JP6454231B2 - Drive device - Google Patents

Description

  The present invention relates to a drive device capable of transmitting power between a first gear member and a second gear member.

  Conventionally, a technique of providing an electric seat on a vehicle is known, and an example of the electric seat is described in Patent Document 1. The electric seat described in Patent Literature 1 includes a driving device and a seat. The drive device includes an electric motor and a speed reduction mechanism, and the speed reduction mechanism is provided in the gear case. The electric motor has a worm shaft, and the worm shaft can rotate forward and backward. The reduction mechanism includes a worm wheel that meshes with the worm shaft, a small-diameter gear that is a first gear member coaxial with the worm wheel, and a spur gear that is a second gear that meshes with the small-diameter gear. The worm wheel and the small-diameter gear are rotatably attached to the support shaft, and the support shaft is supported by a cover.

  An output shaft is provided over the inside and outside of the gear case, and the output shaft is rotatably supported by a guide member. The guide member is attached to the gear case via a bracket. The guide part has an annular part. The output shaft has an eccentric cam, and the eccentric cam is disposed in the annular portion. The spur gear is rotatably attached to the outer peripheral surface of the output shaft. A cam plate is attached to the eccentric cam of the output shaft. The cam plate is provided with a fitting hole at a position eccentric from the axis, and the eccentric cam is disposed in the fitting hole. An elongated hole is provided in the cam plate. Further, a pin is provided on the spur gear, and the pin is inserted into the elongated hole.

  In the electric seat described in Patent Document 1, the rotational force of the worm shaft of the electric motor is transmitted to the spar gear via the worm wheel and the small diameter gear. The rotational force of the spur gear is transmitted to the cam plate via the pin, and the rotational force of the cam plate is transmitted to the eccentric cam and the output shaft. Therefore, when the worm shaft rotates forward or backward, the seat surface of the seat can be raised and lowered.

  On the other hand, when an external force is applied to the seat and a rotational force is applied to the output shaft, the eccentric cam tends to rotate about the axis. For this reason, the cam plate moves within a range corresponding to the gap between the long hole and the pin, and the outer peripheral surface of the cam plate is pressed against the inner surface of the annular portion. As a result, the frictional force between the cam plate and the annular portion becomes a braking force, and the rotational force of the output shaft can be prevented from being transmitted to the spar gear. In this way, the spur gear, cam plate, and output shaft serve as a clutch device that prevents the rotational force of the output shaft from being transmitted to the electric motor in addition to transmitting the rotational force of the electric motor to the seed. Fulfill.

JP 2013-148118 A

  However, the drive device described in Patent Document 1 includes a cover for positioning the first gear member in the radial direction via the support shaft, and a guide member for positioning the second gear member in the radial direction via the output shaft. It is provided separately. For this reason, the accuracy of positioning the first gear member and the second gear member in the radial direction may be reduced.

  The objective of this invention is providing the drive device which can improve the precision which positions a 1st gear member and a 2nd gear member in radial direction.

The present invention includes a first reduction mechanism and a second reduction mechanism that are arranged in series in a power transmission path from a motor to an output member, and a casing that includes an accommodating portion that accommodates the first reduction mechanism and the second reduction mechanism. The first reduction mechanism includes a worm shaft that transmits the power of the motor and a worm wheel that meshes with the worm shaft, and the second reduction mechanism includes the worm wheel and the worm wheel. A first gear member disposed concentrically and rotatable about a first axis, and a first gear member meshing with the first gear member and rotatable about a second axis parallel to the first axis. Two gear members, positioning the first gear member and the second gear member in a direction intersecting the first axis and the second axis, and covering the housing portion. Cover is installed Is, while transmitting a rotational force of the second gear member to said output member, a clutch mechanism is provided to prevent the rotational force of the output member is transmitted to the second gear member, the clutch mechanism, A brake member that prevents the rotational force of the output member from being transmitted to the second gear member by applying a brake force to the output member; and the brake member is supported by the cover; the cover, position the first gear member via the brake member.

  The present invention includes a first support shaft that rotatably supports the first gear member, and a second support shaft that rotatably supports the second gear member, and the casing includes the first axis. And a positioning mechanism that positions the first support shaft and the second support shaft in a direction intersecting the second axis.

  In the present invention, the second gear member is disposed concentrically with the output member and is rotatably attached to the output member, and the cover is connected to the second gear via the output member. Position the member.

