power transmission portion 52b is disposed on the outermost radial direction within the radial movement range. At this time, a part of the power transmission part 52b protrudes radially outward from the outer peripheral surface of the first drive plate 61, and the arrangement position of the roller member 52 at this time depends on the drive-side rotating body 51 and that described later. This corresponds to an engagement position where the driven-side rotator 56 is engaged in the rotation direction. The cam engaging portion 52c moves radially outward when moving from the first guide portion P1 to the second guide portion P2. Accordingly, the cam engagement portion 52c moves from the first guide portion P1 to the second guide portion P2 while contracting the return spring 53 in the radial direction against the urging force of the return spring 53. In the cam mechanism, the roller engagement member 52 is engaged by disposing the cam engagement portion 52c in the second guide portion P2 of the cam groove 55d of the guide member 55 disposed on the innermost radial direction as described above. A state where the rotary shaft 20 and the worm shaft 32 are connected is a state where the rotary shaft 20 and the worm shaft 32 are connected.

  The clutch 50 is constituted by a guide member 55 with which a roller member 52 is engaged, and the roller 50 is moved by the guide member 55 moved radially outward by the centrifugal force generated by rotating with the drive side rotating body 51. A holding mechanism for holding 52 in the engaged position is provided. In this holding mechanism, as shown in FIG. 8, the state in which the guide member 55 is disposed on the innermost radial direction within the movement range is an initial state in which the rotary shaft 20 and the worm shaft 32 are disconnected. Then, after the roller member 52 is moved to the second guide portion P2 by the cam mechanism and placed at the engagement position, the guide member 55 is guided to the drive side rotating body 51 while being moved radially outward by centrifugal force. When the member 55 is relatively rotated, the guide member 55 is rotated in the circumferential direction with respect to the roller member 52. At this time, although the cam engagement portion 52c moves from the second guide portion P2 to the first guide portion P1, the cam groove 55d is moved radially outward as the guide member 55 moves radially outward. The roller member 52 is maintained in a state of being disposed at the engagement position. In the holding mechanism, as described above, the guide member 55 is arranged on the outermost radial direction within the movement range, thereby guiding the cam engagement portion 52c while arranging the cam engagement portion 52c on the first guide portion P1 of the cam groove 55d. A state in which the roller member 52 is held at the engagement position by the member 55 is a connection state in which the rotary shaft 20 and the worm shaft 32 are connected.

  As shown in FIG. 3, the driven side rotating body 56 includes a bottomed cylindrical driven cylindrical portion 56a and a driven side shaft connecting portion 56b formed integrally with the driven cylindrical portion 56a. As shown in FIG. 1, the driven-side rotating body 56 is accommodated in the clutch accommodating portion 31b so that the opening of the driven cylindrical portion 56a faces the motor main body 12 side.

  As shown in FIG. 3, the outer diameter of the driven cylindrical portion 56 a is equal to the outer diameters of the second drive plate 62 and the holding case 54. Further, the inner depth of the driven side rotating body 56 is substantially equal to the axial length of the first drive plate 61. As shown in FIG. 6, on the inner peripheral surface of the cylindrical side wall portion 56c of the driven cylindrical portion 56a, there are two circumferentially equiangular intervals (180 ° intervals in the present embodiment), radially inward. A protruding control projection 56d is formed. In the driven-side rotator 56, the inner diameter of the portion where the control convex portion 56 d is formed is slightly larger than the outer diameter of the first drive plate 61. And as shown in FIG. 3, the 1st drive plate 61 and the accommodating part 62b are accommodated in the inside of the driven cylindrical part 56a. The outer periphery of the first drive plate 61 accommodated in the driven cylindrical portion 56a faces the control convex portion 56d in the radial direction. Further, the power transmission portion 52 b of the roller member 52 is disposed between the first drive plate 61 and the side wall portion 56 c of the driven side rotating body 56 that are opposed in the radial direction. The drive-side rotator 51 and the holding case 54 are arranged coaxially (so that the central axes coincide). Further, the end of the side wall portion 56 c on the opening side of the driven cylindrical portion 56 a faces the outer peripheral edge portion of the guide portion 62 a of the second drive plate 62 in the axial direction.

  As shown in FIG. 6, by forming the control convex portion 56d on the inner peripheral surface of the side wall portion 56c, the control concave portion 56e is formed between the control convex portions 56d adjacent to each other in the circumferential direction inside the driven-side rotating body 56. Is formed. The two control recesses 56e are formed at equal angular intervals in the circumferential direction (180 ° intervals in the present embodiment). The circumferential width of the control recess 56e is formed wider than the outer diameter of the power transmission portion 52b. And the inner side surface (the end surface of the circumferential direction of the control convex part 56d) of the both sides of the circumferential direction of the control recessed part 56e forms a pair of transmission surfaces 56f with which the space | interval of the circumferential direction becomes wide as it goes to radial inside. Yes. Each transmission surface 56f is parallel to the axial direction and has an arc shape with a curvature substantially equal to the curvature of the outer peripheral surface of the power transmission portion 52b.

  As shown in FIG. 3, a plate concave portion 56g that opens to the inside of the driven cylindrical portion 56a is formed in the center of the bottom of the driven cylindrical portion 56a, and the plate concave portion 56g has a disk-like shape. A thrust receiving plate 72 is accommodated. The thrust receiving ball 72 received in the ball receiving hole 61c of the first drive plate 61 is in contact with the thrust receiving plate 72. The thrust receiving plate 72 receives the thrust load of the rotary shaft 20 together with the thrust receiving ball 71.

  The driven side shaft coupling portion 56b extends along the axial direction from the center of the bottom of the driven cylindrical portion 56a and protrudes to the outside of the driven cylindrical portion 56a. Further, as shown in FIG. 1, the driven side shaft coupling portion 56 b has a cylindrical shape, and the outer diameter thereof is equal to the outer diameter of the worm side shaft coupling portion 32 b provided at the base end portion of the worm shaft 32. The size is assumed. In addition, the shaft connection recessed part 32c is formed in the base end surface (upper end surface in FIG. 1) of the worm side shaft connection part 32b in two places which become equiangular intervals (120 degree intervals) in the circumferential direction. FIG. 1 shows only one of the shaft coupling recesses 32c. Each of the shaft coupling recesses 32c is recessed along the axial direction of the worm shaft 32 from the base end surface of the worm side shaft coupling portion 32b, and on the base end side (upper side in FIG. 1) and radially outward of the worm shaft 32. It is open.

  As shown in FIG. 5, a shaft coupling convex portion 56h corresponding to the shaft coupling concave portion 32c (see FIG. 1) protrudes from the tip of the driven side shaft coupling portion 56b. The shaft coupling convex portion 56h is an outer peripheral edge at the tip of the driven side shaft coupling portion 56b, and projects in the axial direction from three locations that are equiangularly spaced in the circumferential direction (120 ° intervals in the present embodiment). Further, each of the shaft coupling convex portions 56h has a circumferential width, a radial width, and an axial length that are the circumferential width, radial width, and axial direction of the shaft coupling concave portion 32c (see FIG. 1). The depth of each is formed equal. As shown in FIGS. 1 and 3, by inserting the three shaft coupling convex portions 56h into the three shaft coupling concave portions 32c of the worm shaft 32, the driven-side rotating body 56 and the worm shaft 32 are connected to each other. It is engaged in the rotational direction and can rotate integrally. The driven-side shaft coupling portion 56b protrudes from the bottom of the clutch housing portion 31b into the shaft housing tube portion 31c and is pivotally supported by a bearing 36 disposed on one end side of the shaft housing tube portion 31c.

  In addition, the driven-side rotator 56 and the drive-side rotator 51 constitute a clamping mechanism that clamps the roller member 52 disposed at the engagement position. In this clamping mechanism, as shown in FIG. 6 or FIG. 11A, the power transmission portion 52b of the roller member 52 is formed by the wedge surface 61g of the driving side rotating body 51 and the transmission surface 56f of the driven side rotating body 56. The state in which the rotating shaft 20 and the worm shaft 32 are disconnected is a state in which the rotating shaft 20 and the worm shaft 32 are disconnected. On the other hand, as shown in FIG. 10, in the clamping mechanism, the state where the power transmission portion 52b of the roller member 52 disposed at the engagement position is clamped by the wedge surface 61g and the transmission surface 56f is the rotational shaft 20 and the worm. The shaft 32 is connected to the shaft 32. In this connected state, the first drive plate 61 is rotated relative to the second drive plate 62 while contracting the connection spring 63 against the urging force of the connection spring 63.

Next, the operation of the clutch 50 of this embodiment will be described.
In the clutch 50, the return of the cam mechanism from the connected state to the initial state and the return of the holding mechanism from the connected state to the initial state are performed by the urging force of the return spring 53 that urges the roller member 52.

  As shown in FIG. 8, in the cam mechanism in the coupled state, the return spring 53 attaches the radially inner cam surface S to the radially inner side along the radial direction via the cam engaging portion 52 c of the roller member 52. By returning to the initial state, the initial state is restored. Here, the urging force of the return spring 53 is F1, and the component force of the urging force F1 is F1a and F1b. The biasing force F1 of the return spring 53 is a force that biases the roller member 52 radially inward along the radial direction. The component force F1a is a component force of the urging force F1 in a direction parallel to the tangent L at the contact point between the cam engagement portion 52c disposed on the second guide portion P2 and the cam surface S, and the component force F1b is The force of the urging force F1 in the direction perpendicular to the tangent line is the force by which the cam engaging portion 52c disposed in the second guide portion P2 urges the cam surface S vertically. The component force F1b urges the inner peripheral surface of the cam groove 55d via the cam engagement portion 52c disposed in the second guide portion P2. The cam engaging portion 52c urges the inner peripheral surface of the cam groove 55d by the action of the component force F1b, so that the guide member 55 together with the holding case 54 moves the cam engaging portion 52c from the second guide portion P2. It is rotated in the direction of movement to the one guide part P1. As a result, the cam mechanism is returned to the initial state in which the cam engagement portion 52c is disposed in the first guide portion P1. The component force F1a biases the cam engaging portion 52c toward the first guide portion P1 substantially along the longitudinal direction of the cam groove 55d.

  Further, as shown in FIG. 9, in the holding mechanism in the connected state, the urging force of the return spring 53 is transmitted from the cam engagement portion 52c disposed in the first guide portion P1 to the inner peripheral surface of the cam groove 55d. To return to the initial state. More specifically, due to the action of the urging force F1 of the return spring 53, the cam engagement portion 52c disposed in the first guide portion P1 of the cam groove 55d attaches the inner peripheral surface of the cam groove 55d to the radially inner side. Rush. As a result, the guide member 55 is moved radially inward, and the holding mechanism returns to the initial state. As the holding mechanism returns to the initial state, the roller member 52 also returns to the disengaged position on the radially inner side.

  As shown in FIG. 10, the clamping mechanism in the connected state is returned to the initial state by the urging force of the connecting spring 63. More specifically, the first drive plate 61 is rotated relative to the second drive plate 62 by the biasing force of the coupling spring 63 that biases the return convex portion 61h (see arrow α in FIG. 10), and the first drive plate. 61 and the second drive plate 62 are returned to the neutral position. Then, the wedge surface 61g is separated from the transmission surface 56f, and the pinching between the wedge surface 61g and the transmission surface 56f is released. That is, the clamping mechanism is returned to the initial state.

Next, the operation of the motor 11 of this embodiment will be described focusing on the operation of the clutch 50.
When the rotary shaft 20 is not rotationally driven as when the motor body 12 is stopped, as shown in FIGS. 6 and 7, the relative rotational positions of the first drive plate 61 and the second drive plate 62 are as follows. By the urging force of the connecting spring 63 that urges the return convex portion 61h, the circumferential position of the two control grooves 61d and the circumferential position of the two guide concave portions 62f are maintained at a neutral position. In addition, since each guide member 55 is not subjected to centrifugal force, the most radial direction within the radial movement range of the guide member 55 due to the urging force of the return spring 53 transmitted through the cam engagement portion 52c. Arranged inside. Further, the cam engaging portion 52c is maintained in the state of being disposed in the first guide portion P1 by the urging force of the return spring 53, and the power transmission portion 52b is disengaged by the urging force of the return spring 53. It is maintained in a state of being placed inside. Therefore, the roller member 52 is located at the innermost radial position within the radial movement range, and is disposed at a non-engagement position where the roller member 52 does not engage with the driven side rotating body 56 in the rotational direction. Therefore, the cam mechanism, the holding mechanism, and the clamping mechanism are in an initial state, and the clutch 50 disconnects the rotating shaft 20 and the worm shaft 32.

  In this state, as shown in FIGS. 1 and 2, when the output shaft 35 is rotated from the slide door 3 side so as to manually open or close the slide door 3, the output shaft 35 is rotated. Thus, the worm shaft 32 is rotated. As shown in FIG. 6, when the rotary shaft 20 is not rotationally driven, the roller member 52 is disposed at the non-engagement position, so that the driven-side rotator 56 is engaged with the roller member 52 in the rotation direction. First, the rotating shaft 20 and the worm shaft 32 are in a disconnected state. Therefore, the driven-side rotator 56 idles with respect to the drive-side rotator 51 as the worm shaft 32 rotates. Therefore, rotation from the output shaft 35 side becomes easy. Therefore, it is possible to easily open and close the slide door 3 manually without requiring a large operating force.

  Then, as shown in FIGS. 1 to 3, when a command to automatically open or close the slide door 3 is generated, the motor body 12 is driven by the controller 25 and the rotary shaft 20 is driven to rotate. The drive side rotating body 51 connected to the rotating shaft 20 starts to rotate. As shown in FIG. 6, at the start of the rotational drive of the drive-side rotator 51, the first drive plate 61 and the second drive plate 62 rotate almost integrally (with almost no relative rotation). The roller member 52 also transmits the rotational driving force of the second drive plate 62 from the inner peripheral surface of the insertion engaging portion 62g to the cam engaging portion 52c, so that the center axis of the driving side rotating body 51 is the center of rotation. It rotates integrally with the drive side rotator 51. On the other hand, the rotation position of the guide member 55 and the holding case 54 that holds the guide member 55 is maintained by the inertial force that acts on the guide member 55 when the drive-side rotating body 51 starts to rotate. As a result, as shown in FIGS. 11A and 11B, the drive side rotating body 51 rotates relative to the guide member 55 and the holding case 54 at the start of the rotation drive. Then, a difference in rotation angle occurs between the drive side rotating body 51 and the guide member 55 held by the holding case 54. Then, since the cam engaging portion 52c is rotated in the circumferential direction of the holding case 54 with respect to the cam groove 55d, the cam mechanism is operated and the cam engaging portion 52c is guided to the cam surface S of the cam groove 55d. However, the first guide portion P1 is moved toward the second guide portion P2 on the front side in the rotation direction of the drive side rotating body 51. At this time, the cam engaging portion 52c is moved from the first guide portion P1 to the second guide portion P2 while contracting the return spring 53 in the radial direction against the urging force of the return spring 53. Then, the roller member 52 is moved from the radially inner non-engagement position to the radially outer engagement position by the action of the cam groove 55d. In addition, since the rotation position of the guide member 55 held by the holding case 54 is maintained by the inertial force when the drive side rotating body 51 starts to rotate, centrifugal force acts on the guide member 55. Not done. Therefore, when the cam engagement portion 52c moves relatively from the first guide portion P1 to the second guide portion P2 at the start of the rotational drive of the drive side rotating body 51, the guide member 55 moves in the radial direction. It is arranged on the innermost radial direction within the range.

  Then, as shown in FIGS. 12 (a) and 12 (b), the power transmission portion 52b of the roller member 52 disposed at the engagement position is moved into the control recess 56e as the drive side rotating body 51 rotates. Thus, it contacts the transmission surface 56f on the front side in the rotational direction of the drive-side rotator 51. Thereby, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 61, the connecting spring 63, the second driving plate 62, and the roller member 52, and further, the driven side rotation from the power transmission portion 52b of the roller member 52. It can be transmitted to the body 56.

  Further, at the start of the rotational drive of the drive side rotator 51, the slide door 3 connected to the driven side rotator 56 is stopped, so that a large load acts on the driven side rotator 56. Therefore, when the power transmission portion 52b of the roller member 52 disposed at the engagement position contacts the front transmission surface 56f in the rotation direction of the driving side rotating body 51, the roller member is caused by the reaction force received from the driven side rotating body 56. 52 is decelerated. And the 2nd drive plate 62 engaged with the roller member 52 in the cam engaging part 52c is also decelerated. On the other hand, as shown in FIG. 13A, the first drive plate 61 rotates in advance with respect to the second drive plate 62 while contracting the connection spring 63 against the urging force of the connection spring 63. That is, the first drive plate 61 rotates relative to the second drive plate 62. Accordingly, the first drive plate 61 rotates relative to the power transmission portion 52b of the roller member 52 that rotates integrally with the second drive plate 62, and the first drive plate 61 out of the pair of engaging recesses 61f of each control groove 61d. The power transmission portion 52b is disposed in the engagement concave portion 61f on the rear side in the rotational direction of the rotation, and the wedge surface 61g of the engagement concave portion 61f contacts the power transmission portion 52b from the rotational direction. And the power transmission part 52b is clamped by the wedge surface 61g and the transmission surface 56f. As a result, the rotational driving force of the rotary shaft 20 is transmitted from the first drive plate 61 to the driven-side rotator 56 via the power transmission portion 52b of the roller member 52 without passing through the connection spring 63 and the second drive plate 62. Then, the driven side rotator 56 starts to rotate.

