JP2010038360A - Clutch device, motor device, and wiper motor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a clutch device restricting application of a load to a driving means and also restricting a height of an output shaft. <P>SOLUTION: This clutch device 40 has: an output shaft 38; a pinion gear 92; a first clutch member 94 extended from the pinion gear 92 in one way in the radial direction of the output shaft 38; a spring holder 96 fixed to the output shaft 38 and extended in one way in the radial direction of the output shaft 38; a projecting member 108 and a coil spring 98 housed in the spring holder 96; and a recessed part 112 formed in the first clutch member 94. When a load exceeding driving force is applied to the output shaft 38, the projecting member 108 is removed from the recessed part 112 and the output shaft 38 is idly rotated. This structure prevents application of a load to a motor body 32. Since a driving force by the clutch device 40 is transmitted in the radial direction of the output shaft 38, the height of the output shaft is lowered. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a clutch device, a motor device, and a wiper motor.

  Among wiper motors that are applied to wiper devices that wipe the window glass of a vehicle, a wiper motor that has a built-in swing mechanism, a wiper arm to which a wiper blade is attached is fixed to an output shaft, and a wiping surface is wiped back and forth is known. . In this type of wiper motor, if the operation of the wiper arm is hindered and an excessive load is applied to the output shaft of the wiper motor, the built-in swing mechanism and speed reduction mechanism may be damaged. For this reason, there is one in which a clutch device is further provided around the output shaft of the wiper motor or around the output shaft (for example, see Patent Documents 1 and 2).

  The clutch device of Patent Document 1 is provided with a clutch disk that can move in the axial direction of the output shaft and cannot rotate about the axis. An input disk that is immovable in the axial direction of the output shaft and that can rotate about the axis and that receives driving force is provided at a position facing the clutch disk. A coil spring that urges the clutch disk toward the input disk is provided.

  The clutch device of Patent Document 2 is provided with an output gear that is rotatably supported around the axis of the output shaft and is provided with a circular opening groove in the circumferential direction. In the circular opening groove of the output gear, a first fitting groove and a second fitting groove are formed at two locations on the inner wall facing each other across the output shaft. And the 1st connection piece and the 2nd connection piece are each urged | biased by the repulsive force of the spring toward the 1st fitting groove and the 2nd fitting groove from the output shaft.

  However, in the clutch device of Patent Document 1, since the clutch disk is arranged in the axial direction of the output shaft, the size of the output shaft must be increased at least for the moving range of the clutch disk. It is difficult to reduce the thickness.

Further, in the clutch device of Patent Document 2, when the first connection piece and the second connection piece are disengaged from the first fitting groove and the second fitting groove, respectively, the first connection piece and the second connection piece are springs. Since the force is still urged toward the circular opening groove by the repulsive force, the release of the connection is not sufficient, and an excessive load acting on the output shaft acts on the drive source.
JP2007-302038 JP 62-166748 A

  It is an object of the present invention to obtain a clutch device, a motor device, and a wiper motor that can suppress the load from acting on the driving means and can reduce the height of the output shaft.

  A clutch device according to a first aspect of the present invention includes an output shaft that is rotatably supported, a driven portion that is rotatably supported by the output shaft and receives a driving force, and the output shaft from the driven portion. A first clutch member extending in one radial direction, a second clutch member fixed to the output shaft and extending in one radial direction of the output shaft, and the first clutch member A convex member provided on any one of the second clutch members so as to be movable in the radial direction of the output shaft, and a facing surface of any one of the convex members of the second clutch member and the first clutch member And an urging means for engaging the convex member, and an urging means for urging the convex member to engage the concave portion.

  According to the said structure, when a 1st clutch member and a 2nd clutch member are located in the same direction of the radial direction of an output shaft, a convex member and a recessed part oppose. Then, the convex member is urged by the urging means and engaged with the concave portion, so that the first clutch member and the second clutch member can rotate together. Subsequently, when the driving force is input to the driven portion by the external driving means, the driving force is transmitted from the first clutch member to the second clutch member, and the output shaft to which the second clutch member is fixed rotates. .

  Here, when the external force that suppresses the rotation is hardly applied to the output shaft, the first clutch member and the second clutch member rotate at the drive timing of the driven part, so that the load exceeding the drive force is applied to the drive means. Has little effect.

  On the other hand, when an external force that suppresses rotation is applied to the output shaft, the output shaft and the second clutch member stop in place. At this time, since the first clutch member continues to rotate, the convex member is released from the concave portion, and the engaged state is released. Since the first clutch member and the second clutch member face each other only in one radial direction of the output shaft, the first clutch member and the second clutch member are displaced in the circumferential direction when the engagement between the convex member and the concave portion is released. The driven portion and the first clutch member are idled without being interfered with the output shaft. Thereby, it can suppress that a load acts on an external drive means.

  In addition, since the driving force is transmitted in the radial direction of the output shaft, the height of the output shaft can be reduced compared to a clutch device that transmits the driving force in the axial direction of the output shaft, and the entire clutch device Can be reduced in height.

  In the clutch device according to claim 2 of the present invention, the second clutch member houses the convex member and the urging means, and a lower part is opened, and a hole in which the convex member enters and exits is formed. The opening of the box is closed by the first clutch member.

  According to the above configuration, even if the engagement state between the convex member and the concave portion is released, the first clutch member is the bottom of the second clutch member, so that the bottom of the second clutch member is not closed with another member. Even in this case, the convex member and the urging means are held in the second clutch member. Thereby, drop-off of the convex member can be prevented.

  Further, when the tip of the convex member protrudes outward from the hole portion of the box, the convex member is easily positioned because it is guided by the hole portion and directed toward the concave portion. Further, when the tip of the convex member moves in the rotational direction in accordance with the rotation of the second clutch member, the convex member is held in contact with the hole, so that the positional variation (backlash) of the convex member is reduced.

  Further, the engagement region between the convex member and the concave portion is located farther in the radial direction from the center of the output shaft than in the case where the convex member is provided on the first clutch member side. Thereby, the urging | biasing force of the urging means required to hold | maintain the engagement of a convex member and a recessed part can be restrained small. Furthermore, when the biasing means is a coil spring, the outer diameter and wire diameter of the coil spring can be reduced.

  In the clutch device according to claim 3 of the present invention, the hole is a long hole in the same direction as the axis of the output shaft. According to the said structure, a convex member can be positioned in one place in the circumferential direction.

  In the clutch device according to claim 4 of the present invention, the hole portion is connected to the opening. According to the above configuration, when the urging means and the convex member are assembled to the second clutch member, both are assembled from the same opening direction, so that the assembly is facilitated.

  In the clutch device according to claim 5 of the present invention, a through hole is formed in an upper portion of the box. According to the above configuration, the biasing means and the convex member can be visually recognized through the through hole. For example, when the biasing means is not correctly in contact with the convex member, a tool such as a driver is entered through the through hole. Thus, the arrangement of the urging means can be corrected.

  In the clutch device according to claim 6 of the present invention, the convex member and the concave portion are provided one by one. According to the above configuration, since the engagement between the convex member and the concave portion is only one place in the circumferential direction, the engagement is facilitated when the engaged state is released and returned again. Further, it is not necessary to align the dimensional accuracy of the convex members and the concave portions at a plurality of locations.

  In the clutch device according to claim 7 of the present invention, an outer inclined surface is formed outside the recess, and an inclination angle of the outer inclined surface is smaller than an inclination angle of the inner inclined surface of the recess. According to the said structure, a torque required when a convex member and a recessed part engage again becomes small, and engagement return becomes easy.

