JP5595166B2 - Clutch mechanism, reducer, actuator - Google Patents

Description

  The present invention relates to a clutch mechanism, a reducer, and an actuator suitable for various units of a vehicle.

  Conventionally, when an actuator including an electric motor and a speed reducer is provided in a power window device for a vehicle, the wind speed of the window glass is prevented from rising and lowering due to an input from the wind glass by using the speed reducer normally composed of a worm gear mechanism as a reverse input preventing means. Yes. In order to enhance such a reverse input prevention function, for example, a spacer that generates a friction braking force by contacting a gear case is provided at the end of a worm gear shaft of an actuator (see, for example, Patent Document 1).

JP-A-8-275454

  However, in the above conventional configuration, the drive resistance of the actuator is intentionally generated to ensure the resistance against the reverse input, so that there is a problem that the electric motor (drive source) is prevented from being driven efficiently. .

  Therefore, an object of the present invention is to provide a clutch mechanism, a reduction gear, and an actuator that can enhance a reverse input prevention function without hindering efficient driving of a driving source.

As means for solving the above problems, the invention described in claim 1
An input member and an output member that rotate independently of each other via an engagement means while sharing a rotation axis and rotating separately;
A storage section for storing the input member and the output member;
A shaft provided on the output member in parallel with the rotation axis;
A cam member that is swingably supported by the shaft portion, and engages with the housing portion to lock the rotation of the output member when the output member tries to rotate prior to the input member;
Disengagement means provided on the input member for abutting the cam member and retracting the cam member from an engagement position with the storage portion when the input member tries to rotate prior to the output member; , equipped with a,
An outer engagement portion that engages with the storage portion is provided outside the cam member in the clutch radial direction,
A clutch mechanism is provided in which an inner engagement portion that engages with a central axis in the storage portion is provided on an inner side in the clutch radial direction of the cam member .

In the clutch mechanism, as in the invention described in claim 2, the engaging means includes a concave portion provided in the input member, and a convex portion provided in the output member and engaged with the concave portion. And the convex portion may form the shaft portion.
In the clutch mechanism, as in the invention described in claim 3, a first gap is formed in the circumferential direction of the clutch between the convex portion and the concave portion, and between the cam member and the engagement releasing means. A second gap that is smaller than the first gap in the circumferential direction of the clutch may be formed.
The clutch mechanism may be provided such that a plurality of cam members are arranged in the circumferential direction of the clutch, as in the invention described in claim 4.

In the clutch mechanism, as in the invention described in claim 5 , the insertion hole of the shaft portion of the cam member is formed in an elliptical shape to allow displacement of the cam member in the clutch radial direction. It may be a thing.

The clutch mechanism may include a cam urging unit that urges the cam member to bring the outer engagement portion into contact with the storage portion, as in the invention described in claim 6. .
In the clutch mechanism, as in the invention described in claim 7 , the cam member constitutes a first cam member that restricts the rotation of the output member in the forward rotation direction, and is viewed in the clutch axial direction. The contact point between the first cam member and the storage portion on the outer side in the clutch radial direction is shifted from the clutch radius passing through the shaft center of the shaft portion supporting the first cam member in the forward rotation direction. It may be done.
Further, the clutch mechanism is provided with a plurality of cam members as in the invention described in claim 8 , and a part of each cam member constitutes the first cam member, and each cam member The other part constitutes a second cam member that restricts the rotation of the output member in the other direction, and the storage portion on the outer side in the clutch radial direction of the second cam member in the clutch axial direction view May be arranged so as to be displaced in the other direction with respect to the clutch radius passing through the shaft center of the shaft portion supporting the second cam member.

The invention described in claim 9 is the reduction gear for outputting the worm wheel decelerates the rotational power input to the worm gear shaft, between the worm wheel and the housing part for accommodating this, claims 1 to 8 The clutch mechanism according to any one of the above is configured.
According to a tenth aspect of the present invention, there is provided an actuator used for raising and lowering a door glass of a vehicle, comprising: an electric motor that generates rotational power; and a speed reducer that decelerates and outputs the rotational power input from the electric motor. A clutch mechanism according to any one of claims 1 to 8 is provided between an output gear of the reduction gear and a storage portion for storing the output gear.

