JP6562794B2 - Actuator - Google Patents

Description

  The present invention relates to an actuator that drives two output members by a common motor.

  Among actuators that drive various members, there are actuators that drive two output members with a common motor. Patent Document 1 discloses a filter driving device that drives a filter of an air conditioner. The filter drive device of Patent Document 1 includes a common actuator (drive device) that drives two filters. In the drive device of Patent Document 1, an output gear of a gear train rotated by a drive motor meshes with a rack provided in a filter.

JP 2006-71135 A

  The filter driving device of Patent Document 1 moves two filters simultaneously by the driving force of a motor. Therefore, a large driving force is required. If the driving force of the motor is alternately transmitted to the two output members and driven alternately, the driving force of the motor can be smaller than when driving simultaneously. However, when the two output members are alternately driven by the motor, the configuration of the driving force transmission mechanism interposed between the motor and the output member is complicated. Further, if the reduction ratio is increased in order to increase the torque transmitted to the output member, the driving force transmission mechanism is increased in size. Therefore, it is difficult to reduce the size of the actuator.

  In view of the above problems, an object of the present invention is to downsize an actuator that drives two output members with a common motor.

In order to solve the above problems, an actuator of the present invention rotates a first output member, a second output member, a motor, and the first output member and the second output member based on rotation of the motor. A driving force transmission mechanism, and the driving force transmission mechanism includes a driving gear to which rotation of the motor is transmitted, a first gear that rotates the first output member based on rotation of the driving gear, A second gear that rotates the second output member based on the rotation of the drive gear, a first state in which the rotation of the drive gear is transmitted to the first gear, and the rotation of the drive gear And the driving force transmission mechanism includes a sun gear, a planetary gear meshing with the sun gear, a planet carrier holding the planetary gear, and the planetary gear. Internal teeth that mesh with gears A planetary gear mechanism having a vehicle, a drive-side rotator including the drive gear and the sun gear, a first output-side rotator including the first gear and the planet carrier, the second gear, A second output-side rotator including the internal gear, and the outer diameter of the second gear formed on the outer periphery of the second output-side rotator is formed on the outer periphery of the drive-side rotator. It is smaller than the root diameter of the drive gear and the bottom diameter of the first gear formed on the outer peripheral edge of the first output side rotating body .

According to the present invention, the first output member and the second output member can be driven by a common motor. The driving force transmission mechanism is switched between a first state where the rotation of the driving gear is transmitted to the first gear and a second state where the rotation of the driving gear is transmitted to the second gear. In this way, since the transmission destination of the driving force of the motor can be switched, it is not necessary to increase the size of the motor while the two output members are driven by a common motor. Therefore, the actuator that drives the two output members can be reduced in size. In addition, since the two output members can be directly driven by the first gear and the second gear that can be the output elements of the planetary gear mechanism, the driving force transmission mechanism can be reduced in size. Moreover, since the reduction ratio by the planetary gear mechanism is large, a large torque can be obtained without increasing the size of the motor and the driving force transmission mechanism. Furthermore, the drive-side rotating body or the first output-side rotating body can be made thin, and the meshing width between the gears can be ensured between the driving gear or the gear that meshes with the first gear. Therefore, the driving force transmission mechanism is made thinner.
be able to.

  In the present invention, it is desirable that the drive gear, the first gear, and the second gear are arranged coaxially. In this case, since the two output members can be directly driven by the first gear and the second gear arranged coaxially with the drive gear, the drive force transmission mechanism can be miniaturized and the actuator can be miniaturized.

  In the present invention, it is preferable that the outer diameter of the first gear is smaller than the root diameter of the drive gear. If it does in this way, about each of three rotary bodies, thickness reduction can be achieved and the meshing width of gears can be ensured between the gears meshed with the gear provided in the outer periphery of each rotary body. Therefore, the driving force transmission mechanism can be thinned. Further, since the drive gear can be made larger in diameter than the first gear and the second gear, the reduction ratio can be increased.

  In the present invention, the driving side rotating body, the first output side rotating body, and a support shaft passing through the rotation center of the second output side rotating body, and a case for supporting an end portion of the support shaft, The drive-side rotator, the first output-side rotator, and the second output-side rotator are in the order of the second output-side rotator, the first output-side rotator, and the drive-side rotator. It is desirable that it is attached to the support shaft. In this case, the planetary gear mechanism is assembled by attaching the support shaft to the case and dropping the three rotating bodies into the case in the order of the second output side rotating body, the first output side rotating body, and the driving side rotating body. be able to. Therefore, the assembly of the driving force transmission mechanism is easy.

  In the present invention, it is desirable that the driving force transmission mechanism is switched between the first state and the second state based on the rotational load of the first output member and the rotational load of the second output member. . In this way, when one of the two output members is driven first and, as a result, the magnitude of the rotational load is reversed, the drive force transmission destination can be switched to the other and the other driven. Accordingly, the two output members can be alternately driven by a common motor.

  In the present invention, the driving force transmission mechanism decelerates the rotation of the motor with a first reduction ratio and transmits it to the first output member, and decelerates the rotation of the motor with a second reduction ratio. Preferably, the first reduction ratio and the second reduction ratio are the same. If it does in this way, the 1st output member and the 2nd output member can be driven with the same torque.

According to the present invention, the first output member and the second output member can be driven by a common motor. The driving force transmission mechanism is switched between a first state where the rotation of the driving gear is transmitted to the first gear and a second state where the rotation of the driving gear is transmitted to the second gear. In this way, since the transmission destination of the driving force of the motor can be switched, it is not necessary to increase the size of the motor while the two output members are driven by a common motor. Therefore, the actuator that drives the two output members can be reduced in size. In addition, since the two output members can be directly driven by the first gear and the second gear that can be the output elements of the planetary gear mechanism, the driving force transmission mechanism can be reduced in size. Moreover, since the reduction ratio by the planetary gear mechanism is large, a large torque can be obtained without increasing the size of the motor and the driving force transmission mechanism. Furthermore, the drive-side rotating body or the first output-side rotating body can be made thin, and the meshing width between the gears can be ensured between the driving gear or the gear that meshes with the first gear. Therefore, the driving force transmission mechanism can be thinned.