  In the clutch device according to claim 8 of the present invention, the inner inclined surface of the concave portion is a bottom inclined surface formed on the bottom surface side of the concave portion, and from the end of the bottom inclined surface to the opening side of the concave portion. The opening-side inclined surface is formed so that the inclination angle of the opening-side inclined surface is smaller than the inclination angle of the bottom-side inclined surface.

  According to the above configuration, the release torque is generated by bringing the convex member into contact with the bottom inclined surface. And the inclination angle of the opening side inclined surface provided continuously from the bottom side inclined surface is made smaller than the inclination angle of the bottom side inclined surface. As a result, the opening of the recessed portion is widened, so that when the convex member that has been disengaged is returned to the recessed portion, the protruding member is engaged with the recessed portion in a wider range (displacement) than when the opening is not widened. Can be restored.

  In the clutch device according to claim 9 of the present invention, the inclination angle of the outer inclined surface is smaller than the inclination angle of the opening-side inclined surface. According to the above configuration, it is possible to easily return the engagement by making the torque necessary for reengaging the convex member with the concave portion smaller than the release torque.

  In the clutch device according to claim 10 of the present invention, the width of the outer inclined surface is made smaller than the width of the second clutch member.

  According to the above configuration, by accommodating the outer inclined surface of the recess within the width of the second clutch member, the clutch device can be accommodated if there is a space corresponding to the angle of the output shaft and the width of the second clutch member, The clutch device can be made small.

  In the clutch device according to an eleventh aspect of the present invention, a through hole through which the output shaft is inserted is formed in the second clutch member, and a part of the output shaft is formed in the through hole or the output shaft. The press-fitting portion to be press-fitted is provided in a range that receives the urging force of the urging means. According to the said structure, since press injection is performed in the position near the center part of a 2nd clutch member, the height of a 2nd clutch member can be made low.

  A motor device according to a twelfth aspect of the present invention includes the clutch device according to any one of the first to eleventh aspects, a motor body that generates a driving force, and the driven portion of the clutch device. Driving force transmitting means for transmitting a driving force generated in the motor body.

  According to the above configuration, the driving force generated in the motor body is transmitted to the driven portion of the clutch device via the driving force transmitting means. Then, due to the engagement between the convex member and the concave portion, the first clutch member and the second clutch member rotate together, and the output shaft is driven to rotate. Here, since the engaging direction of the convex member and the concave portion in the clutch device is the radial direction of the output shaft, the height of the output shaft is kept lower than that of the clutch device that is engaged in the axial direction of the output shaft. It is done. Thereby, the height of the whole motor apparatus can be made low and the installation space of a motor apparatus can be reduced.

  In the motor device according to a thirteenth aspect of the present invention, the driving force transmission means includes a link member, and the movable region of the link member overlaps the rotation region of the first clutch member and the second clutch member. According to the above configuration, the link member, the first clutch member, for driving the output shaft, as compared with the motor device in which the movable region of the link member and the rotation regions of the first clutch member and the second clutch member do not overlap. And the area | region where a 2nd clutch member operate | moves can be reduced, and the whole motor apparatus can be reduced in size.

  A wiper motor according to a fourteenth aspect of the present invention is a wiper member directly or indirectly connected to the motor device according to the twelfth or thirteenth aspect and to the output shaft and driven by a driving force of the motor body. And having. According to the above configuration, since the height of the output shaft of the motor device can be kept low, the overall height of the wiper motor can be reduced, and the installation space of the wiper motor in the vehicle can be reduced.

  A first embodiment of a clutch device, a motor device, and a wiper motor of the present invention will be described with reference to the drawings.

  As shown in FIG. 1, a back door 14 having a rear window glass 12 is provided at the rear of the vehicle 10. A rear spoiler 16 is provided at the upper end of the rear window glass 12 so as to protrude rearwardly of the vehicle 10 in a substantially triangular shape. The rear spoiler 16 is formed with an opening 18 that is open toward the rear window glass 12 and is hollow inside.

  Inside the rear spoiler 16, the space between the inner panel 15 (see FIG. 9) and the outer panel 17 (see FIG. 9) constituting the vehicle panel of the back door 14 is fixed to the inner panel 15 and has a predetermined rotational drive ( A motor device 20 that swings) and a wiper member 22 that is rotationally driven by the motor device 20 and wipes the surface of the rear window glass 12 are provided. The motor device 20 and the wiper member 22 constitute a wiper motor 26.

  The wiper member 22 includes a wiper blade 28 that wipes the surface of the rear window glass 12, and a wiper arm 30 that holds the wiper blade 28 and has one end rotatably attached to the motor device 20.

  Next, the configuration of the motor device 20 will be described.

  As shown in FIGS. 2 and 3, the motor device 20 includes a motor main body 32 that generates a driving force, an energization unit 34 that energizes the motor main body 32, and a link mechanism that transmits the driving force generated by the motor main body 32. 36, a clutch device 40 in which a connection operation or a connection release operation is performed by a rotation operation of the link mechanism 36, and an output shaft 38 that is rotated (fluctuated) by driving force transmitted through the link mechanism 36 and the clutch device 40. And are provided.

  The motor main body 32 is connected to the energization unit 34, and is energized from the power source (not illustrated) via the energization unit 34 under the control of the control unit (not illustrated) of the vehicle 10 (see FIG. 1). It is supposed to occur.

  As shown in FIG. 4, the motor main body 32 includes a yoke housing 42. The yoke housing 42 is a flat cylindrical body, one end portion in the axial direction is drawn and a bottomed bearing portion 44 is provided, and the other end portion is opened. The opening side of the yoke housing 42 is integrally attached to a housing 70 that houses the link mechanism 36 and the clutch device 40. The housing 70 has a lower opening and is closed by a bottom cover (not shown).

  A bearing 46 is disposed in the bearing portion 44. On the other hand, an end housing 48 made of an insulating resin is fixed to the other end portion of the yoke housing 42 so as to close the opening, and a bearing 50 is disposed in a central portion of the end housing 48.

  In addition, an armature 52 (rotor) having a rotation shaft 54 is accommodated in the yoke housing 42. The armature 52 is supported rotatably about the rotation shaft 54 by inserting both ends of the rotation shaft 54 into the bearing 46 and the bearing 50. Furthermore, a magnet 56 (stator) is fixed to a portion of the inner peripheral wall of the yoke housing 42 that faces the armature 52.

  A brush 60 is held in the end housing 48 via a brush case 58. The brush 60 is formed in a substantially prismatic shape, and is in pressure contact with the outer peripheral surface of a commutator 62 (commutator) provided on one end side (lower side in the figure) of the armature 52. When the rotating shaft 54 rotates, the commutator 62 also rotates integrally with the armature 52. Further, a coupling pigtail 64 is drawn out from the upper part of the brush 60, and the tip of the pigtail 64 is connected to a power supply connection line (not shown).

  On the other hand, the rotating shaft 54 of the motor main body 32 (armature 52) is connected to the worm gear 68 of the link mechanism 36 by a coupling 66 provided on the outer side in the axial direction from the end housing 48.

  Both ends of the worm gear 68 are inserted into a bearing 72 (motor body 32 side) and a bearing 74 (clutch device 40 side) provided in the housing 70, and are supported rotatably. The worm gear 68 meshes with a worm wheel 76 that is rotatably supported in the housing 70.

