JP2014234078A - Telescopic actuator - Google Patents

Abstract

An object of the present invention is to reduce abnormal noise and vibration caused by gear backlash, and to damage a power transmission member such as a gear due to excessive external force input from a wheel to a telescopic actuator due to road surface unevenness. To prevent. In a telescopic actuator that changes a steering angle of a wheel by an expansion / contraction operation, a main body that has two connecting portions to a knuckle and a vehicle body at both ends and is configured to be extendable and contracted, a motor that drives the main body to extend and contract, A feed screw mechanism that converts the rotational motion of the motor into a telescopic motion of the main body, a drive gear 51 that rotates in conjunction with the rotation of the motor, and a driven gear that meshes with the drive gear and inputs the power of the motor to the feed screw mechanism. A gear 52, a bearing 54 that supports the drive gear, and a spring 71 that is interposed between the second housing 24 that constitutes the main body and the bearing and applies a biasing force that presses the drive gear against the driven gear. It shall be provided. [Selection] Figure 5

Description

  The present invention relates to an expansion / contraction actuator that is connected to a knuckle and a vehicle body in a vehicle and changes a steering angle of a wheel by an expansion / contraction operation.

  In four-wheeled vehicles, in recent years, for the purpose of improving the running stability of a vehicle, a rear wheel steering device that individually changes the rudder angle (toe angle) of left and right rear wheels has been provided. In the rear wheel steering device, a telescopic actuator that changes the steering angle of the wheel by extending and contracting a main body having two connecting portions to the knuckle and the vehicle body by a motor is provided on each of the left and right rear wheels.

  In such a telescopic actuator, a motor and a feed screw mechanism that converts the rotational motion of the motor into a telescopic motion of the main body are coaxially arranged with respect to the central axis of the main body that connects the centers of the two connecting portions to the knuckle and the vehicle body. An arrangement technique is known (see Patent Document 1). In this technique, a planetary gear mechanism is employed as the speed reduction mechanism in order to coaxially arrange the motor with respect to the central axis of the main body. In this technique, a configuration in which the speed reduction mechanism and the feed screw mechanism are coupled via a coupling is employed.

JP 2009-241853 A

  Now, in the telescopic actuator, the speed reduction mechanism or the like is composed of a plurality of gears, and these gears are provided with a backlash in order to ensure a smooth operation. When a reverse switching operation is performed, rattling occurs, which causes abnormal noise and vibration.

  In recent years, it has been required to simplify the structure of the telescopic actuator from the viewpoint of reducing the manufacturing cost. As one of the proposals for simplifying the structure of the telescopic actuator, a planetary gear mechanism or a coupling is used. Can be abolished.

  However, if the coupling is abolished, when an excessive external force is input from the wheel to the telescopic actuator due to road surface irregularities, this external force reverses the power transmission path that transmits the motor power to the output rod. As a result, the power transmission member such as a gear constituting the speed reducer on the power transmission path may be damaged.

  The present invention has been devised to solve such problems of the prior art, and its main purpose is to reduce abnormal noise and vibration caused by gear backlash, as well as unevenness on the road surface. Accordingly, an object of the present invention is to provide a telescopic actuator configured to prevent a power transmission member such as a gear from being damaged by an excessive external force input to the telescopic actuator from a wheel.

  A first invention made to solve the above-mentioned problems is a telescopic actuator that is connected to a knuckle and a vehicle body and changes a steering angle of a wheel by an expansion and contraction operation, and has two connection portions for the knuckle and the vehicle body at both ends. A main body configured to be extendable and retractable, a motor that drives the main body to extend and contract, a motion conversion mechanism that converts the rotational motion of the motor into the telescopic motion of the main body, and the motor that rotates in conjunction with the rotation of the motor A drive gear that engages with the drive gear and inputs the power of the motor to the motion conversion mechanism, a bearing that supports the drive gear, and a bearing that is interposed between the bearing and the main body. And a spring for applying a biasing force to the bearing to press the driving gear against the driven gear.

  According to this, since the drive gear is pressed against the driven gear by the biasing force of the spring, it is possible to reduce backlash and reduce abnormal noise and vibration. Since the bearing is elastically supported by the main body via the spring, when an excessive external force is input from the wheel to the telescopic actuator due to road surface unevenness, the spring is deformed to reduce the impact. Therefore, damage to the power transmission member such as a gear can be prevented.

