CN110936861A

CN110936861A - Concentric adjustment seat angle adjuster

Info

Publication number: CN110936861A
Application number: CN201911335744.8A
Authority: CN
Inventors: 王其良; 黎聪; 乔平
Original assignee: Yanfeng Adient Changshu Seating Mechanism Co Ltd
Current assignee: Keiper Changshu Seating Mechanisms Co Ltd
Priority date: 2019-12-23
Filing date: 2019-12-23
Publication date: 2020-03-31
Anticipated expiration: 2039-12-23
Also published as: CN110936861B

Abstract

The invention relates to a concentric adjustment seat angle adjuster, which comprises two toothed plates respectively connected with a backrest and a seat basin, wherein the two toothed plates are respectively meshed with a gear positioned between the two toothed plates from two sides, a clearance eliminating mechanism is accommodated in a central shaft hole of the gear, and the peripheries of the two toothed plates are fixedly connected together through a hoop. According to the invention, the gear is additionally arranged between the two toothed plates to form two sets of gear-toothed plate matching mechanisms, so that the output end of the angle adjuster rotates concentrically, and the concentric adjustment of the backrest is ensured. The invention meets the requirement of fast and stable adjustment of the angle adjuster and avoids the problems of shaking, dead blocking of a stop point and noise caused in the operation process of the angle adjuster. Meanwhile, the invention adopts the clearance adjusting mechanism matched with the two sets of gear-toothed plates, eliminates the clearance in the angle adjuster and improves the riding comfort. In addition, the angle adjuster has simple structure and part configuration, easy realization of processing technology and better application prospect.

Description

Concentric adjustment seat angle adjuster

Technical Field

The invention relates to the field of automobile seats, in particular to a concentric adjustment seat angle adjuster.

Background

The angle adjuster is a device which is arranged on an automobile seat and realizes the angle adjustment of a seat backrest. The device generally comprises a chair back connecting plate, a chair seat connecting plate, a core piece, a hand wheel or an adjusting handle, a return spring and the like. With the high-speed development of new energy automobiles, people have higher and higher requirements on the electric automation of automobile seats.

At present, most of the seat electric angle adjusters which are generally used in the market adopt an eccentric structure. The seat back does not rotate concentrically about a point but eccentrically with a certain eccentricity when adjusted. Due to the existence of the eccentricity, in the moving process, the backrest moves forward and backward in the horizontal direction and moves up and down in the vertical direction, so that the backrest moves in a wave manner. This causes the problem such as shake abnormal sound easily, can't satisfy the demand of quick steady adjustment to influence customer experience. In addition, the eccentric adjustment is prone to the problem that the gear point is stuck, so that the angle adjuster for eccentric adjustment needs to check the gear point, but even if the gear point is checked manually, the problem cannot be avoided completely. In the prior art, angle adjusters with concentric structures are also available, but on the one hand, the angle adjusters have various parts, complex structures and large volumes. On the other hand, although the concentric angle adjuster in the prior art can solve the problems of jitter and gear point blocking, the clearance between the internal gear and the toothed plate of the angle adjuster cannot be eliminated. If the gap is not eliminated, when a passenger leans against the backrest of the seat, the backrest can obviously shake, and the gap can cause abnormal sound when the passenger is unloaded, so that serious comfort problems can be caused, and the riding experience of the user is influenced.

Disclosure of Invention

The invention provides a concentric adjustment seat angle adjuster which can eliminate shaking abnormal sound, a backrest dead point and a gap between a gear and a toothed plate while realizing rapid, stable and continuous adjustment.

The invention provides a concentric adjustment seat angle adjuster, which comprises two toothed plates respectively connected with a backrest and a seat basin, wherein the two toothed plates are respectively meshed with a gear positioned between the two toothed plates from two sides, a clearance eliminating mechanism is accommodated in a central shaft hole of the gear, and the peripheries of the two toothed plates are fixedly connected together through a hoop.

The angle adjuster also comprises a shaft sleeve which is arranged between the central shaft hole of the gear and the clearance eliminating mechanism.

The central shaft holes of the two toothed plates are flanged holes.

The two toothed plates are provided with sunk grooves at the positions adjacent to the inner sides of the peripheries and connected with the teeth.

And double-side flanges for supporting the outer edge of the shaft sleeve are arranged at the central shaft hole of the gear.

The gear ratio of the two toothed plates to the gear is one toothed plate: gear: the other toothed plate is n + 1: n: n +2, n is a positive integer.