  The worm wheel 76 is configured to rotate around a rotation shaft 78 that is erected in a direction perpendicular to the axis of the worm gear 68 and the rotation shaft 54 (a direction toward the front side in FIG. 4). The worm wheel 76 is disposed on one side with respect to the axis of the worm gear 68, and is rotatably accommodated in the housing 70 while meshing with the worm gear 68.

  As shown in FIGS. 4 and 5, the worm wheel 76 is connected to a sector gear 80 that constitutes a part of the link mechanism 36. The sector gear 80 has a crank pin (support shaft) 82 erected at a position different from the rotation shaft 78 of the worm wheel 76 (a position displaced in the radial direction of the worm wheel 76) and in the same direction as the rotation shaft 78. Is rotatably connected to the worm wheel 76. At the other end of the sector gear 80, a plurality of tooth portions 84 are formed as meshing portions. The tooth portion 84 meshes with a pinion gear 92 of the clutch device 40 described later.

  A holding lever 86 is disposed on one side of the sector gear 80 in the thickness direction (the side opposite to the worm wheel 76). The holding lever 86 is connected to a support shaft 88 provided at the swing center (the center of the pitch circle of the tooth portion 84) of the tooth portion 84 of the sector gear 80 through a through hole 86A formed on one end side. . The holding lever 86 is rotatably connected to an output shaft 38 that is rotatably supported by the housing 70 through a through hole 86B at the other end.

  Thereby, the inter-axis distance (inter-axis pitch) between the output shaft 38 and the support shaft 88 is maintained, and the meshing state of the sector gear 80 and the pinion gear 92 along the radial direction of the output shaft 38 is maintained. When the worm wheel 76 rotates, the sector gear 80 is reciprocally swung, and a first clutch member 94 described later is driven to reciprocate.

  A sliding member 90 made of a resin material or the like penetrating the holding lever 86 is attached on the opposite side of the holding lever 86 from the sector gear 80. The sliding member 90 is slidably in contact with a bottom lid (not shown) that closes the back side of the housing 70. Thereby, the movement along the thickness direction of the holding lever 86 (the axial direction of the output shaft 38) is restricted.

  Here, the link mechanism 36 is mainly configured by the worm wheel 76, the sector gear 80, and the holding lever 86.

  On the other hand, as shown in FIGS. 5 and 6, the clutch device 40 is disposed above the pinion gear 92 as the driven portion, the first clutch member 94, and the first clutch member 94 of the output shaft 38. A spring holder 96 as a second clutch member, a coil spring 98 as an urging means, and a convex member 108 are provided.

  The first clutch member 94 extends from the pinion gear 92 in one radial direction of the output shaft 38 on the upper surface of the pinion gear 92, and the pinion gear 92 and the first clutch member 94 are integrated. In addition, a through hole 95 is formed in the center of the end portion of the first clutch member 94 on the pinion gear 92 side so that the output shaft 38 can be inserted and penetrates the center of the first clutch member 94 and the pinion gear 92 in a substantially vertical direction. Is formed.

  Here, one end of the first clutch member 94 and the pinion gear 92 is disposed on the upper surface side of the other end of the holding lever 86, and the output shaft 38 is in a state where the through hole 95 and the through hole 86B at the other end communicate with each other. By being inserted, it can rotate in the circumferential direction of the output shaft 38.

  The spring holder 96 is formed with a through hole 99 having a size that allows the output shaft 38 to be inserted in a substantially vertical direction at one end, and the other end extends from the through hole 99 in one direction in the radial direction of the output shaft 38. It is composed of a box. The spring holder 96 is hollow and has a lower portion (bottom surface) opened, and a long hole 104 communicating with the inside of the spring holder 96 in the same direction as the axis of the output shaft 38 is formed in the center of the outer wall 102 at the other end. Is formed. The long hole 104 is connected to the lower opening of the spring holder 96. Further, a through hole 106 is formed in the upper part (upper surface) of the spring holder 96, which is a long hole extending in the radial direction of the output shaft 38 from the through hole 99 and penetrates to the inside of the spring holder 96.

  The spring holder 96 is fixed to the output shaft 38 with the output shaft 38 inserted through the through hole 99. Examples of the fixing means include adhesion, interference fitting, and means for D-cutting and fixing the output shaft 38 and the through hole 99. The fixed position of the spring holder 96 is such that when the output shaft 38 is inserted into the through hole 95 of the first clutch member 94, the lower opening of the spring holder 96 is partially or entirely blocked by the upper surface of the first clutch member 94. It is a possible position.

  Here, a coil spring 98 and a convex member 108 are accommodated in the spring holder 96. One end of the coil spring 98 is fixed to the inner wall surface on the output shaft 38 side, and the other end is a free end. Further, the convex member 108 has a disc shape and comes into contact with the other end of the coil spring 98 to be biased toward the radially outer side of the output shaft 38, and the coil spring of the biased portion 108A. A convex portion 108 </ b> B protruding from the surface opposite to 98 toward the radially outer side of the output shaft 38 is provided.

  The convex portion 108 </ b> B can be inserted into the long hole 104 and can project from the outer wall 102 to the radially outer side of the output shaft 38 by a predetermined length. Further, the contact surface of the biased portion 108 </ b> A with the coil spring 98 is larger than the opening area of the elongated hole 104 of the spring holder 96. Thereby, the movement of the convex member 108 to the outside in the radial direction of the output shaft 38 is restricted by the biased portion 108 </ b> A coming into contact with the inner wall surface of the spring holder 96.

  In this way, the convex member 108 is urged by the coil spring 98 in one direction radially outward of the output shaft 38, and is held in a state where the convex portion 108 B protrudes from the elongated hole 104 of the spring holder 96. Yes. Note that the convex member 108 is movable in the radial direction of the output shaft 38 inside the spring holder 96 by the expansion and contraction of the coil spring 98 by the magnitude of the external force acting on the convex portion 108B.

  On the other hand, at the end of the first clutch member 94 opposite to the pinion gear 92, a wall 110 is erected upward from the upper surface of the first clutch member 94. The wall 110 is extended with a predetermined width in the circumferential direction around the output shaft 38 in accordance with the width of the first clutch member 94 (width in a direction substantially perpendicular to the radial direction of the output shaft 38). . Further, a concave portion 112 having a size capable of engaging with the convex portion 108B is formed at the center of the inner wall surface (the surface on the output shaft 38 side) of the wall portion 110. Here, the engaging means 114 of the clutch device 40 is constituted by one convex member 108 and one concave portion 112.

  As shown in FIG. 7, on both outer sides of the recess 112 in the circumferential direction (direction perpendicular to the radial direction of the output shaft 38), a curved portion (mountain) that protrudes toward the output shaft 38 and a vertex of the curved portion Outer inclined surfaces 116A and 116B are formed which are inclined in a direction away from the output shaft 38 as they are shifted outward in the circumferential direction. In FIG. 7, the coil spring 98 is not shown and hatched in order to clarify the inclination angle.

  Here, with the tangential direction of the arc centered on the output shaft 38 as the reference line (angle 0 °), the inclination angle from the reference line of the inner inclined surface of the recess 112 is θ1, and the outer inclined surface 116B (116A is also the same angle) Θ1> θ2, where θ2 is an inclination angle from the reference line of (setting). Note that tapered surfaces are formed on both sides at the tip of the convex portion 108B, and the angles of these tapered surfaces are substantially equal to the inclination angle θ1 of the inner inclined surface of the concave portion 112.