It is a perspective view of a filter drive device provided with an actuator to which the present invention is applied. It is an exploded perspective view of an actuator to which the present invention is applied. FIG. 3 is a plan view and a partial perspective view showing a state where a second case is removed from the actuator of FIG. 2. It is the disassembled perspective view which looked at the differential gear mechanism, the 1st output member, and the 2nd output member from the 2nd case side. It is the disassembled perspective view which looked at the differential gear mechanism, the 1st output member, and the 2nd output member from the 1st case side. It is sectional drawing of a differential gear mechanism. It is a disassembled perspective view of a 1st case and a rocking | fluctuation mechanism. It is a cross-sectional perspective view which shows the state which positioned the link drive gear with the cap. It is a cross-sectional perspective view of an output member and a bearing part. It is a disassembled perspective view which shows the state which attached the output member of the rocking | fluctuation mechanism to the bearing part of the 1st case. It is sectional drawing of the differential gear mechanism of a modification.

  Hereinafter, an embodiment of an actuator to which the present invention is applied will be described with reference to the drawings.

(overall structure)
FIG. 1 is a perspective view of a filter driving device including an actuator to which the present invention is applied. The actuator 1 of this embodiment is used for the filter driving device 100. The filter driving device 100 includes an actuator 1, a first filter driving shaft 200 </ b> A and a second filter driving shaft 200 </ b> B driven by the actuator 1, and a swing member driving shaft 300. The actuator 1 alternately rotates the first filter drive shaft 200A and the second filter drive shaft 200B, and reciprocally rotates (swings) the swing member drive shaft 300 within a predetermined angular range, thereby rotating the swing member drive shaft. A cleaning member (not shown) attached to 300 is swung. Based on the rotation of the first filter drive shaft 200A and the second filter drive shaft 200B, the filters (not shown) incorporated in the air inlets and the air outlets of ventilators, air conditioners and the like are shown in the directions of arrows A1 and A2 shown in FIG. Moving. When the oscillating cleaning member comes into contact with the moving filter, foreign matter adhering to the filter is removed.

  In this specification, the three axes of XYZ are directions orthogonal to each other, one side of the X-axis direction is shown as -X direction, the other side is shown as -X direction, one side of Y-axis direction is + Y direction, and the other side is -Y direction, one side of the Z-axis direction is shown as + Z direction and the other side is shown as -Z direction. The Z-axis direction is a direction along the rotation axis L of the motor 2 (see FIG. 2) that is a drive source of the actuator 1. The rotation axes L1 and L2 of the first filter drive shaft 200A and the second filter drive shaft 200B and the rotation axis L3 of the swing member drive shaft 300 are parallel to the rotation axis L of the motor 2. The + Z direction is a direction (output side) in which the first filter drive shaft 200A, the second filter drive shaft 200B, and the swinging member drive shaft 300 protrude from the actuator 1, and the -Z direction is the non-output side.

FIG. 2 is an exploded perspective view of the actuator 1 to which the present invention is applied. 3A is a plan view showing a state where the second case is removed from the actuator 1 of FIG. 2, and FIG. 3B is a partial perspective view in which the region B of FIG. 3A is enlarged. . As shown in FIG. 2, the actuator 1 includes a case 10, a motor 2 accommodated in the case 10, a first output member 3 </ b> A and a second output member 3 </ b> B rotatably supported by the case 10, A driving force transmission mechanism 4 that rotates the first output member 3A and the second output member 3B based on the rotation and a swing mechanism 7 that swings the swing member drive shaft 300 based on the rotation of the motor 2 are provided. The driving force is transmitted from the motor 2 to the swing mechanism 7 through the reduction gear train 40 of the driving force transmission mechanism 4.

(Case)
The case 10 includes a first case 11 disposed on a side where the first filter drive shaft 200A, the second filter drive shaft 200B, and the swing member drive shaft 300 are provided (that is, the + Z direction side), and the first case 11 The second case 12 is provided on the −Z direction side. The case 10 has a substantially rectangular parallelepiped shape that is thin in the Z-axis direction as a whole.

  The first case 11 includes an end plate portion 111 to which the motor 2, the first output member 3 </ b> A and the second output member 3 </ b> B, the driving force transmission mechanism 4, and the swing mechanism 7 are assembled, and the outer peripheral edge of the end plate portion 111. A side plate portion 112 rising in the direction is provided. A circular recess 13 is formed in a region on the + Y direction side of the end plate portion 111. The motor 2 is assembled in the recess 13. Further, in the region on the −Y direction side of the end plate portion 111 and the region on the −X direction side, bearing portions 14A and 14B that rotatably support the first output member 3A and the second output member 3B are formed. Is done. The bearing portions 14A and 14B are shaft holes that penetrate the end plate portion 111 and are arranged side by side in the Y direction. The first output member 3A is supported by the bearing portion 14A so as to be rotatable around the rotation axis L1. Further, the second output member 3B is supported by the bearing portion 14B so as to be rotatable around the rotation axis L2. The second output member 3B and the bearing portion 14B are located on the + Y direction side with respect to the first output member 3A and the bearing portion 14A. Further, the end plate portion 111 is formed with a recess 15 in a region on the + X direction side with respect to the bearing portions 14A and 14B, and the swing mechanism 7 is assembled to the recess 15.

  The second case 12 includes an end plate portion 121 that faces the end plate portion 111 of the first case 11 in the Z-axis direction, and a side plate portion 122 that rises in the + Z direction from the outer peripheral edge of the end plate portion 121. On the side plate portion 112 of the first case 11, convex portions 113 are formed at a plurality of locations. On the other hand, a hook 123 is formed on the side plate portion 122 of the second case 12 at a position corresponding to the convex portion 113 of the first case 11. When the hook 123 and the convex portion 113 are engaged with each other and the first case 11 and the second case 12 are coupled, the case 10 can be configured.

