JP2008169911A - Bidirectional clutch and wind direction adjuster - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve response of transmission of rotary torque in a bidirectional clutch. <P>SOLUTION: A drive-side rotor 4 having a cam surface, an interlock-side rotor 5 having a circumference surface, and a retainer 7 are rotatably supported to a center shaft 3. The retainer 7 holds engagement pieces 6 housed in a wedge-shaped space between the cam surface and the circumference surface. A friction holding means 8 holds the retainer 7 with respect to the center shaft 3 by predetermined frictional holding force allowing the retainer 7 to rotate along with the drive-side rotor 4 and the interlock-side rotor 5 connected by the engagement pieces 6 in a wedge engagement state, and regulating rotation of the retainer 7 along with the drive-side rotor 4 or the interlock-side rotor 5 through the engagement pieces 6 in a non-engagement state. A positioning means 9 circumferentially positions and holds the retainer 7 with respect to the drive-side rotor 4 to bring the engagement pieces 6 in to a non-engagement state, and allows the retainer 7 held to the center shaft 3 by the friction holding means 8 to be relatively rotated with respect to the drive-side rotor 4 to bring the engagement pieces 6 into a wedge engagement state when the drive-side rotor 4 rotates. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a bidirectional clutch and a wind direction adjusting device, and more specifically, while transmitting rotational torque in both the forward and reverse directions from a driving side rotating body to an interlocking side rotating body, The present invention relates to a bidirectional clutch that blocks torque transmission in both the forward direction and the reverse direction, and a wind direction adjusting device that includes the bidirectional clutch.

  Among wind direction adjusting devices used in automobile air conditioners, there is a device (swing register) that can swing a swing fin automatically and continuously change the wind direction. The swing fin in this kind of wind direction adjusting device is driven by a driving source such as a stepping motor to swing. However, even in such a swing register that can automatically adjust the wind direction, it is desirable that the passenger can manually change the wind direction according to the sense at that time. However, the swing fins in the swing register are connected to the drive source. For this reason, when the passenger manually moves the swing fin, a load is applied to the drive source. Further, since there is resistance based on the connection structure with the drive source, the operation feeling during manual operation is not so good.

  Therefore, a swing register having a bidirectional clutch is known as a swing register that does not apply a load to the drive source during manual operation and also has improved operational feeling (see Patent Document 1, etc.).

In the two-way clutch in this swing register, the drive cylinder connected to the drive source and the interlocking cylinder connected to the swing fin are pressed and connected by two large and small coil springs wound in opposite directions. Yes. Then, when the driving cylinder portion is rotated by the rotational driving force from the driving source in the automatic mode, the rotational torque in both the forward and reverse directions is transmitted from the driving cylinder portion to the interlocking cylinder portion through the tightening by the reduced diameter of the coil spring. The swing fin swings. On the other hand, when the swing fin is moved by manual operation of the operation knob, etc., the rotational force is transmitted from the swing fin to the interlocking cylinder part, and the interlocking cylinder part rotates. Torque transmission in both forward and reverse directions from the cylinder part to the drive cylinder part is interrupted.
Japanese Patent Laid-Open No. 2003-130083

  However, the conventional bi-directional clutch in the conventional swing register has a problem that the response of torque transmission is low.

  That is, in the above-described conventional bidirectional clutch, rotational torque is transmitted due to the reduced diameter of the coil spring. Therefore, when the diameter of the coil spring is reduced, it slips between the coil spring and the drive cylinder portion and the interlocking cylinder portion. If this occurs, the responsiveness of transmission of the rotational torque is deteriorated accordingly.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to improve the response of rotational torque transmission in a bidirectional clutch.

  (1) A bidirectional clutch of the present invention that solves the above-described problem is a center shaft, a drive-side rotating body that is rotatably supported by the center shaft, has a cam surface, and is rotatably supported by the center shaft. The interlocking-side rotating body having a circumferential surface facing the cam surface in the radial direction, and both circumferential ends formed between the cam surface and the circumferential surface are accommodated in a narrow wedge-shaped space, By moving from the circumferential center of the wedge-shaped space to the circumferential end, the drive-side rotator and the interlocking-side rotator are in a wedge-engaged state, while the wedge-shaped space is circumferentially centered from the circumferential end. Is disposed between the driving side rotating body and the interlocking side rotating body, and is relatively rotatable with both the driving side rotating body and the interlocking side rotating body. The center shaft is rotatably supported so that A retainer having a retaining hole for retaining a child in a cylindrical peripheral wall, and the retainer together with the driving side rotating body and the interlocking side rotating body integrally coupled via the engaging element in the wedge engagement state Is allowed to rotate integrally and restricts the cage from rotating with the driving side rotating body or the interlocking side rotating body via the engaging element in the non-engaged state. The friction holding means that holds the cage with respect to the center shaft with the friction holding force of the drive, and the drive so that the engagement element held in the holding hole of the cage is in the disengaged state. The retainer is positioned and held in the circumferential direction with respect to the side rotating body, and when the driving side rotating body rotates, the engagement element changes from the non-engaged state to the wedge engaged state according to the rotation. The center shaft with the friction holding force of the friction holding means Retained the cage is characterized in that it comprises a positioning means for allowing the relative rotation with respect to the driving-side rotator.