  Further, the inclination angle θ1 and the radial depth of the inner inclined surface of the recess 112 are such that when the predetermined driving force capable of driving the output shaft 38 is applied to the first clutch member 94, the protrusion 108B is formed in the recess 112. When a load exceeding a predetermined driving force is applied to the engaging portion between the convex portion 108B and the concave portion 112, the convex portion 108B moves along the inner inclined surface of the concave portion 112 and engages. Is the size to be released.

  Next, assembly of the motor device 20 and the wiper motor 26 will be described.

  As shown in FIG. 5, first, the spring holder 96 is fixed to the output shaft 38. Subsequently, with the coil spring 98 and the convex member 108 housed inside the spring holder 96, the lower end side of the output shaft 38 is inserted into the through hole 95 of the first clutch member 94, and the first clutch member 94 is moved to the spring holder. The clutch device 40 is assembled by closing the lower opening of 96.

  Subsequently, the upper end side of the output shaft 38 is inserted into the bearing 39, and the upper end side of the output shaft 38 is inserted into a through hole 71 formed in the housing 70, whereby the bearing 39 is held in the housing 70 and the clutch device 40. Is installed.

  On the other hand, the motor main body 32 and the energizing portion 34 are assembled, the worm gear 68 protruding from the motor main body 32 is covered, and the housing 70 is assembled by fixing means such as screws. Subsequently, the rotation shaft 78 of the housing 70 is inserted into the through hole of the worm wheel 76, and the worm gear 68 and the worm wheel 76 are engaged with each other.

  Subsequently, the crank pin 82 is rotatably supported by a connecting portion (not shown) formed on the lower surface side of the worm wheel 76, whereby the sector gear 80 is connected to the worm wheel 76. At this time, the tooth portion 84 of the sector gear 80 and the pinion gear 92 are engaged with each other.

  Here, the lower end side of the output shaft 38 is inserted into the through hole 86B of the holding lever 86, and the support shaft 88 of the sector gear 80 is inserted into the through hole 86A of the holding lever 86, whereby the link mechanism 36 is formed. Subsequently, the lower opening of the housing 70 is closed by a bottom lid (not shown) with a bearing and a retaining means (not shown) provided below the pinion gear 92 of the output shaft 38, and the motor device 20 is assembled. .

  In the assembly of the motor device 20, when the extending direction of the first clutch member 94 and the extending direction of the spring holder 96 are matched, the lower opening of the spring holder 96 is closed by the first clutch member 94. At the same time, the convex portion 108B of the convex member 108 enters the concave portion 112 and engages. Thus, the coupling of the clutch device 40 is completed, and the driving force generated in the motor main body 32 is input to the output shaft 38 via the link mechanism 36 and the clutch device 40.

  As shown in FIGS. 1, 5, and 9, the completed motor device 20 has a substantially U-shape when screws (not shown) are fastened to a plurality of fastening holes 118 formed in the housing 70. It is fixed to the stay 27. Further, the motor device 20 is housed in a space between the inner panel 15 and the outer panel 17 by fastening the stay 27 to the inner panel 15 with a bolt or the like (not shown). A through hole 23 is formed in the outer panel 17, and an output shaft 38 of the motor device 20 protrudes from the through hole 23. Here, the wiper motor 30 is assembled by attaching the wiper arm 30 to the upper end of the output shaft 38.

  The wiper motor 26 is located at the upper end of the rear window glass 12. Then, the rear spoiler 16 is fixed to the back door 14 so as to cover the wiper motor 26. The wiper member 22 of the wiper motor 26 is disposed at a position facing the opening 18 of the rear spoiler 16 and swings back and forth to wipe the rear window glass 12.

  FIG. 8 schematically shows the distance between the output shaft 38 of the wiper motor 26 and the regulation line 24. The restriction line 24 represents the installation limit when the motor device 20 is installed with the minimum width in the space between the inner panel 15 and the outer panel 17 (see FIG. 9). The rotation range of the output shaft 38 by the aforementioned link mechanism 36 (see FIG. 2) is a rotation angle range that does not exceed 180 ° from the reference line M passing through the center of the output shaft 38 and parallel to the regulation line 24. The distance from the center of the shaft 38 to the restriction line 24 is d1.

  Here, if the output shaft 38 rotates 360 ° (one rotation), the distance from the center of the output shaft 38 to the necessary installation limit (imaginary plane N) of the housing of the motor device 20 is d2 (d2> d1), and the installation space of the motor 20 formed by the inner panel 15 and the outer panel 17 (see FIG. 9) must be enlarged. However, in the motor device 20 of the present embodiment, the installation space can be saved by suppressing the rotation range of the output shaft 38 as described above.

  In FIG. 9, a part of the vehicle 10 near the rear spoiler 16 is schematically illustrated. In FIG. 9, the hatching of the cross section is partially omitted for easy understanding of the drawing. The vehicle 10 includes an inner panel 15 on the indoor side and an outer panel 17 on the outdoor side, and the motor device 20 is disposed in a space surrounded by the inner panel 15 and the outer panel 17. One end of the rear window glass 12 is attached to the outer panel 17.

  Here, as described above, the clutch device 40 in the motor device 20 extends in the radial direction of the output shaft 38 (in the direction of arrow R in FIG. 9) and is connected (engaged) in the circumferential direction. Therefore, the height d3 of the output shaft 38 in the axial direction (arrow L direction) is not affected by the operation of the clutch device 40. Thus, the height d3 of the output shaft 38 can be kept low, the overall height of the clutch device 40 can be lowered, and the height of the rear spoiler 16 can be kept low.

  Next, the operation of the first embodiment of the present invention will be described.

  As shown in FIGS. 3 and 4, in the motor device 20 (wiper motor 26) configured as described above, when the motor main body 32 is energized via the energization unit 34 and the armature 52 rotates, it rotates to the worm wheel 76 via the worm gear 68. The force is transmitted, and the worm wheel 76 continuously rotates in one direction.

  Subsequently, as shown in FIGS. 10A to 10C, when the worm wheel 76 rotates, the sector gear 80 connected to the worm wheel 76 reciprocally swings. As the sector gear 80 reciprocally swings, the pinion gear 92 is driven to reciprocate and the first clutch member 94 is reciprocally swung. The position of the first clutch member 94 in FIG. 10B is the initial origin position, and the first clutch member 94 is moved from the initial origin position to the position shown in FIG. As shown in FIG. 10 (c), it is displaced in the circumferential direction.

  As shown in FIG. 11A, at the initial origin position of the first clutch member 94 (see FIG. 10B), the convex portion 108B and the concave portion 112 are engaged. Here, when a load (external force) exceeding the driving force is not applied to the output shaft 38, the engagement state between the convex portion 108 </ b> B and the concave portion 112 is maintained, so that the first clutch member 94 is synchronized with the swing. The output shaft 38 swings (engaged state). As a result, the wiper member 22 (see FIG. 1) connected to the output shaft 38 is driven to reciprocate as the output shaft 38 reciprocates, and repeatedly moves downward from the opening 18 of the rear spoiler 16 in an arc shape. The surface of the rear window glass 12 is wiped off.

  On the other hand, for example, when an excessive load (load) is applied around the output shaft 38 via the wiper member 22, the output shaft 38 is rotated or constrained in the reverse direction. 11B and 11C show a state where the output shaft 38 rotates in the reverse direction.