  The present invention is provided with a detent mechanism that prevents the brake member from rotating about the second axis with respect to the cover.

  According to the present invention, the accuracy of positioning the first gear member and the second gear member in the radial direction is improved.

It is a disassembled perspective view which shows the drive device of this invention. It is a typical top view which shows the drive device of this invention. It is a typical front view which shows the drive device of this invention. It is sectional drawing in the IV-IV line of FIG. It is a partial top view which shows the drive device of this invention. It is a side view of the electric seat which attached the drive device of the present invention. It is a rear view of the electric seat which attached the drive device of the present invention. It is a typical top view which shows the other structural example of the drive device of this invention. It is sectional drawing in the IX-IX line of FIG.

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

  The drive device 10 shown in FIGS. 1 to 4 includes an electric motor 11, a first reduction mechanism 12, a second reduction mechanism 44, and a casing 13 having an accommodating portion 45 that accommodates the first reduction mechanism 12 and the second reduction mechanism 44. And a cover 14 fixed to the casing 13 with a screw member. The casing 13 may be made of either metal or synthetic resin, and the cover 14 covers the accommodating portion 45. The electric motor 11 is a motor with a brush, a cylindrical yoke 15 fixed to the casing 13, a permanent magnet 16 fixed to the inner periphery of the yoke 15, and a rotor 17 disposed rotatably in the yoke 15. Have.

  The rotor 17 includes a rotating shaft 18, a commutator 19 fixed to the rotating shaft 18, a brush that energizes the commutator 19, a brush holder 20 that supports the brush, and a rotor core 21 that is attached to the rotating shaft 18. The rotor core 21 has a coil connected to the commutator 19. A worm shaft 22 that rotates integrally with the rotary shaft 18 is provided, and the worm shaft 22 is disposed in the casing 13. A worm gear 23 is formed on the outer peripheral surface of the worm shaft 22. The rotating shaft 18 and the worm shaft 22 are rotatably supported by bearings, and can rotate about an axis A1 that is the rotation center of the rotating shaft 18.

  A housing part 45 is provided in the casing 13, and the worm wheel 24, the small diameter gear 25, and the large diameter gear 26 are housed in the housing part 45. The worm wheel 24 is connected to the small diameter gear 25 so as to rotate integrally, and the worm wheel 24 and the small diameter gear 25 are disposed concentrically. The worm wheel 24 and the small diameter gear 25 are supported by a support shaft 27. A gear 28 is formed on the outer periphery of the worm wheel 24, and the gear 28 meshes with the worm gear 23. When the rotational force of the worm shaft 22 is transmitted to the worm wheel 24, the rotational speed of the worm wheel 24 is lower than the rotational speed of the worm shaft 22. That is, the worm shaft 22 and the worm wheel 24 constitute the first reduction mechanism 12. Further, a support hole 29 is provided in the casing 13, and one end of the support shaft 27 is inserted into the support hole 29.

  The cover 14 is fixed to the casing 13 using a fixing element such as a screw member. Both the casing 13 and the cover 14 are fixed to the vehicle body. That is, the cover 14 does not rotate. The cover 14 is formed by pressing a metal material, and is provided with a support hole 30 that penetrates the cover 14 in the thickness direction. The cover 14 includes an annular storage portion 31 that surrounds the support hole 30, and a storage portion. And a concave portion 32 continuous to the outside in the radial direction of 31. The support hole 30 is provided in a circle around the axis A2. A brake ring 33 is accommodated in the accommodating portion 31 and the recessed portion 32.

  The brake ring 33 is made of metal, and the brake ring 33 has an annular main body 34 and a detent 35 that protrudes outward from the main body 34 in the radial direction. The main body 34 is accommodated in the accommodating portion 31, and the rotation stopper 35 is accommodated in the recessed portion 32. For this reason, the brake ring 33 is fixed so as not to rotate in the circumferential direction about the axis A2. The inner peripheral surface 34A of the main body 34 is circular with the axis A2 as the center. Moreover, the brake ring 33 is positioned in the direction which cross | intersects with respect to axis line A2 because the outer peripheral surface of the brake ring 33 contacts the inner surface of the accommodating part 31, and the inner surface of the recessed part 32. FIG. Furthermore, a support hole 36 is provided in the rotation stopper 35.