According to the first aspect of the present invention, even if the output member tries to rotate prior to the input member, the cam member engages with the storage portion and locks the rotation of the output member.
On the other hand, when the input member tries to rotate prior to the output member, the engagement release means retracts the cam member from the engagement position with the storage portion to release the engagement with the storage portion, and the input member inputs the input member. The output member can be rotated.
In this way, input from the input member to the output member is permitted, but reverse input from the output member to the input member is prohibited, so that the output member can be prevented without hindering efficient driving of a drive source such as an electric motor. Therefore, the effect of preventing the rotation of the input member due to reverse input to the input member can be enhanced.
In addition, since the cam member is swingably supported by the output member, the configuration and assembly can be simplified as compared with the reverse input prevention means in which a roller or the like is disposed between the input member and the output member. Smaller and lighter can be achieved.
Further, the rotation of the output member can be effectively locked on the clutch outer peripheral side.
In addition, the rotation of the output member can be locked even on the inner circumferential side of the clutch, and the braking force on the outer circumferential side of the clutch can be increased by the reaction force from the central axis.

According to the second aspect of the present invention, the cam member can be supported by using the convex portion that engages the input member and the output member so as to be integrally rotatable, thereby further simplifying the configuration.
According to the invention described in claim 3, when inputting rotational power from the input member to the output member, the engagement release means first comes into contact with the cam member and retracts it from the engagement position with the storage portion, Thereafter, the concave portion comes into contact with the convex portion, and rotational power can be input from the input member to the output member, and the output member can be rotated by the rotational power of the input member.
According to the invention described in claim 4, the rotation of the output member can be locked in a balanced manner by the plurality of cam members.

According to the fifth aspect of the present invention, the cam member can be reliably engaged with the storage portion while absorbing the tolerance of the cam member.

According to the sixth aspect of the present invention, the cam member can be kept in contact with the storage portion without any other input, and even if the output member tries to rotate ahead of the input member, the rotation of the output member is prevented. It can be locked without delay.
According to the seventh aspect of the present invention, even if the output member tries to rotate in one direction, the first cam member is stretched between the shaft portion and the storage portion to lock the rotation of the output member in one direction. can do.
According to the invention described in claim 8 , regardless of whether the output member rotates in the forward or reverse direction, the first or second cam member stretches between the shaft portion and the storage portion, so that the output member Forward / reverse rotation can be locked.

According to the ninth aspect of the invention, the function of preventing reverse input from the output unit can be further enhanced in combination with the worm gear mechanism.
According to the tenth aspect of the present invention, when there is a reverse input due to a load on the door glass or its vibration without hindering the door glass from being raised and lowered by driving the electric motor, the door glass is surely raised and lowered. Can be prevented.

It is a perspective view of an actuator in an embodiment of the present invention. It is a disassembled perspective view of the clutch mechanism of the said actuator. It is the arrow view which looked at the said clutch mechanism from the axial direction. FIG. 4 is a partial explanatory diagram of FIG. 3. FIG. 4 is an arrow view corresponding to FIG. 3 when the worm wheel rotates forward prior to the output member. FIG. 4 is an arrow view corresponding to FIG. 3 when the worm wheel is reversed prior to the output member.

Embodiments of the present invention will be described below with reference to the drawings.
An actuator 1 shown in FIG. 1 is used, for example, for raising and lowering a door glass in a power window device of a vehicle, and integrally includes an electric motor 2 and a worm speed reducer 3 connected to the electric motor 2. The worm speed reducer 3 includes a clutch mechanism 4 that will be described in detail later.

  The electric motor 2 includes a bottomed cylindrical yoke 5 and an armature 6 rotatably provided inside the yoke 5. The armature 6 includes a rotating shaft 7, an armature core (not shown) that is externally fixed to the rotating shaft 7, and a commutator (not shown) provided on one end side of the rotating shaft 7. The worm speed reducer 3 is connected to one end side of the rotating shaft 7. A brush holder (not shown) that houses a brush that is in sliding contact with the commutator is housed inside the yoke 5. One end of the rotary shaft 7 is supported by a bearing (not shown) provided in a brush holder (not shown), and the other end is supported by a bearing (not shown) provided in the yoke 5.

  The worm speed reducer 3 includes a casing 11 in which a holder portion 8 that receives one end of the armature 6 and a gear housing portion 10 that houses the worm gear mechanism 9 and the clutch mechanism 4 are integrated. The holder portion 8 is formed in a box shape that opens to the electric motor 2 side, and accommodates a connector 13 that can connect an external power source in the holder portion 8. The electric motor 5 and the casing 11 are integrated by fixing the electric motor 5 and the casing 11 in a state where the connector 13 accommodated in the holder portion 8 is electrically connected to a brush holder (not shown). Is done.