  Here, as shown in FIG. 11 (b), when the motor device 20 (see FIG. 3) is stopped or in an operating state and the first clutch member 94 is in a restrained or rotating state, an excessive force is generated around the output shaft 38 due to an external force. When a load (load) is applied, the spring holder 96 rotates in the direction opposite to the first clutch member 94. For this reason, the relative rotational force acts on the contact portion between the inner inclined surface of the concave portion 112 and the tapered surface of the convex member 108. When the reaction force acting on the convex member 108 acting on the contact portion exceeds the urging force of the coil spring 98, the convex member 108 slides toward the output shaft 38. Then, the engagement between the convex portion 108B and the concave portion 112 is released (released state).

  Subsequently, as illustrated in FIG. 11C, when the spring holder 96 continues to rotate, the convex portion 108 </ b> B is completely separated from the outer inclined surface 116 </ b> B of the concave portion 112. Thereby, the pinion gear 92 and the first clutch member 94 are idled without being interfered with the output shaft 38 (idle state). Since the first clutch member 94 and the spring holder 96 are configured to face each other only in one radial direction of the output shaft 38, the first clutch member 94 and the spring holder 96 are mutually circumferential in a state in which the engagement between the convex member 108 and the concave portion 112 is released. The movement of the first clutch member 94 is not interfered with the movement of the spring holder 96.

  Here, even when the engagement between the convex member 108 and the concave portion 112 is released, the first clutch member 94 is the bottom of the spring holder 96, so that the bottom of the spring holder 96 is not closed by another member. However, the convex member 108 and the coil spring 98 are held in the spring holder 96. Thereby, dropping of the convex member 108 can be prevented.

  Further, when the tip of the convex member 108 protrudes outward from the long hole 104 of the spring holder 96, the convex member 108 is guided to the long hole 104 and directed toward the concave portion 112, so that the convex member 108 can be easily positioned. Further, when the tip of the convex member 108 (the convex portion 108B) moves in the rotational direction in accordance with the rotation of the spring holder 96, the convex member 108 is held in contact with the inner wall of the elongated hole 104. Position fluctuation (backlash) is reduced.

  Further, the engagement region between the convex member 108 and the concave portion 112 is located farther in the radial direction from the center of the output shaft 38 than when the convex member is provided on the first clutch member 94 side. Thereby, the urging | biasing force of the coil spring 98 required to hold | maintain engagement with the convex member 108 and the recessed part 112 can be restrained small. Further, when the biasing means is the coil spring 98, the outer diameter and the wire diameter of the coil spring 98 can be reduced to reduce the size of the clutch device 40.

  Further, since the elongated hole 104 is formed in the same direction as the axis of the output shaft 38, the convex member 108 can be positioned at one place in the circumferential direction. Further, the long hole 104 is connected to the lower opening of the spring holder 96. For this reason, when the convex member 108 and the coil spring 98 are assembled to the spring holder 96, both are assembled from the same lower opening direction, so that the assembly is facilitated.

  Further, since the convex member 108 and the coil spring 98 are visible through the through hole 106 in the upper part of the spring holder 96, for example, when the coil spring 98 is not correctly in contact with the convex member 108, the through hole A tool such as a driver can be entered via 106 to correct the arrangement of the coil spring 98.

  The wiper motor 26 (see FIG. 1) is used, for example, when an excessive external force is applied to the output shaft 38 via the wiper member 22 during operation within the rotation range (within the normal wiping range) of the wiper member 22. When the pinion gear 92 and the first clutch member 94 are idling, an excessive load is applied to the driving force transmission components (configuration of the sector gear 80, the worm wheel 76, the worm gear 68, the motor main body 32, etc.) in front of the first clutch member 94. Can be prevented from acting.

  Subsequently, the stopper protrusion (not shown) provided on the spring holder 96 is in contact with the inner wall of the housing 24 (see FIG. 1), or the spring holder 96 main body and the housing 24 are in contact. When the motor main body 32 is operated in a state where the pressure is restricted, the first clutch member 94 rotates, and the convex portion 108B rides on the outer inclined surface 116B of the concave portion 112 (or the outer inclined surface 116A in the case of the opposite side). In the initial engagement position.

  Thereby, the origin return of the first clutch member 94 and the spring holder 96 is automatically performed, and the output shaft 38 (and the wiper member 22) can be driven again. As described above, the outer inclined surfaces 116A and 116B of the concave portion 112 are set to be smaller than the inclination angle of the inner inclined surface of the concave portion 112, so that the motor output shaft generated torque is smaller than the predetermined release torque. The engagement between the portion 108B and the recess 112 can be restored.

  In addition, since the clutch device 40 is provided with the convex member 108 and the concave portion 112 one by one, the convex member 108 and the concave portion 112 are engaged at only one location in the circumferential direction. This facilitates the engagement when the engagement state between the convex member 108 and the concave portion 112 is released and then returned again. Further, it is not necessary to align the dimensional accuracy of the convex members and concave portions at a plurality of locations.

  As shown in FIG. 10A, in the motor device 20 of the present embodiment, the link mechanism 36 has a sector gear 80 and a holding lever 86. These movable regions, the first clutch member 94, and the spring holder 96 are included. Overlap with the rotation region (region S). Thereby, the area where the sector gear 80, the holding lever 86, the first clutch member 94, and the spring holder 96 operate for driving the output shaft 38 can be reduced, and the entire motor device 20 can be downsized.

  Next, a second embodiment of the clutch device, the motor device, and the wiper motor of the present invention will be described with reference to the drawings. Note that components that are basically the same as those in the first embodiment described above are given the same reference numerals as those in the first embodiment, and descriptions thereof are omitted.

  FIG. 12 shows the configuration of a clutch device 120 provided in place of the clutch device 40 of the motor device 20 (see FIG. 3). The clutch device 120 includes a pinion gear 122 as a driven portion, a first clutch member 124, a second clutch member 136 disposed above the first clutch member 124 of the output shaft 38, and an urging means. A coil spring 98 and a convex member 108 are provided.

  The first clutch member 124 extends from the pinion gear 122 in one radial direction of the output shaft 38 on the upper surface of the pinion gear 122, and the pinion gear 122 and the first clutch member 124 are integrated. In addition, a through hole 132 having a size that allows the output shaft 38 to be inserted and penetrating through the center of the first clutch member 124 and the pinion gear 122 in a substantially vertical direction is provided at the center of the end portion of the first clutch member 124 on the pinion gear 122 side. Is formed.

  Here, the first clutch member 124 and the pinion gear 122 are arranged at one end on the upper surface side of the other end of the holding lever 86 (see FIG. 5), and the through hole 132 and the through hole 86B at the other end communicate with each other. Thus, the output shaft 38 is inserted so that it can rotate in the circumferential direction of the output shaft 38.

  Further, a holder portion 126 made of a box extending in one radial direction of the output shaft 38 is provided at the end of the first clutch member 124 opposite to the pinion gear 122. The holder portion 126 is formed with a hollow portion 128 and is open at the top. An elongated hole 130 is formed in the center of the wall on the output shaft 38 side of the holder portion 126 along the axial direction of the output shaft. The long hole 130 communicates with the hollow portion 128.

  A coil spring 98 and a convex member 108 are accommodated in the hollow portion 128 of the holder portion 126. The convex member 108 is urged toward the output shaft 38 by the coil spring 98 and can move in the radial direction of the output shaft 38 in the hollow portion 128, and the convex portion 108 B is moved from the elongated hole 130 to the output shaft 38. Protrusively toward. A flat upper cover 134 is attached to the upper portion of the holder portion 126 in a state where the coil spring 98 and the convex member 108 are accommodated, and is closed. Thereby, the coil spring 98 and the convex member 108 are prevented from jumping out of the hollow portion 128.

