Actuator for a seat cushion lift mechanism of a vehicle seat

Abstract

An actuator (20) for a vehicle seat (10) comprises a motor (29), a reduction gear (36) comprising a wheel (43) with an eccentric cam (44) driving a rack gear (47), an output member (33) forming an internal ring gear (48) receiving the rack gear (47), a backlash compensation washer (100; 200; 300) comprising a member (114; 314) for rotatably coupling to the rack gear (47) and a toothed section (118; 218) adapted to cooperate with the internal ring gear (48) of the output member (33). The backlash compensation washer (100; 200; 300) comprises an elastically deformable arm (122) between the rotatable coupling member (114; 314) and the toothed section (118; 218).

Description

Technical Field

[0001] This invention relates to an actuator for a vehicle seat, particularly for a motor vehicle seat. More specifically, this invention relates to an actuator for a seat cushion raising mechanism for a vehicle seat, particularly for a motor vehicle seat. Background Technology

[0002] In particular, in the automotive field, a vehicle seat with a seat cushion frame arranged on a base is known, the seat cushion being equipped with seat cushion lifting movement.

[0003] In this type of configuration, the actuator is provided with an output member that is selectively driven to rotate, causing the seat frame to rise and / or fall. The output member includes teeth that mesh with toothed sections facing each other. The toothed sections are connected to a motion mechanism for raising and lowering the seat. Application FR-A-3 086 597 describes an example of such an actuator.

[0004] The actuator includes a reduction gear with a high reduction ratio to change the rapid rotation of the electric motor to the slow or very slow rotation of the output member. The reduction gear in question has the functional backlash required for its operation in all cases. This backlash is particularly present when the electric motor is not controlled and the output pinion should not move.

[0005] In addition, seat cushion lifting movements are typically equipped with an upward resilient return system to compensate for all or part of the weight of the occupant sitting in the seat, and secondarily to compensate for a portion of the weight of the seat itself.

[0006] Especially when the load polarity changes, such as when an occupant is sitting on the seat or when an occupant is leaving the seat, the clearance of the reduction gear can be perceptible.

[0007] To conceal the backlash of the reduction gear, FR-A-3 135 026 discloses an actuator comprising a friction ring mounted around and rotatably fixed to an output member. The friction ring includes a skirt-like portion, and the actuator housing includes an inner bearing for receiving the skirt-like portion. The skirt-like portion contacts at least the inner bearing to form a friction brake between the output member and the inner bearing.

[0008] Through these arrangements, the contact between the skirt and the inner bearing generates friction, which acts as a brake when rotational torque is applied to the output pinion.

[0009] However, when the actuator is driven by a motor, the friction ring tends to reduce the actuator efficiency. Summary of the Invention

[0010] This disclosure improves upon this situation.

[0011] To this end, a vehicle seat actuator is proposed, which includes: - A motor, which has an output shaft; - A reduction gear, driven by the output shaft of a motor, which includes an eccentric cam wheel that drives a track gear; - An output component that forms a pinion and an internal gear ring adapted to receive a track gear, the pinion and the internal gear ring being aligned along the rotation axis of the output component; - A backlash compensation washer comprising at least one member for rotatably connecting to a track gear and at least one toothed section adapted to cooperate with an internal gear ring of an output member, the backlash compensation washer comprising at least one elastically deformable arm located between the rotatable connecting member and the at least one toothed section.

[0012] According to a preferred embodiment, the vehicle seat actuator includes one or more of the following features, either individually or in combination: - The track gear is adapted to move in a circumferential translational manner within the internal gear ring of the output member, and the actuator preferably includes a guide slide for the track gear; - The at least one connecting member includes at least one of a stud and a lug fixed to the central gear ring, the stud or lug being adapted to be received in the complementary housing of the track gear so as to rotatably connect the backlash adjusting washer and the track gear. - The at least one arm extends in an arc shape between a first end and a second end, the first end being integral with the central toothed ring when applicable, and the second end being integral with the at least one toothed segment; - The vehicle seat actuator includes multiple different toothed sections that are separated from each other by circumferential clearance; - Each arm is attached to a single toothed segment; - The vehicle seat actuator comprises a single toothed segment extending substantially the entire circumference of a backlash compensation washer. - The backlash compensation washer is substantially flat, except for the at least one connecting member, and especially when applicable, except for at least one lug; - The backlash compensation washer includes at least one relief portion projecting in the direction of the rotation axis of the output member and adapted to contact a front surface of the output member perpendicular to the rotation axis of the output member; and -The at least one protrusion includes at least one of the following: --Center gear ring; and --Arm base, which connects the arm to the center gear ring.