  The gear housing portion 10 of the casing 11 includes a cylindrical worm housing portion 17 that houses the worm gear shaft 15 of the worm gear mechanism 9, a worm wheel 16 of the worm gear mechanism 9 formed integrally with a side of the worm housing portion 17, and the worm gear mechanism 9. And a cup-shaped wheel storage portion 18 for storing the coaxial clutch mechanism 4. The rotating shaft 7 of the electric motor 2 passes through the holder portion 8 and is connected to the worm gear shaft 15 in the worm storage portion 17 so as to be integrally rotatable. The rotational power input from the electric motor 2 to the worm gear shaft 15 is appropriately decelerated and output to the worm wheel 16.

  As shown in FIGS. 2 and 3, a stopper ring 21, a pair of cam biasing springs 22, four cam plates 23, a worm wheel 16 and an output are provided in the wheel storage portion 18 in order from the bottom 18a side (lower side). The member 24 is accommodated. The stopper ring 21, the worm wheel 16 and the output member 24 are coaxial with each other, and the stopper ring 21 and the worm wheel 16 are rotatable on a center shaft 25 erected as a part of the central portion in the wheel storage portion 18. Supported by

  The stopper ring 21 includes an annular ring portion 21a that matches the inner periphery of the wheel storage portion 18 on the bottom portion 18a side, a cylindrical hub portion 21b that matches the outer periphery of the center shaft 25, and the ring portion 21a and the hub portion 21b. A plurality of (six in this embodiment) spoke portions 21c that connect the two are integrally formed. The ring portion 21a is fixed to the wheel storage portion 18 so as to form a part thereof, and the hub portion 21b is fixed to the center shaft 25 so as to form a part thereof.

  The clutch mechanism 4 is mainly configured in the wheel storage portion 18 with the stopper ring 21 (wheel storage portion 18), the cam biasing springs 22, the cam plates 23, the worm wheel 16 and the output member 24. The clutch mechanism 4 permits input from the worm wheel 16 to the output member 24, but prohibits reverse input from the output member 24 to the worm wheel 16. This prevents the worm wheel 16 from rotating when there is a reverse input due to a load on the door glass, vibration thereof, or the like, without hindering the raising and lowering of the door glass by driving the electric motor 2.

  In addition, the line C1 in the figure indicates the center axis of the center shaft 25 (the center axis of the worm wheel 16, the wheel storage portion 18, and the clutch mechanism 4). Hereinafter, the direction along the axis C1 is referred to as a clutch axial direction, the rotation direction around the axis C1 is referred to as a clutch circumferential direction, and the direction orthogonal to the axis C1 is referred to as a clutch radial direction.

  The worm wheel 16 has an insertion hole 16a of the center shaft 25 at the center of rotation and gear teeth 16b at the outer periphery. The clutch radial direction intermediate part (between the rotation center part and the outer peripheral part) of the worm wheel 16 has an upper and lower side that forms an arc shape about the axis C1 and a side side that extends along the clutch radial direction when viewed in the clutch axial direction. A plurality (four in this embodiment) of trapezoidal engagement holes 16c are formed so as to be arranged at equal intervals in the circumferential direction of the clutch.

  Each engagement hole 16c linearly penetrates the clutch radial direction intermediate portion of the worm wheel 16 in parallel with the clutch axial direction. From the upper side in the clutch axial direction of the worm wheel 16 (on the side opposite to the bottom 18a of the wheel storage portion 18), it protrudes toward the lower surface side (the bottom 18a side of the wheel storage portion 18) of the output member 24 corresponding to each engagement hole 16c. The plurality of engaging protrusions 26 provided are respectively inserted. Each engagement protrusion 26 has a substantially trapezoidal shape similar to the cross-sectional shape of the corresponding engagement hole 16c (as viewed in the clutch axial direction), and protrudes linearly in parallel with the clutch axial direction. The output member 24 includes a disc-shaped main body portion 24a coaxial with the worm wheel 16, each engaging protrusion 26 projecting from the lower surface side of the main body portion 24a in the clutch radial direction, and a central portion on the upper surface side of the main body. And an output part 24b that protrudes from the part.

  Each engagement protrusion 26 has a width in the circumferential direction of the clutch (an angle between both sides) smaller than that of the engagement hole 16c, and each of the engagement protrusions 26 is engaged with the corresponding engagement hole 16c. It is loosely fitted with a predetermined play in the circumferential direction. Using each of the engagement holes 16c and the engagement protrusions 26 as engagement means, the individually rotatable worm wheel 16 and the output member 24 can be rotated together, and can be relatively rotated by the amount of play.

  A columnar shaft portion 27 parallel to the axis C <b> 1 is protruded from the tip of each engagement protrusion 26. Each shaft portion 27 protrudes from the lower surface side of the worm wheel 16, and each cam plate 23 is swingably supported by each shaft portion 27. In other words, a plurality of cam plates 23 are arranged in the clutch radial direction intermediate portion of the worm wheel 16 in the clutch circumferential direction.