  According to a second aspect of the present invention, the main body includes a recess that receives the bearing, and the spring is formed so as to surround the bearing, and is formed between an inner peripheral surface of the recess and an outer peripheral surface of the bearing. It is assumed that the arrangement is arranged.

  According to this, after mounting the spring on the bearing connected to the drive gear, the bearing and the spring may be fitted into the recess, and the assembly becomes easy.

  According to a third aspect of the present invention, the spring partially contacts the inner peripheral surface of the recess and the outer peripheral surface of the bearing, and is at a position opposite to the center of the driven gear across the center of the bearing. A first contact portion that contacts the outer peripheral surface of the bearing and a first contact portion that contacts the inner peripheral surface of the recess on both sides of the first contact portion on the side opposite to the center of the driven gear across the center of the bearing. It is set as the structure which has a 2 contact part and a 3rd contact part.

  According to this, since the second contact portion and the third contact portion press the inner peripheral surface of the recess at positions on both sides of the position where the first contact portion presses the outer peripheral surface of the bearing, the drive gear is driven by the driven gear. It is possible to stably obtain a large urging force that presses against.

  According to a fourth aspect of the present invention, the spring is provided on the outer peripheral surface of the bearing at a position in a diametrical direction perpendicular to a center line connecting the center of the bearing and the drive gear and the center of the driven gear when viewed from the axial direction. The fourth contact portion and the fifth contact portion are in contact with each other.

  According to this, since the pressing force by the fourth contact portion and the fifth contact portion acts so as to perform the centering of the bearing, the driving gear and the driven gear can be held in an optimal meshing state.

  According to a fifth aspect of the present invention, the spring projects inward in the radial direction of the bearing, and is a retaining piece that is disposed between the bottom surface of the recess and the surface of the bearing facing the recess. And an anti-rotation projecting piece that projects in the axial direction of the bearing and engages the bottom of the recess.

  According to this, it is possible to prevent the spring from being displaced or dropped out by the retaining piece. Further, the rotation-preventing projecting piece can prevent the spring from rotating according to the normal rotation and reverse rotation of the motor. Thereby, the urging force that presses the drive gear against the driven gear can be stably obtained.

  As described above, according to the present invention, since the drive gear is pressed against the driven gear by the urging force of the spring, it is possible to reduce backlash and reduce noise and vibration. Since the bearing is elastically supported by the main body via the spring, if an excessive load is input from the wheel to the telescopic actuator due to road surface unevenness, the spring is deformed to reduce the impact. Therefore, damage to the power transmission member such as a gear can be prevented.

1 is a perspective view showing a rear suspension 1 according to the present embodiment. It is a top view of the expansion-contraction actuator 7 shown in FIG. It is the side view which looked at the expansion-contraction actuator 7 shown in FIG. 1 from the vehicle body 3 side. It is sectional drawing of the expansion-contraction actuator 7 cut | disconnected by the IV-IV line | wire shown in FIG. It is principal part sectional drawing of the speed reduction mechanism 33 shown in FIG. FIG. 5 is a perspective view of a second housing 24, a drive gear 51, and a bearing 54 shown in FIG. FIG. 5 is a perspective view of main parts of a second housing 24, a drive gear 51, and a bearing 54 shown in FIG. It is sectional drawing which cut | disconnected the axial part 76 of the drive gear 51 shown in FIG. 7, and looked at the spring 71 from the axial direction.

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

  FIG. 1 is a perspective view showing a rear suspension 1 according to the present embodiment. Although FIG. 1 shows the rear suspension 1 on the left side of the wheel, the rear suspension on the right side of the wheel appears symmetrically.

  The rear suspension 1 includes a knuckle 2 that rotatably supports a wheel (rear wheel) (not shown), an upper arm 4 and a lower arm 5 that connect the knuckle 2 to the vehicle body 3 so that the knuckle 2 can move up and down, and a suspension spring that buffers the vertical movement of the wheel. And a telescopic actuator 7 which is connected to the knuckle 2 and the vehicle body 3 and changes the steering angle (toe angle) of the wheel by an expansion / contraction operation.

  The rear suspension 1 is a multi-link type double wishbone suspension, and the upper arm 4 is a so-called A-type arm, which has a connection portion 12 connected to the knuckle 2 and two front and rear connections connected to the vehicle body 3. Parts 13a and 13b. The lower arm 5 has a connection portion 14 connected to the knuckle 2 and a connection portion 15 connected to the vehicle body 3.