(Wiring extraction part)
As shown in FIGS. 2 and 3, the first case 11 includes a wiring take-out portion 30 formed on an edge located on the + Y direction side of the side plate portion 112. The wiring take-out portion 30 includes a recess 31 that opens in the −Z direction, and a plurality of terminal pins 32 are disposed in the recess 31. One ends of the plurality of terminal pins 32 protrude in the −Z direction in the recess 31. As shown in FIG. 1, the recess 31 is exposed to the outside of the case 10 in a state where the first case 11 and the second case 12 are coupled. Therefore, a lead wire for power feeding to the motor 2 can be connected to the terminal pin 32 protruding into the recess 31.

  As shown in FIG. 2, a terminal portion 20 is provided on the outer peripheral surface of the motor 2. The terminal unit 20 includes a plurality of terminal pins 21. As shown in FIG. 3B, in the first case 11, the terminal portion 20 of the motor 2 faces the wiring extraction portion 30, and the flat cable 33 is routed from the terminal portion 20 to the wiring extraction portion 30. The Via the flat cable 33, the terminal pin 21 on the motor 2 side and the terminal pin 32 of the wiring takeout part 30 are connected. In addition, illustration of the flat cable 33 is abbreviate | omitted in Fig.3 (a).

As shown in FIG. 3B, the wiring take-out portion 30 includes a wall portion 34 located on the −Y direction side of the recessed portion 31 and a guide wall that protrudes from the + X direction side end portion of the wall portion 34 toward the motor 2 side. 35. The outer peripheral surface of the guide wall 35 facing the motor 2 has an arc shape. The flat cable 33 heading from the terminal portion 20 of the motor 2 to the wiring take-out portion 30 is drawn into a shape that is bent in a convex shape in the + X direction, and is guided in contact with the arc-shaped outer peripheral surface of the guide wall 35. . That is, the portion of the guide wall 35 that contacts the flat cable 33 has a shape (arc-shaped outer peripheral surface) that is less likely to damage the flat cable 33.

(Driving force transmission mechanism)
As shown in FIG. 2, a pinion 22 is attached to the output shaft of the motor 2. The driving force transmission mechanism 4 includes a reduction gear train 40 composed of a first gear 41, a second gear 42, and a third gear 43, and a differential gear mechanism that transmits the rotation of the motor 2 via the reduction gear train 40. 50. The first gear 41 is an input gear of the driving force transmission mechanism 4, and includes a large-diameter gear portion 411 that meshes with the pinion 22 and a small-diameter gear portion 412 that is located on the −Z direction side of the large-diameter gear portion 411. The second gear 42 includes a large-diameter gear portion 421 that meshes with the small-diameter gear portion 412 of the first gear 41, and a small-diameter gear portion 422 that is located on the −Z direction side of the large-diameter gear portion 421. The third gear 43 includes a large-diameter gear portion 431 that meshes with the small-diameter gear portion 422 of the second gear 42 and a small-diameter gear portion 432 that is located on the + Z direction side of the large-diameter gear portion 431. The gear shaft 413 passing through the rotation center of the first gear 41 is supported by a recess (not shown) having an end in the + Z direction provided on an end surface in the −Z direction of the motor 2. Further, the gear shafts 423 and 433 passing through the rotation centers of the second gear 42 and the third gear 43 are supported at the end portions in the + Z direction by the concave portions 114 and 115 provided in the end plate portion 111 of the first case 11. . On the other hand, end portions in the −Z direction of the gear shafts 413, 423, and 433 are supported by recesses (not shown) provided in the end plate portion 121 of the second case 12.

  The third gear 43, which is the final stage gear of the reduction gear train 40, includes two output gears. That is, the large-diameter gear portion 431 of the third gear 43 is an output gear that transmits the rotation of the motor 2 to the differential gear mechanism 50. On the other hand, the small-diameter gear portion 432 of the third gear 43 is an output gear that transmits the rotation of the motor 2 to the swing mechanism 7. A gear having the same diameter as the large-diameter gear portion 431 or a gear having a larger diameter than the large-diameter gear portion 431 may be used as an output gear that transmits the rotation of the motor 2 to the swing mechanism 7. In this embodiment, the number of teeth of the small-diameter gear portion 432 is made smaller than that of the large-diameter gear portion 431 so that the reduction ratio when the rotation of the motor 2 is transmitted to the swing mechanism 7 is increased.

  FIG. 4 is an exploded perspective view of the differential gear mechanism 50, the first output member 3A, and the second output member 3B as viewed from the second case 12 side (−Z direction side). FIG. 5 is an exploded perspective view of the differential gear mechanism 50, the first output member 3A, and the second output member 3B as viewed from the first case 11 side (+ Z direction side). The first output member 3A includes a shaft body 60A that is rotatably supported by the bearing portion 14A of the first case 11, and a first driven gear 61A provided at the end of the shaft body 60A on the −Z direction side. . The second output member 3B includes a shaft body 60B that is rotatably supported by the bearing portion 14B of the first case 11, and a second driven gear 61B provided at an end portion on the −Z direction side of the shaft body 60B. Is provided. The first driven gear 61A and the second driven gear 61B have larger diameters than the shaft bodies 60A and 60B, respectively. Each of the shaft bodies 60A and 60B includes a recess 62 that opens at the end surface in the + Z direction, and a plurality of protrusions 63 are arranged on the inner peripheral surface of the recess 62 in the circumferential direction. When the actuator 1 is used in the filter driving device 100, the recess 62 is used as a connecting portion for connecting the first filter driving shaft 200A and the second filter driving shaft 200B so as not to rotate about the rotation axes L1 and L2.