  Also, as shown in FIGS. 12B and 13B, after the cam engaging portion 52c is disposed in the second guide portion P2, the roller that rotates together with the drive-side rotator 51 that has started to rotate. The guide member 55 to which the urging force of the return spring 53 is transmitted from the member 52 also starts to rotate with the drive side rotating body 51. When the rotation speed of the guide member 55 increases, the inertial force acting on the guide member 55 decreases as the rotation speed increases. The guide member 55 acts as a component force F1b (see FIG. 8) of the urging force F1 of the return spring 53 transmitted through the cam engagement portion 52c as the inertial force acting on the guide member 55 decreases. Thus, together with the holding case 54, the drive side rotator 51 rotates relative to the drive side rotator 51 in the same direction. Along with the relative rotation of the guide member 55 with respect to the drive-side rotator 51, the cam groove 55d of the guide member 55 held by the holding case 54 rotates in the circumferential direction of the holding case 54 with respect to the cam engaging portion 52c. Therefore, the cam engagement portion 52c is relatively moved from the second guide portion P2 to the first guide portion P1. At the same time, as the rotational speed of the guide member 55 increases, the centrifugal force acting on the guide member 55 gradually increases. Therefore, the guide member 55 is moved radially outward while being guided by the guide surface 54h. The Accordingly, since the radial position of the cam engagement portion 52c is maintained without changing in the radial direction, the roller member 52 is held at the engagement position by the guide member 55 (that is, the holding mechanism is in a connected state). .

  Then, after the driven-side rotator 56 starts to rotate, as shown in FIG. 13A, when the load acting on the driven-side rotator 56 is larger than the urging force of the connection spring 63, the first drive is performed. The plate 61 is rotated in the rotation direction of the first drive plate 61 with respect to the second drive plate 62 while contracting the connection spring 63 against the urging force of the connection spring 63. As a result, of the pair of wedge surfaces 61g of each control groove 61d, the wedge surface 61g on the rear side in the rotational direction of the first drive plate 61 comes into contact with the outer peripheral surface of the power transmission portion 52b from the rotational direction, and the wedge surface 61g. And the transmission surface 56f sandwich the power transmission unit 52b (that is, the clamping mechanism is in a connected state). Then, the rotational driving force of the rotary shaft 20 is transmitted from the first drive plate 61 to the driven side rotating body 56 via the roller member 52. As a result, since the driven-side rotator 56 is rotated, the worm shaft 32 connected to the driven-side rotator 56 is rotated. And the rotational force decelerated by the worm part 32a and the worm wheel 33 is output from the output shaft 35, and the sliding door 3 is automatically opened or closed.

  On the other hand, as shown in FIGS. 14A and 14B, when the load acting on the driven-side rotator 56 is equal to or less than the urging force of the connection spring 63, the first drive plate 61 and the second drive The plate 62 rotates integrally with the plate 62 while being held at the neutral position by the urging force of the coupling spring 63. Accordingly, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 61, the coupling spring 63, the second driving plate 62, the roller member 52, and the driven side rotating body 56. As a result, since the driven-side rotator 56 is rotated, the worm shaft 32 connected to the driven-side rotator 56 is rotated. And the rotational force decelerated by the worm part 32a and the worm wheel 33 is output from the output shaft 35, and the sliding door 3 is automatically opened or closed.

  When the motor main body 12 is stopped, the rotation speed of the rotating shaft 20 decreases. And as shown to Fig.13 (a), when the state when the motor main body 12 was stopped was a state where the load which acts on the driven side rotary body 56 is larger than the urging force of the connection spring 63, The connecting spring 63 that urges the return convex portion 61h rotates the first drive plate 61 in the direction opposite to the previous rotation direction. As a result, since the first drive plate 61 is rotated relative to the second drive plate 62, the holding of the power transmission portion 52b by the transmission surface 56f and the wedge surface 61g is released (that is, the holding mechanism is in the initial state). To return). Further, due to the urging force of the connecting spring 63, the relative rotational position of the first drive plate 61 and the second drive plate 62 matches the circumferential position of the two control grooves 61d and the circumferential position of the two guide recesses 62f. Return to the neutral position.

  Further, when the rotational speed of the drive-side rotator 51 decreases, the rotational speed of the guide member 55 and the driven-side rotator 56 that have been rotated by the rotational drive force transmitted from the drive-side rotator 51 via the roller member 52 is also increased. descend. Then, since the centrifugal force acting on the guide member 55 is reduced, the guide member 55 is moved radially inward by the urging force of the return spring 53 (that is, the holding mechanism returns to the initial state). As shown in FIGS. 6 and 7, the roller member 52 in which the cam engagement portion 52 c is inserted into the cam groove 55 d of the guide member 55 is moved radially inward together with the guide member 55. At this time, the cam engaging portion 52c is positioned in the first guide portion P1 in the cam groove 55d. Accordingly, the roller member 52 is moved from the engagement position to the non-engagement position. As a result, the rotation direction engagement between the driving side rotating body 51 and the driven side rotating body 56 is released, and the rotating shaft 20 and the worm shaft 32 are disconnected.

  14A and 14B, when the motor main body 12 is stopped, the load acting on the driven-side rotator 56 is smaller than the urging force of the connection spring 63. In such a case, when the centrifugal force acting on the guide member 55 decreases as the rotational speed of the drive-side rotator 51 decreases, the guide member 55 is moved radially inward by the urging force of the return spring 53 ( That is, the holding mechanism is returned to the initial state). As shown in FIGS. 6 and 7, the roller member 52 is moved radially inward together with the guide member 55. At this time, since the cam engagement portion 52c is located at the first guide portion P1 in the cam groove 55d, the roller member 52 is moved from the engagement position to the non-engagement position. As a result, the rotation direction engagement between the driving side rotating body 51 and the driven side rotating body 56 is released, and the rotating shaft 20 and the worm shaft 32 are disconnected.

  11A to 14A show the clutch 50 when the drive side rotating body 51 (rotating shaft 20) is rotated clockwise in the drawing. However, the clutch 50 connects the rotary shaft 20 and the worm shaft 32 in the same manner even when the rotary shaft 20 is rotated counterclockwise in FIGS. 11 (a) to 14 (a).

As described above, the first embodiment has the following effects.
(1) The return spring 53 exerts a biasing force so as to return the two mechanisms of the cam mechanism and the holding mechanism to the initial state. Therefore, the return spring 53 for returning the plurality of mechanisms to the initial state is provided. Compared with the case where it provides, the number of the return springs 53 can be decreased. As a result, the number of parts can be reduced. Further, the structure of the clutch 50 can be simplified and the assemblability can be improved.

  (2) The return spring 53 is configured so that the roller member 52 is disposed at the non-engagement position when the drive-side rotating body 51 is stopped by using two mechanisms of the cam mechanism, the holding mechanism, and the holding mechanism. That is, it is energized so as to be in the initial state. Therefore, the number of return springs 53 for returning the two mechanisms of the cam mechanism and the holding mechanism to the initial state can be reduced.

  (3) In the clutch 50 provided with the cam mechanism, when the drive-side rotator 51 and the guide member 55 are rotated together at the start of the rotational drive of the drive-side rotator 51, the clutch 50 is held by the drive-side rotator 51. The roller member 52 and the cam groove 55d of the guide member 55 are rotated relative to each other. When the driving-side rotator 51 and the guide member 55 rotate together, the roller member 52 is guided by the cam groove 55d and moves from the non-engagement position to the engagement position. As described above, the movement of the roller member 52 is performed in a state where the movement direction is regulated by the cam groove 55d. Therefore, the roller member 52 is stabilized from the non-engagement position to the engagement position while being guided by the cam groove 55d. Moved. In the conventional clutch, since the roller member is moved from the non-engagement position to the engagement position by the centrifugal force acting on the roller member, when the roller member is vigorously ejected radially outward by the centrifugal force when the motor body is driven. The roller member may be bounced back by the driven cylinder and return to the inside. Therefore, until the roller member is stably disposed at the engagement position, the operation of the roller member protruding outward in the radial direction due to centrifugal force being bounced back to the driven cylindrical portion may be repeated a plurality of times. . However, like the clutch 50 of the present embodiment, the roller member 52 is guided from the non-engagement position to the engagement position by the operation of the cam mechanism, so that the roller member can be quickly moved at the start of the rotational drive of the drive side rotating body 51. 52 can be stably arranged at the engagement position. Therefore, it is possible to improve the reliability of the operation of connecting the driving side rotating body 51 and the driven side rotating body 56.

  (4) In the clutch 50 provided with the holding mechanism, the roller member 52 is held at the engagement position by the guide member 55 moved radially outward by the centrifugal force when the drive side rotating body 51 is driven to rotate. Accordingly, since the state where the driving side rotating body 51 and the driven side rotating body 56 are connected via the roller member 52 is stably maintained, the driving side rotating body 51 and the driven side rotating body are connected via the roller member 52. The rotational driving force can be transmitted to 56 stably. In addition, since the roller member 52 is held at the engagement position by the guide member 55, friction is generated in order to maintain the state where the driving side rotating body 51 and the driven side rotating body 56 are connected when the driving side rotating body 51 is rotationally driven. There is no need to separately provide a means for generating a force or the like. Accordingly, the configuration and operation of the clutch 50 are suppressed from being complicated.

  (5) In the clutch 50 provided with the clamping mechanism, the roller member 52 arranged at the engagement position is clamped by the drive side rotary body 51 and the driven side rotary body 56, so that the roller member 52 is brought into the engagement position. It is easy to maintain the arrangement, and the rotational driving force can be stably transmitted from the driving side rotating body 51 to the driven side rotating body 56.

  (6) The return spring 53 urges the guide member 55 so as to rotate the drive-side rotator 51 and the guide member 55 so that the roller member 52 is moved to the non-engagement position side. 55 is urged radially inward. Therefore, the return spring 53 can easily return both the cam mechanism and the holding mechanism to the initial state only by urging the guide member 55.

  (7) The return spring 53 urges the cam surface S that guides the movement of the roller member 52 from the non-engagement position to the engagement position, radially inward along the roller member 52. Thus, the guide member 55 can be urged in the radial direction, and the guide member 55 can be urged in the rotational direction. Therefore, in order to return the two mechanisms of the cam mechanism and the holding mechanism to the initial state, it is not necessary to newly add a configuration for applying the urging force of the return spring 53 to the two mechanisms. As a result, it is suppressed that the structure of the clutch 50 is complicated.

  (8) Since the roller member 52 is a part related to all the mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism, by energizing the roller member 52 with the return spring 53, the return spring 53 and the mechanism Even if a new part is not added in between, the urging force of the roller member 52 can be easily applied to the cam mechanism and the holding mechanism via the roller member 52.

  (9) The clamping mechanism releases the clamping of the roller member 52 by the driving side rotating body 51 and the driven side rotating body 56 by the biasing force of the coupling spring 63, that is, returns to the initial state by the biasing force of the coupling spring 63. . Therefore, since the return spring 53 only needs to have an urging force enough to return the cam mechanism and the holding mechanism to the initial state, the urging force of the return spring 53 can be kept small. Therefore, it is possible to reduce the size of the return spring 53, and thus it is possible to reduce the size of the clutch 50. Further, if the urging force of the return spring 53 is suppressed to a small value, the weight of the guide member 55 that moves radially outward by centrifugal force against the urging force of the return spring 53 can be suppressed to be small. As a result, the weight of the clutch 50 can be reduced.

  (10) When the rotation drive of the rotation shaft 20 is stopped and the rotation drive of the first drive plate 61 is stopped, the first drive plate 61 is moved in the direction opposite to the previous rotation direction with respect to the second drive plate 62. The wedge surface 61g can be easily separated from the transmission surface 56f by urging the first drive plate 61 with the connecting spring 63 so as to rotate. Therefore, the clamping mechanism can be easily returned to the initial state by the urging force of the connecting spring 63.

  (11) The roller member 52 is guided to move between the non-engagement position and the engagement position by a groove-like cam groove 55d into which the cam engagement portion 52c is inserted. Therefore, when the return spring 53 biases the roller member 52 radially inward, the roller member 52 presses the inner peripheral surface of the cam groove 55d radially inward. Therefore, since the guide member 55 can be easily moved radially inward by the urging force of the return spring 53, the holding mechanism can be easily returned to the initial state. In addition, since the cam groove 55d has a simple shape such as a groove shape, the configuration of the guide member is prevented from being complicated.

  (12) Since the radial movement of the guide member 55 is guided by the holding case 54, the holding mechanism functions well. Further, the guide member 55 receives the urging force of the return spring 53 when the drive-side rotator 51 is stopped, and moves radially inward while being guided by the holding case 54, so that the holding mechanism is returned to the initial state. It is done smoothly.

  (13) At the start of the rotational drive of the drive-side rotator 51, the drive-side rotator 51 and the guide member 55 are rotated together using the inertial force acting on the guide member 55. Therefore, it is not necessary to separately provide a means for rotating the drive side rotating body 51 and the guide member 55 in order to move the roller member 52 from the non-engagement position to the engagement position.

  (14) The motor 11 includes the clutch 50 in which the number of return springs 53 is reduced. Therefore, since the number of parts constituting the motor 11 is reduced, the manufacturing cost is reduced. Further, since the clutch 50 is provided between the rotating shaft 20 of the motor main body 12 and the worm shaft 32 constituting the speed reducing mechanism 34, before the rotational driving force of the rotating shaft 20 in the motor 11 is decelerated. However, it is provided. Therefore, the load applied to each component constituting the clutch 50 can be kept small, and the clutch 50 can be downsized. Therefore, the motor including the clutch 50 can be reduced in size. The miniaturized motor 11 can be easily installed in a narrow space such as the inside of the slide door 3. Further, by providing the clutch 50 before the motor 11 is decelerated, a centrifugal force acting on the guide member 55 is easily generated. Therefore, it is advantageous when the guide member 55 is moved radially outward by centrifugal force as in the clutch 50 of the present embodiment.

  (15) The motor 11 used as a drive source of the slide door opening / closing device 1 is provided with a clutch 50 in which the number of return springs 53 is reduced. Accordingly, the number of parts constituting the slide door opening / closing device 1 is reduced, so that the manufacturing cost is reduced.

(Second Embodiment)
Hereinafter, a second embodiment of the present invention will be described with reference to the drawings. In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  A clutch 80 of the second embodiment shown in FIG. 15 is provided in the motor 11 in place of the clutch 50 of the first embodiment. The clutch 80 includes a driving side rotating body 81, two roller members 52, two return springs 82, a holding case 54, two guide members 55, and a driven side rotating body 56.

The drive-side rotator 81 includes a first drive plate 91 and a second drive plate 92 that is disposed so as to overlap the first drive plate 91.
As shown in FIG. 17, the first drive plate 91 has a substantially disk shape, and the outer diameter of the first drive plate 91 is the inner diameter of the portion where the control convex portion 56 d is formed in the driven side rotating body 56. It is formed slightly smaller than. A drive-side shaft coupling portion 61a, a shaft coupling recess 61b, and a ball housing hole 61c are formed in the radial center portion of the first drive plate 91. A thrust receiving ball 71 is accommodated in the ball accommodation hole 61c.

  As shown in FIGS. 15 and 16, two control grooves 91 a are formed in the outer peripheral edge portion of the first drive plate 91. The two control grooves 91a are formed at two locations in the first drive plate 91 that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment). Each control groove 91a is recessed radially inward from the outer peripheral edge of the first drive plate 91, thereby opening outward in the radial direction. Each control groove 91a is opened only in the axial direction only on the side opposite to the bottom of the driven side rotating body 56 (that is, on the second drive plate 92 side).

  A pair of wedge surfaces 91b are formed on the inner peripheral surface of each control groove 91a. The pair of wedge surfaces 91b each have a planar shape parallel to the axial direction, and with respect to the radial direction of the first drive plate 91 such that the distance between the pair of wedge surfaces 91b increases from the radially inner side toward the radially outer side. Inclined. Each wedge surface 91b faces radially outward.

  As shown in FIG. 17, the second drive plate 92 includes a guide part 62a and a storage part 62b, and has a disk shape. An insertion hole 62 c is formed in the central portion in the radial direction of the second drive plate 92. In addition, an insertion recess 92a that opens to the first drive plate 91 side is provided in the axial direction at the radial center of the housing portion 62b. The inner diameter of the insertion recess 92a is formed to be substantially equal to the outer diameter of the drive side shaft connecting portion 61a. In addition, guide recesses 62f are formed in the housing portion 62b at two locations that are equiangularly spaced in the circumferential direction (180 ° intervals in the present embodiment). Furthermore, the guide portion 62a is formed with insertion engagement portions 62g at two locations adjacent to the two guide recess portions 62f in the axial direction.

  As shown in FIGS. 16 and 17, the first drive plate 91 and the second drive plate 92 as described above are configured so that the drive side shaft connecting portion 61a is inserted into the insertion recess 92a and two controls are performed. The groove 91a and the two guide recesses 62f are overlapped in the axial direction so as to overlap each other in the axial direction. In the drive-side rotator 81, the first drive plate 91 and the second drive plate 92 are arranged coaxially (so that their center axes coincide with each other). The drive-side rotator 81 is disposed with respect to the driven-side rotator 56 so that the first drive plate 91 and the accommodating portion 62b are accommodated inside the driven cylindrical portion 56a. They are arranged on the same axis (so that their center axes coincide with each other). Further, the holding case 54 holding the pair of guide members 55 is overlapped in the axial direction with respect to the drive side rotating body 81 so that the insertion portion 54b is inserted into the insertion hole 62c from the guide portion 62a side. The holding case 54 is also coaxial with the driving side rotating body 81 and the driven side rotating body 56 (the center axes of the holding case 54 coincide with each other).

  Further, in the pair of roller members 52, the power transmission portions 52b are respectively inserted into the two control grooves 91a of the first drive plate 91, and the connection portions 52a are respectively connected to the two guide recesses 62f of the second drive plate 92. It is assembled to the drive side rotating body 81 so as to be inserted. In each roller member 52, the cam engagement portion 52c is positioned radially inward of the power transmission portion 52b, and the urging surface 52d faces the radially outer side. Further, in each roller member 52, the roller member 52 is disposed between the first drive plate 91 and the side wall portion 56 c of the driven side rotating body 56 that face each other in the radial direction. Further, the tip side portions of the cam engaging portions 52 c of the two roller members 52 are respectively inserted into the cam grooves 55 d of the two guide members 55. Each roller member 52 is urged radially inward by a return spring 82 accommodated in the insertion engagement portion 62g. The return spring 82 is disposed on the radially outer side of the cam engaging portion 52c in the insertion engaging portion 62g, and urges the urging surface 52d radially inward. Note that the return spring 82 of the present embodiment is a compression coil spring.