  As shown in FIG. 4, the support hole 36 of the brake ring 33 and the support hole 29 of the casing 13 are arranged concentrically with the drive device 10 assembled, and the end of the support shaft 27 supports the brake ring 33. It is pivotally supported by the hole 36 and the support hole 29 of the casing 13. In this way, the worm wheel 24 and the small diameter gear 25 are supported so as to be rotatable about the axis A3 passing through the rotation center of the support shaft 27.

  An output member 37 is disposed from the inside of the housing portion 45 to the outside of the cover 14. The output member 37 is made of metal, and the output member 37 is concentric with the first shaft portion 38, the power transmission portion 39 provided concentrically with the first shaft portion 38, and the first shaft portion 38. It has the provided 2nd shaft part 40 and the gear part 41 which follows the 2nd shaft part 40. A support hole 42 is provided in the casing 13, and the first shaft portion 38 is rotatably disposed in the support hole 42. The axis A2 is a line passing through the rotation center of the output member 37.

  Further, the second shaft portion 40 is rotatably disposed in the support hole 30 of the cover 14. In other words, the output member 37 is supported by the casing 13 and the cover 14 so as to be rotatable about the axis A2, and is positioned in the radial direction about the axis A2. The second shaft portion 40 and the power transmission portion 39 are disposed between the first shaft portion 38 and the gear portion 41 in the direction of the axis A2. Further, the power transmission unit 39 is disposed between the first shaft portion 38 and the second shaft portion 40 in the direction of the axis A2. The gear portion 41 is disposed outside the cover 14, the power transmission portion 39 is disposed in the housing portion 31, and the first shaft portion 38 is disposed in the housing portion 45.

  The large diameter gear 26 has a shaft hole 43, and the first shaft portion 38 of the output member 37 is inserted into the shaft hole 43 of the large diameter gear 26 and the support hole 42 of the casing 13. That is, the large-diameter gear 26 is disposed concentrically with the output member 37 and can rotate relative to the output member 37. Further, the large diameter gear 26 meshes with the small diameter gear 25. The outer diameter of the large-diameter gear 26 is larger than the outer diameter of the small-diameter gear 25, and when the rotational force of the small-diameter gear 25 is transmitted to the large-diameter gear 26, the large-diameter gear 26 corresponds to the rotational speed of the small-diameter gear 25. The rotation speed of is slower. That is, the small diameter gear 25 and the large diameter gear 26 constitute a second reduction mechanism 44. The first reduction mechanism 12 and the second reduction mechanism 44 are arranged in series with each other in a power transmission path from the electric motor 11 to the output member.

  A plurality of, specifically six, pins 46 are fixed to the large diameter gear 26. The six pins 46 are provided at intervals in the rotation direction of the large-diameter gear 26. The six pins 46 are all made of metal and have a cylindrical shape. The center Q1 of each pin 46 is arranged on the same circumference centering on the axis A2. The distance from the axis A2 to the center Q1 of the pin 46 is L1.

  The power transmission portion 39 of the output member 37 has three engaging portions 47 arranged at intervals in the rotation direction, specifically, at intervals of 120 degrees. Further, as shown in FIG. 5, cam surfaces 48 and 49 are respectively formed on the power transmission unit 39 between the engaging portions 47. The cam surfaces 48 and 49 are curved in a plan view perpendicular to the axis A2. The cam surface 48 and the cam surface 49 are formed to be curved so that the distance from the rotation center of the output member 37 decreases as the predetermined engagement portion 47 approaches the other engagement portion 47. That is, the cam surfaces 48 and 49 are located farthest from the engaging portion 47, that is, at an intermediate portion between the two engaging portions 47, and the distance from the rotation center of the output member 37 is the shortest and closest to the engaging portion 47. The distance from the rotation center of the output member 37 is the largest at the location.

  Further, the six rollers 50 and 51 are disposed between the main body 34 of the brake ring 33 and the power transmission unit 39 of the output member 37. Specifically, the rollers 50 are respectively disposed between the cam surface 48 and the main body 34, and the rollers 51 are respectively disposed between the cam surface 49 and the main body 34. That is, in the rotation direction of the output member 37, three of the six pins 46 are arranged between the engaging portion 47 and the roller 50, and the remaining three pins 46 are engaged. They are respectively arranged between the joint portion 47 and the roller 51. The rollers 50 and 51 are cylindrical, and the center lines of the rollers 50 and 51 are parallel to the axis A2. The diameters of the rollers 50 and 51 are all the same, and the diameters of the rollers 50 and 51 are larger than the diameters of the pins 46.