The differential gear mechanism 50 includes a support shaft 51 extending in parallel with the rotation axes L1 and L2 of the first output member 3A and the second output member 3B, a drive-side rotating body 52 rotatably supported by the support shaft 51, and a first output member 3A. 1 output side rotary body 53, 2nd output side rotary body 54, and the three planetary gears 55 (refer FIG. 5) are provided. The planetary gear 55 is held by a first output-side rotator 53 including a planet carrier 533 described later. When the differential gear mechanism 50 is assembled to the first case 11, the first case 11
The end portion of the support shaft 51 is press-fitted into the concave portion 116 provided in the end plate portion 111, and the second output side rotating body 54 and the first output side are sequentially formed from the base side (first case 11 side) of the support shaft 51. The rotating body 53 and the driving side rotating body 52 are assembled in this order. When the first case 11 and the second case 12 are combined, the other end of the support shaft 51 is a recess 124 (see FIG. 5) provided at the end plate 121 of the second case 12 at a position facing the recess 116. 6).

  As shown in FIG. 5, the drive-side rotator 52 has a large-diameter portion in which a drive gear 521 that meshes with the large-diameter gear portion 431 of the third gear 43 that is the final gear of the reduction gear train 40 is formed on the outer peripheral edge. 522 and a small diameter portion 523 projecting in the + Z direction from the center of the large diameter portion 522. A sun gear 524 is formed on the outer peripheral surface of the small diameter portion 523. As will be described later, the sun gear 524 meshes with the planetary gear 55 held by the first output side rotating body 53. The drive-side rotator 52 is rotatably supported by the support shaft 51 by passing the support shaft 51 through a shaft hole 525 that passes through the centers of the large-diameter portion 522 and the small-diameter portion 523.

  The first output-side rotating body 53 includes a cylindrical portion 532 having a first gear 531 that meshes with a first driven gear 61A of the first output member 3A, and a planetary carrier integrally formed with the cylindrical portion 532. 533. The planet carrier 533 includes an end plate portion 534 (see FIG. 4) that closes the −Z direction end of the cylindrical portion 532, and three support shafts that are arranged at equal intervals in the circumferential direction on the inner peripheral side of the cylindrical portion 532. 535 and a wall portion 536 extending in an arc shape at three locations between the support shafts 535 adjacent in the circumferential direction. The support shaft 535 and the wall portion 536 protrude from the end plate portion 534 in the + Z direction. A convex portion 537 is formed on the end surface of the wall portion 536 in the + Z direction. The planetary gear 55 is attached to the three support shafts 535 in a rotatable state.

  The first output-side rotator 53 includes a circular opening 538 (see FIG. 4) formed in the center of the end plate portion 534. The circular opening 538 is fitted with a cylindrical base end portion which is a portion where the sun gear 524 is not formed in the small diameter portion 523 of the driving side rotating body 52. The first output side rotator 53 is assembled to the support shaft 51 via the small diameter portion 523 of the drive side rotator 52.

  The second output-side rotating body 54 includes an end plate portion 543 in which a second gear 541 that meshes with the second driven gear 61B of the second output member 3B is formed on the outer peripheral edge, and the + Z direction from the outer peripheral edge of the end plate portion 543 A cylindrical portion 542 that rises from the top. An internal gear 544 (see FIG. 4) is formed on the inner peripheral surface of the cylindrical portion 542. The second output side rotator 54 is rotatably supported by the support shaft 51 by passing the support shaft 51 through a shaft hole 545 (see FIG. 5) formed in the end plate portion 543.

  As for the 1st output side rotary body 53, the cyclic | annular clearance gap is formed between the internal peripheral surface of the cylindrical part 532, the planetary gear 55, and the wall part 536 (refer FIG. 4). After the second output-side rotator 54 is assembled to the support shaft 51, the first output-side rotator 53 is assembled to the second output-side rotator 54. That is, the cylindrical portion 542 of the second output-side rotating body 54 is inserted into the gap between the inner peripheral surface of the cylindrical portion 532 and the planetary gear 55 and the wall portion 536. Thereby, the internal gear 544 formed on the inner peripheral surface of the cylindrical portion 542 meshes with the three planetary gears 55. The distal end of the support shaft 535 of the planetary gear 55 is supported by a recess 546 formed in the end plate portion 543 of the second output side rotating body 54. Further, the convex portion 537 protruding from the wall portion 536 is fitted into a concave portion 547 formed in the end plate portion 543. After the first output-side rotator 53 is assembled, when the drive-side rotator 52 is further assembled to the support shaft 51, the sun gear 524 is inserted on the inner peripheral side of the three planetary gears 55, and the sun gear 524 and the planetary gears are inserted. 55 meshes.

The differential gear mechanism 50 includes a sun gear 524 formed on the drive-side rotator 52, a planet carrier 533 formed on the first output-side rotator 53, and three planet gears 55 held on the planet carrier 533, A planetary gear mechanism 50A including an internal gear 544 formed on the second output-side rotator 54 is provided. Here, since the drive-side rotator 52 includes a drive gear 521 to which the rotation of the motor 2 is transmitted via the reduction gear train 40, the sun gear 524 provided on the drive-side rotator 52 is a planetary gear mechanism. Functions as an input element of 50A.

  On the other hand, the first output-side rotator 53 including the planetary carrier 533 includes the first gear 531 that meshes with the first driven gear 61A of the first output member 3A, and the second output-side rotation including the internal gear 544. The body 54 includes a second gear 541 that meshes with the second driven gear 61B of the second output member 3B. The first output member 3A and the second output member 3B are both rotatable. Accordingly, in the planetary gear mechanism 50A, of the first output member 3A and the second output member 3B, the member that transmits the rotation to the one with the larger rotational load functions as a fixed element, and transmits the rotation to the one with the smaller rotational load. The member functions as an output element. That is, the planetary gear mechanism 50A of the present embodiment is configured so that the first output member 3A is rotated based on the rotational loads of the first output member 3A and the second output member 3B, and the second output member 3B is rotated. Switch to the second state of rotation.