  Similarly to the clutch 50 of the first embodiment, the clutch 80 of the second embodiment also includes a cam mechanism including a cam groove 55d and a cam engagement portion 52c, a holding mechanism including a guide member 55, and a drive side. A clamping mechanism including a rotating body 81 and a driven rotating body 56 is provided.

Next, the operation of the clutch 80 of the present embodiment will be described.
In the clutch 80, the return of the cam mechanism from the connected state to the initial state, the return of the holding mechanism from the connected state to the initial state, and the return of the clamping mechanism from the connected state to the initial state are performed by the urging force of the return spring 82. Done.

  Similar to the return spring 53 of the first embodiment, the return spring 82 biases the roller member 52 radially inward along the radial direction. The return of the cam mechanism from the connected state to the initial state and the return of the holding mechanism from the connected state to the initial state are performed in the same manner as in the first embodiment.

  In the clamping mechanism, as shown in FIG. 16, the power transmission portion 52b of the roller member 52 is not clamped by the wedge surface 91b of the driving side rotating body 81 and the transmission surface 56f of the driven side rotating body 56 (that is, The state where the clamping is released is an initial state in which the rotary shaft 20 and the worm shaft 32 are disconnected. On the other hand, as shown in FIG. 18, in the clamping mechanism, the state where the power transmission part 52b of the roller member 52 arranged at the engagement position is clamped by the wedge surface 91b and the transmission surface 56f is the rotation shaft 20 and the worm. The shaft 32 is connected to the shaft 32. Here, the biasing force of the return spring 82 that biases the roller member 52 radially inward along the radial direction is F2, the component force of the biasing force F2 in the direction parallel to the wedge surface 91b is F2a, and perpendicular to the wedge surface 91b. The component force of the urging force F2 in any direction is defined as F2b. The wedge surface 91b holding the power transmission portion 52b together with the transmission surface 56f is pressed in a direction away from the transmission surface 56f by the component force F2b transmitted through the power transmission portion 52b. As a result, the first driving plate 91 is rotated relative to the second driving plate 92 and the driven-side rotator 56 by the component force F2b, and the wedge surface 91b is separated from the transmission surface 56f and transmitted to the wedge surface 91b. The clamping by the surface 56f is released. That is, the clamping mechanism returns to the initial state.

Next, the operation of the motor 11 of this embodiment will be described focusing on the operation of the clutch 80.
When the rotating shaft 20 is not driven to rotate as when the motor main body 12 is stopped, the relative rotational position of the first drive plate 91 and the second drive plate 92 is adjusted by the return spring 82 as shown in FIG. By biasing the member 52 radially inward, the circumferential position of the two control grooves 91a and the circumferential position of the two guide recesses 62f are maintained at a neutral position. In addition, since each guide member 55 is not subjected to centrifugal force, it is the most radial direction within the radial movement range of the guide member 55 due to the urging force of the return spring 82 transmitted through the cam engagement portion 52c. Arranged inside. Further, the cam engagement portion 52c is maintained in a state where it is disposed in the first guide portion P1 by the urging force of the return spring 82, and the power transmission portion 52b is disengaged by the urging force of the return spring 82. It is maintained in a state of being placed inside. Therefore, the roller member 52 is located at the innermost radial position within the radial movement range, and is disposed at a non-engagement position where the roller member 52 does not engage with the driven side rotating body 56 in the rotational direction. Therefore, the cam mechanism, the holding mechanism, and the clamping mechanism are in an initial state, and the clutch 80 disconnects the rotating shaft 20 and the worm shaft 32.

  In this state, as shown in FIGS. 1 and 2, when the output shaft 35 is rotated from the slide door 3 side so as to manually open or close the slide door 3, the output shaft 35 is rotated. Thus, the worm shaft 32 is rotated. When the rotary shaft 20 is not driven to rotate, the rotary shaft 20 and the worm shaft 32 are disconnected by the clutch 80, so that the driven-side rotator 56 rotates the worm shaft 32 as shown in FIG. Along with this, the drive-side rotator 81 idles. Therefore, rotation from the output shaft 35 side becomes easy. Therefore, it is possible to easily open and close the slide door 3 manually without requiring a large operating force.

  Then, as shown in FIGS. 1 to 3, when a command to automatically open or close the slide door 3 is generated, the motor body 12 is driven by the controller 25 and the rotary shaft 20 is driven to rotate. The drive-side rotator 81 connected to the rotary shaft 20 starts to rotate. At the start of the rotational drive of the drive-side rotator 81, as shown in FIG. 16, the first drive plate 91 and the second drive plate 92 are controlled by the roller member 52 urged radially inward by the return spring 82. Since the bottom surface on the radially inner side of the groove 91a and the bottom surface on the radially inner side of the guide recess 62f are biased radially inward, the groove 91a rotates substantially integrally (with almost no relative rotation). Further, the roller member 52 also transmits the rotational driving force of the second drive plate 62 from the inner peripheral surface of the insertion engagement portion 62g to the cam engagement portion 52c, so that the central axis of the drive side rotating body 81 is the center of rotation. Rotates integrally with the drive side rotating body 81. On the other hand, as shown in FIGS. 19A and 19B, the guide member 55 and the holding case 54 holding the guide member 55 are placed on the guide member 55 at the start of the rotational drive of the drive side rotating body 81. The rotational position is maintained by the acting inertial force. As a result, the drive-side rotator 81 rotates relative to the guide member 55 and the holding case 54 at the start of the rotation drive. Then, a difference in rotation angle occurs between the drive side rotating body 81 and the guide member 55 held by the holding case 54. Then, since the cam engaging portion 52c is rotated in the circumferential direction of the holding case 54 with respect to the cam groove 55d, the cam mechanism is activated, and the cam engaging portion 52c is guided to the cam groove 55d while being guided by the cam groove 55d. It is moved from the part P1 toward the second guide part P2 on the front side in the rotational direction of the drive side rotating body 81. At this time, the cam engaging portion 52c is moved from the first guide portion P1 to the second guide portion P2 while contracting the return spring 53 in the radial direction against the urging force of the return spring 82. Then, the roller member 52 is moved from the radially inner non-engagement position to the radially outer engagement position by the action of the cam groove 55d. In addition, since the rotation position of the guide member 55 held by the holding case 54 is maintained by the inertial force at the start of the rotation drive of the drive-side rotator 81, centrifugal force acts on the guide member 55. Not done. Therefore, when the cam engagement portion 52c moves relatively from the first guide portion P1 to the second guide portion P2 at the start of the rotational drive of the drive side rotating body 81, the guide member 55 moves in the radial direction. It is arranged on the innermost radial direction within the range.

  As the drive-side rotator 81 rotates, the power transmission portion 52b of the roller member 52 disposed at the engagement position is transmitted to the front-side transmission surface 56f in the rotation direction of the drive-side rotator 81 in the control recess 56e. Abut. Further, as shown in FIGS. 20A and 20B, the first drive plate 91 moves relative to the second drive plate 92 as the roller member 52 moves from the non-engagement position to the engagement position. Thus, the first drive plate 91 rotates relative to the rotation direction. Then, the power transmission part 52b is clamped by the transmission surface 56f and the wedge surface 91b on the rear side in the rotation direction of the first drive plate 91 among the pair of wedge surfaces 91b of each control groove 91a (that is, the clamping mechanism is Connected). As a result, the rotational driving force of the rotating shaft 20 is transmitted from the first driving plate 91 to the driven side rotating body 56 via the power transmission portion 52b of the roller member 52 without passing through the second driving plate 92, and the driven side The rotating body 56 begins to rotate.

  Further, as shown in FIGS. 20B and 21B, after the cam engaging portion 52c is disposed in the second guide portion P2, the roller that rotates together with the drive-side rotator 81 that has started to rotate. The guide member 55 to which the urging force of the return spring 82 is transmitted from the member 52 also starts to rotate with the drive side rotating body 51. When the rotation speed of the guide member 55 increases, the inertial force acting on the guide member 55 decreases as the rotation speed increases. As the inertial force acting on the guide member 55 becomes smaller, the guide member 55 rotates together with the holding case 54 on the driving side by the action of the urging force of the return spring 53 transmitted through the cam engagement portion 52c. Rotate relative to the body 81 in the same direction as the drive-side rotator 81. Along with the relative rotation of the guide member 55 with respect to the drive-side rotator 81, the cam groove 55d of the guide member 55 held by the holding case 54 rotates in the circumferential direction of the holding case 54 with respect to the cam engaging portion 52c. Therefore, the cam engagement portion 52c is relatively moved from the second guide portion P2 to the first guide portion P1. At the same time, as the rotational speed of the guide member 55 increases, the centrifugal force acting on the guide member 55 gradually increases. Therefore, the guide member 55 is moved radially outward while being guided by the guide surface 54h. The Accordingly, since the radial position of the cam engagement portion 52c is maintained without changing in the radial direction, the roller member 52 is held at the engagement position by the guide member 55.

  Then, when the rotational driving force of the rotary shaft 20 is transmitted from the first drive plate 91 to the driven side rotating body 56 via the roller member 52 as shown in FIG. Since it is rotated, the worm shaft 32 connected to the driven side rotating body 56 is rotated. And the rotational force decelerated by the worm part 32a and the worm wheel 33 is output from the output shaft 35, and the sliding door 3 is automatically opened or closed.

  Moreover, when the motor main body 12 is stopped, the rotational speed of the rotating shaft 20 falls. Then, as shown in FIG. 18, the return spring 82 rotates the first drive plate 91 in the direction opposite to the immediately preceding rotation direction via the roller member 52. As a result, as shown in FIG. 16, the first drive plate 91 is rotated relative to the second drive plate 92, so that the holding of the power transmission portion 52b by the transmission surface 56f and the wedge surface 91b is released ( That is, the clamping mechanism is returned to the initial state). Further, due to the biasing force of the return spring 82, the relative rotational position of the first drive plate 91 and the second drive plate 92 matches the circumferential position of the two control grooves 91a and the circumferential position of the two guide recesses 62f. Return to the neutral position.

  Further, when the rotational speed of the drive-side rotator 81 decreases, the rotational speeds of the guide member 55 and the driven-side rotator 56 that have been rotated by the rotational drive force transmitted from the drive-side rotator 81 via the roller member 52 are also increased. descend. Then, since the centrifugal force acting on the guide member 55 is reduced, the guide member 55 is moved radially inward by the urging force of the return spring 82 (that is, the holding mechanism returns to the initial state). The roller member 52 in which the cam engaging portion 52 c is inserted into the cam groove 55 d of the guide member 55 is moved radially inward together with the guide member 55. At this time, the cam engaging portion 52c is positioned in the first guide portion P1 in the cam groove 55d. Accordingly, the roller member 52 is moved from the engagement position to the non-engagement position. As a result, the rotation direction engagement between the driving side rotating body 81 and the driven side rotating body 56 is released, and the rotating shaft 20 and the worm shaft 32 are disconnected.

  FIGS. 19A to 21A show the clutch 80 when the drive side rotating body 81 (rotating shaft 20) is rotated in the clockwise direction in the drawing. However, the clutch 80 connects the rotary shaft 20 and the worm shaft 32 in the same manner even when the rotary shaft 20 is rotated counterclockwise in FIGS. 19 (a) to 21 (a).

As described above, according to the second embodiment, in addition to the same effects as (1), (3) to (7) and (11) to (15) of the first embodiment, the following effects are obtained. Have
(16) The return spring 82 is configured such that the three mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism are arranged so that the roller member 52 is disposed at the non-engagement position when the driving side rotating body 51 is stopped. Is energized. Therefore, the number of return springs 82 for returning the three mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism to the initial state can be minimized.

  (17) The wedge surface 91b that sandwiches the roller member 52 together with the transmission surface 56f is inclined with respect to the radial direction. Accordingly, the return spring 82 biases the wedge surface 91b radially inward along the radial direction via the roller member 52, so that the wedge surface 91b and the transmission surface 56f are separated from each other. 91 can be biased in the rotational direction. Therefore, in order to return the clamping mechanism to the initial state, it is not necessary to newly add a configuration for applying the urging force of the return spring 82 to the clamping mechanism. As a result, it is further suppressed that the configuration of the clutch 80 is complicated. Further, since the return spring 82 biases the roller member 52 radially inward along the radial direction, the cam surface S can also be biased in the radial direction, so that the cam mechanism, the holding mechanism, and the clamping mechanism It is not necessary to separately provide a configuration for applying the urging force of the return spring 82 to the three mechanisms. Therefore, the configuration of the clutch 80 is further suppressed from being complicated.

  (18) The roller member 52 is a part related to all the mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism. The biasing force of the member 52 can be easily applied to all the mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism.

(Third embodiment)
Hereinafter, a third embodiment of the present invention will be described with reference to the drawings. In the third embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  A clutch 100 of the third embodiment shown in FIG. 22 is provided in the motor 11 in place of the clutch 50 of the first embodiment. Compared with the clutch 50, the clutch 100 includes a second drive plate 102 instead of the second drive plate 62. The second drive plate 102 constitutes the drive side rotating body 51 together with the first drive plate 61 and the connecting spring 63. As shown in FIGS. 22, 23 (a) and 23 (b), the second drive plate 102 has a shape in which the insertion path 103 is added to the second drive plate 62 of the first embodiment. Yes.

  As shown in FIGS. 22 and 24, the pair of spring accommodating recesses 62d formed in the second drive plate 102 is the circumferential direction of the clutch 100 (the same as the rotation direction of the first drive plate 61 and the second drive plate 102). It has an arc shape extending along. Further, as shown in FIG. 23A, each spring accommodating recess 62d penetrates the accommodating portion 62b from the axial end surface of the accommodating portion 62b on the first drive plate 61 side, and the accommodating portion 62b in the guide portion 62a. It is recessed in the axial direction up to the axial end of the side.

  Further, as shown in FIG. 24, a first pressing surface 62m and a second pressing surface 62n are formed on the inner side surfaces of both ends in the circumferential direction of each spring accommodating recess 62d. At both ends in the circumferential direction of each spring accommodating recess 62d, the first pressing surface 62m is a surface located radially outward from the return recess 62e, and the second pressing surface 62n is radially inward from the return recess 62e. It is a surface to be located. The first pressing surface 62m and the second pressing surface 62n extend along the radial direction, are parallel to the axial direction, and have a planar shape perpendicular to the circumferential direction. In addition, the first pressing surface 62m and the second pressing surface 62n that are adjacent in the radial direction at both ends in the circumferential direction of each spring housing recess 62d are formed in the same plane. Furthermore, the second pressing surface 62n is formed longer in the radial direction than the first pressing surface 62m. That is, the radial length L2 of the second pressing surface 62n is set to a value longer than the radial length L1 of the first pressing surface 62m. In other words, each spring accommodating recess 62d and the pair of return recesses 62e provided on both sides in the circumferential direction of the spring accommodating recess 62d are such that the second pressing surface 62n is longer in the radial direction than the first pressing surface 62m. Thus, the radial formation position in the second drive plate 102 is set. The first pressing surface 62m and the second pressing surface 62n are pressed (biased) in the circumferential direction by the connecting spring 63 that is accommodated in a compressed state in the spring accommodating recess 62d.

  As shown in FIGS. 22 and 24, in the second drive plate 102, the insertion path 103 is formed on the radially outer side of each spring accommodating recess 62d. Each insertion path 103 is linear along the radial direction from the center in the circumferential direction of each spring accommodating recess 62d to the outer peripheral surface of the second drive plate 102 (that is, the outer peripheral surface of the accommodating portion 62b and the outer peripheral surface of the guide portion 62a). It extends to. And each insertion path 103 is extended so that it may orthogonally cross with respect to the expansion-contraction direction (illustrated by arrow (beta) in FIG. 24) of the connection spring 63 arrange | positioned in the spring accommodation recessed part 62d. In this embodiment, the expansion / contraction direction of the connection spring 63 is the same as the rotation direction of the second drive plate 102 when the clutch 100 is operated. Further, as shown in FIGS. 23A and 23B, each insertion path 103 opens in the axial direction toward the first drive plate 61 and in the radial direction inside the spring accommodating recess 62d and An opening is formed on the outer peripheral side of the second drive plate 102. Each insertion path 103 communicates with a spring accommodating recess 62d located on the radially inner side. Furthermore, the bottom surface of each insertion path 103 has a planar shape orthogonal to the axial direction and is flush with the bottom surface of the spring accommodating recess 62d.

  As shown in FIG. 24, the side surfaces 103a, 103b at both ends in the circumferential direction of each insertion path 103 are formed in parallel with the center line X1 of the insertion path 103 that passes through the center in the circumferential direction of the insertion path 103 and extends in the radial direction. ing. The side surfaces 103a and 103b are formed in parallel with the axial direction. Each insertion path 103 has an end in the expansion / contraction direction of the connection spring 63 at the insertion path 103 even when the connection spring 63 is compressed between the first drive plate 61 and the second drive plate 102 when the clutch 100 is operated. It is formed so as not to reach. More specifically, as shown in FIG. 25, the position Y1 of one side surface 103a in the circumferential direction (the side surface on the clockwise side in FIG. 25) is such that the first drive plate 61 in FIG. It is located closer to the other side surface 103a than the position Y2 of one end of the connecting spring 63 in the expansion / contraction direction (clockwise end in FIG. 25) when it is relatively rotated counterclockwise to the maximum. Similarly, the other side surface 103b in the circumferential direction (the side surface on the counterclockwise side in FIG. 25) is the maximum rotation of the first drive plate 61 relative to the second drive plate 102 in the clockwise direction in FIG. The connecting spring 63 is formed so as to be located on the side surface 103a side of the other end (end in the counterclockwise direction in FIG. 25) in the expansion / contraction direction. Therefore, even if the coupling spring 63 is compressed during the operation of the clutch 100, the end of the coupling spring 63 in the expansion / contraction direction is not caught on the circumferential side surfaces 103a and 103b of the insertion path 103.