  The bidirectional clutch of the present invention transmits rotational torque in both the forward direction and the reverse direction from the driving side rotating body to the interlocking side rotating body by wedge-engaging the driving side rotating body and the interlocking side rotating body with the engagement element. On the other hand, by releasing the wedge engagement, torque transmission is interrupted from the interlocking side rotating body to the driving side rotating body in both the forward and reverse directions.

  In the bidirectional clutch according to the present invention, the driving side rotating body, the interlocking side rotating body, and the retainer that is disposed between the two and holds the engaging element are rotatably supported on the center shaft.

  The cage is held against the center shaft with a predetermined friction holding force by the friction holding means. The friction holding force of the friction holding means allows the cage to rotate integrally with the driving side rotating body and the interlocking side rotating body integrally coupled via the engagement element in the wedge engagement state, And it is the thing of the predetermined magnitude | size which can control that a holder | retainer rotates with a drive side rotary body or a interlocking side rotary body via the engagement element in a non-engagement state.

  The retainer is positioned by the positioning means so that the engagement element held in the retention hole of the retainer is disengaged, that is, the engagement element is positioned at a neutral position in the center in the circumferential direction of the wedge-shaped space. The positioning is performed in the circumferential direction with respect to the driving side rotating body. However, in this positioning means, when the driving side rotating body rotates, the engaging element moves to the engaging position of the circumferential end portion in the circumferential central portion of the wedge-shaped space according to the rotation and disengages. The cage held by the center shaft by the friction holding force of the friction holding means is allowed to rotate relative to the driving side rotating body so that the wedge engagement state is brought about from the state.

  Therefore, when a rotational driving force is input from the driving source to the driving side rotating body and the driving side rotating body rotates, for example, in the forward direction, the cage held by the center shaft by the friction holding force of the friction holding means rotates on the driving side. Rotates relative to the body. That is, the cage held on the center shaft by the predetermined friction holding force of the friction holding means does not rotate, and only the driving side rotating body rotates. As a result, the engagement element held in the holding hole of the cage moves from the circumferential center of the wedge-shaped space to the circumferential end, and enters the wedge-engaged state with the driving side rotating body and the interlocking side rotating body. As a result, the drive-side rotator and the interlocking-side rotator are integrally coupled via the engagement element, and the rotational torque of the drive-side rotator is transmitted to the interlocking-side rotator. Accordingly, the driving side rotating body, the interlocking side rotating body, the engagement element, the cage, and the like rotate integrally. The same effect occurs when the drive-side rotating body rotates in the reverse direction.

  Here, in the bidirectional clutch of the present invention, the cage does not rotate even if the drive side rotator rotates, so if the drive side rotator rotates, the drive side rotator and the cage simultaneously rotate relative to each other. . Therefore, the movement from the neutral position (circumferential center of the wedge-shaped space) to the engagement position (circumferential end of the wedge-shaped space) when the drive-side rotator rotates is the rotation of the drive-side rotator. At the same time, the engaging element quickly enters the wedge engaging state from the non-engaging state. Therefore, the rotational torque is quickly transmitted from the driving side rotating body to the interlocking side rotating body, and the response of torque transmission from the driving side rotating body to the interlocking side rotating body is improved.

  On the other hand, when the interlocking-side rotating body rotates, for example, in the positive direction, when the non-engaged engagement element is in contact with the circumferential surface of the interlocking-side rotating body, The rotational force of the interlocking rotating body is transmitted to the engaging element by the frictional force, and the engaging element tries to move in the circumferential direction. However, the cage that holds the engaging element does not rotate because it is held with a predetermined friction holding force with respect to the center shaft. In addition, when the engaging element in the disengaged state is not in contact with the circumferential surface of the interlocking-side rotating body, the rotational force of the interlocking-side rotating body is not transmitted to the engaging element, so that the engaging element tries to move in the circumferential direction. There is no need to do. For this reason, even if the interlocking-side rotating body rotates, the cage does not rotate with it, and the engaging element held by the cage does not move from the circumferential center of the wedge-shaped space to the circumferential end. The disengaged state is maintained. Therefore, the rotational torque is not transmitted from the interlocking side rotating body to the driving side rotating body. The same effect occurs when the drive-side rotating body rotates in the reverse direction.

  (2) In a preferred aspect of the bidirectional clutch of the present invention, the friction holding means has elasticity that exerts the friction holding force.