  That is, the first state is a state in which the first output-side rotator 53 serves as an output element of the planetary gear mechanism 50A, and the rotation of the drive gear 521 is transmitted to the first gear 531 and meshes with the first gear 531. In this state, the first output member 3A rotates via the one driven gear 61A. In the first state, the second output-side rotator 54 is a fixed element of the planetary gear mechanism 50A. The second state is a state in which the second output-side rotator 54 serves as an output element of the planetary gear mechanism 50A. The rotation of the drive gear 521 is transmitted to the second gear 541 and meshes with the second gear 541. The second output member 3B is rotated through the two driven gears 61B. In the second state, the first output-side rotator 53 is a fixed element of the planetary gear mechanism 50A.

  FIG. 6 is a cross-sectional view of the differential gear mechanism 50. As shown in this figure, when the first output-side rotator 53, the second output-side rotator 54, and the drive-side rotator 52 are assembled to the support shaft 51, a drive gear 521 that is an input gear and two output gears The first gear 531 and the second gear 541 are the outer peripheral surface of the differential gear mechanism 50. That is, the dimension of the differential gear mechanism 50 in the Z-axis direction is determined by the thickness of these three gears. In this embodiment, the outer diameter D1 of the second gear 541 is smaller than the root diameter D2 of the other two gears (first gear 531 and drive gear 521). For this reason, the first driven gear 61A that meshes with the first gear 531 has a thickness that extends to the outer peripheral side of the second gear 541. However, the first driven gear 61A and the second gear 541 do not interfere with each other. Absent.

  Since the driving force transmission mechanism 4 includes the reduction gear train 40 and the planetary gear mechanism 50A, the rotation of the motor 2 is reduced at a predetermined reduction ratio and transmitted to the first output member 3A or the second output member 3B. If the speed reduction ratio between the motor 2 and the first output member 3A is the first speed reduction ratio and the speed reduction ratio between the motor 2 and the second output member 3B is the second speed reduction ratio, in this embodiment, the first speed reduction ratio And the second reduction ratio are substantially equal. Accordingly, the first output member 3A and the second output member 3B can be driven with substantially equal torque.

(Swing mechanism)
FIG. 7 is an exploded perspective view of the first case 11 and the swing mechanism 7. The actuator 1 of this embodiment includes a swing mechanism 7 for swinging the swing member drive shaft 300 within a predetermined angle range, and functions as the swing device 1A. The swing mechanism 7 includes a link drive gear 71, a link driven gear 72, a cap 73 that positions the link drive gear 71, a link 74 that connects the link drive gear 71 and the link driven gear 72, and a link driven gear 72. An output member 75 to which rotation (swing) is transmitted is provided. The output member 75 includes a first member 751 in which an output gear 76 that meshes with the link driven gear 72 is formed, and a second member 752 that rotates integrally with the first member 751. The first member 751 includes a disk part 753 formed with a larger diameter than the output gear 76 on the + Z direction side of the output gear 76, and a positioning protrusion 754 that protrudes radially outward from the disk part 753. A shaft body 755 extending in the Z-axis direction is attached to the center of the output gear 76.

  As described above, the end plate portion 111 of the first case 11 is formed with the recess 15 on the + X direction side of the region where the first output member 3A, the second output member 3B, and the differential gear mechanism 50 are assembled. ing. A cap mounting portion 16 and bearing portions 17 and 18 are formed in the concave portion 15. The bearing portion 18 is located on the −Y direction side of the cap mounting portion 16, and the bearing portion 17 is located on the −X direction side of the bearing portion 18. A link drive gear 71 and a cap 73 are attached to the cap attachment portion 16. The bearing portion 17 rotatably supports the base portion of the output member 75. Further, the bearing portion 18 supports a shaft body 721 provided at the rotation center of the link driven gear 72.

  The cap attaching portion 16 is formed at three locations along the annular convex portion 161, the concave portion 162 provided on the upper end surface of the protruding portion formed at the center of the annular convex portion 161, and the inner peripheral edge of the annular convex portion 161. A positioning unit 163 is provided. An end of a shaft body 711 (see FIG. 8) provided at the rotation center of the link drive gear 71 is assembled to the recess 162. The positioning portion 163 has a protruding shape having a protruding dimension in the −Z direction larger than that of the annular protruding portion 161. The positioning portions 163 are arranged at equiangular intervals in the circumferential direction with the center of the recess 162 (that is, the rotation center of the link drive gear 71) as a reference.

  The bearing portion 17 includes a cylindrical portion 171 that rises from the end plate portion 111 in the −Z direction. A shaft hole that penetrates the end plate portion 111 is formed on the inner peripheral side of the cylindrical portion 171. An annular convex portion 161 is connected to the outer peripheral surface of the cylindrical portion 171. As shown in FIG. 7, the bearing portion 17 includes a restriction portion 173 formed on the end surface in the −Z direction of the cylindrical portion 171. The restricting portion 173 is a protruding portion that protrudes in the −Z direction. The restricting portion 173 is formed on the end surface of the cylindrical portion 171 over a predetermined angle range corresponding to the swing range of the output gear 76. A stepped portion is formed at one end 174 in the circumferential direction and the other end 175 in the circumferential direction of the restricting portion 173.