As shown in FIG. 26, the circumferential length L3 of each insertion path 103 is formed to be longer than the length L4 of the coupling spring 63 compressed to the maximum.
The clutch 100 of the third embodiment described above operates in the same manner as the clutch 50 of the first embodiment when the motor 11 is driven / stopped.

Next, the operation of the clutch 100 of the third embodiment will be described together with the assembly procedure of the clutch 100.
As shown in FIGS. 22, 23 (a), and 23 (b), in order to assemble the clutch 100, first, the components of the clutch 100 other than the two connecting springs 63 and the driven side rotating body 56, that is, the first The first drive plate 61, the second drive plate 102, the two roller members 52, the two return springs 53, the holding case 54, and the two guide members 55 are assembled. The thrust receiving ball 71 and the thrust receiving plate 72 may be assembled at this time, or may be assembled immediately before the driven side rotating body 56 is assembled. When the thrust receiving ball 71 and the thrust receiving plate 72 are assembled at this time, the thrust receiving ball 71 is inserted into the ball receiving hole 61 c of the first drive plate 61, while the thrust receiving plate 72 is inserted into the driven side rotating body 56. It arrange | positions in the plate recessed part 56g.

  When the first drive plate 61, the second drive plate 102, the two roller members 52, the two return springs 53, the holding case 54, and the two guide members 55 are assembled, the housing portion is accommodated with respect to the second drive plate 102. The first drive plate 61 is disposed so as to overlap in the axial direction on the 62b side. Accordingly, the first drive plate 61 closes the openings of the pair of spring accommodating recesses 62d from the axial direction.

  Next, as shown in FIG. 26, the connection spring 63 is inserted into the spring accommodating recess 62 d through the insertion path 103 from the outside of the first drive plate 61 and the second drive plate 102 assembled together. At this time, the connection spring 63 is compressed in advance and is contracted to be shorter than the circumferential length L3 of the insertion path 103. The connection spring 63 is inserted into the insertion path 103 from the outside in the radial direction of the second drive plate 102. Then, the connecting spring 63 is pushed inward in the radial direction until it passes through the insertion path 103 along the radial direction. As shown in FIG. 24, the coupling spring 63 that has passed through the insertion path 103 enters the spring accommodating recess 62d and extends in the circumferential direction in the spring accommodating recess 62d, and both ends of the coupling spring 63 in the expansion / contraction direction are first. 2 abuts on the pressing surface 62n and the first pressing surface 62m. Thus, the connecting spring 63 is assembled. Thereafter, the driven-side rotator 56 is assembled and the clutch 100 is completed.

  As described above, since the insertion path 103 is formed in the second drive plate 102, the connecting spring 63 is assembled to the spring housing recess 62d in a state where the opening of the spring housing recess 62d is closed by the first drive plate 61. Can be attached.

As described above, according to the third embodiment, in addition to the same effects as (1) to (15) of the first embodiment, the following effects are obtained.
(19) With the first drive plate 61 and the second drive plate 102 assembled to each other, the coupling spring 63 can be inserted into the spring accommodating recess 62d through the insertion path 103. Generally, the connection spring 63 housed in the spring housing recess 62d in a compressed state may jump out of the spring housing recess 62d from the opening of the spring housing recess 62d due to stress (internal force) generated by compression. is there. When the connecting spring 63 is compressed in an arc shape as in the present embodiment, the connecting spring 63 generates different stresses in the radially inner portion and the radially outer portion. There is a possibility that it will be easier to jump out of the opening of the recess 62d to the outside of the spring accommodating recess 62d. Accordingly, when the connecting spring 63 can be assembled through the insertion path 103 to the spring accommodating recess 62d whose opening is closed by the first drive plate 61 as in this embodiment, the coupling spring 63 is assembled to the spring accommodating recess 62d. The connected spring 63 is prevented from coming out of the spring accommodating recess 62d from the opening of the spring accommodating recess 62d. As a result, the assembling property of the connecting spring 63 can be improved. In addition, when the other components of the clutch 100 are assembled after the coupling spring 63 is assembled to the spring accommodating recess 62d, the coupling spring 63 is prevented from coming off, so that the assembly of the clutch 100 can be improved.

  (20) Even if the connection spring 63 is compressed between the first drive plate 61 and the second drive plate 102 during the operation of the clutch 100 and the connection spring 63 is shortened in the expansion and contraction direction, the expansion and contraction of the connection spring 63 is achieved. The direction end does not reach the insertion path 103. Therefore, the connection spring 63 is prevented from being caught on the insertion path 103 during the operation of the clutch 100.

  (21) When the coupling spring 63 made of a compression coil spring is inserted into the arc-shaped spring accommodating recess 62d extending in the rotation direction (same as the circumferential direction) of the second drive plate 102, the coupling spring 63 is placed on the outer circumferential side. Compared to the inner peripheral part, the amount of compression increases. Accordingly, the force of the connecting spring 63 that tends to extend at the inner peripheral portion is larger than that at the outer peripheral portion, and therefore the connecting spring 63 moves radially outward in the spring accommodating recess 62d. try to. Therefore, the second pressing surface 62n provided on the inner side in the radial direction is formed longer in the radial direction than the first pressing surface 62m provided on the outer side in the radial direction, so that the coupling spring 63 is stabilized in the spring accommodating recess 62d. Can be accommodated.

  (22) When the spring accommodating recess 62d is formed in an arc shape extending along the rotation direction of the first drive plate 61 and the second drive plate 102 (same as the circumferential direction of the clutch 100), the spring accommodating recess 62d is radially inward. The end portion on the outer side in the radial direction of the spring accommodating recess 62d tends to be longer in the circumferential direction than the end portion. When the first pressing surface 62m and the second pressing surface 62n formed at the circumferential end of the spring accommodating recess 62d extend along the radial direction as in this embodiment, the radial direction in the spring accommodating recess 62d The radially outer end of the spring accommodating recess 62d is longer in the circumferential direction than the inner end. Therefore, by forming the insertion path 103 on the radially outer side of the spring accommodating recess 62d, the insertion path 103 communicating with the spring accommodating recess 62d is formed rather than when the insertion path 103 is formed on the radially inner side of the spring accommodating recess 62d. The range in which can be formed becomes wider in the circumferential direction. Accordingly, since there are fewer restrictions when the insertion path 103 is formed in the second drive plate 102, the insertion path 103 can be easily formed in the second drive plate 102.

(Fourth embodiment)
Hereinafter, a fourth embodiment of the present invention will be described with reference to the drawings. In the fourth embodiment, the same components as those in the first embodiment and the third embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  A clutch 110 according to the fourth embodiment shown in FIG. 27 is provided in the motor 11 in place of the clutch 50 according to the first embodiment. The clutch 110 includes a second drive plate 112 having an insertion path 113 instead of the second drive plate 102 having the insertion path 103 as compared with the clutch 100 of the third embodiment.

  The insertion path 113 is formed in the second drive plate 112 on the radially outer side of each spring accommodating recess 62d. Each insertion path 113 extends linearly from the circumferential center of each spring accommodating recess 62d to the outer peripheral surface of the second drive plate 112 (that is, the outer peripheral surface of the accommodating portion 62b and the outer peripheral surface of the guide portion 62a). Each insertion path 113 opens to the first drive plate 61 side in the axial direction, and opens to the inside of the spring accommodating recess 62d and the outer peripheral side of the second drive plate 112 in the radial direction. Each insertion path 113 communicates with a spring accommodating recess 62d located on the radially inner side. Further, the bottom surface of each insertion path 113 has a planar shape orthogonal to the axial direction and is flush with the bottom surface of the spring accommodating recess 62d.

  Each insertion path 113 extends so as to incline in the radial direction of the second drive plate 112 (same as the radial direction of the clutch 110), and a connecting spring 63 (in FIG. 27) disposed in the spring accommodating recess 62d. Is inclined with respect to the expansion / contraction direction (illustrated by an arrow β in FIG. 27). Therefore, in each insertion path 113, the outer opening 113a on the side opposite to the spring accommodating recess 62d is formed at a position shifted in the circumferential direction with respect to the inner opening 113b on the spring accommodating recess 62d side.

  In addition, a pair of guide surfaces 113c and 113d facing each other in the circumferential direction are formed on the inner peripheral surface of each insertion path 113. The pair of guide surfaces 113c and 113d are both side surfaces in the circumferential direction of the insertion path 113, and are formed from the outer opening 113a to the inner opening 113b, respectively. Further, the pair of guide surfaces 113c and 113d are formed so as to be parallel to each other while forming a planar shape parallel to the axial direction. Furthermore, the pair of guide surfaces 113c and 113d are inclined without being orthogonal to the extending and contracting direction of the connecting spring 63 disposed in the spring accommodating recess 62d. Therefore, the end on the outer opening 113a side of the guide surface 113c is located at a position shifted in the circumferential direction with respect to the end on the inner opening 113b side of the guide surface 113c, and the outer opening 113a of the guide surface 113d. The end on the side is located at a position shifted in the circumferential direction with respect to the end on the inner opening 113b side in the guide surface 113c. Further, the width D1 of each insertion path 113 (that is, the distance between the pair of guide surfaces 113c and 113d) is constant from the outer opening 113a to the inner opening 113b, and is substantially equal to the outer diameter D2 of the connection spring 63. Equally (slightly wider) formed.

  Each insertion path 113 has an end in the expansion / contraction direction of the connection spring 63 at the insertion path 113 even when the connection spring 63 is compressed between the first drive plate 61 and the second drive plate 112 when the clutch 110 is operated. It is formed so as not to reach. That is, the inner opening 113b of the insertion path 113 has an end in the expansion / contraction direction of the connection spring 63 even when the connection spring 63 is compressed between the first drive plate 61 and the second drive plate 112 when the clutch 110 is operated. It is formed in a range that does not enter the inside of the inner opening 113b. Therefore, even if the coupling spring 63 is compressed during the operation of the clutch 110, the end of the coupling spring 63 in the expansion / contraction direction is not caught by the pair of guide surfaces 113c and 113d that are both side surfaces in the circumferential direction of the insertion path 113. It is like that.

The clutch 110 of the fourth embodiment operates in the same manner as the clutch 50 of the first embodiment when the motor 11 is driven / stopped.
Next, the operation of the clutch 110 according to the fourth embodiment will be described together with the assembly procedure of the clutch 110.

  In order to assemble the clutch 110, first, the components of the clutch 110 other than the two coupling springs 63 and the driven side rotating body 56, that is, the first drive plate 61, the second drive plate 112, the two roller members 52, The return spring 53, the holding case 54, and the two guide members 55 are assembled. The thrust receiving ball 71 and the thrust receiving plate 72 may be assembled at this time, or may be assembled before the driven side rotating body 56 is assembled. When the thrust receiving ball 71 and the thrust receiving plate 72 are assembled at this time, the thrust receiving ball 71 is inserted into the ball receiving hole 61 c of the first drive plate 61, while the thrust receiving plate 72 is inserted into the driven side rotating body 56. It arrange | positions in the plate recessed part 56g.

  When the first drive plate 61, the second drive plate 112, the two roller members 52, the two return springs 53, the holding case 54, and the two guide members 55 are assembled, the housing portion is accommodated with respect to the second drive plate 112. The first drive plate 61 is disposed so as to overlap in the axial direction on the 62b side. Accordingly, the first drive plate 61 closes the openings of the pair of spring accommodating recesses 62d from the axial direction.

  Next, the connecting spring 63 is inserted into the spring accommodating recess 62 d through the insertion path 113 from the outside of the first drive plate 61 and the second drive plate 112 assembled together. At this time, without compressing the connection spring 63 in advance, the connection spring 63 is inserted into the insertion path 113 from one end in the expansion / contraction direction (longitudinal direction) of the connection spring 63 along the pair of guide surfaces 113c and 113d. . Then, the connection spring 63 is guided by the pair of guide surfaces 113c and 113d, so that the insertion direction of the connection spring 63 (refer to the dashed line arrow in FIG. 27) causes the connection spring 63 to expand and contract in the spring accommodating recess 62d. Inclined with respect to direction.

  Then, after one end portion of the connection spring 63 in the expansion / contraction direction passes through the insertion path 113 and enters the spring accommodating recess 62d, when the connection spring 63 is further inserted along the guide surfaces 113c and 113d, the expansion direction of the connection spring 63 is increased. The one end part abuts on the radially inner side surface 62s facing the inner opening 113b on the inner peripheral surface of the spring accommodating recess 62d. Since the inner side surface 62s extends along the expansion and contraction direction of the connection spring 63 in the spring accommodating recess 62d, the insertion direction of the connection spring 63 guided by the guide surfaces 113c and 113d is relative to the inner side surface 62s. It is inclined. Accordingly, after one end of the coupling spring 63 in the expansion / contraction direction comes into contact with the inner side surface 62s, when the coupling spring 63 is further pushed along the guide surfaces 113c and 113d toward the spring accommodating recess 62d, the coupling spring 63 accommodates the spring. One end in the circumferential direction of the spring accommodating recess 62d (the end farther from the outer opening 113a) while the portion inserted into the recess 62d bends along the expansion / contraction direction of the connecting spring 63 in the spring accommodating recess 62d. It is inserted into. Then, after one end of the coupling spring 63 in the expansion / contraction direction comes into contact with the second pressing surface 62n and the first pressing surface 62m provided at one end in the circumferential direction of the spring accommodating recess 62d, the coupling spring 63 is compressed, The connecting spring 63 is further pushed in until the other end of the connecting spring 63 passes through the insertion path 113 and is inserted into the spring accommodating recess 62d. When the other end of the connecting spring 63 is inserted into the spring accommodating recess 62d, the connecting spring 63 extends in the spring accommodating recess 62d, and the other end of the connecting spring 63 extends in the other direction in the circumferential direction of the spring accommodating recess 62d. It contacts the second pressing surface 62n and the first pressing surface 62m provided at the end. Thus, the connecting spring 63 is assembled. Thereafter, the driven side rotating body 56 is assembled, and the clutch 110 is completed.

  As described above, since the insertion path 113 is formed in the second drive plate 112, the connecting spring 63 is assembled to the spring accommodating recess 62d in a state where the opening of the spring accommodating recess 62d is closed by the first drive plate 61. be able to. Further, the pair of guide surfaces 113c and 113d formed on the inner peripheral surface of the insertion path 113 is inclined with respect to the expansion / contraction direction of the connecting spring 63 in the spring accommodating recess 62d. Therefore, it is not necessary to compress the connection spring 63 in advance before inserting the connection spring 63 into the insertion path 113 by inserting the connection spring 63 into the insertion path 113 along the guide surfaces 113c and 113d.

As described above, according to the fourth embodiment, in addition to the same effects as (1) to (15) of the first embodiment and (19) to (22) of the third embodiment, It has the effect of.
(23) When the coupling spring 63 is inserted into the insertion path 113 along the guide surfaces 113c and 113d from one end in the expansion / contraction direction of the coupling spring 63, the coupling spring 63 is in contact with the inner side surface 62s of the spring accommodating recess 62d. The connecting spring 63 is inserted into the spring receiving recess 62d while being inclined with respect to the extending and contracting direction of the connecting spring 63 in the spring receiving recess 62d. Then, after one end portion of the coupling spring 63 in the expansion / contraction direction comes into contact with the inner side surface 62s, a portion of the coupling spring 63 inserted into the spring accommodating recess 62d from the insertion path 113 is located along the inner side surface 62s. Enter the depths of 62d. Therefore, the connecting spring 63 can be assembled to the spring accommodating recess 62d without being inserted into the insertion path 113 in a compressed state. As a result, the assembling property of the connecting spring 63 is further improved.

(Fifth embodiment)
Hereinafter, a fifth embodiment of the present invention will be described with reference to the drawings. In the fifth embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  A clutch 150 of the fifth embodiment shown in FIG. 28 is provided in the motor 11 in place of the clutch 50 of the first embodiment. The cross-sectional view of the clutch 150 shown in FIG. 28 is a cross-sectional view of the clutch 150 cut at the same location as the cross-section indicating line AA in the clutch 50 of the first embodiment shown in FIG. Compared with the clutch 50 of the first embodiment, the clutch 150 includes a driven-side rotator 151 having a control recess 151a instead of the driven-side rotator 56 (see FIG. 6) having the control recess 56e. . The clutch 150 includes a first drive plate 152 instead of the first drive plate 61 of the first embodiment. The configuration of the clutch 150 is the same as that of the clutch 50 of the first embodiment except for the driven-side rotator 151 and the first drive plate 152.

  Two control recesses 151a are formed in the inner peripheral surface of the side wall portion 56c included in the driven side rotating body 151. The control recess 151a is formed by recessing radially outward at two locations that are 180 ° apart in the circumferential direction on the inner peripheral surface of the side wall 56c. Each control recess 151a includes a first engagement recess 151b and a pair of second engagement recesses 151c provided in the bottom surface of the first engagement recess 151b. The depth of the first engaging recess 151b in the radial direction is deeper than the radius of the power transmission portion 52b of the roller member 52 and is larger than the radial width of the power transmission portion 52b (that is, the diameter of the power transmission portion 52b). shallow. In addition, the circumferential width of the first engagement recess 151b is wider than the circumferential width of the power transmission unit 52b (that is, the diameter of the power transmission unit 52b). In the present embodiment, the first engagement recess 151b is formed over a range of about 150 ° on the inner peripheral surface of the side wall portion 56c, and its circumferential width is about the diameter of the power transmission portion 52b. It is 9 times wider. Furthermore, the first engaging recess 151b is continuous in the axial direction from the axial end surface of the driven cylindrical portion 56a in the side wall portion 56c to the bottom surface of the driven cylindrical portion 56a. Is formed. And the 1st engagement recessed part 151b is opened to the radial direction inner side and the axial direction one side (opening part side of the driven cylindrical part 56a).