  That is, it is preferable that the friction holding means that holds the cage with a predetermined friction holding force with respect to the center shaft exhibits a predetermined friction holding force by elasticity. For example, by adjusting the fitting allowance between the fitting convex part and the fitting concave part (fitting hole), the friction holding force can be exerted using the frictional force in the concave and convex fitting part. It is difficult to adjust the fitting allowance for making the holding force a predetermined magnitude. In that respect, if the predetermined friction holding force is exerted by the elasticity of the friction holding means, for example, it can be easily adjusted to the predetermined friction holding force as compared with the adjustment of the fitting allowance in the uneven fitting portion. Can do.

  (3) In a preferred aspect of the bidirectional clutch of the present invention, the friction holding means is integrally formed on the disc portion fixed or integrally formed with the center shaft and the outer peripheral surface of the disc portion, and the holding And an elastically deformable curved arm that is in contact with the inner peripheral surface of the cylindrical peripheral wall of the container in an elastically deformed state.

  According to this configuration, the elasticity of the curved arm can be easily changed by changing the shape, size, material, etc. of the curved arm that can be elastically deformed. It is possible to adjust to a predetermined one.

  In addition, when the disk portion integrally formed with the curved arm portion is integrally formed with the center shaft, it is not necessary to separately provide a friction holding means such as a spring member, so that the structure is simplified and the number of parts is reduced. be able to.

  (4) Furthermore, it is preferable that the said curved arm part has a projection part which protruded in the centrifugal direction from this curved arm part and contact | abutted to the internal peripheral surface of the said cylindrical surrounding wall of the said holder | retainer.

  According to this configuration, since the protruding portion of the curved arm portion comes into contact with the inner peripheral surface of the cylindrical peripheral wall of the cage, the contact area between the curved arm portion and the inner peripheral surface of the cage is reduced. . For this reason, when the rotational torque is transmitted from the driving side rotating body to the interlocking side rotating body via the engagement element, and the driving side rotating body, the interlocking side rotating body, the cage and the like rotate integrally, Sliding resistance due to contact with the arm is reduced. Therefore, the rotational driving force for rotationally driving the drive side rotator can be reduced, and the load on the drive source can be reduced.

  (5) In a preferred aspect of the bidirectional clutch of the present invention, the positioning means comprises a spring interposed between the drive side rotator and the cage.

  That is, it is preferable that the positioning means for adjusting the relative positional relationship in the circumferential direction of the cage with respect to the drive side rotator comprises a spring interposed between the drive side rotator and the cage. The spring force can be easily adjusted by changing the shape, size, material, and the like of the spring. For this reason, according to the configuration in which a spring such as a leaf spring is interposed between the driving side rotating body and the cage, the spring force of the spring is adjusted in relation to the magnitude of the friction holding force in the friction holding means. Becomes easy.

  (6) The wind direction adjusting apparatus according to claim 6, wherein the driving side rotating body is connected to a driving source and the interlocking side rotating body is connected to a swing fin. The bi-directional clutch described above is provided.

  That is, the bidirectional clutch of the present invention can be used by being incorporated in a wind direction adjusting device in a preferred embodiment. The wind direction adjusting device needs to transmit torque from the driving side to the interlocking side in the automatic mode, and to block the torque from the interlocking side to the driving side in the manual mode. For this reason, when the bidirectional clutch of the present invention, which is excellent in speediness during torque transmission, is used in the wind direction adjusting device, the response of torque transmission in the automatic mode is improved.

  According to the present invention, it is possible to provide a bidirectional clutch and a wind direction adjusting device with improved torque transmission responsiveness.

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

  First, the configuration of the bidirectional clutch according to the present embodiment will be described. FIG. 1 shows an exploded perspective view of a bidirectional clutch according to this embodiment. FIG. 2 shows an axial sectional view of this bidirectional clutch. As shown in the drawing, the bidirectional clutch 1 according to the present embodiment includes a mounting seat 2, a center shaft 3, a driving side rotating body 4, a interlocking side rotating body 5, five engaging elements 6, and a holding member. A container 7, a friction holding means 8, and a positioning means 9 are provided.

  The mounting seat 2 is a POM integral molded product having a U-shaped cross-sectional shape, and is a side wall that connects a pair of plate portions 20, 20 facing each other and ends of both plate portions 20, 20. Part 21. The pair of plate portions 20 and 20 are provided with a pair of fitting holes 200 and 200 and a pair of cylindrical seat portions 201 and 201 at positions facing each other.

  The center shaft 3 is an integrally molded product made of POM, and includes a shaft portion 30 and a disk portion 31 that is integrally formed at a substantially central portion of the shaft portion 30. The disc part 31 may be fitted and fixed to the shaft part 30 of the center shaft 3. The shaft portion 30 of the center shaft 3 is fitted and fixed in the fitting holes 200 and 200 of the mounting seat. Thereby, the center shaft 3 is held by the mounting seat 2 so as not to rotate. On the outer peripheral surface of the disc portion 31 of the center shaft 3, three elastically deformable curved arm portions 32, 32, 32 extending in an arc shape with a space from the outer periphery of the disc portion 31 are integrally formed. . In addition, a protruding portion 320 that protrudes in the centrifugal direction and abuts on an inner peripheral surface of a cylindrical peripheral wall portion 71 (described later) of the cage 7 is integrated with the tip of each curved arm portion 32.