  FIG. 8 is a cross-sectional perspective view showing a state in which the link drive gear 71 is positioned by the cap 73 (cross-sectional perspective view at the position C1-C1 in FIG. 3). The link drive gear 71 is rotatably supported via a shaft body 711 assembled to the recess 162. A circular protrusion 712 protruding in the −Z direction is formed at the center of the link drive gear 71. The cap 73 includes an annular portion 731 that contacts the outer peripheral portion of the link drive gear 71 from the side opposite to the end plate portion 111 (the −Z direction side), and a peripheral wall that extends from the outer peripheral edge of the annular portion 731 toward the end plate portion 111. 732. A circular opening 735 is formed at the center of the annular portion 731, and the circular convex portion 712 of the link drive gear 71 is fitted into the opening 735. As a result, the link driving gear 71 is positioned with respect to the cap 73 and the upper end of the shaft body 711 is positioned via the link driving gear 71. That is, the upper and lower bearings that rotatably support the link drive gear 71 are configured by the opening 735 formed in the cap 73 and the recess 162 formed in the cap attachment portion 16.

  The cap 73 is positioned in the Z-axis direction when the end surface in the + Z direction of the peripheral wall 732 contacts the end surface in the −Z direction of the annular convex portion 161. Then, the positioning portion 163 of the cap mounting portion 16 abuts on the inner peripheral surface of the peripheral wall 732 at three points, thereby positioning with respect to the first case 11 in a direction intersecting the Z-axis direction. The positioning part 163 positions the cap 73 at a position coaxial with the recess 162. As described above, the inner peripheral surface of the opening 735 formed in the cap 73 functions as a bearing for the link drive gear 71. By positioning the cap 73 coaxially with the recess 162, the link drive gear 71 is Is positioned at a position coaxial with the recess 162. Boss portions 733 are formed on the cap 73 at two locations on the outer peripheral side of the peripheral wall 732. The cap 73 is screwed to the end plate portion 111 via the boss portion 733.

The peripheral wall 732 includes a cutout portion 734 that is cut out in a part in the circumferential direction. The notch 734 faces the small-diameter gear portion 432 of the third gear 43 that is the final gear of the reduction gear train 40. The small-diameter gear portion 432 meshes with the link drive gear 71 via the notch portion 734. Therefore, the rotation of the motor 2 is reduced and transmitted to the link drive gear 71 through the reduction gear train 40 at a predetermined reduction ratio.

  The link driven gear 72 is rotatably supported by the bearing portion 18 via the shaft body 721. One end of a link 74 is connected to the link driven gear 72, and the other end of the link 74 is connected to a circular convex portion 712 of the link drive gear 71. When the link driving gear 71 rotates once, the link 74 reciprocates once in the X-axis direction, and the link driven gear 72 reciprocates (that is, reciprocally swings) within a predetermined angular range. The link driven gear 72 has teeth 722 formed in a partial range in the circumferential direction.

  9 is a cross-sectional perspective view of the output member 75 and the bearing portion 17 (cross-sectional perspective view at the position C2-C2 in FIG. 3). FIG. 10 is an exploded perspective view showing a state in which the output member 75 of the swing mechanism 7 is attached to the bearing portion 17 of the first case 11. As shown in FIG. 9, the output member 75 is rotatably supported by the bearing portion 17 at a portion larger in diameter than the output gear 76. Since the bearing portion 17 penetrates the end plate portion 111, the end portion on the + Z direction side of the output member 75 protrudes to the + Z direction side of the end plate portion 111. Therefore, the swing member drive shaft 300 (see FIG. 1) described above is connected to the output member 75, and the swing motion of the output member 75 can be transmitted to the swing member drive shaft 300.

  As shown in FIG. 10, when the output member 75 is attached to the bearing portion 17, the positioning protrusion 754 of the output member 75 is placed on the end surface of the cylindrical portion 171. The output member 75 can swing between a position where the positioning projection 754 contacts the one end 174 in the circumferential direction of the restricting portion 173 and a position where the positioning projection 754 contacts the other end 175 in the circumferential direction of the restricting portion 173. is there. By assembling the output member 75 so that the positioning protrusion 754 is brought into contact with one end 174 or the other end 175 in the circumferential direction of the restricting portion 173, the rotational position of the output gear 76 can be easily adjusted.

  In the swing mechanism 7, the link driven gear 72 has a larger diameter than the output gear 76, and the link driven gear 72 and the output gear 76 constitute a speed increasing mechanism. In this embodiment, the number of teeth of both gears is set so that the swing angle of the output gear 76 is twice the swing angle of the link driven gear 72. Specifically, the swing angle of the output gear 76 is 220 °, and the swing angle of the link driven gear 72 is 110 °. Thus, by using the speed increasing mechanism, the output gear 76 can be swung within an angle range exceeding 180 degrees.

(Function and effect)
As described above, the actuator 1 of this embodiment can drive the first output member 3 </ b> A and the second output member 3 </ b> B by the common motor 2. The driving force transmission mechanism 4 includes a first state in which the rotation of the driving gear 521 is transmitted to the first gear 531 of the first output-side rotator 53, and the rotation of the driving gear 521 is a second output-side rotator 54. The second state is transmitted to the second gear 541. In this way, since the driving force of the motor 2 can be switched to one of the first output member 3A and the second output member 3B and transmitted, the first output member 3A and the second output member 3B can be transmitted by the common motor 2. Although it is a structure to drive, it is not necessary to enlarge the motor 2. Therefore, the actuator 1 can be reduced in size. In addition, since the transmission destination of the driving force can be switched depending on the magnitude of the rotational load of the first output member 3A and the second output member 3B, the one with the smaller rotational load is driven first, and as a result, the one driven first When the rotational load increases, the transmission destination of the driving force can be switched to the other to drive the other. Accordingly, the first output member 3A and the second output member 3B can be alternately driven by the common motor 2.

In addition, the actuator 1 of the present embodiment uses the planetary gear mechanism 50A having a large reduction ratio, and the first driven gear 61A formed on the first output member 3A and the second driven gear formed on the second output member 3B. The drive gear 61B is directly meshed with the first gear 531 and the second gear 541 formed in the output element of the planetary gear mechanism 50A. Therefore, the installation space of the driving force transmission mechanism 4 can be reduced, and the reduction ratio can be increased. Accordingly, a reduction gear ratio between the motor 2 and the first output member 3A and the second output member 3B is large, and a small actuator can be realized.