  Each cam plate 23 has a flat plate shape having a predetermined thickness in the clutch axial direction, and is formed in an approximately elliptical shape when viewed in the clutch axial direction. Each cam plate 23 is provided so that the elliptical long axis is slightly inclined with respect to the clutch radial direction. In this state, the clutch radial outer end of each cam plate 23 contacts the inner peripheral surface of the ring portion 21a, and the clutch radial inner end of each cam plate 23 contacts the outer peripheral surface of the hub portion 21b. Insertion holes 23a through which the shaft portions 27 are inserted are formed in the clutch radial direction intermediate portions of the cam plates 23, respectively.

  Here, among each cam plate 23, one set (hereinafter referred to as the first cam plate 28) arranged at positions symmetrical to each other in the clutch radial direction has a clutch diameter with respect to the inner side in the clutch radial direction. The outer side in the direction is inclined so as to be located downstream of the worm wheel 16 in the forward rotation direction (forward rotation side, indicated by an arrow F in the figure).

  In this configuration, when the worm wheel 16 is input in the forward rotation direction, the outer end of the first cam plate 28 in the clutch radial direction is not engaged with the inner peripheral surface of the ring portion 21a. The normal rotation of the output member 24 accompanying the rotation is allowed. On the other hand, when inputting in the forward direction from the output member 24, the outer end of the first cam plate 28 in the clutch radial direction is engaged with the inner peripheral surface of the ring portion 21a, so that the output member 24 is rotated forward. Lock it.

  On the other hand, in each cam plate 23, another set different from the first cam plate 28 (hereinafter referred to as the second cam plate 29) has a worm wheel on the outer side in the clutch radial direction with respect to the inner side in the clutch radial direction. It is inclined and arranged so as to be located downstream of the sixteen reverse direction (reverse side, indicated by arrow B in the figure).

  In this configuration, at the time of input from the worm wheel 16 in the reverse direction, the outer end in the clutch radial direction of the second cam plate 29 is not engaged with the inner peripheral surface of the ring portion 21a, so that the worm wheel 16 is reversely rotated. The reverse rotation of the accompanying output member 24 is permitted. On the other hand, when inputting from the output member 24 in the reverse rotation direction, the clutch radial outer end of the second cam plate 29 is engaged with the inner peripheral surface of the ring portion 21a, thereby locking the reverse rotation of the output member 24. .

  Each cam plate 23 is swingably supported by each shaft portion 27 on the distal end side (the bottom portion 18a side of the wheel storage portion 18) of each engagement projection 26. For example, each engagement projection 26 The base end side (the open side of the wheel storage portion 18) may be swingably supported by each engagement protrusion 26 or the like. In this case, the stopper ring 21 (ring part 21 a) is also fixed to the open side of the wheel storage part 18.

  Referring to FIG. 3, an outer engagement surface 23 b having an arc shape smaller in diameter than the inner peripheral surface of the ring portion 21 a when viewed in the clutch axial direction is formed on the outer side in the clutch radial direction of each cam plate 23. Thereby, the outer end in the clutch radial direction of each cam plate 23 is in line contact with the inner peripheral surface of the ring portion 21a through a line segment parallel to the clutch axial direction. Hereinafter, the contact point between each cam plate 23 and the ring portion 21a when viewed in the clutch axial direction is indicated by a symbol t.

Further, on the inner side of each cam plate 23 in the radial direction of the clutch, an inner engagement surface 23c having a circular arc shape in the clutch axial direction that can be engaged with the outer peripheral surface of the hub portion 21b is formed.
Here, the insertion hole 23a of each cam plate 23 has an elliptical shape that is long in the clutch radial direction, and each cam plate 23 can be displaced by a predetermined amount in the clutch radial direction. Thus, each cam plate 23 can reliably engage the outer engagement surface 23b with the inner peripheral surface of the ring portion 21a and the inner engagement surface 23c with the outer peripheral surface of the hub portion 21b.

  Between the forward rotation side edge portion 28a of the first cam plate 28 and the reverse rotation side edge portion 29a adjacent to the forward rotation side edge portion 28a of the second cam plate 29, these respective edge portions 28a, 29a. The cam urging spring 22 is urged to urge the cams toward the sides that are separated from each other in the circumferential direction of the clutch.

  The cam biasing spring 22 is configured as a torsion coil spring, and the coil portion is supported by the support pin 16 d rising from the worm wheel 16, and one of the coil end portions is the forward rotation side of the first cam plate 28. The other side comes into contact with the edge portion 28 a and presses against the reverse side edge portion 29 a of the second cam plate 29.