  On the other hand, the second clutch member 136 is formed with a through hole 142 having a size that allows the output shaft 38 to be inserted in a substantially vertical direction at one end, and the output shaft 38 is inserted in the through hole 142. 38 is fixed. Examples of the fixing means include adhesion, interference fitting, and D-cutting of the output shaft 38 and the through hole 142 to fix the engagement. The second clutch member 136 is fixed at a position where the bottom surface of the second clutch member 136 is disposed on the upper surface of the first clutch member 94 when the output shaft 38 is inserted into the through hole 132 of the first clutch member 124. Is in position.

  Further, a concave portion 138 having a size capable of engaging with the convex portion 108B is formed at the center of the outer wall surface on the other end side (the side opposite to the output shaft 38) of the second clutch member 136. On both outer sides of the recess 138 in the circumferential direction (a direction perpendicular to the radial direction of the output shaft 38), a curved portion (mountain) that protrudes in a direction away from the output shaft 38, and a deviation from the apex of the curved portion toward the outer side in the circumferential direction. An outer inclined surface 140 that is inclined in a direction approaching the output shaft 38 is formed. Note that the inclination angle of the outer inclined surface 140 is smaller than the inclination angle of the inner inclined surface of the recess 138.

  The inclination angle and the radial depth of the inner inclined surface of the concave portion 138 are determined so that the convex portion 108B comes off from the concave portion 138 when a predetermined driving force capable of driving the output shaft 38 acts on the first clutch member 124. When a load exceeding the predetermined driving force is applied to the engaging portion of the convex portion 108B and the concave portion 138, the convex portion 108B moves along the inner inclined surface of the concave portion 138, and the engagement is released. It is a size.

  Next, the operation of the second embodiment of the present invention will be described.

  In the motor device 20 provided with the clutch device 120 having the above-described configuration, when the motor main body 32 is energized through the energization unit 34 and the armature 52 rotates, the rotational force is transmitted to the worm wheel 76 through the worm gear 68, and the worm wheel 76 continuously rotates in one direction.

  Subsequently, when the worm wheel 76 rotates, the sector gear 80 connected to the worm wheel 76 reciprocally swings. By the reciprocating swinging operation of the sector gear 80, the pinion gear 122 is driven to reciprocate and the first clutch member 124 is swung back and forth.

  As shown in FIG. 13A, at the initial origin position of the first clutch member 124, the convex portion 108B and the concave portion 138 are engaged. Here, when a load (external force) exceeding the driving force is not applied to the output shaft 38, the engagement state between the convex portion 108 </ b> B and the concave portion 138 is maintained, so that the first clutch member 124 is synchronized with the swing. The output shaft 38 swings. As a result, the wiper member 22 (see FIG. 1) connected to the output shaft 38 is driven to reciprocate as the output shaft 38 reciprocates (engaged state).

  On the other hand, for example, when an excessive load (load) is applied around the output shaft 38 via the wiper member 22, the output shaft 38 is rotated or constrained in the reverse direction. 13B and 13C show a state where the output shaft 38 rotates in the reverse direction.

  Here, as shown in FIG. 13B, when the motor device 20 (see FIG. 3) is stopped or in an operating state and the first clutch member 124 is in a restrained or rotating state, the output shaft 38 is excessively driven by an external force. When a load (load) is applied, the second clutch member 136 rotates in the opposite direction to the first clutch member 124. For this reason, a relative rotational force acts on a contact portion between the inner inclined surface of the concave portion 138 and the tapered surface of the convex member 108. When the reaction force to the convex member 108 acting on the contact portion exceeds the urging force by the coil spring 98, the convex member 108 slides in a direction away from the output shaft 38. Then, the engagement between the convex portion 108B and the concave portion 138 is released (released state).

  Subsequently, as shown in FIG. 13C, when the second clutch member 136 continues to rotate, the convex portion 108 </ b> B is completely separated from the outer inclined surface 140 of the concave portion 138. As a result, the pinion gear 122 and the first clutch member 124 are idling (idling state).

  The first clutch member 124 and the second clutch member 136 are configured to face each other only in one radial direction of the output shaft 38. The movement of the first clutch member 124 is not interfered with the movement of the second clutch member 136. Thereby, it is possible to prevent an excessive external force from acting on the driving force transmission component (the configuration of the sector gear 80, the worm wheel 76, the worm gear 68, the motor main body 32, etc.) in front of the first clutch member 124.

  Subsequently, when the motor main body 32 is operated in a state where the movement of the second clutch member 136 is restricted by contact with the housing or the like, the first clutch member 124 rotates, and the convex portion 108B becomes the outer inclined surface 140 of the concave portion 138. Riding while abutting, it fits in the initial engagement position. As a result, the origin return of the first clutch member 124 and the second clutch member 136 is automatically performed, and the output shaft 38 can be driven again. As described above, the outer inclined surface 140 of the concave portion 138 is set to be smaller than the inclination angle of the inner inclined surface of the concave portion 138, so that the convex portion 108B has a motor output shaft generation torque smaller than a predetermined release torque. And the recess 138 can be restored.

  Next, another embodiment of the clutch device of the present invention will be described with reference to the drawings. Note that components that are basically the same as those in the first embodiment described above are given the same reference numerals as those in the first embodiment, and descriptions thereof are omitted.

  FIG. 14A shows the clutch device 40 of the first embodiment as a comparative example. FIG. 14B shows the clutch device 150 of the present embodiment.

  As shown in FIG. 14A, in the clutch device 40, the output shaft 38 is inserted into the through hole 99 of the spring holder 96 and the through hole 95 of the first clutch member 94, and is press-fitted provided at the upper part of the through hole 99. The portion 93 is press-fitted and fixed. The press-fit portion 93 may be provided with a part of the through hole 99 having a small diameter, and may be provided with a part of the output shaft 38 having a large diameter. Here, the height of the accommodation area in which the coil spring 98 is accommodated is d6, and the press-fitting allowance of the press-fit portion 93 is d4. For this reason, the height of the upper surface of the press-fit portion 93 is higher by d5 (d5 <d4) than the height of the upper surface of the portion where the through hole 106 of the spring holder 96 is formed.

  On the other hand, as shown in FIG. 14 (b), the clutch device 150 of the present embodiment includes a pinion gear 92, a first clutch member 94, and a first clutch of an output shaft 162 (which has a different press-fitting location from the output shaft 38). A spring holder 152 serving as a second clutch member disposed above the member 94, a coil spring 98, and a convex member 108 are provided.

  The spring holder 152 is formed with a through hole 158 having a size that allows the output shaft 162 to be inserted in a substantially vertical direction at one end, and the other end extends in one direction in the radial direction of the output shaft 162 from the through hole 158. It is composed of a box. The spring holder 152 is hollow and has a lower (bottom) opening, and a long hole 154 that communicates with the inside of the spring holder 152 in the same direction as the axis of the output shaft 162 is formed at the center of the outer wall of the other end. Has been.

  The long hole 154 is connected to the lower opening of the spring holder 152. Further, a through hole 156 is formed in the upper portion (upper surface) of the spring holder 152, which is a long hole extending in the radial direction of the output shaft 162 from the through hole 158 and penetrating to the inside of the spring holder 152. Inside the spring holder 152, the coil spring 98 and the convex member 108 are accommodated.