  Further, in the driving force transmission mechanism 4 of the present embodiment, the outer diameter of the second gear 541 formed on the second output-side rotator 54 is the bottom of the first gear 531 formed on the first output-side rotator 53. Smaller than the diameter. Accordingly, the first driven gear 61 </ b> A that meshes with the first gear 531 can be extended to the outer peripheral side of the second gear 541. Therefore, the meshing width between the gears can be ensured, and the first output-side rotating body 53 can be thinned. As a result, the differential gear mechanism 50 can be thinned in the Z-axis direction.

  Further, the driving force transmission mechanism 4 of the present embodiment has a support shaft 51 attached to the first case 11, and includes a second output side rotating body 54, a first output side rotating body 53, and a driving side rotating body 52 in this order. The differential gear mechanism 50 can be assembled by dropping the rotating body into the first case 11. Therefore, the assembly of the driving force transmission mechanism 4 is easy.

  Further, the driving force transmission mechanism 4 of this embodiment includes a reduction ratio (first reduction ratio) between the motor 2 and the first output member 3A and a reduction ratio (second reduction ratio) between the motor 2 and the second output member 3B. The first output member 3A and the second output member 3B can be driven with substantially the same torque. It is desirable that the first reduction ratio and the second reduction ratio be the same. If the first reduction ratio and the second reduction ratio are the same, the first output member 3A and the second output member 3B can be driven with the same torque.

  Further, the actuator 1 according to the present embodiment not only rotates the first filter drive shaft 200A and the second filter drive shaft 200B alternately, but also swings the swing member drive shaft 300 based on the rotation of the motor 2. It functions as the device 1A. In this embodiment, the link drive gear 71 constituting the swing mechanism 7 is positioned on the first case 11 via the cap 73, and the opening 735 formed in the cap 73 and the recess 162 formed in the cap mounting portion 16. Thus, the upper and lower bearings of the link drive gear 71 are configured. The cap 73 is positioned in contact with the positioning portion 163 of the first case 11. Thus, by providing the positioning part 163 in the first case 11, the assembly accuracy of the cap 73 is high, and the assembly accuracy of the link drive gear 71 that is positioned via the cap 73 is high. And the positioning part 163 is provided in three places of equiangular intervals inside the cap 73, and contact | abuts with respect to the peripheral wall 732 of the cap 73 at three places from the inner peripheral side. In such a configuration, it is not necessary to secure a space for providing the positioning portion on the outer peripheral side of the cap 73, so that the swing device 1A can be reduced in size. Further, the positioning operation of the cap 73 is easy. In addition, the positioning part 163 may be four or more places.

  Further, in the swing mechanism 7 of this embodiment, a bearing portion 17 that rotatably supports the output member 75 is provided in the first case 11, and the bearing portion 17 has a restriction portion 173 that restricts the swing range of the output member 75. In addition, the output member 75 is provided with a positioning protrusion 754. Therefore, the swinging position of the output member 75 can be adjusted by bringing the restricting portion 173 and the positioning protrusion 754 into contact with each other. Therefore, it is not necessary to assemble the output member 75 while visually confirming the swing position of the output member 75, and the assembly work of the output member 75 is easy.

  Further, the swing mechanism 7 of this embodiment includes a shaft hole through which the bearing portion 17 that rotatably supports the base portion of the output member 75 passes through the end plate portion 111 of the first case 11. Therefore, the output member 75 can transmit the swing motion to the swing member drive shaft 300 provided outside the case 10 via the bearing portion 17.

  In the swing mechanism 7 of the present embodiment, the link driven gear 72 has a larger diameter than the output gear 76, and the link driven gear 72 and the output gear 76 constitute a speed increasing mechanism. Therefore, the output gear 76 can be swung within an angle range exceeding 180 degrees.

(Modification)
FIG. 11 is a development view of a differential gear mechanism of a modified example. In the above embodiment, out of the drive gear 521, the first gear 531 and the second gear 541, the outer diameter D1 of the second gear 541 is smaller than the root diameter D2 of the other two gears. Although the tooth bottom diameter D2 and the outer diameter of the gear 531 are the same, the differential gear mechanism 50 according to the modified example is configured such that the outer diameter D1 of the second gear 541 is the tooth bottom of the first gear 531 as shown in FIG. In addition, the outer diameter D3 of the first gear 531 is smaller than the root diameter D4 of the drive gear 521, which is smaller than the diameter D2.

  As described above, the differential gear mechanism 50 according to the modified example has two gears adjacent to each other in the Z-axis direction for each of the three rotating body gears (the drive gear 521, the first gear 531 and the second gear 541). One outer diameter is set to be smaller than the other root diameter. With such a dimension setting, not only the first driven gear 61A that meshes with the first gear 531 protrudes to the outer peripheral side of the second gear 541, but also the large-diameter gear portion 431 that meshes with the drive gear 521. One gear 531 can be projected to the outer peripheral side. Therefore, it is possible to reduce the thickness of each of the three rotating bodies and to secure the meshing width between the gears. Therefore, the differential gear mechanism 50 can be thinned in the Z-axis direction, and the actuator 1 can be thinned in the Z-axis direction. In addition, since the drive gear 521 can have a larger diameter than the first gear 531 and the second gear 541, the reduction ratio can be increased.

  In this way, when the outer diameter is reduced in the order of the drive gear 521, the first gear 531 and the second gear 541, when the parts of the differential gear mechanism 50 are assembled to the support shaft 51, the parts having a smaller diameter. Can be assembled in order. Therefore, the assembly of the driving force transmission mechanism is easy.

(Other embodiments)
(1) In the above embodiment, the differential gear mechanism 50 that alternately rotates the first output member 3A and the second output member 3B based on the rotation of the motor 2 is provided with the planetary gear mechanism 50A. Other differential mechanisms that distribute and rotate the rotation of the motor 2 to the two output members may be used.