[0013] According to another aspect, a vehicle seat is described, which includes actuators and all combinations thereof as described above.

[0014] Vehicle seats may specifically include: -Base; - Seat cushion frame; - At least one hinge mechanism that connects the seat cushion frame to the base, each hinge mechanism including at least one connecting rod that is mounted to be freely rotatable relative to the seat cushion frame at a first end and freely rotatable relative to the base at a second end; - At least one actuator and any combination thereof as described above, to control the rotation of the at least one connecting rod relative to the base or seat frame.

[0015] According to another aspect, a vehicle seat is proposed, the vehicle seat comprising: - Seat cushion frame; - A device for raising the front edge of the seat; - At least one connecting rod that connects the seat cushion frame to the seat front edge lifting device; - At least one actuator and any combination thereof as described above, to control the rotation of the at least one connecting rod relative to the seat cushion frame or the seat front edge lifting device. Attached Figure Description

[0016] Other features, details, and advantages will become apparent upon reading the following detailed description and analysis of the accompanying drawings, in which: [ Figure 1 [Illustration of a vehicle seat with adjustable seat height]

[0017] [ Figure 2 ] showed [ Figure 1 Details of the seat cushions in the vehicle.

[0018] [ Figure 3 ] is able to [ Figure 1 The image shows a perspective view of the actuator used in the vehicle seat.

[0019] [ Figure 4 ]yes[ Figure 3 An exploded perspective view of the actuator.

[0020] [ Figure 5 ]yes[ Figure 3 The actuator along [ Figure 3 A cross-sectional view of the VV section.

[0021] [ Figure 6 ]yes[ Figure 3The image shows a longitudinal sectional view of the actuator.

[0022] [ Figure 7 ] is from along [ Figure 6 The cross section of plane VII-VII was cut off. Figure 3 The perspective view of the actuator shown.

[0023] [ Figure 8 ] showed [ Figure 3 The perspective view of the actuator shown includes a backlash compensation wheel mounted on the track gear.

[0024] [ Figure 9 ]yes[ Figure 8 Detailed cross-sectional view of the actuator.

[0025] [ Figure 10 ] shows that it can be seen in [ Figure 3 A perspective view of a second example of a backlash compensation washer used in the actuator of [the device]. [ Figure 11 ] shows that it can be seen in [ Figure 3 A perspective view of a third example of a backlash compensation washer used in the actuator of [ ]; [ Figure 12 The image shows the installation located in […]. Figure 3 A perspective view of a third example of a backlash compensation washer on the track gear of an actuator. Detailed Implementation

[0026] In the various figures, the same reference numerals refer to the same or similar features. For the sake of brevity, only elements useful for understanding the described embodiments are shown in the figures, and they are described in detail below.

[0027] In the following description, when referring to terms that define absolute position (such as the terms "front", "rear", "top", "bottom", "left", "right", etc.) or terms that define relative position (such as the terms "above", "below", "upper", "lower", etc.) or qualifiers that refer to orientation (such as "horizontal", "vertical", etc.), reference is made to the orientation of the accompanying drawings or the orientation of the vehicle seat in its normal use position, unless otherwise stated.