  In each control recess 151a, the pair of second engagement recesses 151c are formed at both ends in the circumferential direction of the bottom surface of the first engagement recess 151b. Each second engagement recess 151c is formed by recessing the bottom surface of the first engagement recess 151b in a circular arc shape radially outward. The radial depth of each second engagement recess 151c (the depth from the bottom surface of the first engagement recess 151b) is slightly shallower than the radius of the power transmission portion 52b. In addition, each second engagement recess 151c is continuously formed in the axial direction from the end surface in the axial direction on the opening side of the driven cylindrical portion 56a in the side wall portion 56c to the bottom surface of the driven cylindrical portion 56a. Each of the second engaging recesses 151c is open on the radially inner side and the one side in the axial direction (the opening side of the driven cylindrical portion 56a). Furthermore, the inner peripheral surface of each second engagement recess 151c has an arc shape with the same curvature as the outer peripheral surface of the power transmission portion 52b, and has a constant cross-sectional shape along the axial direction. As shown in FIG. 32A, when the power transmission portion 52b is inserted into the second engagement recess 151c from the inside in the radial direction, the power transmission portion 52b is fitted into the second engagement recess 151c. Engage. When the power transmission portion 52b is fitted into the second engagement recess 151c, the outer peripheral surface thereof abuts on the inner peripheral surface of the second engagement recess 151c and is relatively moved in the circumferential direction (rotation direction) with respect to the side wall portion 56c. It becomes impossible.

  As shown in FIG. 28, the two control recesses 151a as described above are formed, so that the side wall 56c has two controls protruding radially inward from the bottom surface of the first engagement recess 151b. A convex portion 56d is formed. The control convex portions 56d are formed at two locations that are 180 ° apart in the circumferential direction. In the inner peripheral surface of the side wall portion 56c, the ratio occupied by the two control concave portions 151a is larger than the ratio occupied by the two control convex portions 56d. The inner side surfaces (the end surfaces in the circumferential direction of the control convex portion 56d) on both sides in the circumferential direction of each control concave portion 151a form a pair of transmission surfaces 56f whose circumferential intervals increase toward the inner side in the radial direction. ing. The power transmission unit 52b located in the first engagement recess 151b can contact the transmission surface 56f from the circumferential direction (rotation direction).

  Compared with the first drive plate 61 of the first embodiment, the first drive plate 152 constituting the drive-side rotator 51 includes a control groove 152a instead of the control groove 61d. The control grooves 152 a are formed at two locations that are spaced 180 ° in the circumferential direction at the outer peripheral edge of the first drive plate 152. Each control groove 152a is formed by recessing the outer peripheral edge of the first drive plate 152 radially inward, and is open radially outward. In addition, each control groove 152a has a substantially fan shape in which the shape seen from the axial direction becomes wider in the circumferential direction as it goes outward in the radial direction. Furthermore, when viewed from the axial direction, each control groove 152a is formed in line symmetry with a straight line (not shown) extending in the radial direction passing through the center in the circumferential direction as a symmetry axis.

  In addition, a pair of wedge surfaces 152b having a substantially planar shape are formed on the inner peripheral surface of each control groove 152a. The pair of wedge surfaces 152b are parallel to the axial direction. The pair of wedge surfaces 152b are respectively formed on both sides in the circumferential direction of the bottom portion (the most radially inner portion) of the control groove 152a located at the circumferential center portion of the control groove 152a. The gap is inclined with respect to the radial direction so that the interval between the bottom of the groove 152a and the opening on the radially outer side of the control groove 152a increases in the circumferential direction. As shown in FIG. 30, each wedge surface 152b can contact the power transmission portion 52b located in the first engagement recess 151b from the rotation direction so as to sandwich the power transmission portion 52b together with the transmission surface 56f. Further, as shown in FIG. 31, each wedge surface 152b abuts on the power transmission portion 52b located in the second engagement recess 151c from the rotation direction so as to contact the inner peripheral surface of the second engagement recess 151c and the transmission surface 56f. At the same time, the power transmission part 52b can be clamped.

  In the clutch 150 of the present embodiment, as shown in FIG. 29A, the arrangement position of the roller member 52 when the power transmission portion 52b is located in the first engagement recess 151b is the drive-side rotator 51. And a driven-side rotator 151 in the rotation direction. As shown in FIG. 32 (a), the arrangement position of the roller member 52 when the power transmission portion 52b is located in the second engagement recess 151c is on the drive side on the radially outer side than the first engagement position. This is a second engagement position where the rotating body 51 and the driven-side rotating body 151 are engaged in the rotation direction. Further, as shown in FIGS. 28 and 29 (b), when the cam engaging portion 52c is disposed at the first guide portion P1 of the cam groove 55d and the roller member 52 is disposed at the non-engaging position, the power The transmission part 52b is located at the bottom of the control groove 152a, and is located radially inward from the tip surface of the control convex part 56d. Further, as shown in FIGS. 29 (a) and 29 (b), a cam engagement is provided on the second guide portion P2 of the cam groove 55d of the guide member 55 arranged on the innermost radial direction within the radial movement range. When the joint portion 52c is located, the power transmission portion 52b is located in the first engagement recess 151b.

Next, the operation of the clutch 150 will be described together with the operation of the clutch 150.
As shown in FIG. 28, when the rotary shaft 20 is not rotationally driven as when the motor body 12 is stopped, the relative rotational position of the first drive plate 152 and the second drive plate 62 is determined by the connecting spring. By the urging force 63, the circumferential position of the two control grooves 152a and the circumferential position of the two guide recesses 62f are maintained at a neutral position. Further, the roller member 52 is arranged at the non-engagement position by the urging force of the return spring 53, and the guide member 55 (see FIG. 29B) is moved within the radial movement range by the urging force of the return spring 53. It is arranged on the innermost radial direction. Therefore, like the clutch 50 of the first embodiment, the cam mechanism, the holding mechanism, and the clamping mechanism are in the initial state, and the clutch 150 disconnects the rotating shaft 20 and the worm shaft 32. Therefore, when the output shaft 35 is rotated from the slide door 3 side, the driven-side rotating body 151 rotates idle with respect to the driving-side rotating body 51 as the worm shaft 32 rotates (see FIG. 1).

  As shown in FIGS. 29A and 29B, when the motor body 12 is driven, the rotary shaft 20 is driven to rotate, and the drive-side rotator 51 connected to the rotary shaft 20 is driven to rotate. Be started. 29 (b) and 32 (b) are cross-sectional views of the clutch 150 at the same location as the cross-section indicating line BB in the clutch 50 of the first embodiment shown in FIG. It is sectional drawing cut | disconnected. At the start of the rotational drive of the drive-side rotator 51, the first drive plate 152 and the second drive plate 62 rotate substantially integrally (with almost no relative rotation). The roller member 52 also transmits the rotational driving force of the second drive plate 62 from the inner peripheral surface of the insertion engaging portion 62g to the cam engaging portion 52c, so that the center axis of the driving side rotating body 51 is the center of rotation. It rotates integrally with the drive side rotator 51. On the other hand, the rotation position of the guide member 55 and the holding case 54 that holds the guide member 55 is maintained by the inertial force that acts on the guide member 55 when the drive-side rotating body 51 starts to rotate. As a result, the drive-side rotator 51 rotates relative to the guide member 55 and the holding case 54 at the start of the rotation drive. Then, a difference in rotation angle occurs between the drive side rotating body 51 and the guide member 55 held by the holding case 54. Then, since the cam engaging portion 52c is rotated in the circumferential direction of the holding case 54 with respect to the cam groove 55d, the cam mechanism is operated and the cam engaging portion 52c is guided to the cam surface S of the cam groove 55d. However, the first guide portion P1 is moved toward the second guide portion P2 on the front side in the rotation direction of the drive side rotating body 51. At this time, the cam engaging portion 52c is moved from the first guide portion P1 to the second guide portion P2 while contracting the return spring 53 in the radial direction against the urging force of the return spring 53. Therefore, the power transmission portion 52b is moved from the bottom portion of the control groove 152a into the first engagement recess 151b by the action of the cam groove 55d, and the roller member 52 is moved radially from the non-engagement position in the radial direction. It is moved to the outer first engagement position. In addition, since the rotation position of the guide member 55 held by the holding case 54 is maintained by the inertial force when the drive side rotating body 51 starts to rotate, centrifugal force acts on the guide member 55. Not done. Therefore, when the cam engagement portion 52c moves relatively from the first guide portion P1 to the second guide portion P2 at the start of the rotational drive of the drive side rotating body 51, the guide member 55 moves in the radial direction. It is arranged on the innermost radial direction within the range.

  Then, the power transmission portion 52b of the roller member 52 disposed at the first engagement position with the rotation of the drive-side rotator 51 rotates the drive-side rotator 51 within the first engagement recess 151b of the control recess 151a. It contacts the transmission surface 56f on the front side in the direction. Thereby, the rotational drive force of the rotating shaft 20 is transmitted in the order of the first drive plate 152, the coupling spring 63, the second drive plate 62, and the roller member 52, and further, the driven side rotation from the power transmission portion 52b of the roller member 52. It can be transmitted to the body 151.

  In addition, since the slide door 3 connected to the driven-side rotator 151 is stopped at the start of the rotational drive of the drive-side rotator 51, a large load is applied to the driven-side rotator 151. Therefore, when the power transmission portion 52b of the roller member 52 disposed at the first engagement position abuts on the transmission surface 56f on the front side in the rotation direction of the driving side rotating body 51, the reaction force received from the driven side rotating body 151 causes The roller member 52 is decelerated. And the 2nd drive plate 62 engaged with the roller member 52 in the cam engaging part 52c is also decelerated. On the other hand, as shown in FIG. 30, the first drive plate 152 that rotates integrally with the rotary shaft 20 is a second drive plate that contracts the connecting spring 63 between the return convex portion 61h and the inner peripheral surface of the spring accommodating concave portion 62d. Rotate relative to 62 in advance. Therefore, the first drive plate 152 rotates relative to the power transmission portion 52b of the roller member 52 that rotates integrally with the second drive plate 62, and the first drive plate 152 of the pair of wedge surfaces 152b of each control groove 152a rotates. The wedge surface 152b on the rear side in the rotational direction contacts the power transmission unit 52b from the rotational direction. And the power transmission part 52b located in the 1st engagement recessed part 151b is clamped by the wedge surface 152b and the transmission surface 56f. As a result, the rotational driving force of the rotary shaft 20 is transmitted from the first drive plate 152 to the driven-side rotator 151 via the power transmission portion 52b of the roller member 52 without passing through the connection spring 63 and the second drive plate 62. Then, the driven side rotating body 151 starts to rotate.

  Further, as shown in FIGS. 29A and 29B, the cam engagement portion 52c is disposed in the second guide portion P2, and at the same time, the power transmission portion 52b is disposed in the first engagement recess 151b. After that, the guide member 55 to which the urging force of the return spring 53 is transmitted from the roller member 52 that rotates together with the drive-side rotator 51 that has started rotating is also started to rotate with the drive-side rotator 51. When the rotation speed of the guide member 55 increases, the inertial force acting on the guide member 55 decreases as the rotation speed increases. As the inertial force acting on the guide member 55 becomes smaller, the guide member 55 rotates together with the holding case 54 on the driving side by the action of the urging force of the return spring 53 transmitted through the cam engagement portion 52c. It rotates relative to the body 51 in the same direction as the driving side rotating body 51. The cam groove 55d of the guide member 55 is rotated in the circumferential direction of the holding case 54 with respect to the cam engagement portion 52c in association with the relative rotation of the guide member 55 with respect to the drive-side rotator 51. 52c is relatively moved from the second guide part P2 to the first guide part P1. At the same time, as the rotational speed of the guide member 55 increases, the centrifugal force acting on the guide member 55 gradually increases. Therefore, the guide member 55 moves radially outward while being guided by the guide surface 54h. Is done. Accordingly, since the radial position of the cam engagement portion 52c is maintained without changing in the radial direction, the roller member 52 is held at the first engagement position by the guide member 55 (that is, the holding mechanism is in the connected state). Become).

  During the rotation of the driven-side rotator 56 based on the rotational drive of the rotating shaft 20, the rotational speed of the drive-side rotator 51 is such that the roller member 52 is brought into the first engagement position by the centrifugal force acting on the guide member 55. In some cases, the guide member 55 may be arranged at a position to be held. In this case, when the load acting on the driven-side rotator 56 is greater than the urging force of the coupling spring 63, the first driving plate 152 contracts the coupling spring 63 and the second driving plate 152 as shown in FIG. The first drive plate 61 is rotated in the rotation direction with respect to 62. As a result, of the pair of wedge surfaces 152b of each control groove 152a, the wedge surface 152b on the rear side in the rotation direction of the first drive plate 152 is rotated from the rotation direction to the power transmission unit 52b located in the first engagement recess 151b. The power transmission part 52b is clamped by the wedge surface 152b and the transmission surface 56f (that is, the wedge mechanism is connected). Then, the rotational driving force of the rotating shaft 20 is transmitted from the first drive plate 152 to the driven side rotating body 151 via the roller member 52, and the driven side rotating body 151 is rotated.

  Further, in the same case where the rotational speed of the drive-side rotator 51 is large enough to place the guide member 55 at a position where the roller member 52 is held at the first engagement position by the centrifugal force acting on the guide member 55. When the load acting on the side rotating body 56 is equal to or less than the urging force of the connection spring 63, the first drive plate 152 and the second drive plate 62 are integrated with each other while being held at the neutral position by the connection spring 63. Rotate to. Accordingly, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 152, the coupling spring 63, the second driving plate 62, the roller member 52, and the driven side rotating body 151, and the driven side rotating body 151 is rotated. .

  Further, as shown in FIGS. 32A and 32B, during the rotation of the driven side rotating body 56 based on the rotational drive of the rotating shaft 20, the rotational speed of the driving side rotating body 51 is the guide member 55. In some cases, the roller member 52 is sized to be arranged from the first engagement position to the second engagement position due to the centrifugal force acting on the lens. That is, the rotational speed of the drive-side rotator 51 may be large enough to fit the power transmission portion 52b into the second engagement recess 151c by centrifugal force acting on the guide member 55. In this case, when the load acting on the driven-side rotator 56 is larger than the urging force of the connection spring 63, the first drive plate 152 contracts the connection spring 63 as shown in FIG. The first drive plate 61 is rotated in the rotation direction with respect to 62. As a result, of the pair of wedge surfaces 152b of each control groove 152a, the wedge surface 152b on the rear side in the rotational direction of the first drive plate 152 is transferred from the rotational direction to the power transmission unit 52b located in the second engagement recess 151c. The power transmission part 52b is clamped by the wedge surface 152b and the driven-side rotator 151 (that is, the wedge mechanism is connected). Then, the rotational driving force of the rotating shaft 20 is transmitted from the first drive plate 152 to the driven side rotating body 151 via the roller member 52, and the driven side rotating body 151 is rotated.

  Further, in the same case where the rotational speed of the driving side rotating body 51 is large enough to arrange the roller member 52 from the first engaging position to the second engaging position by centrifugal force acting on the guide member 55, the driven side rotating body. When the load acting on 56 is equal to or less than the urging force of the connection spring 63, the first drive plate 152 and the second drive plate 62 are brought into the neutral position by the connection spring 63, as shown in FIG. Rotates integrally while being held. Accordingly, the rotational driving force of the rotating shaft 20 is transmitted in the order of the first driving plate 152, the coupling spring 63, the second driving plate 62, the roller member 52, and the driven side rotating body 151, and the driven side rotating body 151 is rotated. .

  Further, in the same case where the rotational speed of the driving side rotating body 51 is large enough to arrange the roller member 52 from the first engaging position to the second engaging position by centrifugal force acting on the guide member 55, the driven side rotating body. A reverse load (that is, a load in the same direction as the rotation direction of the drive-side rotator 51 (see white arrows in FIGS. 31 and 32A)) may be applied to 56. When a reverse load is applied to the driven side rotating body 56, the driven side rotating body 151 tries to rotate ahead of the driving side rotating body 51. However, the power transmission portion 52b is immovable relative to the driven-side rotating body 151 in the rotational direction by being fitted and engaged with the second engaging recess 151c. Accordingly, relative rotation between the driving side rotating body 51 and the driven side rotating body 151 that rotate integrally with the power transmission unit 52b is prevented, and the driving side rotating body 51 and the driven side rotating body 151 are interposed via the roller member 52. The connection is prevented from being released. Therefore, the connection of the driving side rotating body 51 and the driven side rotating body 151 via the roller member 52 during the rotation of the driving side rotating body 51 based on the rotational drive of the rotating shaft 20 is prevented.

  When the motor main body 12 is stopped, the clutch 150 is stopped by the same operation as the clutch 50 of the first embodiment. That is, as shown in FIG. 28, the first drive plate 152 and the second drive plate 62 are returned to the neutral position by the biasing force of the connection spring 63. Thereby, when the power transmission part 52b is clamped by the wedge surface 152b and the driven side rotating body 151, the clamping is cancelled | released. Further, since the centrifugal force acting on the guide member 55 becomes smaller as the rotational speed of the drive side rotating body 51 decreases, the guide member 55 is moved radially inward by the urging force of the return spring 53. As the guide member 55 moves inward in the radial direction, the roller member 52 is moved from the engagement position to the non-engagement position. Thereby, the power transmission part 52b is moved from the inside of the control recessed part 151a to the bottom part of the control groove 152a. As a result, the rotation direction engagement between the driving side rotating body 51 and the driven side rotating body 151 is released, and the rotating shaft 20 and the worm shaft 32 are disconnected.

  29 (a), 30, 31, and 32 (a) show the clutch 150 when the drive side rotating body 51 (rotating shaft 20) is rotated clockwise in the drawing. However, the clutch 150 similarly connects the rotary shaft 20 and the worm shaft 32 even when the rotary shaft 20 is rotated counterclockwise in FIGS. 29 (a), 30, 31, and 32 (a). Is.