  The telescopic actuator 7 has a first connection portion 18 connected to the knuckle 2 and a second connection portion 19 connected to the vehicle body 3 at both ends of the main body 17. The first connection portion 18 and the second connection portion 19 are constituted by rubber bush joints. The first connecting portion 18 is connected to the knuckle 2 at a position above the connecting portion 14 of the lower arm 5 and in front of the spindle 11. The second connecting portion 19 is connected to the vehicle body 3 at a position below the connecting portion 13 a on the front side of the upper arm 4.

  When the telescopic actuator 7 arranged in this manner is expanded and contracted, the knuckle 2 rotates in the toe-in direction and the toe-out direction around the virtual kingpin axis, and the steering angle (toe angle) of the wheel can be changed. The telescopic actuator 7 also functions as a suspension arm that contributes to a change in geometry.

  Next, the telescopic actuator 7 shown in FIG. 1 will be described. FIG. 2 is a plan view of the telescopic actuator 7. FIG. 3 is a side view of the telescopic actuator 7 as seen from the vehicle body 3 side.

  As shown in FIG. 2, the telescopic actuator 7 is an integral member of the output rod (movable body) 22 formed integrally with the first connecting portion 18 and the second connecting portion 19 as members constituting the main body 17. A formed first housing 23 and a second housing 24 fastened to the first housing 23 with bolts 30 are provided. The output rod 22 is supported by the second housing 24 so as to freely advance and retract, and the entire main body 17 expands and contracts in accordance with the advance and retreat of the output rod 22.

  The telescopic actuator 7 includes a motor 25 that is fixed to the first housing 23 to drive the output rod 22 forward and backward, and a solenoid 26 that is fixed to the first housing 23 and restricts the movement of the output rod 22. ing. The solenoid 26 is provided in a state covered with a solenoid cover 27.

  Next, the arrangement positions of the motor 25 and the solenoid 26 will be described.

  In the present embodiment, the motor 25 is arranged in a state where the center axis A0 of the main body 17 connecting the center C1 of the first connection part 18 and the center C2 of the second connection part 19 and the rotation axis A1 of the motor 25 do not coincide. Yes. In particular, in the present embodiment, the motor in a state where the center axis A0 of the main body 17 and the rotation axis A1 of the motor 25 are parallel and the rotation axis A1 of the motor 25 is shifted to the vehicle rear side with respect to the center axis A0 of the main body 17. 25 is arranged.

  The centers C1 and C2 of the first connecting portion 18 and the second connecting portion 19 that define the central axis A0 of the main body 17 are cylindrical in the rubber bush joints that constitute the first connecting portion 18 and the second connecting portion 19. The center of the bushes 28 and 29 may be used.

  In the present embodiment, the motor 25 is disposed on the vehicle rear side and the solenoid 26 is disposed on the vehicle front side with the central axis A0 of the main body 17 interposed therebetween. Regarding the axial positions of the motor 25 and the solenoid 26, the motor 25 is disposed on the vehicle body side, and the solenoid 26 is disposed on the knuckle side.

  Next, the internal structure of the telescopic actuator 7 shown in FIG. 2 will be described. FIG. 4 is a cross-sectional view of the telescopic actuator 7 cut along line IV-IV shown in FIG.

  The telescopic actuator 7 is a feed screw mechanism (motion conversion mechanism) 32 that converts the rotational motion of the motor 25 into a forward / backward motion (linear motion) of the output rod 22, and the motor 25 is decelerated and transmitted to the feed screw mechanism 32. A speed reduction mechanism 33 and a lock mechanism 34 for restricting the forward / backward movement of the output rod 22 are provided. The feed screw mechanism 32, the speed reduction mechanism 33, and the lock mechanism 34 are accommodated in the first housing 23 and the second housing 24.

  The feed screw mechanism 32 includes a male screw member 41 having a trapezoidal screw formed on the outer surface, a female screw member 42 that meshes with the male screw member 41, and a cylindrical guide member 43 that is sheathed by the female screw member 42. doing. The feed screw mechanism 32 is provided coaxially with the central axis A0 of the main body 17 that connects the center C1 of the first connecting portion 18 and the center C2 of the second connecting portion 19.

  The male screw member 41 is formed integrally with the output rod 22, and a slider 44 supported by the guide member 43 so as to be displaceable in the axial direction is fixed to the end opposite to the output rod 22. The guide member 43 is rotatably supported by the second housing 24 via a bearing 45. The female screw member 42 is fixed to the guide member 43 so as not to rotate.