[0028] Specifically, the longitudinal direction X refers to the longitudinal direction of the seat. The longitudinal direction of the seat is considered to be the same as the longitudinal direction of the motor vehicle in which the seat is mounted. This longitudinal direction X corresponds to the normal driving direction of the vehicle. The longitudinal direction X is horizontal. The lateral direction Y of the seat therefore corresponds to the lateral or sideways direction of the motor vehicle. This lateral direction corresponds to the direction perpendicular to the normal driving direction of the vehicle. The lateral direction Y is horizontal. Finally, the vertical direction Z is the vertical direction of the seat, which is perpendicular to both the longitudinal and lateral directions.

[0029] [ Figure 1 The diagram schematically illustrates a vehicle seat 10, comprising a seat cushion 11 with a seat cushion frame 12 and a backrest 13 with a backrest frame 14 mounted on the seat cushion frame 12. The seat cushion frame 12 is mounted on a base 15 via one or more hinge mechanisms. The backrest frame 13 may be secured to a headrest 16, which is connected to the backrest frame 13 via one or more headrest 16 attachment slots or pins 17. Specifically, the hinge mechanism may be a raising mechanism and / or one or two tilting mechanisms, which may be particularly, but not exclusively, obtained via connecting rods 18a, 18b. For example, for each of the connecting rods 18a, 18b, the lower end is connected to the base 15 and the upper end is connected to the seat cushion frame 12 of the vehicle seat 10. More specifically, in the example shown, the first connecting rod 18a connects the front portion 15a of the base 15, which is mounted to pivot about a first transverse axis A1, to the front portion 12a of the seat frame 12, which is mounted to pivot about a second transverse axis A2, and the second rear connecting rod 18b connects the rear portion 15p of the base 15, which is mounted to pivot about a third transverse axis A3, to the rear portion 12p of the seat frame 12, which is mounted to pivot about a fourth transverse axis A4. In the example shown, the pivoting mounts of both the first connecting rod 18a and the second connecting rod 18b have axes A1-A4 parallel to the transverse direction Y.

[0030] The seat cushion frame 12 has a similar architecture on the right and left sides. [In [ Figure 1 In the diagram, only one side is shown. On the side not shown, the seat 10 has additional connecting rods between the seat cushion frame 12 and the base 15, which are equivalent to or even the same as the connecting rods 18a and 18b shown.

[0031] If desired, the seat cushion 11 of the seat 10 may also be equipped with a front edge that is movable in height and / or longitudinal direction. In the event of tilting movement of the front edge, an auxiliary connecting rod 19 connects the seat cushion frame 12 to the front edge, and the auxiliary connecting rod 19 is movable by the actuator 20 via a toothed section 21. Furthermore, the base 15 can be slidably mounted relative to the vehicle floor P via a longitudinal slide rail 22, which includes a fixed rail 22b attached to the vehicle floor P and a movable rail 22a fixed to the base 15. As is known in the art, the backrest 13 can pivot relative to the seat cushion 11, and specifically the backrest frame 14 pivots relative to the seat cushion frame 12. The connecting rods 18a, 18b can be moved independently by corresponding control components, or simultaneously controlled by a synchronization control component or by a mechanical linkage (not shown) that can connect them. When the first connecting rod 18a rotates trigonometrically via actuator 20, the front portion 11a of the seat cushion, connected to the seat, rises upwards; conversely, when the first connecting rod 20a rotates clockwise, the front portion 11a of the seat cushion 11 lowers towards the floor. Similarly, when the second connecting rod 18b rotates counterclockwise via another actuator 20, the rear portion 11p of the seat cushion 11 rises upwards; and when the second connecting rod 18b rotates clockwise, the rear portion 11p of the seat cushion 11 lowers towards the floor P. When both connecting rods 18a and 18b are operated simultaneously, the seat cushion 11 moves substantially parallel to the floor P; this movement is referred to as "raising." A tilting movement of the seat cushion 11 is achieved when the first connecting rod 18a is operated while the second connecting rod 18b remains stationary, or vice versa. [According to...] Figure 1 The arrangement schematically shown in the diagram includes a front hinge mechanism for connecting rod 18a, which may be equipped with a reset member 23. This reset member tends to pivot connecting rod 18a counterclockwise and apply an upward torque to the front portion 11a of seat cushion 11, such that the effects of gravity generated by the weight of seat 10 and / or the occupant mounted on seat 10 can be at least partially compensated by the action of the reset member 23. A similar reset member may be provided on the second connecting rod 18b. This reset member may take any other form, such as a torsion bar, which may advantageously be one of the crossbars mounted on axes A1-A4.