  The drive-side rotator 4 is an integrally molded product made of POM, and is rotatably supported on one end side (the upper end side in FIG. 2) of the shaft portion 30 of the center shaft 3. The drive side rotating body 4 has a drive side gear portion 40 and a drive side cylindrical portion 41. A driving side insertion hole 400 through which one end side of the shaft portion 30 of the center shaft 3 is inserted is formed at the center of the driving side gear portion 40. Further, drive teeth 401 are formed on the periphery of the drive side gear unit 40. Five cam surfaces 410 are formed at equal intervals in the circumferential direction on the inner peripheral surface of the drive side cylindrical portion 41 (see FIGS. 3 to 5). Each cam surface 410 has a substantially U-shaped cross-sectional shape and extends in the entire axial direction of the drive side cylindrical portion 41. Further, a mounting insertion hole 411 that penetrates in the thickness direction of the drive side cylindrical portion 41 is formed between the two cam surfaces 410 and 410 on the distal end side (lower end side in FIG. 2) of the drive side cylindrical portion 41. (See FIG. 4).

  The interlocking-side rotating body 5 is an integrally molded product made of POM and is rotatably supported on the other end side (lower end side in FIG. 2) of the shaft portion 30 of the center shaft 3. The interlocking side rotating body 5 includes an interlocking side gear portion 50 and an interlocking side cylindrical portion 51. An interlocking side insertion hole 500 through which the other end side of the shaft portion 30 of the center shaft 3 is inserted is formed at the center of the interlocking side gear portion 50. Further, interlocking teeth 501 are formed on the peripheral edge of the interlocking gear portion 50. The interlocking-side cylindrical portion 51 has an outer diameter that is a predetermined amount smaller than the inner diameter of the driving-side cylindrical portion 41, and faces the distal end side of the driving-side cylindrical portion 41 in the radial direction. For this reason, the outer peripheral surface of the interlocking side cylindrical portion 51 is a circumferential surface 510 that faces each cam surface 410 in the radial direction. Thereby, between the drive side cylindrical part 41 of the drive side rotating body 4 and the interlocking side cylindrical part 51 of the interlocking side rotating body 5, each cam surface 410 of the driving side cylindrical part 41 and the circle of the interlocking side cylindrical part 51 are provided. Between the circumferential surface 510, five wedge-shaped spaces 511 whose both ends in the circumferential direction are narrowed are formed (see FIG. 3).

  Each engagement element 6 is made of POM and is formed of a cylindrical roller. Each engaging element 6 is larger than the radial gap between the driving side cylindrical part 41 of the driving side rotating body 4 and the interlocking side cylindrical part 51 of the interlocking side rotating body 5, and the circumferential center part of the wedge-shaped space 511. The outer diameter is smaller than the radial gap between the cam surface 410 and the circumferential surface 510. For this reason, each engagement element 6 moves from the circumferential direction center part of the wedge-shaped space 511 to the circumferential direction end part, so that the driving side cylindrical part 41 of the driving side rotating body 4 and the interlocking side cylindrical part 51 of the interlocking side rotating body 5 are obtained. The wedge-shaped space 511 is moved from the circumferential end to the center in the circumferential direction, thereby moving the driving-side cylindrical portion 41 of the driving-side rotating body 4 and the interlocking-side cylindrical portion 51 of the interlocking-side rotating body 5. And a disengaged state.

  The cage 7 is an integrally molded product made of POM, has a bottomed cylindrical shape with one end (lower end in FIG. 2) open, and has a disk-shaped bottom portion 70 and a cylindrical peripheral wall portion 71. . An insertion hole 700 through which one end side of the shaft portion 30 of the center shaft 3 is inserted is formed in the center of the disc-shaped bottom portion 70. The cylindrical peripheral wall portion 71 has an outer diameter slightly smaller than the inner diameter of the driving side cylindrical portion 41 of the driving side rotating body 4 and an inner diameter slightly larger than the outer diameter of the interlocking side cylindrical portion 51 of the interlocking side rotating body 5. It is arranged between the driving side cylindrical part 41 and the interlocking side cylindrical part 51. On one end side (the lower end side in FIG. 2) of the cylindrical peripheral wall portion 71, five holding holes 710 are formed at equal intervals in the circumferential direction. Each holding hole 710 has a circumferential width substantially equal to the outer diameter of each engagement element 6. For this reason, the engaging element 6 held in the holding hole 710 is almost immovable in the circumferential direction in the holding hole 710. Further, on the distal end side (lower end side in FIG. 2) of the cylindrical peripheral wall portion 71 of the cage 7, an engagement hole 711 that penetrates between the two holding holes 710 and 710 in the thickness direction of the cylindrical peripheral wall portion 71. Is formed (see FIG. 4).