  The reduction mechanism 33 is a one-stage reduction mechanism having a drive gear 51 and a driven gear 52. The drive gear 51 and the driven gear 52 are constituted by helical gears. One end of the drive gear 51 is non-rotatably connected to the output shaft 53 of the motor 25, and the other end is held by the bearing 54. The bearing 54 is supported by the second housing 24. The driven gear 52 is fixed to the guide member 43 of the feed screw mechanism 32 and rotates integrally with the guide member 43 and the female screw member 42.

  In the feed screw mechanism 32 and the speed reduction mechanism 33 configured as described above, when the motor 25 is rotated, the drive gear 51 of the speed reduction mechanism 33 rotates in conjunction with the rotation of the output shaft 53. Accordingly, the driven gear 52, the guide member 43 and the female screw member 42 of the feed screw mechanism 32 rotate integrally, and the screw member 41 moves in the axial direction according to the rotation of the female screw member 42. In conjunction with this, the output rod 22 moves back and forth.

  The lock mechanism 34 includes a lock plate 61 and a lock pin 62. The lock plate 61 is fixed to the driven gear 52 of the speed reduction mechanism 33 and rotates integrally with the driven gear 52. The lock plate 61 has a groove into which the lock pin 62 is fitted. The lock pin 62 is provided so as to freely advance and retract in the radial direction of the driven gear 52 and is driven to advance and retract by the solenoid 26.

  The solenoid 26 includes a coil, a plunger (magnetic body), and a spring (not shown) inside, and is a so-called pull type in which the plunger is urged in the protruding direction by the spring, and the plunger is attracted by electromagnetic force generated by energizing the coil. When the solenoid 26 is not energized, the lock pin 62 connected to the plunger is in the forward position, and when the coil is energized, the lock pin 62 moves backward.

  When the solenoid 26 is not energized, the lock pin 62 moves forward and fits into the groove of the lock plate 61, so that the rotation of the driven gear 52 is restricted. When the solenoid 26 is energized, the lock pin 62 moves backward. Thus, the lock plate 61 escapes from the groove and enters the unlocked state in which the driven gear 52 is allowed to rotate.

  Therefore, when the vehicle is running, the solenoid 26 is always energized and held in the unlocked state, so that the rear wheel steering control for moving the output rod 22 back and forth by the motor 25 can be performed. ) At times, the energization of the solenoid 26 is stopped and the output rod 22 is brought into a locked state in which the advance / retreat operation is impossible.

  A configuration in which a lock member such as a lock pin 62 driven by the solenoid 26 is directly engaged with a gear tooth such as the driven gear 52 is also possible.

  As described above, in the present embodiment, as shown in FIG. 2, the motor 25 is arranged with the rotation axis A <b> 1 of the motor 25 shifted from the center axis A <b> 0 of the main body 17. The planetary gear mechanism, which is required when arranged coaxially with each other, is not necessary, and as shown in FIG. 4, a one-stage reduction mechanism composed of the drive gear 51 and the driven gear 52 is sufficient, thus simplifying the structure. can do.

  Next, the speed reduction mechanism 33 shown in FIG. 4 will be described. FIG. 5 is a cross-sectional view of a main part of the speed reduction mechanism 33. FIG. 6 is a perspective view of the second housing 24, the drive gear 51 and the bearing 54. FIG. 7 is a perspective view of main parts of the second housing 24, the drive gear 51, and the bearing 54.

  In the present embodiment, as shown in FIG. 5, the drive gear 51 of the speed reduction mechanism 33 is supported by a bearing 54, and the drive gear 51 is pressed against the driven gear 52 between the bearing 54 and the second housing 24. A spring 71 is provided to apply a biasing force to the bearing 54.

  In particular, in the present embodiment, as shown in FIG. 6, a recess 72 that receives the bearing 54 is formed in the second housing 24, and the spring 71 is fitted into the recess 72 together with the bearing 54. At the time of assembly, the bearings 54 and the springs 71 may be fitted into the recesses 72 after the springs 71 are mounted on the bearings 54 connected to the drive gear 51, and the assembly can be easily performed.

  As shown in FIG. 7, the spring 71 includes a leaf spring portion 73, a retaining piece 74 for preventing removal, and a projecting piece 75 for preventing rotation. The spring 71 can be formed by punching a steel plate into a predetermined shape and then bending the main part.

  The leaf spring portion 73 is formed in a substantially C shape so as to surround the bearing 54, and is disposed between the inner peripheral surface of the recess 72 and the outer peripheral surface of the bearing 54. The leaf spring portion 73 applies a biasing force that presses the drive gear 51 against the driven gear 52 to the bearing 54. The biasing force of the leaf spring portion 73 will be described in detail later.