  The pressing force applied to each cam plate 23 by the cam biasing spring 22 is the same, and if there is no other input to the worm wheel 16 and the output member 24, the shaft portion 27 that engages with each other via each cam plate 23. And the engagement protrusion 26 is arrange | positioned in the center position of the clutch circumferential direction of the corresponding engagement hole 16c. At this time, the both sides of each engagement hole 16c and the both sides of each engagement projection 26 are separated by an angle s1 about the center of the axis C1 (see FIG. 4). Hereinafter, the gap corresponding to the angle s1 is referred to as a first gap s1.

  By this cam biasing spring 22, the first cam plate 28 is moved to the side where the outer side in the clutch radial direction is moved in the reverse direction of the axis C1 (the side where the outer engagement surface 23b is brought into contact with the inner peripheral surface of the ring portion 21a). The second cam plate 29 is moved to the side where the outer side in the clutch radial direction is moved in the forward rotation direction about the axis C1 (the side where the outer engagement surface 23b is brought into contact with the inner peripheral surface of the ring portion 21a). ) Energized.

  A forward rotation disengagement pin 16e that stands up from the worm wheel 16 can be brought into contact with the reverse rotation side end of the first cam plate 28 in the clutch radial direction, and the second cam plate 29 in the clutch radial direction. A reverse rotation release pin 16f that also stands up from the worm wheel 16 can come into contact with the outer forward rotation side end.

  The first cam plate 28 and the forward engagement release pin 16e, and the second cam plate 29 and the reverse engagement release pin 16f are separated from each other by an angle s2 about the center of the axis C1 (see FIG. 4). . Hereinafter, the gap corresponding to the angle s2 is referred to as a second gap s2. The second gap (angle) s2 is set smaller than the first gap (angle) s1.

  In the state in which the first and second gaps s1, s2 are formed, the contact t between the first cam plate 28 and the ring portion 21a passes through the shaft center C2 of the shaft portion 27 corresponding to each cam plate 28. The clutch radius r is shifted to the forward rotation side.

  Similarly, in the state in which the first and second gaps s1 and s2 are formed, the contact t between the second cam plate 29 and the ring portion 21a is the axial center of the shaft portion 27 corresponding to each cam plate 29. The clutch radius r passing through C2 is shifted to the reverse side.

  The angle formed by connecting the contact point t of the first cam plate 28, the shaft center C2 of each shaft portion 27 corresponding to each cam plate 23, and the axis C1 in the clutch axial direction is a flat angle (180 degrees). The obtuse angle close to). For this reason, when the output member 24 tries to rotate forward with respect to the worm wheel 16, the first cam plate 28 tends to swing due to friction between the outer engagement surface 23b and the inner peripheral surface of the ring portion 21a. The outer engagement surface 23b is strongly pressed against the inner peripheral surface of the ring portion 21a. The forward rotation of the output member 24 is limited by such a stretching effect (wedge effect) of the cam plate 23.

  Similarly, the angle formed by connecting the contact t of the second cam plate 29 and the shaft center C2 and the axis C1 of the shaft portion 27 corresponding to the cam plate 23 in the clutch axial direction is a flat angle (180 degrees). The obtuse angle close to). For this reason, when the output member 24 tries to reversely rotate with respect to the worm wheel 16, the second cam plate 29 tries to swing due to the friction of contact between the outer engagement surface 23b and the inner peripheral surface of the ring portion 21a. The engaging surface 23b is strongly pressed against the inner peripheral surface of the ring portion 21a. The reverse rotation of the output member 24 is limited by such a stretching effect (wedge effect) of the cam plate 23.

  In the above-described configuration, if there is no input other than the cam biasing spring 22 to the worm wheel 16 and the output member 24, each cam plate 23 is biased by each cam biasing spring 22, and the outer engagement surface 23b is connected to the ring portion 21a. It is made to contact the inner peripheral surface. From this state, even if the output member 24 tries to rotate forward and backward prior to the worm wheel 16 (even if it tries to reversely input rotational power from the output member 24 to the clutch mechanism 4), due to the tension effect of each cam plate 23 described above, The forward / reverse rotation of the output member 24 is restricted.

  On the other hand, even when the rotation of the output member 24 is restricted as described above, the worm wheel 16 can rotate forward and backward with respect to the output member 24 by the first gap s1.

  First, referring to FIG. 5, when the worm wheel 16 rotates forward prior to the output member 24 (when normal rotation power is input from the worm wheel 16 to the clutch mechanism 4), the second gap s <b> 2 is greater than the first gap s <b> 1. Therefore, before the side portions of the engagement holes 16c and the side portions of the engagement protrusions 26 abut each other, the engagement release pin 16e at the time of forward rotation comes into contact with the first cam plate 28. Is pivoted about the shaft 27.