  The friction holding means 8 includes a disk portion 31, each curved arm portion 32, and each projection portion 320 that are integrally formed with the shaft portion 30 of the center shaft 3. In the friction holding means 8, the projections 320 of the curved arm portions 32 are in contact with the inner peripheral surface of the cylindrical peripheral wall portion 71 of the cage 7 in a state where the curved arm portions 32 are elastically deformed by a predetermined amount. Yes. Thereby, the cage 7 is held with respect to the center shaft 3 with a predetermined friction holding force by the friction holding means 8. The friction holding force of the friction holding means 8 is such that the cage 7 rotates integrally with the driving side rotating body 4 and the interlocking side rotating body 5 which are integrally coupled via the respective engagement elements 6 in the wedge engagement state. In a predetermined manner so that the retainer 7 can be prevented from rotating with the driving side rotating body 4 or the interlocking side rotating body 5 via the engaging elements 6 in the disengaged state. The size is assumed.

  The positioning means 9 is an integrally molded product made of spring steel, and is composed of a spring interposed between the drive side rotating body 4 and the cage 7. Specifically, the positioning means 9 includes an attachment portion 90 and a leaf spring portion 91 having a U-shaped cross section. The attachment portion 90 is inserted and held in an attachment hole (not shown) formed in the drive side cylindrical portion 41 of the drive side rotating body 4. The leaf spring portion 91 is inserted into an attachment insertion hole 411 formed in the drive side cylindrical portion 41 and engaged with an engagement hole 711 formed in the cylindrical peripheral wall portion 71 of the cage 7. As a result, the positioning means 9 is held with respect to the drive-side rotating body 4 by the spring force of the leaf spring portion 91 so that the engaging element 6 held in the holding hole 710 of the cage 7 is in a non-engaged state. The container 7 is positioned and held in the circumferential direction. Further, the spring force of the leaf spring portion 91 in the positioning means 9 is maintained by friction so that when the driving side rotating body 4 rotates, the engagement element 6 changes from the non-engaged state to the wedge engaged state according to the rotation. The retainer 7 held on the center shaft 3 by the friction holding force of the means 8 is sized to allow relative rotation with respect to the drive side rotating body 4.

  Next, a method for manufacturing the bidirectional clutch 1 according to this embodiment will be described. First, the mounting seat 2, the center shaft 3, the driving side rotating body 4, the interlocking side rotating body 5, the engagement element 6 and the cage 7 are respectively produced by injection molding. Next, the other end (lower end in FIG. 2) of the shaft portion 3 of the center shaft 3 is inserted into the interlocking side insertion hole 500 of the interlocking side rotating body 5. Then, one end (upper end in FIG. 2) of the shaft portion 30 of the center shaft 3 is inserted into the insertion hole 700 of the cage 7. At this time, in a state where the curved arm portions 32 of the center shaft 3 are elastically deformed, the projections 320 of the curved arm portions 32 are brought into contact with the inner peripheral surface of the cylindrical peripheral wall portion 71 of the cage 7. Then, after holding each engaging element 6 in each holding hole 710 of the cage 7, one end (upper end in FIG. 2) of the shaft portion 3 of the center shaft 3 is connected to the driving side insertion hole 400 of the driving side rotating body 4. Insert through. Finally, both ends of the shaft portion 30 of the center shaft 3 are fitted and fixed in the fitting holes 200 and 200 of the mounting seat 2 while elastically deforming the mounting seat 2. In this state, the driving side gear portion 40 of the driving side rotating body 4 and the interlocking side gear portion 50 of the interlocking side rotating body 5 can slide with the cylindrical seat portions 201 and 201 of the mounting seat 2. The bidirectional clutch 1 according to this embodiment is manufactured by such a procedure.

  Next, the operation of the bidirectional clutch 1 according to this embodiment will be described by taking as an example a case where it is incorporated in a wind direction adjusting device. FIG. 5 is a sectional view in the axial direction of the wind direction adjusting device 10 in which the bidirectional clutch according to the present embodiment is incorporated.

  As shown in the figure, the wind direction adjusting device 10 includes a stepping motor 11 as a driving source, an ABS mounting plate 12, a bidirectional clutch 1, a swing fin 13, a retainer 14, and a rotation direction switching means 15. And. The attachment plate 12 is attached to the outer surface of the retainer 14 with a screw 16 or the like. On the mounting plate 12, a stepping motor 11 and a bidirectional clutch 1 are juxtaposed with a screw (not shown) or the like. The stepping motor 11 rotates only in the forward direction, and a drive gear 111 is fixed to the drive shaft 110 of the stepping motor 11. A rotation direction switching means 15 is interposed between the drive gear 111 and the drive side gear portion 40 of the drive side rotating body 4 of the clutch 1. This rotation direction switching means 15 selectively transmits the rotation driving force of the drive gear 111 rotating in the forward direction to the forward or reverse direction by timer control or the like, and transmits and inputs it to the drive side rotating body 4. is there.