  The retaining protrusion 74 is formed so as to protrude radially inward from the axial end opposite to the drive gear 51 in the leaf spring portion 73. It arrange | positions between the surfaces of the bearing 54 which opposes. As a result, the movement of the retaining piece 74 is restricted by the bearing 54 and the bottom surface of the recess 72, so that the spring 71 can be prevented from shifting or dropping off.

  The rotation-preventing projecting piece 75 is formed in a state of protruding in the axial direction opposite to the drive gear 51 from the circumferential end of the leaf spring portion 73, and engages with the bottom of the recess 72. In particular, in the present embodiment, the second housing 24 is formed with a locking hole 78 into which the rotation-preventing protruding piece 75 is fitted, with the bottom surface of the concave portion 72 further recessed. Thus, the rotation-preventing projecting piece 75 is restricted by the locking hole 78, so that the spring 71 can be prevented from rotating in accordance with the normal rotation and reverse rotation of the motor 25.

  A center hole 77 for receiving the shaft portion 76 of the drive gear 51 protruding from the bearing 54 is formed in the bottom surface of the recess 72.

  Next, a situation where the leaf spring portion 73 of the spring 71 shown in FIG. 7 biases the bearing 54 will be described. FIG. 8 is a cross-sectional view of the spring 71 viewed from the axial direction by cutting the shaft portion 76 of the drive gear 51.

  The recessed portion 72 is formed in a circular cross-sectional shape except for a portion where the locking hole 78 is formed, and the bearing 54 has a cylindrical outer shape, and the inner peripheral surface of the recessed portion 72 and the bearing 54 A gap having an annular cross section is formed between the outer peripheral surface and the leaf spring portion 73 of the spring 71 is disposed in this gap. The leaf spring portion 73 is disposed in a state where the plate thickness direction is the radial direction of the bearing 54, and is in partial contact with the inner peripheral surface of the recess 72 and the outer peripheral surface of the bearing 54, whereby the bearing 54 is It is elastically supported by the second housing 24 via the spring 71.

  The spring 71 has a first contact portion 81 that contacts the outer peripheral surface of the bearing 54 at a position opposite to the center C4 of the driven gear 52 across the center C3 of the bearing 54, and the driven gear 52 across the center C3 of the bearing 54. The second contact portion 82 and the third contact portion 83 are in contact with the inner peripheral surface of the recess 72 on both sides of the first contact portion 81 on the side opposite to the center C4.

  The first contact portion 81 presses the outer peripheral surface of the bearing 54 inward in the radial direction, and the second contact portion 82 and the third contact portion 83 press the inner peripheral surface of the recess 72 outward in the radial direction. The reaction force of the pressing forces F2 and F3 by the second contact portion 82 and the third contact portion 83 is added to the pressing force F1 by the portion 81, so that a large urging force F0 is applied to the bearing 54 on the driven gear 52 side. Acts in the direction of force.

  Further, the spring 71 comes into contact with the outer peripheral surface of the bearing 54 at a position in the diameter direction perpendicular to the center line CL1 connecting the center C3 of the bearing 54 and the drive gear 51 and the center C4 of the driven gear 52 when viewed from the axial direction. A fourth contact portion 84 and a fifth contact portion 85 are provided.

  The fourth contact portion 84 and the fifth contact portion 85 press the outer peripheral surface of the bearing 54 radially inward, and sandwich and hold the bearing 54 from both sides. Since the fourth contact portion 84 and the fifth contact portion 85 are located on opposite sides of the center C3 of the bearing 54, the pressing forces F4 and F5 by the fourth contact portion 84 and the fifth contact portion 85 are The bearing 54 is centered, that is, the bearing 54 is positioned so that the center C3 of the bearing 54 is located on the center line CL1.

  In the example shown in FIG. 8, the second contact portion 82 and the third contact portion 83 are at an angular position shifted by 45 degrees from the first contact portion 81 with respect to the center C <b> 3 of the bearing 54. The fifth contact portion 85 is at an angular position shifted by 90 degrees from the first contact portion 81 with respect to the center C <b> 3 of the bearing 54.

  Thus, in this embodiment, since the drive gear 51 is pressed against the driven gear 52 by the urging force of the spring 71, the backlash can be reduced and abnormal noise and vibration can be reduced. Since the bearing 54 is elastically supported by the second housing 24 via the spring 71, the spring 71 is deformed when an excessive external force is input from the wheel to the telescopic actuator 7 due to road surface unevenness or the like. By doing so, the impact can be alleviated, so that the power transmission members constituting the speed reduction mechanism 33 and the feed screw mechanism 32 can be prevented from being damaged.