(2) Although the actuator 1 of the said form was used for the filter drive device and rotated a filter drive shaft, the actuator 1 can also be used for the apparatus which drives another drive shaft.

(3) The actuator 1 having the above-described configuration functions as the swinging device 1A that swings the swinging member driving shaft 300, and the swinging member driving shaft 300 drives a member for cleaning the filter. However, it can also be used as a swinging device 1A that drives a swinging member other than the cleaning member.

DESCRIPTION OF SYMBOLS 1 ... Actuator, 1A ... Swing apparatus, 2 ... Motor, 3A ... 1st output member, 3B ... 2nd output member, 4 ... Drive force transmission mechanism, 7 ... Swing mechanism, 10 ... Case, 11 ... 1st case 12 ... second case, 13 ... recess, 14A ... bearing, 14B ... bearing, 15 ... recess, 16 ... cap mounting, 17 ... bearing, 18 ... bearing, 20 ... terminal, 21 ... terminal pin , 22 ... pinion, 30 ... wiring take-out part, 31 ... recess, 32 ... terminal pin, 33 ... flat cable, 34 ... wall part, 35 ... guide wall, 40 ... reduction gear train, 41 ... first gear, 42 ... first 2 gears, 43
3rd gear, 50 ... Differential gear mechanism, 50A ... Planetary gear mechanism, 51 ... Support shaft, 52 ... Drive side rotator, 53 ... 1st output side rotator, 54 ... 2nd output side rotator, 55 ... Planetary gear, 60A ... shaft, 60B ... shaft, 61A ... first driven gear, 61B ... second driven gear, 62 ... concave, 63 ... projection, 71 ... link drive gear, 72 ... link driven gear, 73 DESCRIPTION OF SYMBOLS ... Cap, 74 ... Link, 75 ... Output member, 76 ... Output gear, 100 ... Filter drive device, 111 ... End plate part, 112 ... Side plate part, 113 ... Convex part, 114, 115, 116 ... Concave part, 121 ... End Plate part 122... Side plate part 123... Hook, 124. Recessed part, 161. Annular convex part, 162. Recessed part, 163. Positioning part, 171 ... cylindrical part, 173 ... restricting part, 174 ... one end, 175. 200A: Filter drive shaft, 200B Filter drive shaft, 300 ... Oscillating member drive shaft, 411 ... Large diameter gear portion, 412 ... Small diameter gear portion, 413 ... Gear shaft, 421 ... Large diameter gear portion, 422 ... Small diameter gear portion, 423 ... Gear shaft, 431 ... Large gear portion, 432 ... Small gear portion, 433 ... Gear shaft, 521 ... Drive gear, 522 ... Large diameter portion, 523 ... Small diameter portion, 524 ... Sun gear, 525 ... Shaft hole, 531 ... First gear, 532 ... Cylindrical part, 533 ... planet carrier, 534 ... end plate part, 535 ... support shaft, 536 ... wall part, 537 ... convex part, 538 ... circular opening, 541 ... second gear, 542 ... cylindrical part, 543 ... end plate part 544 ... Internal gear 545 ... Shaft hole 546 547 ... Recessed part 711 ... Shaft body 712 ... Circular convex part 721 ... Shaft body 722 ... Tooth part 731 ... Annular part 732 ... Peripheral wall 733 ... Boss part, 734 ... Notch part, 735 ... Opening 751 ... first member, 752 ... second member, 753 ... disc portion, 754 ... positioning projection, 755 ... shaft, L, L1, L2, L3 ... rotation axis, D1 ... outer diameter of second gear, D2 ... Root diameters of the first gear and the drive gear, D3: outer diameter of the first gear, D4: Root diameter of the drive gear

Claims (6)

A first output member, a second output member, a motor, and a driving force transmission mechanism that rotates the first output member and the second output member based on rotation of the motor;
The driving force transmission mechanism is
A drive gear to which rotation of the motor is transmitted;
A first gear that rotates the first output member based on rotation of the drive gear;
A second gear that rotates the second output member based on the rotation of the drive gear,
Switching between a first state in which the rotation of the drive gear is transmitted to the first gear and a second state in which the rotation of the drive gear is transmitted to the second gear ;
The driving force transmission mechanism is
A planetary gear mechanism having a sun gear, a planetary gear meshing with the sun gear, a planet carrier holding the planetary gear, and an internal gear meshing with the planetary gear;
A drive-side rotator comprising the drive gear and the sun gear;
A first output-side rotator comprising the first gear and the planet carrier;
A second output-side rotator comprising the second gear and the internal gear,
The outer diameter of the second gear formed on the outer peripheral edge of the second output-side rotator is the root diameter of the drive gear formed on the outer peripheral edge of the drive-side rotator and the first output-side rotator. An actuator characterized in that it is smaller than the root diameter of the first gear formed on the outer peripheral edge of the first gear .   The actuator according to claim 1, wherein the drive gear, the first gear, and the second gear are arranged coaxially. 3. The actuator according to claim 1, wherein an outer diameter of the first gear is smaller than a root diameter of the drive gear. A spindle that passes through the rotation center of the drive side rotator, the first output side rotator, and the second output side rotator;
A case for supporting an end portion of the support shaft,
The drive-side rotator, the first output-side rotator, and the second output-side rotator are in the order of the second output-side rotator, the first output-side rotator, and the drive-side rotator. The actuator according to claim 1 , wherein the actuator is attached to a support shaft. The driving force transmission mechanism is switched between the first state and the second state based on the rotational load of the first output member and the rotational load of the second output member. The actuator according to any one of items 1 to 4 . The driving force transmission mechanism is
Decelerating the rotation of the motor with a first reduction ratio and transmitting it to the first output member;
Decelerating the rotation of the motor with a second reduction ratio and transmitting it to the second output member;
The actuator according to any one of claims 1 to 5 , wherein the first reduction ratio and the second reduction ratio are the same.