  The swing fin 13 is disposed inside the retainer 14. Further, the swing shaft 130 of the swing fin 13 protrudes outside the retainer 14. A fin gear 131 is disposed at the protruding end of the swing shaft 130. The fin gear 131 and the interlocking side gear portion 50 of the interlocking side rotating body 5 of the bidirectional clutch 1 are engaged with each other.

  In this way, the stepping motor 11 and the drive side rotating body 4 of the bidirectional clutch 1 are connected. Further, the interlocking-side rotating body 5 of the bidirectional clutch 1 and the swing fin 13 are connected.

  Next, torque transmission from the stepping motor 11 to the swing fin 13 when the wind direction adjusting device 10 is in the automatic mode will be described. When the drive shaft 110 of the stepping motor 11 rotates, the drive gear 111 fixed to the drive shaft 110 also rotates. Then, the rotational driving force is input to the driving side rotating body 4 of the bidirectional clutch 1 via the rotational direction switching means 15.

  For example, as shown in FIG. 6A, when the engagement element 6 in the bidirectional clutch 1 is in a non-engagement state, for example, the forward direction from the stepping motor 11 to the drive side rotating body 4 (the clockwise direction in FIG. 6). ) Is input and the drive side rotating body 4 rotates in the forward direction, the cage 7 held on the center shaft 3 by the friction holding force of the friction holding means 8 is relative to the drive side rotating body 4. Rotate. That is, the cage 7 held on the center shaft 4 by the predetermined friction holding force of the friction holding means 8 does not rotate, and only the driving side rotating body 4 rotates.

  As a result, as shown in FIG. 6B, each engagement element 6 held in each holding hole 710 of the cage 7 is moved from the circumferential center of the wedge-shaped space 511 to the circumferential end (drive-side rotator 4). To the driving side cylindrical portion 41 of the driving side rotating body 4 and the interlocking side cylindrical portion 51 of the interlocking side rotating body 5 to be in a wedge engagement state. As a result, the drive-side rotator 4 and the interlocking-side rotator 5 are integrally coupled via the engagement elements 6, and the rotational torque of the drive-side rotator 4 is transmitted to the interlocking-side rotator 5. Therefore, the driving side rotating body 4, the interlocking side rotating body 5, each engagement element 6, the cage 7 and the like rotate integrally. At this time, each protrusion 320 of each curved arm 32 constituting the friction holding means 8 slides with the inner peripheral surface of the cylindrical peripheral wall 71 of the cage 7. The same effect occurs when the drive-side rotator 4 rotates in the reverse direction (counterclockwise direction in FIG. 6).

  Then, when the interlocking-side gear portion 50 of the interlocking-side rotating body 5 of the bidirectional clutch 1 and the fin gear 131 of the swing fin 13 mesh with each other, a rotational driving force is output from the interlocking-side rotating body 5 to the swing shaft 130. The swing fin 13 swings.

  Here, in the bidirectional clutch 1 according to the present embodiment, the cage 7 does not rotate even if the drive side rotator 4 rotates. Therefore, if the drive side rotator 4 rotates, The cage 7 rotates relative to the cage 7. For this reason, the movement from the neutral position (circumferential center portion of the wedge-shaped space) to the engagement position (circumferential end portion of the wedge-shaped space) of each engaging element 6 when the driving-side rotating body 4 rotates is the drive-side rotating body. 4 occurs simultaneously with the rotation of 4, and each engagement element 6 quickly enters the wedge engagement state from the non-engagement state. Therefore, the rotational torque is quickly transmitted from the driving side rotating body 4 to the interlocking side rotating body 5, and the response of torque transmission from the driving side rotating body 4 to the interlocking side rotating body 5 is improved.

  In the automatic mode, after the swing fin 13 swings to the maximum in one direction, the rotation direction switching means 15 is operated by an operation of a timer or the like. Thereby, the rotational driving force of the drive gear 111 that rotates in the forward direction is switched from the forward direction to the reverse direction, for example, and transmitted to and input to the drive-side rotator 4. Then, the drive side rotator 4 rotates in the reverse direction (counterclockwise direction in FIG. 6). At this time, the cage 7 held by the center shaft 4 with a predetermined friction holding force of the friction holding means 8 does not rotate, and only the driving side rotating body 4 rotates. Thereby, each engagement element 6 held in each holding hole 710 of the cage 7 is connected to the opposite circumferential end (drive-side rotating body) from the circumferential end of the wedge-shaped space 511 via the circumferential central portion. 4 (circumferential end portion in the rotational retreat direction), and the drive side cylindrical portion 41 of the drive side rotating body 4 and the interlocking side cylindrical portion 51 of the interlocking side rotating body 5 are again engaged. Accordingly, the driving side rotating body 4 and the interlocking side rotating body 5 are integrally coupled via the respective engagement elements 6, and the rotational torque of the driving side rotating body 4 is transmitted to the interlocking side rotating body 5. Therefore, a reverse rotational driving force is output from the interlocking-side rotating body 5 to the swing shaft 130, and the swing fin 13 swings in the reverse direction.

