CN110145556B

CN110145556B - Improved braking mechanism of seat height adjusting device

Info

Publication number: CN110145556B
Application number: CN201810150055.9A
Authority: CN
Inventors: 江季达; 二瓶正夫; 奚仲强
Original assignee: Fuzhou Mingfang Automobile Parts Industry Co Ltd; Hsin Chong Machinery Works Co Ltd
Current assignee: Fuzhou Mingfang Automobile Parts Industry Co Ltd; Hsin Chong Machinery Works Co Ltd
Priority date: 2018-02-13
Filing date: 2018-02-13
Publication date: 2024-03-15
Anticipated expiration: 2038-02-13
Also published as: CN110145556A

Abstract

The invention discloses an improved braking mechanism of a seat height adjusting device, which comprises a ring body, an output part, a plurality of elastic pads and a plurality of roller groups, wherein the ring body is provided with a plurality of elastic pads; the outer edge of the cam in the output part is protruded with a plurality of driven convex teeth each having an end edge and two hard-joint edges, a first gap exists between the end edge and the inner edge of the ring body, and the first gap is larger than zero in a static state; the elastic pad is overlapped on the inner surface of the driven convex tooth face to face and is provided with two soft joint edges protruding out of the two hard joint edges respectively, the roller group comprises two rollers adjacent to the two soft joint edges respectively, a second gap exists between the rollers and the outer edge, and the second gap is equal to zero in a static state; when the roller is pressed to start to push the soft joint edge to indent, the second gap is larger than zero; when the roller continues to push the soft joint edge to concave inwards or push the soft joint edge to be in hard contact with the hard joint edge, the end edge of the driven convex tooth in the loading direction is connected with the inner edge so that the first gap is equal to zero, and the second gap is larger than the first gap which is equal to zero, thereby reducing the stress of the roller, reducing abrasion and improving durability.

Description

Improved braking mechanism of seat height adjusting device

Technical Field

The present invention relates to a seat height adjusting device, and more particularly to an improved braking mechanism of a seat height adjusting device.

Background

The seat height adjusting device comprises a clutch mechanism and a brake mechanism which are coaxially arranged, and the control handle is connected with the clutch mechanism. The user drives the clutch mechanism through the control handle, the clutch mechanism is connected with the brake mechanism, and the output part in the brake mechanism drives the lifter in the chairs, such as automobile seats, massage chairs or wheelchairs, and the like to control the lifting.

However, in the braking mechanism of the conventional seat height adjusting device, the roller clamped between the inner edge of the braking mechanism and the outer edge of the cam is often easily worn out due to the large external load (the weight from the seat itself or the weight of the occupant, etc.), and thus the actuation is not smooth and even fails, etc., which has long been a problem.

Therefore, it is an important task of the present inventors to solve the above-mentioned problems.

Disclosure of Invention

The invention aims to provide an improved braking mechanism of a seat height adjusting device, which can enable at least one driven convex tooth to support the inner edge to relieve the stress of a roller when bearing external load, thereby reducing abrasion and improving durability.

In order to achieve the above object, the present invention provides an improved braking mechanism of a seat height adjusting device, comprising: a ring body having an inner edge; the output component is arranged in the ring body in a penetrating way and comprises a cam, the outer edge of the cam is provided with a plurality of driven convex teeth which are respectively provided with two hard-connected edges and one end edge connected between the two hard-connected edges, a first gap exists between each end edge and the inner edge, and the first gap is larger than zero in a static state; the elastic pads are overlapped on the inner surface of each driven convex tooth face to face and are provided with two soft joint edges which are respectively protruded out of the two hard joint edges, each roller group comprises two rollers which are respectively adjacent to the two soft joint edges of each elastic pad, a second gap exists between each roller and the outer edge, and the second gap is equal to zero in a static state; when the roller is driven to start to push the soft joint edge to indent, the second gap between the driven roller and the outer edge is larger than zero; when the roller after being driven continues to push the soft joint edge to indent or continues to push the soft joint edge to indent to the bottom and hard contact the hard joint edge, the end edge of at least one driven convex tooth directly contacts the inner edge in the loading direction so that the first gap is equal to zero, and the second gap is larger than the first gap which is equal to zero.

Compared with the prior art, the invention has the following effects: the roller bearing can relieve the stress of the roller bearing when bearing external load, thereby reducing abrasion and improving durability.

Drawings

FIG. 1 is an exploded perspective view of a first embodiment of the brake mechanism and clutch mechanism of the present invention.

Fig. 2 is a perspective view of the present invention after partial assembly according to fig. 1.

Fig. 3 is a perspective view of the invention according to fig. 1 after complete assembly.

Fig. 4 is a top view of the brake mechanism according to the first embodiment of the present invention in a braking state.

Fig. 5 is a cross-sectional view according to fig. 4 of the present invention.

FIG. 6 is a first schematic illustration of the braking mechanism of the first embodiment of the present invention operating to release the brake.

FIG. 7 is a second operation diagram according to FIG. 6 of the present invention.

FIG. 8 is a third operation diagram according to FIG. 7 of the present invention.

FIG. 9 is a diagram illustrating a fourth operation according to the present invention shown in FIG. 8.

FIG. 10 is a top view of a second embodiment of the brake mechanism of the present invention in a braking state.