  The diameter of the pin 46 is smaller than the minimum value of the gap amount between the cam surface 48 and the inner peripheral surface 34A. Further, the diameter of the roller 50 is larger than the minimum value of the gap amount between the cam surface 48 and the inner peripheral surface 34A and smaller than the maximum value. Further, the diameter of the roller 51 is larger than the minimum value of the gap amount between the cam surface 49 and the inner peripheral surface 34A and smaller than the maximum value. The gap amount between the cam surface 48 and the inner peripheral surface 34A and the gap amount between the cam surface 49 and the inner peripheral surface 34A are values in the radial direction centered on the axis A2. The rollers 50 and 51 can roll independently, respectively, and can move within the gap amount in the radial direction of the output member 37 centering on the axis A2.

  In a state where the rollers 50 and 51 are in contact with the inner peripheral surface 34A of the brake ring 33, the centers Q2 of the rollers 50 and 51 are arranged on the same circumference. Further, since the diameters of the rollers 50 and 51 are larger than the diameter of the pin 46, the radius L2 of the circle passing through the center Q2 is smaller than the radius L1. Further, springs 52 are respectively disposed between the rollers 50 and 51 in the rotation direction of the output member 37. The spring 52 is a metal compression coil spring, and the spring 52 has a resilient force in the rotation direction of the output member 37. The spring 52 is sandwiched between the roller 50 and the roller 51 in a state where the spring 52 is disposed between the roller 50 and the roller 51, receives a compressive load, and is elastically deformed. The rollers 50 and 51 are constantly subjected to a force in the direction of biting between the inner peripheral surface 34A of the brake ring 33 and the cam surface 48 and the cam surface 49 by the elastic force of the spring 52.

  The drive device 10 described above can be used in an electric seat 60 for a vehicle as shown in FIG. The electric seat 60 includes a seat portion 61 and a backrest portion 62 that can change an inclination angle with respect to the seat portion 61. The seat portion 61 is movable in the height direction of the vehicle or in the front-rear direction of the vehicle. The drive device 10 has a function as an actuator for moving the seat portion 61, and FIG. 6 is an example in which the drive device 10 is provided in the seat portion 61. An operation when the electric seat is operated by the power of the driving device 10 will be described. When a current is supplied to the rotor core 21 of the electric motor 11, a rotating magnetic field is formed between the rotor core 21 and the permanent magnet 16, and the rotor 17 rotates. When the direction of the current supplied to the rotor core 21 is switched, the rotation direction of the rotor 17 can be switched between forward and reverse. When the worm shaft 22 rotates together with the rotor 17, the rotational force of the worm shaft 22 is transmitted to the worm wheel 24.

  The small diameter gear 25 rotates integrally with the worm wheel 24, and the rotational force of the small diameter gear 25 is transmitted to the large diameter gear 26. When the large-diameter gear 26 rotates clockwise about the axis A2 in FIG. 5, among the six pins 46, the three pins 46 positioned between the engaging portion 47 and the roller 50 are cam surfaces. The roller 50 biting in between 48 and the inner peripheral surface 34A is pushed out, and the biting of the roller 50 is released. Of the six pins 46, the three pins 46 positioned between the engaging portion 47 and the roller 51 are pressed against the engaging portion 47. 5 is transmitted to the output member 37 via the pin 46 and the engaging portion 47, and the seat portion 61 is moved by the rotational force of the output member 37.

  On the other hand, when the direction of the electric current with respect to the electric motor 11 is switched and the large-diameter gear 26 rotates counterclockwise in FIG. 5, the six pins 46 are positioned between the engaging portion 47 and the roller 51. The three pins 46 push out the roller 51 biting between the cam surface 49 and the inner peripheral surface 34A, and release the biting of the roller 51. Of the six pins 46, the three pins 46 positioned between the engaging portion 47 and the roller 50 are pressed against the engaging portion 47. As described above, the counterclockwise rotational force in FIG. 5 of the large-diameter gear 26 is transmitted to the output member 37 via the pin 46 and the engaging portion 47, and the seat portion 61 moves by the rotational force of the output member 37. . When the electric motor 11 stops, the output member 37 stops and the seat portion 61 also stops.