  On the other hand, torque interruption from the swing fin 13 to the stepping motor 11 when the wind direction adjusting device 10 is in the manual mode will be described. When the operation knob (not shown) of the swing fin 13 shown in FIG. 5 is gripped and operated by the passenger, the swing fin 13 swings around the swing shaft 130. Then, the fin gear 131 rotates. When the fin gear 131 rotates, torque is transmitted to the interlocking-side rotating body 5 through meshing between the fin gear 130 and the interlocking-side gear portion 50 of the interlocking-side rotating body 5 of the bidirectional clutch 1.

  For example, as shown in FIG. 6 (a), when the engaging element 6 in the two-way clutch 1 is in a non-engaged state, the interlocking-side rotating body 5 rotates, for example, in the forward direction (clockwise direction in FIG. 6). In this case, when the non-engaged engagement element 6 is in contact with the circumferential surface 510 of the interlocking-side rotating body 5, the interlocking-side rotating body 5 is caused by the frictional force with the circumferential surface 510 of the interlocking-side rotating body 5. Is transmitted to the engagement element 6 and the engagement element 6 tends to move in the circumferential direction. However, the retainer 7 that holds the engaging element 6 is held by the friction holding means 8 with a predetermined friction holding force with respect to the center shaft 3 and therefore does not rotate. In addition, when the engaging element 6 in the non-engagement state is not in contact with the circumferential surface 510 of the interlocking-side rotating body 5, the rotational force of the interlocking-side rotating body 5 is not transmitted to the engaging element 6. There is no attempt to move in the circumferential direction. For this reason, even if the interlocking-side rotating body 5 rotates, the retainer 7 does not rotate with it, and the engaging element 6 held in the retaining hole 710 of the retainer 7 also rotates from the circumferential center of the wedge-shaped space 511. The disengaged state is maintained without moving to the direction end. Accordingly, the rotational torque is not transmitted from the interlocking side rotating body 5 to the driving side rotating body 4. Note that the same effect occurs when the drive-side rotator 5 rotates in the opposite direction.

  Therefore, the load applied to the swing fin 13 by the passenger is not transmitted to the stepping motor 11. In addition, the passenger does not feel resistance when operating the operation knob or the like.

  Further, in the bidirectional clutch 1 according to the present embodiment, a disk part 31 integrally formed with the shaft part 30 of the center shaft 3 and each elastically deformable curved arm part 32 integrally formed with the disk part 31. Further, the friction holding means 8 is constituted by the projections 320 integrally formed with the curved arm portions 32, and a predetermined friction holding force is exhibited by the resin elasticity of the curved arm portions 32. For this reason, it is possible to easily adjust to a predetermined friction holding force by changing the shape, size, and the like of each curved arm portion 32. Further, since it is not necessary to separately provide a friction holding means such as a spring material in order to exert a predetermined friction holding force, the structure can be simplified and the number of parts can be reduced. Further, since each projection 320 of each curved arm 32 is in contact with the inner peripheral surface of the cylindrical peripheral wall 71 of the cage 7, it is integrally coupled via the engagement element 6 in a wedge engagement state. When the driving side rotating body 4, the interlocking side rotating body 5, the cage 7 and the like rotate integrally, the sliding resistance due to the contact between the cage 7 and the curved arm portion 32 is reduced, and the load on the stepping motor 11 is reduced. Can be reduced.

  In addition, in the bidirectional clutch 1 according to the present embodiment, the positioning means 9 is made of a spring interposed between the drive side rotating body 4 and the cage 7, so that the shape and size of the spring are changed. Thus, the spring force in the positioning means 9 can be easily adjusted. For this reason, it becomes easy to adjust the spring force of the spring in the positioning means 9 in relation to the magnitude of the friction holding force in the friction holding means 8.

  The embodiments of the bidirectional clutch and the wind direction adjusting device of the present invention have been described above. However, the embodiment is not particularly limited to the above embodiment. Various modifications and improvements that can be made by those skilled in the art are also possible.

  For example, in the above-described embodiment, the friction holding means 8 is configured by the disk portion 31 and the curved arm portion 32 formed integrally with the shaft portion 30 of the center shaft 3, and exhibits a predetermined friction holding force by resin elasticity. An example was described. However, for example, a rubber elastic body or a leaf spring may be used as the friction holding means 8 so that a predetermined friction holding force is exhibited by rubber elasticity or metal elasticity. Further, these rubber elastic bodies and leaf springs may be fixed to the center shaft 3 or to the cage 7.