As described above, the fifth embodiment has the following effects in addition to the same effects as (1) to (15) of the first embodiment.
(24) Since the first engaging recess 151b is wider in the rotational direction (rotating direction of the driving side rotating body 51) than the power transmission portion 52b of the roller member 52, the cam is at the start of the rotational driving of the driving side rotating body 51. When the roller member 52 is moved radially outward by the mechanism, the power transmission portion 52b is easily inserted into the first engagement recess 151b. That is, the amount of rotation of the drive-side rotator 51 from when the drive-side rotator 51 starts to rotate until the power transmission portion 52b enters the first engagement recess can be reduced. Therefore, the drive-side rotator 51 and the driven-side rotator 151 can be engaged in the rotation direction via the roller member 52 in a short time after the drive of the drive-side rotator 51 is started. Moreover, when the power transmission part 52b is inserted in the 2nd engagement recessed part 151c, the power transmission part 52b and the driven side rotary body 151 cannot be relatively moved in the rotation direction. For example, when the control recess 151a does not include the second engagement recess 151c, if a reverse load, which is a load in the same direction as the rotation direction of the drive side rotor 51, is applied to the driven side rotor 151, the power transmission There is a possibility that the portion 52b is separated from the transmission surface 56f and the engagement between the driving side rotating body 51 and the driven side rotating body 151 by the roller member 52 is released. On the other hand, in the clutch 150 of the present embodiment, when the power transmission portion 52b is engaged with the second engagement recess 151c, the rotation direction of the drive side rotator 51 with respect to the driven side rotator 151 is Even when a reverse load, which is a load in the same direction, is applied, it is possible to maintain a state where the driving side rotating body 51 and the driven side rotating body 151 are engaged in the rotation direction via the roller member 52. As a result, the transmission of the rotational driving force from the driving side rotating body 51 to the driven side rotating body 151 is prevented from being interrupted. Therefore, the rotational driving force can be stably transmitted from the driving side rotating body 51 to the driven side rotating body 151.

  (25) The second engagement recesses 151c are formed at both ends in the rotation direction on the bottom surface of the first engagement recess 151b. Therefore, the power transmission portion 52b can be inserted into the second engagement recess 151c regardless of the rotation direction of the drive-side rotator 51. Therefore, it is possible to stably transmit the rotational driving force from the driving side rotating body 51 to the driven side rotating body 151 regardless of the rotation direction of the driving side rotating body 51.

  (26) After the power transmission portion 52b is inserted into the first engagement recess 151b, the power transmission portion 52b is inserted into the second engagement recess 151c by centrifugal force acting on the guide member 55. Therefore, it is not necessary to separately provide a means for generating a force for inserting the power transmission part 52b into the second engagement recess 151c. Therefore, it can suppress that the structure of the clutch 150 is complicated.

(Sixth embodiment)
Hereinafter, a sixth embodiment of the present invention will be described with reference to the drawings. In the sixth embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  A clutch 160 of the fifth embodiment shown in FIG. 33 is provided in the motor 11 instead of the clutch 50 of the first embodiment. The clutch 160 includes a blocking recess 55e in the cam groove 55d of each guide member 55, as compared with the clutch 50 of the first embodiment.

  The blocking recess 55e of each guide member 55 is formed by recessing the cam surface S that constitutes the inner peripheral surface of the cam groove 55d. Specifically, the blocking recess 55e is a central portion in the circumferential direction (rotation direction) of the cam surface S on the radially inner side of the pair of cam surfaces S constituting the inner peripheral surface of the cam groove 55d, that is, the first guide portion P1. A radially inner portion (a portion adjacent to the first guide portion P1 in the radial direction) is formed to be recessed radially inward. Of the pair of cam surfaces S of the cam groove 55d, the radially inner cam surface S is a surface that is urged radially inward by the return spring 53 via the roller member 52. The blocking recess 55e penetrates the guide member 55 in the axial direction like the cam groove 55d, and the shape viewed from the axial direction has an arc shape. Further, the curvature of the arc of the blocking recess 55e is equal to the curvature of the outer peripheral surface of the cam engagement portion 52c. The cam engaging portion 52c can be inserted into the blocking recess 55e from the radial direction, and the outer peripheral surface of the cam engaging portion 52c inserted into the blocking recess 55e abuts on the outer peripheral surface of the blocking recess 55e. Thus, the blocking recess 55e is engaged in the rotational direction (same as the circumferential direction of the holding case 54). Further, the depth of the blocking recess 55e is such that when the roller member 52 attempts to rotate in the circumferential direction of the holding case 54 with the cam engaging portion 52c fitted and engaged with the blocking recess 55e, The depth is such that rotation of the roller member 52 with respect to the cam groove 55d (rotation in the circumferential direction of the holding case 54) is prevented by the engagement of the cam engagement portion 52c. In the present embodiment, the depth of the blocking recess 55e in the radial direction is slightly shallower than the radius of the cam engagement portion 52c.

  Further, when the guide member 55 is located on the innermost radial direction within the radial movement range (that is, in contact with the bottom surface 54k) and the roller member 52 is located at the non-engagement position, the inner peripheral surface of the blocking recess 55e. Is positioned radially inward of the outer peripheral surface of the cam engaging portion 52c disposed in the first guide portion P1, and is not in contact with the outer peripheral surface of the cam engaging portion 52c. Accordingly, the cam engaging portion 52c located at the first guide portion P1 of the cam groove 55d of the guide member 55 arranged on the innermost radial direction within the radial movement range is not inserted into the blocking recess 55e and blocked. It is not engaged with the recess 55e.

  Next, the operation of the clutch 160 according to the present embodiment will be described together with the operation of the clutch 160. The clutch 160 connects / disconnects the rotary shaft 20 and the worm shaft 32 in the same manner as the clutch 50 of the first embodiment. Here, operations of the guide member 55 and the roller member 52 will be mainly described.

  When the rotary shaft 20 is not driven to rotate as when the motor body 12 is stopped, the centrifugal force is not applied to each guide member 55, and therefore a return spring transmitted through the cam engaging portion 52c. The guide member 55 is arranged on the innermost radial side within the radial movement range of the guide member 55 by the urging force of 53. Further, the roller member 52 is disposed at the non-engagement position by the urging force of the return spring 53. Accordingly, the cam engaging portion 52c is maintained in the state of being disposed in the first guide portion P1, and is located radially outside the inner peripheral surface of the blocking recess 55e and is not engaged with the blocking recess 55e. Furthermore, the power transmission part 52b is maintained in a state of being disposed in the non-engaging recess 61e. Therefore, in the roller member 52, the clutch 160 disconnects the rotary shaft 20 and the worm shaft 32.

  When the rotational drive of the rotary shaft 20 is started and the drive-side rotator 51 connected to the rotary shaft 20 is started, the roller member 52 is rotated together with the drive-side rotator 51 while the guide member 55 is rotated. The holding case 54 holding the guide member 55 is maintained in the rotational position by the inertial force acting on the guide member 55. Accordingly, since the driving side rotating body 51 that rotates integrally with the roller member 52 rotates relative to the guide member 55 and the holding case 54, the cam engaging portion 52 c extends in the circumferential direction of the holding case 54 with respect to the cam groove 55 d. It is rotated. As a result, the cam mechanism is activated, and the cam engagement portion 52c is moved from the first guide portion P1 to the second guide portion P2 while being guided by the cam surface S of the cam groove 55d. At this time, since the cam engaging portion 52c is not engaged with the blocking recess 55e, it is easily rotated relative to the cam groove 55d. The roller member 52 is moved from the non-engagement position to the engagement position by the action of the cam groove 55d. The power transmission portion 52b of the roller member 52 disposed at the engagement position is similar to the clutch 50 according to the first embodiment in accordance with the rotation of the drive-side rotator 51. It contacts the transmission surface 56f on the front side in the rotational direction (see FIG. 12A). As a result, the rotational driving force of the rotating shaft 20 can be transmitted to the driven side rotating body 56 via the roller member 52.

  The guide member 55 to which the urging force of the return spring 53 is transmitted from the roller member 52 that rotates together with the drive-side rotator 51 that has started to rotate after the cam engagement portion 52c is disposed in the second guide portion P2 is also provided. It starts to rotate with the drive side rotating body 51. When the rotation speed of the guide member 55 increases, the inertial force acting on the guide member 55 decreases as the rotation speed increases. As the inertial force acting on the guide member 55 becomes smaller, the guide member 55 rotates together with the holding case 54 on the driving side by the action of the urging force of the return spring 53 transmitted through the cam engagement portion 52c. It rotates relative to the body 51 in the same direction as the driving side rotating body 51. Along with the relative rotation of the guide member 55 with respect to the drive-side rotator 51, the cam groove 55d of the guide member 55 held by the holding case 54 rotates in the circumferential direction of the holding case 54 with respect to the cam engaging portion 52c. Therefore, as shown in FIG. 34, the cam engagement portion 52c is relatively moved from the second guide portion P2 to the first guide portion P1. At the same time, as the rotational speed of the guide member 55 increases, the centrifugal force acting on the guide member 55 gradually increases. Therefore, the guide member 55 is moved radially outward while being guided by the guide surface 54h. The Accordingly, since the radial position of the cam engagement portion 52c is maintained without changing in the radial direction, the roller member 52 is held at the engagement position by the guide member 55 (that is, the holding mechanism is in a connected state). . Further, after the guide member 55 moves radially outward until the cam engagement portion 52c is disposed at the first guide portion P1, the guide member 55 is engaged with the blocking recess 55e (that is, the cam engagement portion 52c). Until the outer peripheral surface of the inner surface contacts with the inner peripheral surface of the blocking recess 55e), it is further moved radially outward by centrifugal force. During the rotational drive of the drive-side rotator 51, the guide member 55 rotates integrally with the roller member 52 with the cam engaging portion 52c fitted and engaged with the blocking recess 55e.

  When the motor main body 12 is stopped and the rotational drive of the drive side rotator 51 is stopped, the rotational drive force from the drive side rotator 51 via the roller member 52 as the rotational speed of the drive side rotator 51 decreases. The rotational speeds of the guide member 55 and the driven-side rotator 56 that have been transmitted are also reduced. Then, since the centrifugal force acting on the guide member 55 is reduced, the guide member 55 is moved radially inward by the urging force of the return spring 53 (that is, the holding mechanism returns to the initial state). On the other hand, the guide member 55 tends to continue to rotate in the same direction as the direction in which it has been rotated by the inertial force. However, since the cam engaging portion 52c is fitted and engaged with the blocking recess 55e, the guide member 55 is blocked from rotating at a rotational speed different from that of the roller member 52, and the roller member 52 and the cam groove 55d Relative rotation is prevented. That is, the guide member 55 is decelerated integrally with the roller member 52. 33, both the guide member 55 and the roller member 52 are moved radially inward by the urging force of the return spring 53. At this time, since the cam engagement portion 52c is located at the first guide portion P1 in the cam groove 55d, the roller member 52 is moved from the engagement position to the non-engagement position. As a result, the rotation direction engagement between the driving side rotating body 51 and the driven side rotating body 56 is released, and the rotating shaft 20 and the worm shaft 32 are disconnected.

As described above, according to the sixth embodiment, in addition to the same effects as (1) to (15) of the first embodiment, the following effects are obtained.
(27) In a clutch that does not include the blocking recess 55e in the cam groove 55d, the guide member 55 is moved against the roller member 52 by the inertial force that acts on the guide member 55 when the rotational drive of the drive side rotating body 51 is stopped. Relative rotation may occur. Then, the roller member 52 moves wastefully between the engagement position and the non-engagement position. On the other hand, in the clutch 160 according to the present embodiment, even when the rotation of the driving-side rotator 51 is stopped, the guide member 55 tries to rotate relative to the roller member 52 by the inertial force acting on the guide member 55. The roller member 52 and the cam groove 55d are prevented from rotating relative to each other by the blocking recess 55e engaged with the cam engaging portion 52c. Therefore, since the cam engagement portion 52c of the roller member 52 is prevented from relatively moving in the cam groove 55d after the rotation of the driving side rotating body 51 is stopped, the driving side rotating body 51 and the driven side rotation are prevented. The engagement in the rotational direction with the body 56 can be quickly released. In addition, it is possible to prevent the cam engaging portion 52c of the roller member 52 from relatively moving in the cam groove 55d and colliding with the inner peripheral surface of the cam groove 55d after the rotation of the drive side rotating body 51 is stopped. Further, it is possible to prevent the occurrence of collision noise between the roller member 52 and the inner peripheral surface of the cam groove 55d, and it is possible to suppress the impact load from being applied to the roller member 52 and the guide member 55.

  (28) The blocking recess 55e formed by recessing the cam surface S has a simple shape. Therefore, the cam groove 55d can be easily provided with means for preventing the relative rotation between the roller member 52 and the cam groove 55d when the rotational drive of the drive-side rotator 51 is stopped.

  (29) When the roller member 52 is disposed at the non-engagement position, the cam engagement portion 52c of the roller member 52 does not engage with the blocking recess 55e. Therefore, the cam engagement portion 52c can easily move in the cam groove 55d from the first guide portion P1 to the second guide portion P2 when the drive side rotating body 51 starts to rotate. Further, when the guide member 55 moves radially outward due to the centrifugal force generated by the rotation of the drive side rotating body 51, the roller member 52 is held in the engaged position by the guide member 55. It moves relatively in the cam groove 55d from the second guide part P2 to the first guide part P1. Therefore, the cam engaging portion 52c of the roller member 52 can be engaged with the blocking recess 55e that is adjacent to the first guide portion P1 in the radial direction while the drive side rotating body 51 is rotating. When the rotational drive of the drive-side rotator 51 is stopped, the roller member 52 and the guide member 55 that are engaged so as not to rotate relative to each other are moved radially inward by the urging force of the return spring 53. Therefore, the return spring 53 only needs to have an urging force to move the roller member 52 and the guide member 55 radially inward when the rotational drive of the drive-side rotator 51 is stopped. That is, the return spring 53 is not configured to relatively rotate the drive side rotating body 51 and the guide member 55 so that the roller member 52 is moved to the non-engagement position side as in the first embodiment. Also good. Therefore, the cost concerning the return spring 53 can be reduced.

  (30) The blocking recess 55e is provided on the radially inner side of the first guide portion P1. Accordingly, the cam engagement portion 52c can be easily engaged with the blocking recess 55e by the biasing force of the return spring 53 after the rotational drive of the drive side rotator 51 is stopped.

(31) Since the roller member 52 moves in the radial direction, the cam engaging portion 52c can be easily engaged with the blocking recess 55e by forming the blocking recess 55e in the radial direction.
Each embodiment of the present invention may be modified as follows.

  In each of the above embodiments, the present invention has been described by taking the slide door opening / closing device 1 for automatically opening / closing the slide door 3 that opens / closes the entrance / exit 2a provided on the side of the vehicle body 2 as an example. However, the present invention may be applied to a device that opens and closes a door other than the slide door 3 as long as the door is automatically opened and closed using the motor 11 as a drive source. For example, the present invention may be applied to a back door opening and closing device that automatically opens and closes a back door that opens and closes an opening provided in the rear portion of the vehicle by the driving force of the motor 11. The motor 11 of each of the above embodiments is not limited to a door opening / closing device, and transmits the rotational driving force of the rotary shaft 20 to a load connected to the output shaft 35, while allowing the output shaft 35 to rotate from the load side. It may be used in a device that does.

  In each of the above embodiments, the clutch 50, 80, 100, 110, 150, 160 is provided in the motor 11. However, the clutches 50, 80, 100, 110, 150, and 160 may be used for those that operate so as to connect / disconnect the drive shaft and the driven shaft arranged on the same axis in addition to the motor 11.

  In each of the above-described embodiments, at the start of the rotational driving of the drive-side rotators 51 and 81, the guide member 55 rotates behind the drive-side rotators 51 and 81 by the inertial force acting on the guide member 55. The drive-side rotators 51 and 81 and the guide member 55 are rotated together. However, in addition to using the inertial force acting on the guide member 55, means for rotating the drive-side rotators 51 and 81 and the guide member 55 together at the start of the rotational drive of the drive-side rotators 51 and 81 is provided. The clutch 50, 80, 100, 110, 150, 160 may be provided. For example, the clutch 50, 80, 100, 110, 150, 160 is provided with means for generating a frictional force between the guide member 55 and the rotary shaft 20 at the start of the rotational drive of the drive-side rotators 51, 81. You may make it the guide member 55 rotate behind the drive side rotary bodies 51 and 81 by the effect | action of a frictional force.

  In the sixth embodiment, the blocking recess 55e is formed on the cam surface S on the radially inner side of the pair of cam surfaces S of the cam groove 55d, but may be formed on the cam surface S on the radially outer side. Good. In this case, for example, the cam engaging portion 52c is inserted into the blocking recess 55e by centrifugal force acting on the roller member 52. Further, the blocking recess 55e may be formed on the cam surface S at a position shifted in the rotational direction from the first guide portion P1. However, the blocking recess 55e is formed so that the cam engagement portion 52c is engaged when the rotation of the drive-side rotator 51 is stopped and relative rotation between the cam groove 55d and the cam engagement portion 52c is blocked. .

  In the sixth embodiment, the blocking recess 55e is provided in the cam groove 55d as a relative rotation blocking means for blocking the relative rotation between the roller member 52 and the cam groove 55d when the rotational drive of the driving side rotating body 51 is stopped. It was. However, the relative rotation blocking means is not limited to the blocking recess 55e formed on the cam surface S. For example, the relative rotation blocking means may be a convex portion protruding in the radial direction from the cam surface S on the radially outer side of the pair of cam surfaces S of the cam groove 55d. In this case, the radial width of the cam groove 55d is a width obtained by adding the protruding amount of the convex portion in the radial direction to the diameter of the cam engaging portion 52c. Furthermore, a concave portion is formed in the cam engaging portion 52c to engage the convex portion. When the driving-side rotator 51 is stopped, the roller member 52 is urged radially inward by the return spring 53, so the cam engagement portion 52c does not engage with the convex portion. Further, when the driving side rotating body 51 is rotated, the roller member 52 is moved radially outward by centrifugal force, whereby the cam engaging portion 52c is engaged with the convex portion. Even if it does in this way, the effect similar to (27) of the said 6th Embodiment can be acquired. Moreover, you may provide a relative rotation prevention means in the clutch 150 of 5th Embodiment.