[0032] like[ Figure 2As shown, the front connecting rod 18a (and correspondingly the rear connecting rod 18b) is securely connected to a crossbar that extends along the transverse axis Y and connects the shown connecting rods 18a and 18b to an equivalent connecting rod (not shown) arranged on the other side of the seat cushion 11. Furthermore, the connecting rod 18a is fixedly connected to a control flange 25, which is in the form of a metal plate extending along the planes X and Z. The control flange 25 is directly connected to the crossbar 24 and / or the connecting rod 18a, and has a toothed section 26 at one end that is substantially circular in shape. This toothed section is designed to cooperate with an actuator 20, which includes an output pinion 27 that meshes directly with the toothed section 26. Preferably, this actuator 20 is arranged only on one side of the seat cushion frame 12 of the seat 10. The other side may not have an actuator 20. The output pinion 27 is arranged to rotate about an axis A that is substantially parallel to the transverse axis Y. A second actuator similar to the first actuator 20 can be provided to drive the rear connecting rod 18b in a similar manner.

[0033] In the following text, given that [ Figure 3 ]to[ Figure 7 The first example actuator 20 is described in more detail below.

[0034] like Figure 3 As shown, actuator 20 includes: a motor 29; a housing 30 that forms a fixed support relative to the seat cushion 11 of vehicle seat 10, the housing having an outer shell 31 and a flange or cover 32; and an output member 33 that forms an output pinion 27. The outer shell 31 and cover 32 are attached together, for example, by screws 34. A reinforcing element 35 may also be disposed between the outer shell 31 and cover 32. Actuator 20 also includes a reduction gear 36, which in [… Figure 3 It is not visible in [ ], and will be specifically mentioned below regarding [ ] Figure 4 ]and[ Figure 5 [Describe it.]

[0035] The outer casing 31 is bell-shaped or bowl-shaped. In the example shown, the outer casing 31 is formed of a plastic material. This plastic material can be ABS, polypropylene, polyethylene, polyamide, etc. However, the outer casing 31 can also be formed of aluminum alloy, magnesium alloy, or any lightweight metal alloy.

[0036] Motor 29 extends along an axis perpendicular to the rotation axis A of output member 33 and includes a rotor at its end carrying a helical gear screw 38 centered on the axis of motor 29. The helical gear screw 38 extends inside housing 31. The helical gear screw 38 meshes with a first external gear ring 39 of input member 40 of reduction gear 36. Input member 40 is rotatable about axis A via shaft 41 attached to housing 31, preferably rotatable about the rotation axis A. Shaft 41 may be integral with output member 33, or output member 33 may be attached to shaft 41.

[0037] The input component 40 includes a second internal gear ring 42 adapted to drive an eccentric cam wheel 43 to rotate about a rotation axis A. This eccentric cam wheel is characterized by a cam 44 that is eccentric relative to the rotation axis A. The cam 44 is generally cylindrical, with its axis parallel to the rotation axis A. Therefore, the cam 44 takes the form of a substantially cylindrical pin, with its axis parallel to and offset relative to the rotation axis A of the eccentric cam wheel 43.

[0038] Cam 44 extends through a first opening 45 of slider 46, which guides a track gear 47 driven by cam 44 of eccentric cam wheel 43. Gear 47 is received in internal gear ring 48 of output member 33. Track gear 47 has a smaller diameter and number of teeth than internal gear ring 48 of output member 33 so as to mesh with the latter (internal gear ring) and produce a reduction ratio in the manner described below.

[0039] The track gear 47 is locked by the slider 46 and cannot rotate around an axis parallel to the rotation axis A of the output member 33.

[0040] Therefore, such as Figure 5 As shown, the slider 46 includes at least one first longitudinal guide element 50 and at least one second longitudinal guide element 51 in a plane perpendicular to the rotation axis A of the output member 33 along two mutually perpendicular longitudinal directions.