According to an embodiment of the present invention, the gear ratio of the two tooth plates to the gear is one tooth plate: gear: the other toothed plate is 43:42: 44.

According to another embodiment of the present invention, the gear ratio of the two tooth plates to the gear is one tooth plate: gear: the other toothed plate is 37:36: 38.

According to another embodiment of the present invention, the gear ratio of the two tooth plates to the gear is one tooth plate: gear: the other toothed plate is 33:32: 34.

The clearance eliminating mechanism comprises a cam and two groups of wedge block mechanisms respectively positioned on the upper side surface and the lower side surface of the cam.

Each set of wedge mechanism comprises two segments and a spring connected with the two segments.

The cam comprises a cam ring, and a cam shaft is arranged in the middle of the cam ring.

And a driving rod interface is arranged in the cam shaft.

The cam shaft and the cam ring are integrally formed or are combined in a split mode.

According to the concentric adjustment seat angle adjuster, the two toothed plates are meshed with one gear together to form two sets of gear-toothed plate matching mechanisms, so that the output end of the angle adjuster rotates concentrically, concentric adjustment of a backrest is guaranteed, the problems of shaking, blocking of a blocking point and noise caused in the eccentric operation process of the angle adjuster are solved, and the requirement for quick and stable adjustment of the angle adjuster is met. Meanwhile, the invention adopts the clearance adjusting mechanism matched with the two sets of gear tooth plates, eliminates the clearance in the angle adjuster and improves the riding comfort. In addition, the angle adjuster has simple structure and part configuration, easy realization of processing technology and better application prospect.

Drawings

Fig. 1 is an exploded view of a concentric adjustment seat recliner according to the present invention.

Fig. 2 is a schematic cross-sectional view taken along line a-a in fig. 1.

Fig. 3 is a schematic view of a low strength recliner without a flange according to the present invention.

Fig. 4 is a schematic view of a low strength recliner according to the present invention having a flange.

Fig. 5 is an exploded view of a gap elimination mechanism according to the present invention.

Fig. 6 is a schematic view of an integrated cam structure according to the present invention.

Fig. 7 is a structural schematic view of a split cam according to the present invention.

Fig. 8 is a schematic view of the operation of the wedge mechanism according to the invention.

Fig. 9 is a schematic diagram of a seat recliner according to the present invention achieving concentric adjustment.

Fig. 10 is a schematic cross-sectional view taken along line B-B in fig. 9.

Detailed Description

The present invention is further described below in conjunction with the following figures and examples, it being understood that the following examples are intended to illustrate and not to limit the present invention.

As shown in fig. 1, the concentrically adjustable seat angle adjuster provided by the invention comprises a first toothed plate 1 connected with a backrest and a second toothed plate 2 connected with a seat pan, wherein the first toothed plate 1 and the second toothed plate 2 have similar structures and can be interchanged in position, that is, the first toothed plate 1 can be connected with the seat pan, and the second toothed plate 2 is connected with the backrest. The first toothed plate 1 and the second toothed plate 2 are respectively meshed with the gear 3 located between the two from two sides to form two sets of gear-toothed plate matching mechanisms. A shaft sleeve 5 is arranged in a central shaft hole of the gear 3 in a clinging mode, a clearance eliminating mechanism 6 is accommodated in the shaft sleeve 5, and the peripheries of the first toothed plate 1 and the second toothed plate 2 are fixedly connected together through a hoop 4.

As shown in fig. 2, the central shaft hole of the first toothed plate 1 is a flanged hole 7 for fitting the backlash eliminating mechanism 6. In addition, a sunk groove 8 is arranged at a plane which is close to the inner side of the periphery of the first toothed plate 1 and is connected with the teeth. Because at angle modulation ware during operation, the meshing that the tooth of gear 3 and first pinion rack 1's tooth can be continuous can avoid the tooth of gear 3 and the chamfer of the tooth root department of first pinion rack 1 to interfere through heavy groove 8 to avoid noise and influence function and travelling comfort that bring because wearing and tearing. Meanwhile, the sink groove 8 can store grease filled into the angle adjuster, so that enough lubricating oil is available when the gear 3 is meshed with the first toothed plate 1. Similarly, the same hole flanging 7 and the same sinking groove feature are also provided at corresponding positions of the second toothed plate 2, and are not described in detail herein.