-The clutch 160 of the sixth embodiment may be provided with a biasing means for biasing the guide member 55 radially inward.
The shape of the cam groove 55d is not limited to the shape of each of the above embodiments. The cam groove only needs to have a shape that can guide the roller member 52 from the non-engagement position to the engagement position as the driving body rotators 51 and 81 and the guide member 55 rotate together. For example, the cam groove may be formed such that the shape viewed from the axial direction is an arc shape protruding radially inward. The cam groove may be formed so as to extend linearly from the first guide part P1 toward the second guide part P2.

  -The part (cam part) which guides the movement of the roller member 52 between a non-engagement position and an engagement position in the guide member 55 is not restricted to the groove-shaped cam groove 55d. For example, the roller protrusion 52 between the non-engagement position and the engagement position is formed by the cam protrusion formed so as to protrude from the guide member 55 in the axial direction and engaged with the cam engagement portion 52c of the roller member 52. You may make it guide movement. Even if it does in this way, the effect similar to (3) of the said 1st Embodiment can be acquired.

  -In the said 5th Embodiment, the 2nd engagement recessed part 151c is each formed in the both ends of the rotation direction of the bottom face of the 1st engagement recessed part 151b. However, as long as the 2nd engagement recessed part 151c is formed in the bottom face of the 1st engagement recessed part 151b, you may form in places other than the both ends of the rotation direction of the bottom face of the 1st engagement recessed part 151b. For example, the second engagement recess 151c may be formed in the central portion in the rotation direction on the bottom surface of the first engagement recess 151b. In this way, after the power transmission portion 52b is inserted into the first engagement recess 151b, the power transmission portion 52b is driven by the driven side rotor until the power transmission portion 52b is inserted into the second engagement recess 151c. The amount of rotation with respect to 151 can be reduced.

  In the fifth embodiment, the power transmission unit 52b is inserted into the second engagement recess 151c by the guide member 55 that is moved radially outward by centrifugal force. However, the power transmission unit 52b is guided by the cam groove 55d along with the relative rotation of the guide member 55 and the driving side rotating body 51 at the start of the rotational driving of the driving side rotating body 51, and enters the second engaging recess 151c. It may be inserted. Even if it does in this way, since it is not necessary to provide the means for generating the force for inserting the power transmission part 52b in the 2nd engagement recessed part 151c, it can suppress that the structure of the clutch 150 is complicated.

  In the third embodiment and the fourth embodiment, the second pressing surface 62n is longer in the radial direction than the first pressing surface 62m. However, the length of the second pressing surface 62n in the radial direction may be equal to or shorter than the length of the first pressing surface 62m in the radial direction.

  In each of the above embodiments, the connection spring 63 is a compression coil spring. However, the connecting spring 63 biases the driving side rotating body 51 (first driving plates 61 and 152) so as to release the holding of the roller member 52 by the driving side rotating body 51 and the driven side rotating body 56. If it exists, it may be a spring (torsion coil spring or the like) other than the compression coil spring.

  In the third embodiment, the insertion path 103 is formed on the second drive plate 102 on the radially outer side of the spring accommodating recess 62d. However, the insertion path 103 may be formed on the radially inner side of the spring accommodating recess 62d as long as the connecting spring 63 can be inserted into the spring accommodating recess 62d through the insertion path 103. The same applies to the insertion path 113 of the fourth embodiment.

  In each of the above embodiments, the spring accommodating recess 62d is a recess that is recessed in the axial direction and opens toward the first drive plates 61 and 152. Furthermore, the spring accommodating recess 62d has an arc shape extending in the circumferential direction. However, the shape of the spring accommodating recess 62d is not limited to this, and may be a groove shape that can be accommodated in a state where the connecting spring 63 is compressed. The “groove shape” includes not only a recess shape but also a hole shape. For example, the spring accommodating recess 62d may be a linear recess extending so as to be orthogonal to the radial direction of the second drive plates 62, 102, 112. Further, the auxiliary biasing member accommodating portion for accommodating the coupling spring 63 is not limited to the concave shape such as the spring accommodating concave portion 62d, but is a hole shape penetrating the second drive plates 62, 102, 112 in the axial direction. May be. In this case, the opening on the first drive plates 61 and 152 side of the openings in the axial direction at both ends of the auxiliary biasing member accommodating portion is closed from the axial direction by the first drive plates 61 and 152, while the first drive plate The opening opposite to 61 and 152 is closed from the axial direction by the holding case 54 and the guide member 55.

  In each of the above embodiments, as the return accommodating portion into which the pair of return convex portions 61h are inserted, concave return recesses 62e that are recessed in the axial direction are formed on both sides in the circumferential direction of the spring accommodating recess 62d. However, the return accommodating portion may be formed in a hole shape that penetrates the second drive plates 62, 102, and 112 in the axial direction as long as the pair of return convex portions 61h can be inserted.

  In the fourth embodiment, the pair of guide surfaces 113c and 113d are inclined with respect to the extending / contracting direction of the connecting spring 63 disposed in the spring accommodating recess 62d and are parallel to each other. However, instead of the insertion path 113, an insertion path 121 shown in FIG. 35 may be formed in the second drive plate 112. The insertion path 121 is formed in the second drive plate 112 on the radially outer side of each spring accommodating recess 62d. Each insertion path 121 opens to the first drive plate 61 side, and the outer peripheral surface of the second drive plate 112 (that is, the outer peripheral surface of the storage portion 62b and the outer periphery of the guide portion 62a) from the center in the circumferential direction of each spring storage recess 62d. A concave shape extending to the surface). The outer opening 121a on the side opposite to the spring accommodating recess 62d in the insertion path 121 is formed longer in the circumferential direction than the inner opening 121b on the spring accommodating recess 62d side in the insertion path 121.

  Further, on the inner peripheral surface of the insertion path 121, there is a connection spring 63 arranged in the spring accommodating recess 62d so that the distance from each other becomes narrower from the outer opening 121a toward the inner opening 121b. A pair of guide surfaces 121c, 121d inclined with respect to the expansion / contraction direction is formed. In the example shown in FIG. 35, the pair of guide surfaces 121c and 121d constitute side surfaces on both sides in the circumferential direction of the insertion path 121, and each guide surface 121c and 121d extends from the outer opening 121a to the inner opening 121b. It is flat. Further, the pair of guide surfaces 121c and 121d are formed so as to face each other in the circumferential direction and to be close to each other in the circumferential direction from the outer opening 121a toward the inner opening 121b. Accordingly, the end on the outer opening 121a side of the one guide surface 121c is located at a position shifted in the circumferential direction with respect to the end on the inner opening 121b side of the guide surface 121c, and on the other guide surface 121d. The end on the outer opening 121a side is located at a position shifted in the circumferential direction with respect to the end on the inner opening 121b side in the guide surface 121d. Further, the pair of guide surfaces 121c and 121d are formed so as to incline without being orthogonal to the expansion / contraction direction of the coupling spring 63 disposed in the spring accommodating recess 62d, thereby inclining with respect to the radial direction, respectively. doing. Further, the pair of guide surfaces 121c and 121d are parallel to the axial direction. Further, each insertion path 121 has an end in the expansion / contraction direction of the connection spring 63 at the insertion path 121 even when the connection spring 63 is compressed between the first drive plate 61 and the second drive plate 112 when the clutch 110 is operated. It is formed so as not to reach.

  When the connection spring 63 is inserted into the spring accommodating recess 62d through such an insertion path 121, when the connection spring 63 is inserted into the insertion path 121 along one guide surface 121c from one end portion in the expansion and contraction direction, The insertion direction (see the dashed line arrow in FIG. 35) is inclined with respect to the expansion / contraction direction of the connecting spring 63 in the spring accommodating recess 62d. 35, even when the connecting spring 63 is inserted into the insertion path 121 along the other guide surface 121d from one end portion in the expansion / contraction direction, like the connecting spring 63 illustrated by a two-dot chain line in FIG. Is inserted with respect to the direction of expansion and contraction of the connecting spring 63 in the spring accommodating recess 62d. Therefore, in any case, the insertion direction of the connection spring 63 is inclined with respect to the expansion / contraction direction of the connection spring 63 in the spring accommodating recess 62d. Therefore, by inserting the connecting spring 63 from the insertion path 121 into the spring accommodating recess 62d along the guide surface 121c or the guiding surface 121d, the connecting spring 63 is assembled to the spring accommodating recess 62d without compressing the connecting spring 63 in advance. Can do.

  In this way, in addition to the same effect as (23) of the fourth embodiment, the following effect can be obtained. The pair of guide surfaces 121c and 121d are inclined in directions different from each other with respect to the extending and contracting direction of the connecting spring 63 in the spring accommodating recess 62d. Therefore, the connection spring 63 can be inserted into the spring accommodating recess 62d through the insertion path 121 along one of the two directions along the guide surfaces 121c and 121d. Therefore, the assembly direction of the connection spring 63 is not limited to one direction, and the assembly performance of the connection spring 63 is further improved. It should be noted that the pair of guide surfaces 121c and 121d are expanded and contracted by the connecting spring 63 disposed in the spring accommodating recess 62d so that the distance between the guide surfaces 121c and 121d decreases from the inner opening 121b toward the outer opening 121a. It may be inclined with respect to the direction. Even if it does in this way, the same effect can be acquired.

  Further, instead of the insertion path 113, an insertion path 122 shown in FIG. 36 may be formed in the second drive plate 112. The insertion path 122 is formed on the second drive plate 112 on the radially outer side of each spring accommodating recess 62d. Each insertion path 122 opens to the first drive plate 61 side, and the outer peripheral surface of the second drive plate 112 (that is, the outer peripheral surface of the storage portion 62b and the guide portion 62a) from the center in the circumferential direction of each spring storage recess 62d. A concave shape extending to the outer peripheral surface).

  A pair of guide surfaces 122c and 122d facing each other in the circumferential direction are formed on the inner peripheral surface of each insertion path 122. The pair of guide surfaces 122c and 122d are spaced from each other as they go from the outer opening 122a opposite to the spring accommodating recess 62d in the insertion path 122 toward the inner opening 122b on the spring accommodating recess 62d side in the insertion path 122. Is inclined with respect to the extending / contracting direction of the connecting spring 63 disposed in the spring accommodating recess 62d. Further, a pair of inclined surfaces 122e and 122f that are opposed to the inner peripheral surface of the insertion path 122 in the circumferential direction on the inner opening 122b side than the pair of guide surfaces 122c and 122d and are aligned with the pair of guide surfaces 122c and 122d. Is formed. The pair of inclined surfaces 122e and 122f are arranged in the expansion / contraction direction of the connecting spring 63 disposed in the spring accommodating recess 62d so that the interval between the inner opening 122b and the outer opening 122a decreases. It is inclined with respect to it. In addition, the pair of guide surfaces 122c and 122d and the pair of inclined surfaces 122e and 122f each have a planar shape that is inclined with respect to the radial direction and parallel to the axial direction. Furthermore, one inclined surface 122e is formed substantially parallel to one guide surface 122d on the opposite side, and the other inclined surface 122f is formed substantially parallel to the other guide surface 122c on the opposite side. In the example shown in FIG. 36, one inclined surface 122e is formed in parallel with one guide surface 122d on the opposite side, and the other inclined surface 122f is formed in parallel with the other guide surface 122c on the opposite side. . Furthermore, the distance between one inclined surface 122e and one guide surface 122d on the opposite side is substantially equal to the outer diameter of the connecting spring 63, and the other guide on the other side on the other inclined surface 122f. The distance from the surface 122c is also approximately equal to the outer diameter of the coupling spring 63.

  In this way, in addition to the same effect as (23) of the fourth embodiment and the same effect as the example shown in FIG. 35, the following effect can be obtained. The pair of inclined surfaces 122e and 122f are formed at the end portion on the inner opening 122b side in the insertion path 122 so as to be aligned with the pair of guide surfaces 122c and 122d. Further, the pair of inclined surfaces 122e and 122f are extended and contracted by the connecting spring 63 disposed in the spring accommodating recess 62d so that the interval between the inner opening 122b and the outer opening 122a decreases. Inclined with respect to direction. Accordingly, when the connection spring 63 is inserted into the spring accommodating recess 62d through the insertion path 122 along one of the pair of guide surfaces 122c and 122d, the connection spring 63 is not easily caught by the inner opening 122b. Become. Therefore, the connecting spring 63 can be more smoothly inserted into the spring accommodating recess 62d. Furthermore, one inclined surface 122e is formed in parallel with one guide surface 122d on the opposite side, and the other inclined surface 122f is formed in parallel with the other guide surface 122c on the opposite side. Therefore, when the connection spring 63 is inserted into the spring accommodating recess 62d through the insertion path 122 along one of the pair of guide surfaces 122c and 122d, the connection spring 63 is hardly caught by the inner opening 122b. Become. Therefore, the connecting spring 63 can be more smoothly inserted into the spring accommodating recess 62d. In the example shown in FIG. 36, the distance between one inclined surface 122e and one guide surface 122d on the opposite side, and the distance between the other inclined surface 122f and the other guide surface 122c on the opposite side are as follows. The value is substantially equal to the outer diameter of the connecting spring 63. Therefore, when the connection spring 63 is inserted into the spring accommodating recess 62d from the insertion path 122, the connection spring 63 is guided not only by the guide surface 122c or the guide surface 122d but also by the inclined surface 122f or the inclined surface 122e in the insertion direction. Therefore, the assembling property of the connecting spring 63 is further improved.

  In the third embodiment and the fourth embodiment, the insertion paths 103 and 113 for inserting the coupling spring 63 into the spring accommodating recess 62d are formed at positions adjacent to the spring accommodating recess 62d in the radial direction. ing. However, like the clutch 130 shown in FIG. 37, the insertion path 133 adjacent to the spring accommodating recess 62d in the axial direction may be formed. The clutch 130 includes a first drive plate 131 instead of the first drive plate 61 as compared with the clutch 50 of the first embodiment. The first drive plate 131 has a shape in which an insertion path 133 is added to the first drive plate 61 of the first embodiment. The insertion paths 133 are formed at two locations that are 180 ° apart in the circumferential direction, and are formed between the pair of return convex portions 61h (see FIG. 4). Each insertion path 133 is formed in the first drive plate 131 at a position adjacent to the spring accommodating recess 62d in the axial direction. These insertion paths 133 have a hole shape penetrating the first drive plate 131 in the axial direction, and the internal space of each insertion path 133 is in communication with the spring accommodating recess 62d. Each insertion path 133 extends in an arc shape along the rotation direction of the first drive plate 131 (same as the circumferential direction of the clutch 130), and the radial width thereof is the radial width of the spring accommodating recess 62d. Are formed approximately equal. Furthermore, the circumferential length of each insertion path 133 is formed shorter than the circumferential length of the spring accommodating recess 62d. Therefore, both ends in the circumferential direction of the spring accommodating recess 62d are closed from the axial direction by the portions on both sides in the circumferential direction of the insertion path 133 in the first drive plate 131.

  In order to assemble the clutch 130, first, components of the clutch 130 other than the two coupling springs 63 and the driven side rotating body 56, that is, the first drive plate 131, the second drive plate 62, the two roller members 52, The two return springs 53, the holding case 54, and the two guide members 55 are assembled. The thrust receiving ball 71 and the thrust receiving plate 72 may be assembled at this time, or may be assembled before the driven side rotating body 56 is assembled. When the first drive plate 131, the second drive plate 62, the two roller members 52, the two return springs 53, the holding case 54 and the two guide members 55 are assembled, the housing 62 b side with respect to the second drive plate 62. Thus, the first drive plate 131 is disposed so as to overlap in the axial direction. Thereby, each spring accommodating recess 62d and each insertion path 133 are adjacent to each other in the axial direction, and both end portions in the circumferential direction of the opening of each spring accommodating recess 62d are closed from the axial direction by the first drive plate 131. Next, the connection spring 63 compressed and contracted to be shorter than the circumferential length of the insertion path 133 is inserted into the insertion path 133 from the axial direction. The connection spring 63 is pushed in the axial direction toward the spring accommodating recess 62d until it passes through the insertion path 133. The connecting spring 63 passing through the insertion path 133 enters the spring accommodating recess 62d and extends in the circumferential direction in the spring accommodating recess 62d, and both ends of the connecting spring 63 are the second pressing surface 62n and the first pressing surface 62m, respectively. Abut. Thus, the connecting spring 63 is assembled. Thereafter, the driven-side rotator 56 is assembled and the clutch 130 is completed. Even if it does in this way, the effect similar to (19) of the said 3rd Embodiment can be acquired.

  The connection spring 63 may be inserted into the insertion path 133 from one end portion in the expansion / contraction direction (longitudinal direction) of the connection spring 63 instead of being contracted in advance into the insertion path 133. In this case, the connection spring 63 is inserted into the insertion path 133 in a state where the connection spring 63 is inclined with respect to the expansion / contraction direction of the connection spring 63 in the spring accommodating recess 62d. Then, the connecting spring 63 is pushed in through the insertion path 133 until it is accommodated in the spring accommodating recess 62d.

  37, when the coupling spring 63 is inserted into the insertion path 133 on the inner circumferential surface of the insertion path 133, the insertion direction of the coupling spring 63 is the expansion and contraction of the coupling spring 63 in the spring accommodating recess 62d. You may form the guide surface which guides insertion of the connection spring 63 so that it may incline with respect to a direction. This guide surface has a planar shape inclined with respect to the extending and contracting direction of the connecting spring 63 in the spring accommodating recess 62d.

  In the third embodiment, when the clutch 100 is assembled, after the components of the clutch 100 other than the two coupling springs 63 and the driven side rotating body 56 are assembled, the coupling spring 63 is inserted into the spring accommodating recess 62d through the insertion path 103. Assemble. However, the assembly order of the connection spring 63 is not limited to this. As long as the opening of the spring accommodating recess 62 d is closed by the first drive plate 61, the connecting spring 63 may be assembled to the spring accommodating recess 62 d through the insertion path 103 at any time. Even if it does in this way, the effect similar to (19) of the said 3rd Embodiment can be acquired. This also applies to the clutch 110 of the fourth embodiment.