  In the clutch device 150, the output shaft 162 is inserted into the through hole 158 of the spring holder 152 and the through hole 95 of the first clutch member 94, and is press-fitted and fixed by a press-fit portion 160 provided at a substantially vertical center portion of the through hole 158. Has been. The press-fit portion 160 may be provided with a part of the through hole 158 having a small diameter, and may be provided with a part of the output shaft 162 having a large diameter.

  Here, in the spring holder 152, the height of the accommodation area in which the coil spring 98 is accommodated is d6. Further, the press-fit portion 160 is disposed in a region having the same height as the housing region of the coil spring 98 in the axial direction of the output shaft 162 (a range where the urging force of the coil spring 98 is received), and the press-fit allowance is d4. ing. For this reason, the height of the upper surface of the site where the through hole 158 is formed in the spring holder 152 is the same as the height of the upper surface of the site where the through hole 156 is formed. In other words, the spring holder 152 is configured such that d5 = 0 of the spring holder 96, and is lower in height and thinner than the spring holder 96.

  In addition, this invention is not limited to said embodiment.

  The biasing means of the convex member 108 is not limited to the coil spring 98, and can be replaced if it is an elastic member (rubber or the like) having the same elastic performance as the coil spring 98. Further, the number of the coil springs 98 is not limited to one and may be a plurality. The wiper member 22 may be attached not only directly to the output shaft 38 but also indirectly via an arm member or a link mechanism. Further, in the configuration in which the convex member 108 and the coil spring 98 are held by the spring holder 96 so as not to drop off, the spring holder 96 may be disposed below the first clutch member 94.

  Next, a third embodiment of the clutch device, the motor device, and the wiper motor of the present invention will be described with reference to the drawings. Note that components that are basically the same as those in the first embodiment described above are given the same reference numerals as those in the first embodiment, and descriptions thereof are omitted.

  As shown in FIG. 15, on the outer side in the circumferential direction of the concave portion 180, a curved portion (mountain) that protrudes toward the output shaft 38 (see FIG. 16), and the output shaft as it shifts from the apex of the curved portion to the outer side in the circumferential direction. Outer inclined surfaces 182A and 182B that are inclined in a direction away from 38 are formed.

  Furthermore, the inner peripheral inclined surface 186 of the concave portion 180 is formed from the bottom inclined surface 186A formed on the bottom surface 188 side of the concave portion 180, and from the end of the bottom inclined surface 186A toward the opening side of the concave portion 180. It is comprised from the opening side inclined surface 186B.

  Here, with the tangential direction of the arc centered on the output shaft 38 as the reference line (angle 0 °), the inclination angle from the reference line of the bottom inclined surface 186A of the recess 180 is θ3, and the reference line of the opening inclined surface 186B Θ3> θ4, where θ4 is an inclination angle from.

  Further, when the inclination angle of the outer inclined surfaces 182A and 182B with respect to the reference line is θ5, θ4> θ5. Note that tapered surfaces are formed on both sides at the tip of the convex portion 108B, and the angles of these tapered surfaces are substantially equal to the inclination angle θ3 of the bottom inclined surface 186A of the concave portion 180.

  Further, the inclination angle θ3 and the depth of the bottom-side inclined surface 186A of the concave portion 180 are such that when a predetermined driving force capable of driving the output shaft 38 acts on the first clutch member 94 (see FIG. 16), the convex portion The coil spring 98 is compressed when the load exceeding the predetermined driving force is applied to the engaging portion between the convex portion 108B and the concave portion 180, and the convex portion 108B is compressed into the concave portion 180. It moves along the bottom-side inclined surface 186A and the opening-side inclined surface 186B so that the engagement is released.

  That is, the angle of the inclination angle θ3 of the bottom side inclined surface 186A is determined in relation to the spring force of the coil spring 98 in order to generate the release torque. The opening-side inclined surface 186B releases the engagement while compressing the coil spring 98 and increasing the load. The torque generated here must be smaller than the release torque. For this reason, the inclination angle θ4 of the opening-side inclined surface 186B is determined by the load when the spring is compressed (when the stroke is maximum).

  Further, the widths of the outer inclined surfaces 182A and 182B are smaller than the width of the spring holder 96 (W shown in FIG. 15).

  As shown in FIG. 16A, at the initial origin position of the first clutch member 94, the convex portion 108B and the concave portion 180 are engaged. Here, when a load (external force) exceeding the driving force is not applied to the output shaft 38, the engagement state between the convex portion 108 </ b> B and the concave portion 180 is maintained, so that the first clutch member 94 is synchronized with the swing. The output shaft 38 swings (engaged state). As a result, the wiper member connected to the output shaft 38 is driven to reciprocate as the output shaft 38 reciprocates.

  On the other hand, for example, when an excessive load (load) is applied around the output shaft 38 via the wiper member, the output shaft 38 is rotated or restrained in the reverse direction. 16B and 16C show a state where the output shaft 38 rotates in the reverse direction.

  Here, as shown in FIG. 16B, when the first clutch member 94 is in a restrained or rotating state with the motor device being stopped or operating, an excessive load (load) due to an external force acts around the output shaft 38. Then, the spring holder 96 rotates in the direction opposite to the first clutch member 94. For this reason, the relative rotational force acts on the contact portion between the bottom-side inclined surface 186 </ b> A of the concave portion 180 and the tapered surface of the convex member 108. When the reaction force acting on the convex member 108 acting on the contact portion exceeds the urging force of the coil spring 98, the convex member 108 slides toward the output shaft 38. Then, the engagement between the convex portion 108B and the concave portion 180 is released (released state).

  Subsequently, as illustrated in FIG. 16C, when the spring holder 96 continues to rotate, the convex portion 108 </ b> B is completely separated from the outer inclined surface 182 of the concave portion 180. Accordingly, the pinion gear and the first clutch member 94 are idled without being interfered with the output shaft 38 (idle state). Since the first clutch member 94 and the spring holder 96 are configured to face each other only in one radial direction of the output shaft 38, the first clutch member 94 and the spring holder 96 are mutually circumferential in a state where the engagement of the convex member 108 and the concave portion 180 is released. The movement of the first clutch member 94 is not interfered with the movement of the spring holder 96.

  On the other hand, the stopper protrusion (not shown) provided on the spring holder 96 is in contact with the inner wall of the housing, or the spring holder 96 main body and the housing 24 are in contact with each other. When the main body is operated, the first clutch member 94 is rotated, and the convex portion 108B rides on the outer inclined surface 182B (or the outer inclined surface 182A in the case of the opposite side) while abutting on it, and stays in the initial engagement position. It is like that.

  Further, as shown in FIG. 17, the position and size of the stopper protrusion are determined so that the wiper 190 that has been disengaged can be moved within the range A shown in FIG. When wiped, the wiper 190 does not come out of the glass 192.

  Since the normal swinging range of the wiper 190 is narrower than the above-described range A, there is a case where the unevenness does not move to the point where the engagement is completely matched even when the engagement of the clutch is restored by the operation of the motor. Further, by providing the opening-side inclined surface 186 </ b> B of the recess 180, it becomes easier to return by increasing the opening width of the recess 180. Furthermore, in order to return the engagement, a force for moving the wiper 190 along the surface of the glass 192 is required. Therefore, the inclination angle of the opening-side inclined surface 186B needs to be an angle that generates a torque of 1 N · m (force to move the glass surface in the WET state) or more.