The gear ratio of the first toothed plate 1, the gear 3 and the second toothed plate 2 is set as n + 1: n: n +2, n is a positive integer. The design can ensure that the difference of the tooth number among the gear 3, the first toothed plate 1 and the second toothed plate 2 is minimum, and the smaller difference of the tooth number can ensure that the tooth number meshed simultaneously is more, so that the bearing capacity is stronger, and the transmission is more stable; and a greater transmission ratio can be obtained while achieving a smaller volume and weight.

When n takes different values, the maximum external force born by the angle adjuster is different, namely different n values correspond to the angle adjusters with different strengths. For example, for a high strength of 5000Nm, the gear ratio of the first toothed plate 1, the gear 3 and the second toothed plate 2 may be set to 43:42: 44; for the medium strength of 2500 plus 3000Nm, the gear ratio of the first toothed plate 1, the gear 3 and the second toothed plate 2 is 37:36: 38; and for a low strength of 2000Nm, the gear ratio of the first toothed plate 1, the gear 3 and the second toothed plate 2 can be set to 33:32: 34.

For low strength recliners, the thickness of the gear 3 can be designed thinner than for high strength recliners, but the bushing 5 and clearance relief mechanism 6 are still shared with the high strength recliners for maximum error proofing and cost reduction. As shown in fig. 3, when the thin gear 3 is engaged with the sleeve 5, both ends of the sleeve 5 are suspended due to lack of support, thereby being easily deformed by force. Therefore, when the recliner of the present invention is a low strength recliner, as shown in fig. 4, the central shaft hole of the gear 3 is provided with a double-sided burring structure 9. This flange structure 9 can give axle sleeve 5 better more even support, guarantees axle sleeve 5's relative stability, avoids axle sleeve 5 about the both ends atress uneven and warp the damage.

As shown in fig. 5, the backlash elimination mechanism 6 includes a cam 61 and two sets of wedge mechanisms 62. Two sets of wedge mechanisms 62 are respectively mounted on the upper and lower side surfaces of the cam 61. Wherein the cam 61 is provided with spaced cam stops 63a and 63b for cooperating with the wedge mechanism 62 for stopping. Each set of wedge means 62 comprises two

segments

66a and 66b, respectively, and a spring 65 connected thereto, wherein the spring 65 is adapted to provide a force to the play relief means 6. The cam 61 is further provided with a driving rod interface 64 for connecting a driving motor (not shown).

The cam 61 includes a cam shaft 70 and a cam ring 67, and as shown in fig. 6, the cam shaft 70 and the cam ring 67 may be integrally formed. The integral cam integrally adopts a powder metallurgy part, so that the bearing capacity is high, but the relative weight is increased. The cam shaft 70 and the cam ring 67 can also be assembled separately, as shown in fig. 7, the two parts are made of different materials (for example, the cam shaft 70 is made of polymer plastic, and the cam ring 67 is made of powder metallurgy), so as to achieve the purposes of reducing cost and weight. In actual use, different structures can be selected according to specific stress conditions.

In a preferred embodiment, the driving rod interface 64 is a flower-shaped interface that can meet the requirements of the existing hexagonal synchronization rod, and the flower-shaped interface has no installation angle requirement. In other embodiments, the interface is designed differently according to the actual requirements, depending on the torque value to be transmitted.

Referring to fig. 1, the first toothed plate 1, the second toothed plate 2 and the cam 61 are designed coaxially, and the gear 3 and the shaft sleeve 5 are designed coaxially, so that the first toothed plate 1 and the gear 3, and the second toothed plate 2 and the gear 3 form a two-stage structure. The cam 61 of the clearance elimination mechanism 6 separates the two sets of wedge mechanisms 62, and when the wedge mechanisms are static, the fan-shaped

blocks

66a and 66b of the two sets of wedge mechanisms 62 are both spread under the action of the spring 65, so that the two sets of wedge mechanisms 62 are respectively matched with the two-stage eccentric structure, and the purpose of eliminating the clearance of the two sets of gear-toothed plate structures is achieved.

As shown in fig. 8, the segment 66a has an inner running surface 68a and an outer running surface 69a, and the segment 66b has an inner running surface 68b and an outer running surface 69b, the inner and outer running surfaces being of eccentric design with an eccentricity e. In operation, the outer running surfaces 69a and 69b rotate along the inner surface of the bushing 5 and the inner running surfaces 68a and 68b rotate against the outer wall of the tooth plate counterbore 7. When the angle adjuster is under a loaded condition, the pressure between the fan-shaped

blocks

66a and 66b and the outer wall of the hole flanging 7 is increased, the sliding friction force is correspondingly increased, and in order to reduce the friction loss and ensure the driving smoothness, strict requirements are imposed on the roughness, the roundness and the verticality of the surface of the hole flanging 7. In addition, when a vehicle collision occurs, the recliner will be subjected to a large external force, which is partially transmitted to the burring 7. The hole flanging must therefore also take sufficient strength into account during the design to ensure the locking strength of the recliner in the event of a crash.