  The insertion paths 103 and 113 of the third embodiment and the fourth embodiment are both recessed in the axial direction. However, the insertion paths 103 and 113 communicate with the spring accommodating recess 62d and are connected through the insertion paths 103 and 113 in a state where at least a part of the opening of the spring accommodating recess 62d is closed by the components of the clutches 100 and 110. Any shape may be used as long as the spring 63 can be assembled to the spring accommodating recess 62d. For example, the insertion path may be formed in a slit shape extending from the radially inner side surface of the spring accommodating recess 62d to the outer circumferential surface of the second drive plate 102 and penetrating the second drive plate 102 in the axial direction.

  In the first embodiment, the first drive plate 61 is formed with the return projection 61h, while the second drive plate 62 is formed with the spring accommodating recess 62d and the return recess 62e. However, the spring accommodating recess 62d and the return recess 62e may be formed on the first drive plate, while the return protrusion 61h may be formed on the second drive plate 62. The same applies to the clutch 100 of the third embodiment, the clutch 110 of the fourth embodiment, the clutch 150 of the fifth embodiment, and the clutch 160 of the sixth embodiment.

  In each of the above embodiments, the return springs 53 and 82 are arranged so as to bias the roller member 52 radially inward. However, the return springs 53 and 82 may be arranged to urge the roller member 52 in a direction other than the radial direction (for example, the circumferential direction). In this case, a configuration for changing the direction of the urging force or generating a component force so that the cam mechanism, the holding mechanism, and the clamping mechanism are returned to the initial state by the urging force of the return springs 53 and 82. May be provided.

  In the first embodiment, the return spring 53 biases the two mechanisms of the cam mechanism and the holding mechanism to return to the initial state. However, the return spring 53 may return the two mechanisms of the cam mechanism and the clamping mechanism, or the two mechanisms of the holding mechanism and the clamping mechanism to the initial state. Further, the clutch 50 according to the first embodiment does not necessarily include a clamping mechanism. The same applies to the third to sixth embodiments.

  The cam mechanism, the holding mechanism, and the clamping mechanism of the above embodiments disconnect the worm shaft 32 from the rotating shaft 20 when the rotating shaft 20 is not driven, while the rotating shaft 20 and the worm shaft 32 are driven from the rotating shaft 20 side. Is a mechanism for operating the clutches 50, 80, 100, 110, 150, 160 so as to connect the two. The clutches 50, 80, 100, 110, 150, and 160 of the above embodiments are in an initial state in which the rotary shaft 20 and the worm shaft 32 are disconnected when the rotary shaft 20 is not driven, in addition to the cam mechanism, the holding mechanism, and the clamping mechanism. On the other hand, a mechanism for connecting the rotary shaft 20 and the worm shaft 32 during driving from the rotary shaft 20 side may be provided. In this case, at least two of the plurality of mechanisms are configured to return to the initial state by the same biasing member.

  In each of the above embodiments, the return spring 53, the coupling spring 63, and the return spring 82 are compression coil springs, but tension coil springs may be used. Further, for the return spring 53, the connecting spring 63, and the return spring 82, a biasing member that generates a biasing force other than the coil spring may be used.

  In the clutch 50 of the first embodiment, the number of guide members 55 having the roller member 52, the control groove 61d, the guide recess 62f, the insertion engagement portion 62g, the connection spring 63, and the cam groove 55d may be changed as appropriate. . It is sufficient that at least one of these parts is provided in the clutch 50. The same applies to the clutch 100 of the third embodiment, the clutch 110 of the fourth embodiment, the clutch 150 of the fifth embodiment, and the clutch 160 of the sixth embodiment. In the clutch 80 of the second embodiment, the number of guide members 55 having the roller member 52, the control groove 91a, the guide recess 62f, the insertion engagement portion 62g, and the cam groove 55d may be appropriately changed. It is sufficient that at least one of these parts is provided in the clutch 80.

  In each of the above embodiments, the first drive plates 61, 91, and 152 are formed separately from the rotary shaft 20, but may be formed integrally. In each of the above embodiments, the driven-side rotators 56 and 151 are formed separately from the worm shaft 32, but may be integrally formed.

The technical ideas that can be grasped from each of the above embodiments and each of the above modifications will be described below.
(B) pre-Symbol cam mechanism includes the holding mechanism and the wedge mechanism, the biasing member, the said power transmission member in stopping of the driving side rotational member so as to place said disengaged position the cam mechanism , characterized in that biases the holding mechanism and the wedge mechanism. According to this configuration, the urging member includes the three mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism so that the power transmission member is disposed at the non-engagement position when the driving side rotating body is stopped, that is, in the initial state. It is energized to do. Therefore, the number of urging members for returning the three mechanisms of the cam mechanism, the holding mechanism, and the clamping mechanism to the initial state can be minimized.

  (B) In the clutch according to (A), the driving-side rotating body includes a wedge surface that is inclined with respect to a radial direction and is capable of contacting the power transmission member from the rotating direction, and the driven-side rotating body is The clutch includes a transmission surface for sandwiching the power transmission member together with the wedge surface, and the biasing member biases the wedge surface in the radial direction. According to this configuration, the wedge surface that holds the power transmission member together with the transmission surface is inclined with respect to the radial direction. Therefore, the urging member can urge the drive-side rotator in the rotational direction so that the wedge surface and the transmission surface are separated by urging the wedge surface in the radial direction. Therefore, in order to return the clamping mechanism to the initial state, it is not necessary to newly add a configuration for applying the urging force of the urging member to the clamping mechanism. As a result, the clutch configuration is further suppressed from being complicated.

(C) before Symbol power transmission member by the guide member to move radially outward by centrifugal force generated by rotating with the rotation of the driving side rotational member, which is inserted into the second engaging recess it shall be the features a. According to this configuration, since it is not necessary to separately provide a means for generating a force for inserting the power transmission member into the second engagement recess, it is possible to suppress a complicated configuration of the clutch.

(D) pre-Symbol power transmitting member, you being inserted is guided to the second engagement recess to the cam portion with the relative rotation between the guide member and the driving side rotational member. According to this configuration, since it is not necessary to separately provide a means for generating a force for inserting the power transmission member into the second engagement recess, it is possible to suppress a complicated configuration of the clutch.

  DESCRIPTION OF SYMBOLS 1 ... Slide door opening / closing apparatus as a vehicle door opening / closing apparatus, 2 ... Vehicle body as vehicle, 2a ... Entrance / exit as opening, 3 ... Slide door as door, 11 ... Motor, 12 ... Motor body, 20 ... Drive Rotating shaft as shaft, 32 ... Worm shaft as driven shaft, 34 ... Deceleration mechanism, 50, 80, 100, 110, 130, 150, 160 ... Clutch, 51, 81 ... Driving side rotating body constituting clamping mechanism, 52 ... Roller member as a power transmission member constituting the cam mechanism, 53, 82 ... Return spring as an urging member, 54 ... Holding case, 55 ... Guide member constituting the holding mechanism, 55d ... Cam constituting the cam mechanism Cam groove as a part, 55e ... a blocking recess as a relative rotation blocking means, 56, 151 ... a driven side rotating body constituting a clamping mechanism, 56c ... a side wall part, 56f ... a transmission surface 61, 131, 152: first driving plate as a first rotating body, 61g, 152b: wedge surface, 61h: return convex portion, 62, 102, 112 ... second driving plate as second rotating body, 62d: auxiliary Spring accommodating recess as an urging member accommodating portion, 62e ... Returning recess as a returning accommodating portion, 62m ... First pressing surface, 62n ... Second pressing surface, 63 ... Connecting springs as auxiliary urging members, 103, 113, 121, 122, 133 ... insertion path, 113a, 121a, 122a ... outer opening, 113b, 121b, 122b ... inner opening, 113c, 113d, 121c, 121d, 122c, 122d ... guide surface, 122e, 122f ... inclined surface , 151b ... first engaging recess, 151c ... second engaging recess, F1, F2 ... biasing force, P1 ... first guide, P2 ... second guide, S ... cam .

Claims (25)

Provided with a plurality of mechanisms that are in an initial state in which the drive shaft and the driven shaft are disconnected when the drive shaft is not driven, and that are connected to connect the drive shaft and the driven shaft when driven from the drive shaft side. A clutch operating to disconnect the driven shaft from the drive shaft when the drive shaft is not driven, and to connect the drive shaft and the driven shaft when driven from the drive shaft side. In a clutch provided with a biasing member that exerts a biasing force so as to return at least two of the mechanisms to the initial state ,
A drive-side rotator provided so as to be integrally rotatable with the drive shaft;
A driven-side rotator provided to be rotatable integrally with the driven shaft;
It is arranged between the driving side rotating body and the driven side rotating body in the radial direction and is provided so as to be able to rotate integrally with the driving side rotating body. The driving side rotating body and the driven side rotating body are rotated in the rotation direction. Is moved between a non-engagement position that does not engage with and an engagement position that engages the drive-side rotator and the driven-side rotator in the rotational direction on the radially outer side of the non-engagement position. A power transmission member;
Accompanying the relative rotation of the driving member and the guide member having a cam portion that engages the power transmission member and guides the movement of the power transmission member between the engagement position and the non-engagement position. A cam mechanism that guides the power transmission member from the non-engagement position to the engagement position by the cam portion, and the guide that is moved radially outward by a centrifugal force generated by rotating with the driving side rotating body. Three mechanisms: a holding mechanism that holds the power transmission member at the engagement position by a member, and a clamping mechanism that clamps the power transmission member arranged at the engagement position between the driving side rotating body and the driven side rotating body. And at least two mechanisms of
The biasing member biases at least two of the at least two mechanisms so as to dispose the power transmission member at the non-engagement position when the driving side rotating body is stopped. clutch. The clutch according to claim 1 , wherein
At least the cam mechanism and the holding mechanism;
The biasing member biases the guide member so as to rotate the driving-side rotating body and the guide member together so that the power transmission member is moved to the non-engagement position side, and A clutch characterized by urging the guide member radially inward. The clutch according to claim 2 ,
The cam portion is provided with a first guide portion for disposing the power transmission member at the non-engagement position, and radially outside the first guide portion, and guides the power transmission member to the engagement position. A second guide part for carrying out, and a cam surface extending from the first guide part to the second guide part to which the power transmission member is slidably contacted,
The urging member urges the cam surface in a radial direction. The clutch according to claim 3 ,
The urging member urges the power transmission member radially inward. In the clutch according to any one of claims 2 to 4 ,
The clamping mechanism;
A clutch, comprising: an auxiliary biasing member that biases the driving-side rotating body so that the drive-side rotating body is released from being pinched by the driving-side rotating body and the driven-side rotating body. The clutch according to claim 5 ,
The drive-side rotator is provided so as to be able to rotate integrally with the drive shaft, and includes a first rotator having a wedge surface capable of coming into contact with the power transmission member from a rotation direction, and provided to be rotatable relative to the first rotator. A second rotating body that holds the power transmission member movably in the radial direction and rotates integrally with the power transmission member,
The driven-side rotating body includes a transmission surface for sandwiching the power transmission member together with the wedge surface,
The auxiliary biasing member is interposed between the first rotating body and the second rotating body, and the power generated by the wedge surface and the transmission surface when the rotational driving of the first rotating body is stopped. A clutch that biases the first rotating body so as to rotate the first rotating body in a direction opposite to the immediately preceding rotation direction with respect to the second rotating body so as to release the clamping of the transmission member. . The clutch according to claim 6 , wherein
In either one of the first rotating body and the second rotating body, the auxiliary biasing member having elasticity is accommodated while being compressed and opened by either the first rotating body or the second rotating body. An auxiliary urging member accommodating portion in which at least a part of the portion is closed is formed,
The auxiliary urging member is connected to the first rotator or the second rotator from the outside of the first rotator and the second rotator which are connected to the auxiliary urging member housing portion and assembled to each other. A clutch characterized in that an insertion path for insertion into an urging member accommodating portion is formed. The clutch according to claim 7 ,
Even if the auxiliary biasing member is compressed between the first rotating body and the second rotating body when the clutch is operated, the end of the auxiliary biasing member in the expansion / contraction direction reaches the insertion path. A clutch characterized by being formed so as not to have. In the clutch according to claim 7 or 8 ,
A clutch characterized in that a guide surface that is inclined with respect to a direction in which the auxiliary urging member is disposed in the auxiliary urging member accommodating portion is formed on an inner peripheral surface of the insertion path. The clutch according to claim 9 ,
The inner circumferential surface of the insertion path is directed from the outer opening on the opposite side of the auxiliary biasing member accommodating portion in the insertion path toward the inner opening on the auxiliary biasing member accommodating portion side in the insertion path. With respect to the expansion / contraction direction of the auxiliary urging member disposed in the auxiliary urging member accommodating portion so that the interval between the inner urging member and the inner opening is reduced toward the outer opening. A clutch having a pair of inclined guide surfaces. Clutch according to claim 1 0,
The auxiliary urging member disposed in the auxiliary urging member accommodating portion on the inner peripheral surface of the insertion path so that the interval between the outer opening and the inner opening becomes narrower toward the inner opening. A pair of the guide surfaces inclined with respect to the expansion / contraction direction of the guide and a pair of the guide surfaces on the inner opening side of the pair of guide surfaces, and from the inner opening toward the outer opening. And a pair of inclined surfaces that are inclined with respect to the expansion / contraction direction of the auxiliary biasing member disposed in the auxiliary biasing member accommodating portion so as to reduce the distance between them. Clutch according to claim 1 1,
One of the inclined surfaces is formed substantially parallel to the one guide surface on the opposite side, and the other inclined surface is formed substantially parallel to the other guide surface on the opposite side. clutch. Clutch according to any one of claims 7 to 1 2,
The auxiliary biasing member accommodating portion has an arcuate groove shape extending along the rotation direction of the first rotating body and the second rotating body,
The clutch, wherein the insertion path is formed on a radially outer side of the auxiliary biasing member accommodating portion. Clutch according to claim 1 3,
The auxiliary biasing member comprises a compression coil spring,
The second rotator is connected to the auxiliary urging member accommodating portion on both sides in the circumferential direction of the auxiliary urging member accommodating portion and has a diameter larger than that of the auxiliary urging member accommodating portion. A return accommodating portion with a narrow width in the direction is formed,
The first rotating body has a pair of return convex portions that are respectively inserted into the return accommodating portion and the auxiliary biasing member is interposed therebetween,
At both ends in the circumferential direction of the auxiliary biasing member accommodating portion, a first pressing surface that extends radially outside the return accommodating portion along the radial direction and is pressed by the auxiliary biasing member, and the return accommodating portion The clutch further includes a second pressing surface that extends radially inward and is pressed by the auxiliary biasing member and is longer in the radial direction than the first pressing surface. Clutch according to any one of claims 2 to 1 4,
The driven-side rotator has a cylindrical side wall disposed on the outer periphery of the drive-side rotator and opposed to the drive-side rotator in the radial direction;
The power transmission member that is wider in the rotational direction than the power transmission member and is moved radially outward by the cam mechanism is inserted into the inner peripheral surface of the side wall portion and can be engaged in the rotational direction. The engaging recess and the power transmission member formed and inserted on the bottom surface of the first engagement recess are disposed radially outside the first engagement recess and are not relatively movable in the rotational direction with respect to the power transmission member. And a second engaging recess for engaging with the clutch. Clutch according to claim 1 5,
The clutch, wherein the second engaging recess is formed at both ends in the rotational direction on the bottom surface of the first engaging recess. In the clutch according to claim 15 or claim 16 ,
The clutch, wherein the second engagement recess is formed at a central portion in the rotational direction on the bottom surface of the first engagement recess. The clutch according to any one of claims 2 to 17 ,
The clutch, wherein the cam portion is a cam groove into which the power transmission member is inserted. The clutch according to claim 18 ,
The clutch characterized in that the cam groove is provided with a relative rotation preventing means for preventing relative rotation between the power transmission member and the cam groove when the rotational drive of the driving side rotating body is stopped. The clutch according to claim 19 ,
The cam groove has a first guide portion for disposing the power transmission member at the non-engagement position, a position shifted in a rotational direction with respect to the first guide portion, and a radial direction from the first guide portion. A second guide portion provided on the outside for guiding the power transmission member to the engagement position; and a cam surface extending from the first guide portion to the second guide portion and in contact with the power transmission member;
The clutch is characterized in that the relative rotation blocking means is a blocking recess that is recessed in the cam surface and engages the power transmission member so as not to be relatively rotatable when at least the rotation of the driving side rotating body is stopped. . Clutch according to claim 2 0,
The biasing member biases the power transmission member radially inward,
When the guide member moves radially outward due to the centrifugal force generated by the rotation of the drive-side rotating body, the power transmission member is held in the engagement position by the guide member. Moving relatively in the cam groove from the second guide part to the first guide part,
The blocking recess is inserted into the first guide portion in the cam groove of the guide member that is disposed on the innermost radial direction within the radial movement range of the guide member, and is disposed at the non-engagement position. A portion of the cam surface that is adjacent to the first guide portion in the radial direction is formed in a radial recess so that the power transmission member does not engage with the blocking recess. To clutch. In the clutch according to any one of claims 2 to 21,
A holding case is provided so as to be able to rotate with the drive-side rotating body, hold the guide member so as to guide the radial movement of the guide member, and rotate integrally with the guide member. To clutch. Clutch according to any one of claims 1 to 2 2,
At the start of rotational driving of the driving side rotating body, the driving side rotating body and the guide member are relatively moved by the guide member rotating later than the driving side rotating body by an inertial force acting on the guide member. A clutch characterized by being rotated. A motor body having the drive shaft that is rotationally driven;
A reduction mechanism that is arranged coaxially with the drive shaft and has the driven shaft that is rotated by the rotational drive force of the drive shaft, and that decelerates and outputs the rotation of the drive shaft;
Motor, characterized in that a clutch according to any one of the deployed claims 1 to 2 3 between the driven shaft and the drive shaft. A vehicle door opening and closing device configured to open and close operation by the driving force of the motor according to the door to claims 2 to 4 for opening and closing an opening provided in a vehicle,
When a command to automatically open and close the door is generated, the drive shaft is connected to the driven shaft by the clutch and the door is automatically opened and closed while the motor main body is driven. Thus, the driven shaft is disconnected from the drive shaft to reduce the operating load when the door is manually opened and closed.