  On the other hand, when a clockwise rotational force in FIG. 5 is applied from the seat portion 61 to the output member 37 due to a vehicle occupant exerting a force on the seat portion 61, the engaging portion 47 is Prior to being pressed against the pin 46 positioned between the engaging portion 47 and the roller 50, the roller 50 positioned outside the cam surface 48 is moved by the elastic force of the spring 52 to the cam surface 48 and the inner peripheral surface 34A. I bite in between. Therefore, a braking force is generated by the wedge action that the roller 50 bites between the cam surface 48 and the inner peripheral surface 34 </ b> A, and the rotational force of the output member 37 is not transmitted to the large-diameter gear 26.

  When the counterclockwise rotational force in FIG. 5 is applied from the seat portion to the output member 37, the engaging portion 47 is pressed against the pin 46 positioned between the engaging portion 47 and the roller 51. Before that, the roller 51 located outside the cam surface 49 bites between the cam surface 49 and the inner peripheral surface 34 </ b> A by the elastic force of the spring 52. Therefore, the braking force is generated by the wedge action that the roller 51 bites between the cam surface 49 and the inner peripheral surface 34 </ b> A, and the rotational force of the output member 37 is not transmitted to the large-diameter gear 26. As described above, the output member 37, the rollers 50 and 51, the brake ring 33, and the cam surfaces 48 and 49 have a function as the clutch mechanism 63. Therefore, the rotational force applied from the seat portion 61 to the output member 37 can be prevented from being transmitted to the electric motor 11.

  When the rotational force of the electric motor 11 is applied to the output member 37 from the seat portion 61 while the large-diameter gear 26 is rotating in a predetermined direction, the driving device 10 applies the force from the seat portion 61 to the output member 37. The applied force can prevent the large-diameter gear 26 from rotating in the reverse direction. That is, the clutch mechanism 63 also serves as a reverse rotation prevention mechanism.

  In the driving device 10, the small diameter gear 25 and the large diameter gear 26 are both positioned in the radial direction by the casing 13 and the brake ring 33. That is, the elements for positioning the small diameter gear 25 and the large diameter gear 26 in the radial direction are common. Therefore, the meshing accuracy between the small diameter gear 25 and the large diameter gear 26 can be improved, and the noise can be reduced. Further, when the operation of assembling the drive device 10 is performed, the small diameter gear 25 and the large diameter gear 26 can be easily positioned in the radial direction, and the assembling workability is improved.

  Further, the radius L1 of the circle passing through the center Q1 of the pin 46 is larger than the radius L2 of the circle passing through the center Q2 of the rollers 50, 51 in a state where the rollers 50, 51 are in contact with the inner peripheral surface 34A. For this reason, the projection area of the drive device 10 can be reduced in plan view perpendicular to the axis A2. Therefore, when the drive device 10 is mounted in the vehicle, the layout is improved, and the drive device 10 is disposed in the seat 61 so that the axis A2 is in the horizontal direction as shown in FIG. Can contribute to the suppression of height.

  Furthermore, the cross-sectional shape of the pin 46 is circular. Therefore, manufacture of the pin 46 is easy. Further, the diameter of the pin 46 is smaller than the diameter of the rollers 50 and 51. Further, the radius L1 is larger than the radius L2. Accordingly, the pin 46 surely acts to release the biting of the rollers 50 and 51. Also, when a rotational force is applied from the seat portion to the output member 37, the roller 50 bites between the cam surface 48 and the inner peripheral surface 34A before the engaging portion 47 contacts the pin 46, or The roller 50 bites between the cam surface 49 and the inner peripheral surface 34A. Therefore, when a rotational force is applied from the seat portion to the output member 37, the braking force can be applied to the output member 37 before the rotational force is transmitted to the large-diameter gear 26.

  Further, the detent 35 plays a role of detent preventing the brake ring 33 from rotating about the axis A2 in addition to the role of positioning the support shaft 27 in the radial direction. Therefore, it is not necessary to provide a dedicated detent element for the brake ring 33. Further, the detent 35 is provided outside in the radial direction of the main body 34. Therefore, the brake ring 33 is thick in the radial direction, and the strength is improved.

  Further, a pin 46 and an engaging portion 47 that play a role of transmitting the rotational force of the large-diameter gear 26 to the output member 37, and a clutch mechanism 63 having a function of applying a braking force to the output member 37 are provided separately. Yes. Therefore, even if the rollers 50 and 51 or the cam surfaces 48 and 49 are worn, it is possible to suppress a decrease in the function of transmitting the rotational force of the large-diameter gear to the output member 37.