[0041] The first longitudinal guide element 50 is adapted to cooperate with the first mating element 52 of the outer shell 31 of the housing 30. The first longitudinal guide element 50 has a first guide surface 53 adapted to slide in or against the first mating element 52.

[0042] The first guide surface 53 is adapted to guide the slider 46 so that the slider can only move in a straight line relative to the outer shell 31 of the housing 30.

[0043] For example, the first guide surface 53 can lock the slider 46 relative to the housing 30 in the vertical direction Z, which is perpendicular to the longitudinal direction X and the transverse direction Y.

[0044] The rotation of the slider 46 relative to the housing 30 about the axis of rotation A can also be locked. Conversely, the slider 46 can slide freely relative to the housing 31 in the longitudinal direction X.

[0045] Therefore, the cooperation of the first longitudinal guide element 50 and the first mating element 52 locks the translation of the slider 46 relative to the housing 31 in the vertical direction Z and the rotation around the rotation axis A, while allowing the slider to slide freely in the longitudinal direction X.

[0046] The second longitudinal guide element 51 is adapted to cooperate with the second mating element 54 of the gear 47. For this purpose, the second longitudinal guide element 51 has a second guide surface 55 adapted to slide against the second mating element 54. In this way, the track gear 47 can only move in a straight line relative to the slider 46.

[0047] The second guide surface 55 can, for example, lock the translation of the track gear 47 relative to the slider 46 in the longitudinal direction X. The rotation of the track gear 47 relative to the slider 46 in the vertical direction Z about the rotation axis A can also be locked.

[0048] The cooperation between the second longitudinal guide element 51 and the second mating element 54 thus locks the translation of the track gear 47 relative to the slider 46 in the longitudinal direction X and its rotation around the axis of rotation A, while allowing the track gear to slide freely in the vertical direction Z.

[0049] In this way, the gear 47 can only move in a circular translation relative to the housing 30 in a plane perpendicular to the axis of rotation A, and in particular, due to the cooperation of the first longitudinal guide element 50 and the second longitudinal guide element 51 of the slider 46 with the first mating element 52 and the second mating element 54 of the outer shell 31 of the housing 30 and the track gear 47, the rotation of the gear relative to the housing 30 about the axis of rotation A is locked.

[0050] A complete revolution of the track gear 47 in the output member 33 of the internal gear ring 48 causes the output member 33 to be angularly offset relative to the housing 31. This angular offset corresponds to the difference in the number of teeth between the track gear 47 and the internal gear ring 48, thereby generating the reduction ratio of the reduction gearbox 36.

[0051] In one embodiment, the first longitudinal guide element 50 may be formed by a plurality of extensions (e.g., two or four extensions) with rectangular cross-sections projecting from the body of the slider 46 in the longitudinal direction X. The extensions may extend in pairs on either side of the body of the slider 46. In this way, the extensions may form a “U” shape with the body on either side. The two extensions may be symmetrical with respect to the longitudinal midplane. The side wings of the extensions may then form a first guide surface 53. The first mating element 52 may include longitudinal grooves in the housing 30 (e.g., the outer casing 31) for receiving these extensions. The second longitudinal guide element 51 may be formed by a straight opening in the slider 46, the side wings of which form a second guide surface 55. The second mating element 54 may include axially projecting square-section fingers of the track gear 47 adapted to fit into the straight opening. Alternatively, other shapes are contemplated for the first longitudinal guide element 50 and the second longitudinal guide element 51, as well as the first mating element 52 and the second mating element 54.

[0052] like[ Figure 4 As shown, a bearing 56 can also be arranged between the output member 33 and the cover 32 to guide the rotation of the output member 33.

[0053] Furthermore, according to the first example, the actuator 20 includes a backlash compensation washer 100, which is functionally arranged between the track gear 47 and the internal gear ring 48 inside the output member 33.