The principle of the seat recliner of the present invention to achieve concentric adjustment is shown in fig. 9 and 10. The first toothed plate 1 is connected with a backrest, is an output end of the angle adjuster and rotates around an axis A; the second gear plate 2 is connected with the seat basin and is an angle adjuster fixing end. When the motor works, the cam 61 is driven to rotate, one wedge mechanism starts to rotate under the action of the cam 61 and compresses the spring 65, and when the spring force is enough to overcome the friction force borne by the other wedge mechanism, the two wedge mechanisms 62 and the spring 65 synchronously rotate in the same direction under the drive of the cam 61. When the wedge mechanism 62 rotates, the gear 3 is driven to perform an eccentric motion with an eccentricity e, which can also be understood as follows: the central axis B of the gear 3 is driven by the wedge mechanism 62 to rotate around the axis a with a radius e. Meanwhile, the gear 3 also performs self-rotation motion around a self central shaft B under the meshing action of the gears. Because second pinion rack 2 is fixed, first pinion rack 1 is the movable tooth board, consequently when gear 3 was eccentric motion, the meshing between the teeth can drive first pinion rack 1 and rotate. Since the first toothed plate 1 can only rotate around the axis a, the movement pattern of the first toothed plate 1 will be concentric rotation, and since the first toothed plate is connected with the backrest, concentric adjustment of the backrest is achieved.

The above embodiments are merely preferred embodiments of the present invention, which are not intended to limit the scope of the present invention, and various changes may be made in the above embodiments of the present invention. All simple and equivalent changes and modifications made according to the claims and the content of the specification of the present application fall within the scope of the claims of the present patent application. The invention has not been described in detail in order to avoid obscuring the invention.

Claims

1. A concentric adjustment seat angle adjuster, characterized in that it comprises two toothed plates respectively connected with the backrest and the seat basin, and the two toothed plates are respectively meshed with a gear located between the two from both sides, so that the A gap eliminating mechanism is arranged in the center shaft hole of the gear, and the outer peripheries of the two tooth plates are fixedly connected together by a hoop.

2 . The seat recliner according to claim 1 , wherein the recliner further comprises a shaft sleeve installed between the central shaft hole of the gear and the backlash eliminating mechanism. 3 .

3 . The seat recliner according to claim 1 , wherein the central shaft holes of the two tooth plates are all turning holes. 4 .

4 . The seat recliner according to claim 1 or 3 , wherein the two tooth plates are provided with sink grooves at the planes adjacent to the inner side of the outer periphery and connected to the teeth. 5 .

5 . The seat recliner according to claim 2 , wherein the center shaft hole of the gear is provided with double-sided flanges supporting the outer edge of the shaft sleeve. 6 .

6 . The seat recliner according to claim 1 , wherein the gear ratio of the two tooth plates to the gear is one tooth plate: gear: another tooth plate=n+1:n:n+2. 6 . , where n is a positive integer.

7 . The seat recliner according to claim 6 , wherein the gear ratio between the two tooth plates and the gear is one tooth plate: gear: another tooth plate=43:42:44. 8 .

8 . The seat recliner according to claim 6 , wherein the gear ratio between the two tooth plates and the gear is one tooth plate:gear:the other tooth plate=37:36:38. 9 .

9 . The seat recliner according to claim 6 , wherein the gear ratio of the two tooth plates to the gear is one tooth plate: gear: another tooth plate=33:32:34. 10 .

10 . The seat recliner according to claim 1 , wherein the clearance elimination mechanism comprises a cam and two sets of wedge mechanisms respectively located on the upper and lower sides of the cam. 11 .

11 . The seat recliner of claim 10 , wherein each group of wedge block mechanisms includes two sector blocks and a spring connected to both. 12 .

12 . The seat recliner according to claim 10 , wherein the cam comprises a cam ring, and a cam shaft is disposed in the middle of the cam ring. 13 .

13. The seat recliner according to claim 12, wherein a drive rod interface is provided in the camshaft.

14 . The seat recliner according to claim 12 , wherein the camshaft and the cam ring are integrally formed or separately assembled. 15 .