  Further, the pins 46 and the engaging portions 47 that transmit the rotational force of the large-diameter gear 26 to the output member 37 are arranged at predetermined intervals in the circumferential direction around the axis A2 and on the same width. ing. The rollers 50 and 51 and the brake ring 33 for applying a braking force to the output member 37 are arranged in the circumferential direction about the axis A2 and arranged on the circumference of the same width. Therefore, the radial load received by the output member 37 and the support holes 30 and 42 can be reduced.

  Further, as shown in FIG. 5, the outer diameter L3 of the main body 34 of the brake ring 33 is smaller than the distance L4 between the axis A2 and the axis A3. Furthermore, the distance L5 between the axis A1 and the axis A2 shown in FIG. 2 is smaller than the outer diameter L3. Accordingly, when the driving device 10 is provided on the seat portion 61 as shown in FIG. 6, the height of the seat portion 61 can be suppressed by arranging the axes A1 and A2 horizontally.

  Further, the small diameter gear 25 and the large diameter gear 26 constituting the second reduction mechanism 44 may be either a helical gear or a spur gear, but if a spur gear is used, the small diameter gear 25 and the large diameter gear 26 Generation of component forces in the directions of the axes A2 and A3 can be suppressed at the meshing locations. Therefore, it is possible to suppress the occurrence of periodic meshing sound at the meshing location between the small diameter gear 25 and the large diameter gear 26.

  Furthermore, since the clutch mechanism 63 and the second speed reduction mechanism 44 are constituted by separate elements, the second speed reduction mechanism 44 can employ a meshing mechanism with high power transmission efficiency. Therefore, it is possible to reduce the size of the driving device 10 and to reduce the size of the entire system.

  FIG. 7 is an example in which the driving device 10 is attached to the side surface of the electric seat 60. Since the first reduction mechanism 12 and the second reduction mechanism 44 are provided between the casing 13 and the cover 14, the driving device 10 can be thinned in the direction of the axis A2. The axis A2 is disposed in the horizontal direction and along the width direction of the vehicle. Therefore, the electric seat 60 can be made as wide as possible in the width direction of the vehicle.

  8 and 9 show other structural examples of the driving device 10. The cover 14 shown in FIGS. 8 and 9 does not include the recess 32. Further, the main body 34 of the brake ring 33 does not have a detent 35. The cover 14 has an engagement groove 64 that is continuous with the circular housing portion 31. An engagement protrusion 65 is provided on the outer peripheral surface of the main body 34, and the engagement protrusion 65 is disposed in the engagement groove 64. The brake ring 33 is prevented from rotating with respect to the cover 14 by the engaging force between the engaging protrusion 65 and the cover 14.

  In addition, a recess 66 is provided on the cover 14 on the housing portion 45 side, and one end of the support shaft 27 is supported by the recess 66. The recess 66 is disposed concentrically with the support hole 29. The recess 66 is disposed at a distance from the outer peripheral end of the housing portion 31. The support shaft 27 is positioned in the radial direction by the cover 14 and the casing 13. Other structures and operational effects of the driving device 10 shown in FIGS. 8 and 9 are the same as those of the driving device 10 shown in FIGS.

  The correspondence between the configuration described in this embodiment and the configuration of the present invention is as follows. The electric motor 11 corresponds to the motor of the present invention, the output member 37 corresponds to the output member of the present invention, the first reduction mechanism 12 is the first reduction mechanism of the present invention, and the second reduction mechanism 44 is This is the second reduction mechanism of the present invention. The housing portion 45 is the housing portion of the present invention, the casing 13 corresponds to the casing of the present invention, the worm shaft 22 corresponds to the worm shaft of the present invention, and the worm wheel 24 corresponds to the worm shaft of the present invention. Corresponds to the wheel. The axis A3 corresponds to the first axis of the present invention, the small diameter gear 25 corresponds to the first gear member of the present invention, the axis A2 corresponds to the second axis of the present invention, and the large diameter gear 26 The cover 14 corresponds to the second gear member of the present invention, and the cover 14 corresponds to the cover of the present invention.