[0054] like[ Figure 8 ]or[ Figure 9 As shown, specifically, the backlash adjusting washer 100 first includes a toothed ring 102 that defines an opening 104 through which the shaft 41 passes. Furthermore, the toothed ring 102 is significantly thicker in the direction of the rotation axis A of the output member 33 than the rest of the backlash compensating washer 100. [See...] Figure 6 As shown, this allows the backlash compensation washer 100 to wedge into the output member 33 in the direction of the rotation axis A of the output member 33 between the output member 33 and the track gear 47, wherein the crown 102 contacts the front surface 106 of the housing 108 of the output member 33 that receives the backlash compensation washer 100. The front surface 106 extends in a plane perpendicular to the rotation axis A of the output member 33.

[0055] A circular flange 110 extends inside the crown 102 in a plane perpendicular to the direction of the rotation axis A of the output member 33. This circular flange 110 can contact the front surface 112 of the cam 44 of the eccentric cam wheel 43.

[0056] The backlash compensation washer 100 also forms studs 114, for example, two or four studs 114, preferably angularly equidistant from each other and received in corresponding complementary housings 116 formed in the track gear 47. When the studs 114 are received in the housings 116, the track gear 47 and the backlash compensation washer 100 are rotatably connected.

[0057] In addition, such as [ Figure 8 As shown, the backlash compensation washer 100 has a single toothed segment 118 extending around the entire circumference of the backlash compensation washer 100. [As shown in the image] Figure 7 As shown, the toothed section 120 of the backlash compensation washer 100 is offset at an angle relative to the toothed section 120 of the track gear 47 about the common axis of the track gear 47 and the backlash compensation washer 100. The toothed section 118 of the backlash adjustment washer 100 is adapted to cooperate with the teeth of the internal gear ring 48 of the output member 33.

[0058] Finally, the backlash compensation washer 100 has arms 122 extending between the gear ring 102 and the toothed section 118. Here, the compensation washer 100 has four such arms 122, which are identical and angularly equidistant. Each arm 122 extends substantially in an arc. Each arm 122 is separated from the gear ring 102 by a first arc-shaped slot 124. Each arm 122 is also separated from the toothed section 118 by a second arc-shaped slot 126. Therefore, the arms 122 can be elastically deformable, allowing slight movement of the toothed section 118 relative to the gear ring 102 and thus relative to the track gear 47 about the axis of the backlash compensation washer 100. In this way, the deformation of the arms 122 maintains contact between the teeth 118 of the backlash compensation washer 100 and the teeth 120 of the inner gear ring 48 of the output member 33. In this way, large backlash, which could lead to noise and synchronization loss in the reduction gear 36 during use, is avoided.

[0059] In addition, such as [ Figure 8 As shown, the base 128 of each arm 122 (through which the arm 122 is connected to the gear ring 102) can be thicker so that it protrudes in the direction of the axis of rotation A of the output member 33 relative to the rest of the arm 122. The base 128 can then contact the front surface 129 of the output member 33 to help hold the backlash adjusting washer 100 in the proper position in the actuator 20.

[0060] The backlash adjusting washer 100 is made of metal, or preferably plastic, to ensure that the arm 122 can deform elastically.

[0061] [ Figure 10A second example of a backlash compensation washer 200 is shown, specifically the side of the backlash compensation washer 200 intended to face the track gear 47. The difference between the backlash compensation washer 200 and the first example described above is substantially that it includes four distinct toothed sections 218 separated in pairs by circumferential clearance 230. Due to the circumferential clearance 230, the arm 122 of the backlash compensation 200 can be significantly softer.

[0062] Therefore, the backlash adjusting washer 200 is more specifically designed to be made of metal, but it can also be made of plastic.

[0063] at last,[ Figure 11 ]and[ Figure 12 A third example of a backlash compensation washer 300 without a stud 114 but with a lug 314 is shown, which is obtained, for example, by bending a radial tongue. Thus, the backlash compensation washer 300 can be produced, for example, by stamping and then bending the lug 314. Therefore, the backlash compensation washer 300 is particularly suitable to be made of metal, but it can also be made of plastic.