  In the above embodiment, a spring made of a leaf spring is used as the positioning means 9 and this spring is fixed to the drive side rotating body 4. However, instead of the leaf spring, a rubber elastic body is used. Alternatively, it may be a resin elastic portion integrally formed with the driving side rotating body 4. Further, these plate springs, rubber elastic bodies and the like may be fixed to the cage 7, or the resin elastic portion may be integrally formed with the cage 7.

  In addition, the shape, number, and the like of the engaging element 6 and the cam surface 410 can be appropriately set within a range in which those functions can be appropriately performed. Further, as the engagement element 6, a metal roller or a ball having a small sliding resistance may be employed.

  Further, the bidirectional clutch of the present invention can be used by being incorporated in a paper feeding device such as a copy, a printer or a fax machine in addition to the wind direction adjusting device.

It is a disassembled perspective view of the bidirectional clutch which concerns on this embodiment. It is an axial sectional view of the bidirectional clutch according to the present embodiment. It is AA arrow sectional drawing in FIG. FIG. 3 is a cross-sectional view taken along line B-B in FIG. 2. It is an axial sectional view of a wind direction adjusting device incorporating a bidirectional clutch according to the present embodiment. It is a partial expanded sectional view explaining the action | operation of the bidirectional | two-way clutch which concerns on this embodiment, (a) shows the state in which an engagement element is in a non-engagement state, (b) shows an engagement element in a wedge engagement state. Indicates the state.

Explanation of symbols

1: two-way clutch, 2: mounting seat, 3: center shaft, 30: shaft portion, 31: disk portion, 32: curved arm portion, 320: protrusion, 4: drive side rotating body, 40: drive side gear Part: 41: driving side cylindrical part, 5: interlocking side rotating body, 50: interlocking side gear part, 51: interlocking side cylindrical part, 6: engagement element, 7: retainer, 71: cylindrical peripheral wall part, 710: holding Hole: 8: Friction holding means, 9: Positioning means, 10: Wind direction adjusting device, 11: Stepping motor (drive source), 13: Swing fin

Claims (6)

A center axis,
A driving side rotating body rotatably supported on the center shaft and having a cam surface;
An interlocking-side rotating body that is rotatably supported by the center shaft and has a circumferential surface facing the cam surface in the radial direction;
Both ends in the circumferential direction formed between the cam surface and the circumferential surface are accommodated in a narrow wedge-shaped space, and the drive side is moved by moving from the circumferential central portion of the wedge-shaped space to the circumferential end portion. While being in wedge-engaged state with the rotating body and the interlocking-side rotating body, it is disengaged from the driving-side rotating body and the interlocking-side rotating body by moving from the circumferential end of the wedge-shaped space to the center in the circumferential direction. An engagement element to be in a state;
A holding hole that is disposed between the drive-side rotating body and the interlocking-side rotating body and is rotatably supported by the center shaft so as to be relatively rotatable with both of them is formed in a cylindrical peripheral wall. A cage having;
The cage is allowed to rotate integrally with the driving side rotating body and the interlocking side rotating body integrally coupled via the engaging element in the wedge engaged state, and the non-engaging state. The cage is held with respect to the center shaft with a predetermined frictional holding force that restricts the cage from rotating with the driving side rotating body or the interlocking side rotating body via the engaging element in the combined state. Friction holding means for holding;
The retainer is positioned and held in the circumferential direction with respect to the driving side rotating body so that the engaging element held in the holding hole of the cage is in the disengaged state, and the driving side rotation is performed. The retainer held on the center shaft by the friction holding force of the friction holding means so that the engagement element changes from the non-engaged state to the wedge engaged state according to the rotation of the body. And a positioning means for permitting relative rotation with respect to the drive-side rotating body.   The bidirectional clutch according to claim 1, wherein the friction holding means has elasticity to exert the friction holding force.   The friction holding means is a state in which the disc portion fixed to or integrally molded with the center shaft and the outer peripheral surface of the disc portion are integrally formed and elastically deformed on the inner peripheral surface of the cylindrical peripheral wall of the cage The two-way clutch according to claim 2, further comprising an elastically deformable curved arm portion that is in contact with each other.   4. The bidirectional clutch according to claim 3, wherein the curved arm portion has a protruding portion that protrudes in a centrifugal direction from the curved arm portion and abuts against an inner peripheral surface of the cylindrical peripheral wall of the cage.   The bidirectional clutch according to any one of claims 1 to 4, wherein the positioning means includes a spring interposed between the driving side rotating body and the cage.   The bidirectional clutch according to any one of claims 1 to 5, wherein the driving side rotating body is connected to a driving source and the interlocking side rotating body is connected to a swing fin. Wind direction adjustment device.

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