  Then, the outer engagement surface 23b of the cam plate 23 is retracted from the engagement position with the inner peripheral surface of the ring portion 21a (the wheel storage portion 18), and a gap s3 is formed therebetween. That is, the forward rotation restriction of the output member 24 by the cam plate 23 is released.

  Thereafter, the worm wheel 16 further rotates in the forward direction, and the side portions of the engagement holes 16c and the side portions of the engagement protrusions 26 abut each other, whereby the normal rotation power of the worm wheel 16 is transmitted to the output member 24. Thus, the output member 24 rotates in the normal direction as the worm wheel 16 rotates in the normal direction.

  At this time, the second cam plate 29 brings its outer engagement surface 23b into contact with the inner peripheral surface of the ring portion 21a. Even if the cam plate 23 swings due to friction of this contact, the cam plate 23 Since the outer engagement surface 23b of the plate 23 and the inner peripheral surface of the ring portion 21a are separated from each other, the cam plate 23 only slides on the ring portion 21a and does not lock the forward rotation of the output member 24. .

  Next, referring to FIG. 6, when the worm wheel 16 is reversely rotated prior to the output member 24 (when reverse rotation power is input from the worm wheel 16 to the output member 24), the side portion of each engagement hole 16 c and each engagement protrusion Before the side portion of the portion 26 abuts against each other, the reverse engagement release pin 16f abuts against the second cam plate 29 and swings about the shaft portion 27.

  Then, the outer engagement surface 23b of the cam plate 23 is retracted from the engagement position with the inner peripheral surface of the ring portion 21a (the wheel storage portion 18), and a gap s3 is formed therebetween. That is, the limitation on the reverse rotation of the output member 24 by the cam plate 23 is released.

  Thereafter, the worm wheel 16 is further reversely rotated, and the side portions of the engagement holes 16c and the side portions of the engagement protrusions 26 abut each other, whereby the reverse rotation power of the worm wheel 16 can be transmitted to the output member 24. As the worm wheel 16 is reversed, the output member 24 is reversed.

  At this time, the first cam plate 28 is merely in sliding contact with the ring portion 21a, and the reverse rotation of the output member 24 is not locked.

  As described above, at the time of input to the clutch mechanism 4 by forward / reverse rotation of the worm wheel 16, it becomes possible to transmit rotational power to the output member 24 in both forward and reverse rotations. At the time of input to the mechanism 4, transmission of rotational power to the worm wheel 16 becomes impossible due to the biting effect of the one set or the second cam plate 23 in either the forward or reverse direction.

  For this reason, it is not necessary to intentionally generate the driving resistance of the actuator 1, etc., and even when external force is applied to the door glass or when vibration during traveling acts on the output member 24, rotational power is reversely input to the output member 24. This reverse input can be prevented from reaching the worm gear shaft 15 and the electric motor 2.

  As described above, the clutch mechanism 4 in the above embodiment shares the rotation axis C1 and rotates separately, while the worm wheel 16 and the output member 24 that can rotate integrally with each other via the engaging means, and the worm A wheel housing portion 18 for housing the wheel 16 and the output member 24, a shaft portion 27 provided on the output member 24 in parallel with the rotation axis C 1, and a swingable support on the shaft portion 27, and the output member 24. Is provided on the worm wheel 16 and the cam plate 23 that engages with the wheel storage portion 18 to lock the rotation of the output member 24 when the worm wheel 16 is to rotate before the worm wheel 16. When it is going to rotate prior to the output member 24, it comes into contact with the cam plate 23 and this cam Disengagement pin 16e to retract the door 23 from the engagement position between the wheel housing portion 18, but comprising a 16f, a.

According to this configuration, even if the output member 24 attempts to rotate ahead of the worm wheel 16, the cam plate 23 engages with the wheel storage portion 18 to lock the rotation of the output member 24.
On the other hand, when the worm wheel 16 tries to rotate before the output member 24, the disengagement pins 16e and 16f retract the cam plate 23 from the engagement position with the wheel storage portion 18 to engage with the wheel storage portion 18. And the output member 24 can be rotated by the input to the worm wheel 16.
As described above, the input from the worm wheel 16 to the output member 24 is permitted, while the reverse input from the output member 24 to the worm wheel 16 is prohibited, thereby preventing efficient driving of the drive source such as the electric motor 2. The effect of preventing the rotation of the worm wheel 16 due to the reverse input from the output member 24 to the worm wheel 16 can be enhanced.
Further, since the cam plate 23 is swingably supported by the output member 24, the configuration and assembly can be simplified as compared with the reverse input prevention means in which a roller or the like is disposed between the worm wheel 16 and the output member 24. Thus, cost reduction and reduction in size and weight can be achieved.