  In the present embodiment, the second contact portion 82 and the third contact portion 83 press the inner peripheral surface of the recess 72 at positions on both sides of the position where the first contact portion 81 presses the outer peripheral surface of the bearing 54. Therefore, a large urging force that presses the drive gear 51 against the driven gear 52 can be stably obtained.

  Further, in the present embodiment, the pressing force by the fourth contact portion 84 and the fifth contact portion 85 acts so as to center the bearing 54, so that the drive gear 51 and the driven gear 52 are held in an optimal meshing state. be able to.

  As mentioned above, although this invention was demonstrated based on specific embodiment, these embodiment is an illustration to the last, Comprising: This invention is not limited by these embodiment. Moreover, all the components of the telescopic actuator 7 according to the present invention shown in the above embodiment are not necessarily essential, and can be appropriately selected as long as they do not depart from the scope of the present invention.

  That is, in the present embodiment, the spring 71 that biases the bearing 54 is configured by a leaf spring, but the spring that biases the bearing can also be configured by a spring of another form such as a coil spring. Further, the spring 71 that biases the bearing 54 is formed in a substantially C shape so as to surround the bearing 54, but the spring that biases the bearing is not limited to such a shape. Absent.

  Further, in the present embodiment, as shown in FIG. 8, the spring 71 has two contact portions with the inner peripheral surface of the recess 72 and three contact portions with the outer peripheral surface of the bearing 54. It is also possible to provide more or less contact portions with respect to the inner peripheral surface of the recess 72 and contact portions with respect to the outer peripheral surface of the bearing 54.

DESCRIPTION OF SYMBOLS 1 Rear suspension 2 Knuckle 3 Car body 7 Telescopic actuator 17 Main body 18 1st connection part 19 2nd connection part 22 Output rod 23 1st housing 24 2nd housing 25 Motor 26 Solenoid 32 Feed screw mechanism (motion conversion mechanism)
33 Deceleration mechanism 34 Lock mechanism 51 Drive gear 52 Driven gear 53 Output shaft 71 Spring 72 Recess 73 Plate spring part 74 Retaining protrusion 75 Nonrotating protrusion 81 First contact part 82 Second contact part 83 Third Contact portion 84 Fourth contact portion 85 Fifth contact portion

Claims (5)

A telescopic actuator connected to the knuckle and the vehicle body to change the rudder angle of the wheel by the telescopic operation,
A main body having two connecting portions to the knuckle and the vehicle body at both ends, and configured to be stretchable;
A motor for extending and retracting the main body;
A motion conversion mechanism that converts the rotational motion of the motor into the expansion and contraction motion of the main body;
A drive gear that rotates in conjunction with the rotation of the motor;
A driven gear that meshes with the drive gear and inputs the power of the motor to the motion conversion mechanism;
A bearing that supports the drive gear;
A spring interposed between the bearing and the main body to apply a biasing force to the bearing to press the driving gear against the driven gear;
A telescopic actuator characterized by comprising: The body includes a recess for receiving the bearing;
2. The telescopic actuator according to claim 1, wherein the spring is formed so as to surround the bearing and is disposed between an inner peripheral surface of the recess and an outer peripheral surface of the bearing. The spring partially contacts the inner peripheral surface of the recess and the outer peripheral surface of the bearing;
A first contact portion that contacts the outer peripheral surface of the bearing at a position that is opposite to the center of the driven gear across the center of the bearing;
A second contact portion and a third contact portion that respectively contact the inner peripheral surface of the recess on both sides of the first contact portion on the side opposite to the center of the driven gear across the center of the bearing;
The telescopic actuator according to claim 2, comprising:   The spring includes a fourth contact portion that comes into contact with an outer peripheral surface of the bearing at a position in a diametrical direction perpendicular to a center line that connects the center of the bearing and the driving gear and the center of the driven gear when viewed from the axial direction; The telescopic actuator according to claim 3, further comprising a fifth contact portion.   The spring protrudes inward in the radial direction of the bearing, and protrudes in the axial direction of the bearing, and a retaining piece disposed between the bottom surface of the recess and the surface of the bearing facing the recess. The telescopic actuator according to claim 2, further comprising an anti-rotation projecting piece that engages with a bottom portion of the concave portion.

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