  Further, the support shaft 27 corresponds to the first support shaft of the present invention, the first shaft portion 38 corresponds to the second support shaft of the present invention, and the support holes 29 and 42 correspond to the positioning mechanism of the present invention. The clutch mechanism 63 corresponds to the clutch mechanism of the present invention, and the brake ring 33 corresponds to the brake member of the present invention. The anti-rotation 35 and the recess 32 correspond to the anti-rotation mechanism of the present invention, and the engagement groove 64 and the engagement protrusion 65 correspond to the anti-rotation mechanism of the present invention.

  It goes without saying that the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the invention. For example, the first structure in which the small diameter gear 25 and the worm wheel 24 are rotatable with respect to the support shaft 27, and the support shaft 27 is fitted and fixed to the support holes 29 and 36, the small diameter gear 25 and the worm wheel 24. May be fixed to the support shaft 27, and the support shaft 27 may be any of the second structures that can rotate relative to the brake ring 33 and the casing 13. The rollers 50 and 51 may be either cylindrical or spherical. That is, the rollers 50 and 51 may be rolling elements that can move between the inner peripheral surface 34 </ b> A of the brake ring 33 and the cam surfaces 48 and 49.

  In the present invention, the direction intersecting the first axis and the second axis is a plane direction perpendicular to the first axis and the second axis, a plane direction not perpendicular to the first axis and the second axis, It includes the radial direction of a circle centered on the first axis and the second axis. The motor of the present invention includes a hydraulic motor and a pneumatic motor in addition to the electric motor. When an electric motor is used as the motor in the present invention, either a motor with a brush or a brushless motor may be used. The output member in the present invention may be an element that transmits a rotational force, and the output member includes a gear, a sprocket, a pulley, and a roller. The accommodating part in this invention is the recessed part or space provided in the casing.

DESCRIPTION OF SYMBOLS 10 Drive apparatus 11 Electric motor 12 1st reduction mechanism 13 Casing 14 Cover 15 Yoke 16 Permanent magnet 17 Rotor 18 Rotating shaft 19 Commutator 20 Brush holder 21 Rotor core 22 Worm shaft 23 Worm gear 24 Worm wheel 25 Small diameter gear 26 Large diameter gear 27 Support shaft 28 Gears 29, 30, 36, 42 Support holes 31, 45 Housing portions 32, 66 Recess 33 Brake ring 34 Main body 34A Inner circumferential surface 35 Detent 37 Output member 38 First shaft portion 39 Power transmission portion 40 Second shaft portion 41 Gear part 43 Shaft hole 44 Second reduction mechanism 46 Pin 47 Engagement part 48, 49 Cam surface 50, 51 Roller 52 Spring 60 Electric seat 61 Seat part 62 Backrest part 63 Clutch mechanism 64 Engagement groove 65 Engagement protrusion A1, A2 , A3 Axis L1, L2 Radius L3 Outer diameter L4, L5 Distance Q1 Q2 center

Claims (4)

A drive having a first speed reduction mechanism and a second speed reduction mechanism arranged in series in a power transmission path from the motor to the output member, and a casing having a housing portion for housing the first speed reduction mechanism and the second speed reduction mechanism. In the device
The first reduction mechanism is
A worm shaft to which the power of the motor is transmitted;
A worm wheel meshing with the worm shaft;
Have
The second reduction mechanism is
A first gear member disposed concentrically with the worm wheel and rotatable about a first axis;
A second gear member that meshes with the first gear member and is rotatable about a second axis parallel to the first axis;
Have
A cover for positioning the first gear member and the second gear member with respect to each other in a direction intersecting the first axis and the second axis and covering the accommodating portion ;
A clutch mechanism is provided for transmitting the rotational force of the second gear member to the output member, while preventing the rotational force of the output member from being transmitted to the second gear member;
The clutch mechanism includes a brake member that prevents a rotational force of the output member from being transmitted to the second gear member by applying a brake force to the output member;
The brake member is supported by the cover,
The cover, position the first gear member via the brake member driving device. The drive device according to claim 1, wherein
A first support shaft that rotatably supports the first gear member;
A second support shaft for rotatably supporting the second gear member;
Is provided,
The casing includes a positioning mechanism that positions the first support shaft and the second support shaft in a direction that intersects the first axis and the second axis. The drive device according to claim 1 or 2,
The second gear member is disposed concentrically with the output member and is rotatably attached to the output member;
The cover, positioning the second gear member via the output member, the drive device. The drive device according to any one of claims 1 to 3 ,
The detent mechanism of the brake member is prevented from rotating about said second axis relative to said cover that is provided, the drive device.

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