  The clutch mechanism 4 includes an engaging hole 16c provided in the worm wheel 16 and an engaging protrusion 26 provided in the output member 24 and engaged with the engaging hole 16c. And the engaging projection 26 forms the shaft portion 27, so that the cam plate 23 is engaged with the engaging projection 26 that engages the worm wheel 16 and the output member 24 so as to be integrally rotatable. It becomes possible to support, and further simplification of the configuration can be achieved.

  Further, in the clutch mechanism 4, a first gap s1 is formed in the circumferential direction of the clutch between the engagement protrusion 26 and the engagement hole 16c, and between the cam plate 23 and the engagement release pins 16e and 16f. In addition, since the second gap s2 smaller than the first gap s1 is formed in the clutch circumferential direction, when the rotational power is input from the worm wheel 16 to the output member 24, first, the disengagement pins 16e, 16f comes into contact with the cam plate 23 and retreats it from the engagement position with the wheel storage portion 18, and then the engagement hole 16c comes into contact with the engagement projection 26 to rotate from the worm wheel 16 to the output member 24. Can be input, and the output member 24 can be rotated by the rotational power of the worm wheel 16.

  The clutch mechanism 4 is provided with a plurality of cam plates 23 arranged in the circumferential direction of the clutch, so that the rotation of the output member 24 can be locked in a balanced manner by the plurality of cam plates 23.

  Further, the clutch mechanism 4 is provided with an outer engagement surface 23b that engages with the wheel storage portion 18 on the outer side in the clutch radial direction of the cam plate 23, so that the output member 24 is effectively provided on the outer periphery side of the clutch. You can lock the rotation.

  Further, the clutch mechanism 4 is provided with an inner engagement surface 23c that engages with the center shaft 25 in the wheel storage portion 18 on the inner side in the clutch radial direction of the cam plate 23, so that the clutch mechanism 4 also outputs on the inner peripheral side of the clutch. The rotation of the member 24 can be locked, and the braking force on the clutch outer peripheral side can be increased by the reaction force from the center shaft 25.

  Further, in the clutch mechanism 4, the cam plate 23 has an insertion hole 23a of the shaft portion 27 formed in an elliptical shape so as to allow displacement of the cam plate 23 in the clutch radial direction. Thus, the cam plate 23 can be reliably engaged with the wheel storage portion 18 while absorbing the tolerance.

  Further, the clutch mechanism 4 includes a cam biasing spring 22 that biases the cam plate 23 so as to bring the outer engagement surface 23b into contact with the wheel storage portion 18, and if there is no other input, the cam plate 23 can always be brought into contact with the wheel storage portion 18, and even if the output member 24 tries to rotate before the worm wheel 16, the rotation of the output member 24 can be locked without delay.

  In the clutch mechanism 4, the cam plate 23 constitutes a first cam plate 28 that restricts the rotation of the output member 24 in the forward rotation direction, and restricts the rotation of the output member 24 in the reverse rotation direction. The second cam plate 29 is configured, and the contact point t with the wheel storage portion 18 on the outer side in the clutch radial direction of the first cam plate 28 as viewed in the clutch axial direction causes the first cam plate 28 to Disposed in the forward rotation direction with respect to the clutch radius r passing through the shaft center C2 of the shaft portion 27 to be supported, and contacts with the wheel storage portion 18 on the outer side in the clutch radial direction of the second cam plate 29 t is arranged so as to be shifted in the reverse rotation direction from the clutch radius r passing through the shaft center C2 of the shaft portion 27 supporting the second cam plate 29.

  According to this configuration, even if the output member 24 tries to rotate in the forward rotation direction, the first cam plate 28 is stretched between the shaft portion 27 and the wheel storage portion 18, so that the output member 24 is rotated in the forward rotation direction. Rotation can be locked. Similarly, even when the output member 24 tries to rotate in the reverse direction, the second cam plate 29 is stretched between the shaft portion 27 and the wheel storage portion 18 to lock the rotation of the output member 24 in the reverse direction. Can do.

  Further, the worm speed reducer 3 in the above-described embodiment decelerates the rotational power input to the worm gear shaft 15 and outputs it to the worm wheel 16, and between the worm wheel 16 and the wheel storage portion 18 for storing it. In addition, the clutch mechanism 4 is configured.

  According to this configuration, the function of preventing reverse input from the output unit can be further enhanced in combination with the worm gear mechanism 9.