[0064] Furthermore, the central gear ring 302 is substantially flat. Additionally, in order for the arm 122 to be elastically deformable, the arm can extend along a substantially helical path.

[0065] This disclosure is not limited to the examples described above for non-limiting illustrative purposes only; rather, this disclosure covers all variations that may be considered by those skilled in the art in the context of the protection sought.

Claims

1. An actuator (20) for a vehicle seat (10), said actuator comprising: - Motor (29), the motor having an output shaft; - Reduction gear (36), which is driven by the output shaft of the motor (29), the reduction gear (26) includes an eccentric cam (44) wheel (43) that drives the track gear (47). - Output member (33), the output member (33) forming a pinion (27) and an internal gear ring (48) adapted to receive the track gear (47), the pinion (27) and the internal gear ring (48) being aligned along the rotation axis (A) of the output member (33); - A backlash compensation washer (100; 200; 300), the backlash compensation washer comprising at least one member (114; 314) for rotatably connecting to the track gear (47) and at least one toothed section (118; 218) adapted to engage with the internal gear ring (48) of the output member (33), the backlash compensation washer (100; 200; 300) comprising at least one elastically deformable arm (122) located between the rotatable connecting member (114; 314) and the at least one toothed section (118; 218).

2. The actuator for a vehicle seat according to claim 1, wherein the track gear (47) is adapted to move in a circumferentially translating manner in the internal gear ring (48) of the output member (33).

3. The actuator for a vehicle seat according to claim 2, wherein the actuator includes a slider (46) for guiding the track gear (47).

4. The actuator for a vehicle seat according to claim 1, wherein at least one connecting member (114; 314) comprises at least one of a stud (114) and a lug (314) integral with a central gear ring (102; 302), the stud (114) or the lug (314) being adapted to be received in a complementary housing (116) of the track gear (47) to rotatably connect the backlash compensation washer (100; 200; 300) and the track gear (47).

5. The actuator for a vehicle seat according to claim 1, wherein the at least one arm (122) extends in an arcuate shape between a first end and a second end, the second end being integral with the at least one toothed segment (118; 218).

6. The actuator for a vehicle seat according to claim 4, wherein the at least one arm (122) extends in an arc shape between a first end and a second end, the first end being integral with the central gear ring (102; 302), and the second end being integral with the at least one toothed segment (118; 218).

7. The actuator for a vehicle seat according to claim 1, the actuator comprising a plurality of different toothed segments (218) separated from each other by a circumferential gap (230).

8. The actuator for a vehicle seat according to claim 5, wherein the actuator comprises a plurality of different toothed segments (218) separated from each other by a circumferential gap (230), wherein each arm (122) is integral with a single corresponding toothed segment (218).

9. The actuator for a vehicle seat according to claim 1, the actuator comprising a single toothed segment (118) extending substantially around the entire circumference of the backlash compensation washer (100).

10. The actuator for a vehicle seat according to claim 1, wherein the backlash adjusting washer (200) is substantially flat except for the at least one connecting member (114; 314).

11. The actuator for a vehicle seat according to claim 4, wherein the backlash adjusting washer (200) is substantially flat except for at least one lug (314).

12. The actuator for a vehicle seat according to claim 1, wherein the backlash adjusting washer (100; 200) includes at least one protrusion (102; 110) that protrudes in the direction of the axis of rotation (A) of the output member (33) and is adapted to contact a front surface (106; 129) of the output member (33) perpendicular to the axis of rotation (A) of the output member (33).

13. The actuator for a vehicle seat according to claim 4, wherein the backlash adjusting washer (100; 200) includes at least one protrusion (102; 110) projecting in the direction of the axis of rotation (A) of the output member (33) and adapted to contact a front surface (106; 129) of the output member (33) perpendicular to the axis of rotation (A) of the output member (33), and wherein the at least one protrusion (102; 110) includes at least one of the following: -The central gear ring (102); and - The base of the arm (122) that connects the arm (122) to the central gear ring (102).

14. A vehicle seat (10) comprising an actuator (20) according to any of the preceding claims.

Images