  Thus, the inclination angle of the opening-side inclined surface 186B provided continuously from the bottom-side inclined surface 186A is smaller than the inclination angle of the bottom-side inclined surface 186A. Thereby, since the frontage of the recessed part 180 spreads, the convex part 108B can be engaged and returned to the recessed part 180 in a wider range (displacement) than in the case where the frontage is not widened.

  Further, by making the inclination angle of the outer inclined surfaces 182A and 182B smaller than the inclination angle of the opening-side inclined surface 186B, the torque required when the convex portion 108B is re-engaged with the concave portion 180 is made smaller than the release torque. The return can be facilitated.

  The inclination angles of the outer inclined surfaces 182A and 182B are set so that the convex portion 108B can contact the outer inclined surface 182B when the output shaft 38 is rotated in the state of FIG. By making this contact position outside the W direction in FIG. 15, the inclination angle becomes small, and the returning torque is small and can be easily restored.

  Further, by making the width of the outer inclined surfaces 182A, 182B smaller than the width of the spring holder 96, the angle at which the outer inclined surface 182 of the recess 180 is accommodated within the width of the spring holder 96 and the output shaft 38 swings. If there is a space corresponding to the width of the spring holder 96, the clutch device 40 can be accommodated and the clutch device 40 can be made smaller.

It is a perspective view which shows the attachment state to the vehicle rear part of the wiper motor which concerns on 1st Embodiment of this invention. It is a perspective view which shows the structure of the wiper motor which concerns on 1st Embodiment of this invention. It is the perspective view which saw through a part which shows the structure of the wiper motor which concerns on 1st Embodiment of this invention. It is a plane sectional view showing the composition of the wiper motor concerning a 1st embodiment of the present invention. It is a disassembled perspective view which shows the structure of the wiper motor which concerns on 1st Embodiment of this invention. It is a disassembled perspective view which shows the structure of the clutch apparatus which concerns on 1st Embodiment of this invention. It is a schematic diagram which shows the engagement state of the convex member and recessed part of the clutch apparatus which concern on 1st Embodiment of this invention. It is a schematic diagram which shows the distance of the output shaft and housing outer wall of the wiper motor which concern on 1st Embodiment of this invention. It is a schematic diagram which shows the distance of the output shaft and rear spoiler of the wiper motor which concerns on 1st Embodiment of this invention. (A)-(c) It is a schematic diagram which shows the rotational drive state of the 1st clutch member which concerns on 1st Embodiment of this invention. (A)-(c) It is a plane sectional view showing the engagement state, the release state, and the idling state of the clutch device concerning a 1st embodiment of the present invention. It is a disassembled perspective view which shows the structure of the wiper motor which concerns on 2nd Embodiment of this invention. (A)-(c) It is a plane sectional view showing the engagement state, the release state, and the idling state of the clutch device concerning a 2nd embodiment of the present invention. (A) It is sectional drawing of the clutch apparatus which concerns on 1st Embodiment of this invention. (B) It is sectional drawing of the clutch apparatus of the other Example of this invention. It is a schematic diagram which shows the engagement state of the convex member and recessed part of the clutch apparatus which concern on 3rd Embodiment of this invention. (A)-(c) It is a plane sectional view showing the engagement state, the release state, and the idling state of the clutch device concerning a 3rd embodiment of the present invention. It is the schematic diagram which showed the wiper etc. which were attached to the wiper motor by which the clutch apparatus which concerns on 3rd Embodiment of this invention was employ | adopted.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Vehicle, 20 ... Motor apparatus (motor apparatus), 22 ... Wiper member (wiper member), 26 ... Wiper motor (wiper motor), 32 ... Motor main body (motor main body), 36 ... Link mechanism (driving force transmission means), 38 ... output shaft (output shaft), 40 ... clutch device (clutch device), 80 ... sector gear (link member), 86 ... holding lever (link member), 92 ... pinion gear (driven portion), 94 ... first clutch member ( First clutch member), 96 ... Spring holder (second clutch member, box), 98 ... Coil spring (biasing means), 104 ... Long hole (hole), 106 ... Through hole (through hole), 108 ... Convex member (convex member), 112 ... concave portion (concave portion, inner inclined surface), 114 ... engaging means (engaging means), 116A ... outer inclined surface (outer inclined surface), 116B ... outer inclined surface (outer side) Slope), 120 ... Clutch device (clutch device), 124 ... First clutch member (first clutch member), 136 ... Second clutch member (second clutch member), 138 ... Recess (recess), 140 ... Outer inclined surface (Outer inclined surface) 158 ... Through hole (through hole), 180 ... Recessed part, 182A, 184B ... Outer inclined surface, 186 ... Inner peripheral inclined surface, 186A ... Bottom side inclined surface, 186B ... Opening side inclined surface, 188 ... Bottom

Claims (14)

An output shaft rotatably supported;
A driven portion that is rotatably supported by the output shaft and receives a driving force;
A first clutch member extending from the driven portion in one direction of the radial direction of the output shaft;
A second clutch member fixed to the output shaft and extending in one radial direction of the output shaft;
A convex member provided on one of the first clutch member and the second clutch member so as to be movable in the radial direction of the output shaft, and one of the second clutch member and the first clutch member. An engaging means having a concave portion that is formed on a surface facing the convex member and engages with the convex member;
A biasing means for biasing the convex member to engage the concave portion;
A clutch device.   The second clutch member includes a box body that houses the convex member and the urging means, has a lower opening, and has a hole portion through which the convex member enters and exits. The clutch device according to claim 1, wherein the clutch device is closed by one clutch member.   The clutch device according to claim 2, wherein the hole is a long hole in the same direction as the axis of the output shaft.   The clutch device according to claim 2 or 3, wherein the hole is connected to the opening.   The clutch device according to any one of claims 2 to 4, wherein a through hole is formed in an upper portion of the box.   The clutch device according to any one of claims 1 to 5, wherein the convex member and the concave portion are provided one by one.   The clutch device according to any one of claims 1 to 6, wherein an outer inclined surface is formed outside the concave portion, and an inclination angle of the outer inclined surface is smaller than an inclination angle of the inner inclined surface of the concave portion. . The inner inclined surface of the recess includes a bottom inclined surface formed on the bottom surface side of the recess, and an opening-side inclined surface formed from the end of the bottom inclined surface toward the opening side of the recess. ,
The clutch device according to claim 7, wherein an inclination angle of the opening-side inclined surface is smaller than an inclination angle of the bottom-side inclined surface.   The clutch device according to claim 8, wherein an inclination angle of the outer inclined surface is smaller than an inclination angle of the opening-side inclined surface.   The clutch device according to any one of claims 7 to 9, wherein a width of the outer inclined surface is smaller than a width of the second clutch member.   A through hole into which the output shaft is inserted is formed in the second clutch member, and a press-fitting portion into which a part of the output shaft is press-fitted into the through hole or the output shaft is provided in the biasing means. The clutch device according to any one of claims 1 to 10, wherein the clutch device is provided in a range to receive an urging force. The clutch device according to any one of claims 1 to 11,
A motor body that generates a driving force;
Driving force transmitting means for transmitting a driving force generated in the motor main body to the driven portion of the clutch device;
A motor device having:   The motor device according to claim 12, wherein the driving force transmission means includes a link member, and a movable region of the link member overlaps a rotation region of the first clutch member and the second clutch member. A motor device according to claim 12 or claim 13,
A wiper member connected directly or indirectly to the output shaft and driven by the driving force of the motor body;
Wiper motor with

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