  The actuator 1 in the above embodiment includes an electric motor 2 that generates rotational power and a worm speed reducer 3 that decelerates and outputs the rotational power input from the electric motor 2, and moves up and down the door glass of the vehicle. The clutch mechanism 4 is configured between the output gear (worm wheel 16) in the worm reduction gear 3 and a storage portion (wheel storage portion 18) for storing it.

  According to this configuration, when there is a reverse input due to a load on the door glass, vibration thereof, or the like without hindering the raising and lowering of the door glass by driving the electric motor 2, the door glass can be reliably prevented from rising and lowering. Can do.

  Note that the present invention is not limited to the above-described embodiment. For example, the clutch mechanism 4 can be applied to an actuator other than an actuator for raising and lowering a door glass and a worm speed reducer. Needless to say, it is possible to make changes.

DESCRIPTION OF SYMBOLS 1 Actuator 2 Electric motor 3 Worm reduction gear (reduction gear)
4 Clutch mechanism 15 Worm gear shaft 16 Worm wheel (input member, output gear)
16c engagement hole (concave)
16e Disengagement pin at normal rotation (disengagement means)
16f Reverse release engagement release pin (disengagement means)
18 Wheel storage (storage)
22 Cam biasing spring (cam biasing means)
23 Cam plate (cam member)
23a Insertion hole 23b Outer engagement surface (outer engagement portion)
23c Inner engagement surface (inner engagement portion)
24 Output member 25 Center shaft 26 Engaging protrusion (convex)
27 Shaft 28 First cam plate (first cam member)
29 Second cam plate (second cam member)
C1 axis of rotation C2 axis center s1 first gap s2 second gap t contact r clutch radius

Claims (10)

An input member and an output member that rotate independently of each other via an engagement means while sharing a rotation axis and rotating separately;
A storage section for storing the input member and the output member;
A shaft provided on the output member in parallel with the rotation axis;
A cam member that is swingably supported by the shaft portion, and engages with the housing portion to lock the rotation of the output member when the output member tries to rotate prior to the input member;
Disengagement means provided on the input member for abutting the cam member and retracting the cam member from an engagement position with the storage portion when the input member tries to rotate prior to the output member; , equipped with a,
An outer engagement portion that engages with the storage portion is provided outside the cam member in the clutch radial direction,
A clutch mechanism in which an inner engagement portion that engages with a central axis in the storage portion is provided on the inner side in the clutch radial direction of the cam member .   The engaging means has a concave portion provided in the input member and a convex portion provided in the output member and engaged with the concave portion, and the convex portion forms the shaft portion. The clutch mechanism according to claim 1.   A first clearance is formed in the clutch circumferential direction between the convex portion and the concave portion, and a second clearance smaller than the first clearance in the clutch circumferential direction is formed between the cam member and the engagement releasing means. The clutch mechanism according to claim 2, wherein the clutch mechanism is formed.   The clutch mechanism according to any one of claims 1 to 3, wherein a plurality of the cam members are arranged in a circumferential direction of the clutch. The insertion hole of the said shaft part in the said cam member is formed in an elliptical shape in order to allow the displacement in the clutch radial direction of this cam member, The any one of Claim 1 to 4 characterized by the above-mentioned. Clutch mechanism. 6. The clutch mechanism according to claim 1, further comprising a cam urging unit that urges the cam member to bring the outer engagement portion into contact with the storage portion. The cam member constitutes a first cam member that restricts rotation of the output member in the forward rotation direction, and the storage portion on the outer side in the clutch radial direction of the first cam member when viewed in the clutch axial direction; the contacts, to any one of claims 1 to 6, than the clutch radius being disposed offset in the forward direction through the axial center of the shaft portion for supporting said first cam member The clutch mechanism described. A plurality of the cam members are provided, and a part of each of the cam members constitutes the first cam member, and the other part of the cam members regulates the rotation of the output member in the other direction. The shaft of the shaft portion that constitutes the second cam member, and that the contact point with the storage portion on the outer side in the clutch radial direction of the second cam member supports the second cam member when viewed in the clutch axial direction. The clutch mechanism according to claim 7 , wherein the clutch mechanism is arranged to be shifted in the other direction from a clutch radius passing through a center. In the reducer that decelerates the rotational power input to the worm gear shaft and outputs it to the worm wheel.
The speed reducer according to any one of claims 1 to 8, wherein the clutch mechanism according to any one of claims 1 to 8 is configured between the worm wheel and a storage portion that stores the worm wheel. In an actuator that includes an electric motor that generates rotational power and a speed reducer that decelerates and outputs rotational power input from the electric motor.
The actuator according to any one of claims 1 to 8, wherein the clutch mechanism according to any one of claims 1 to 8 is configured between an output gear in the speed reducer and a storage portion for storing the output gear.

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