Symbol description in the drawings:

100. a clutch mechanism; 1. a drive plate; 14. a disk surface; 15. a drive tooth; 151. a beveled edge; 2. an input member; 3. an action assembly; 4. an outer cover; 500. a brake mechanism; 5. 5a an elastic pad; 51. 531 soft edges; 52. anti-slip lines; 53. a support pad body; 6. a fixing frame; 7. an output member; 71. a cam; 710. an outer edge; 72. 72a driven teeth; 720. an inner face; 721. 721a stiffener; 722a recess; 723. 723a end edges; 73. driving the ratchet; 75. a first rectangular body; 76. a second rectangular body; 8. a ring body; 81. an inner edge; 9. a roller group; 91. a roller; a contact point A; l load direction; s1a, S1b, S1c first gaps; s2a, S2b second gap.

Detailed Description

The detailed description and technical content of the present invention are described below with reference to the drawings, which are, however, provided for reference and illustration only and are not intended to limit the present invention.

The invention provides an improved braking mechanism of a seat height adjusting device, which is mainly used for the height adjusting device of a chair such as an automobile seat, a massage chair or a wheelchair. As shown in fig. 1, the height adjusting device includes a clutch mechanism 100 and a brake mechanism 500 coaxially disposed with each other, wherein the clutch mechanism 100 includes an input member 2, a plurality of actuating members 3, a housing 4, and a driving disc 1 shared with the brake mechanism 500 of the present invention, a recess (not shown) for accommodating the input member 2 and the actuating members 3 is provided on a side of the driving disc 1 not shown, the housing 4 covers the recess of the driving disc 1, and the input member 2 is controlled to rotate by a control handle (not shown) to drive the driving disc 1 to rotate via the actuating members 3. The seat height adjusting device is fixed on the chair, and the braking mechanism 500 is meshed with a lifting mechanism arranged in the chair to drive the chair.

As shown in fig. 1 to 5, a first embodiment of a brake mechanism 500 according to the present invention includes a plurality of elastic pads 5, a fixing frame 6, an output member 7, a ring 8, a plurality of roller sets 9, and a driving disc 1. The driving disc 1 and the clutch mechanism 100 share a disc surface 14, the ring body 8 is hollow and has an inner edge 81, and one surface of the driving disc 1 corresponding to the ring body 8 is covered.

The output member 7 is rotatably disposed through the ring body 8 and includes a cam 71 and a driving ratchet 73 coaxially connected to each other. The outer edge 710 of the cam 71 protrudes with a plurality of driven teeth 72, and at this time, as shown in fig. 5 and fig. 4, each driven tooth 72 is located between the outer edge 710 and the inner edge 81 corresponding to each other. Preferably, as shown in fig. 4 and fig. 1, the cam 71 is a rectangular body and has four sides (not labeled with reference numerals), any two adjacent sides are connected by a rounded corner (not labeled with reference numerals), and each of the driven teeth 72 protrudes from between two adjacent rounded corners of the four sides to form a cross-shaped configuration.

Each driven tooth 72 has two hard edges 721 and an end 723 connected between the two hard edges 721. Preferably, the driven teeth 72 are rectangular or thick, so that the two hard edges 721 of each driven tooth 72 are straight and spaced apart from each other, and the end edges 723 connected between the same ends of the two hard edges 721 are shaped like the letter U, except that the connection between each hard edge 721 and the end edge 723 is not rounded, and each end edge 723 is adjacent to the inner edge 81 in a stationary state (i.e., a stationary braking state).

The elastic pads 5 and the roller sets 9 are disposed between the outer edge 710 and the inner edge 81, as follows.

The structure and arrangement of the elastic pad 5 are not limited to the elastic pad 5, as long as each elastic pad 5 can be arranged corresponding to each driven tooth 72 and has two soft joint edges 51 protruding from two hard joint edges 721, respectively, and in this embodiment, the following description will be given by way of example in this section: the elastic pads 5 are overlapped face-to-face between the inner face 720 (shown in fig. 1) of each driven tooth 72 and the disk face 14 (shown in fig. 1) of the driving disk 1, and the width of each elastic pad 5 is slightly larger than the width of each driven tooth 72, so that the two soft joint edges 51 slightly protrude from the two hard joint edges 721 respectively. Preferably, the elastic pads 5 are also rectangular or thick rectangular, so that the two soft edges 51 of each elastic pad 5 are also straight and are spaced apart from each other; the spring pad 5 of this shape is in face-to-face overlapping engagement with the identically shaped driven teeth 72 such that the two soft edges 51 are respectively substantially parallel to the two hard edges 721 to facilitate the soft-contact followed by hard-contact operational setting. In addition, the sum of the thicknesses of each elastic pad 5 and the corresponding driven tooth 72 after being overlapped face to face is equal to or slightly greater than (close to) the thickness of the cam 71, so that the elastic pad 5 is elastically clamped between the inner face 720 of the driven tooth 72 and the disc surface 14 of the driving disc 1.

The elastic pad 5 is an elastic pad body which can be elastically deformed by force or can be elastically concave by force. Each adjacent edge of each elastic pad 5 may further be provided with at least one anti-slip pattern 52, for example, between each elastic pad 5 and the disk surface 14, between each elastic pad 5 and the inner face 720 of the corresponding driven tooth 72, and between each elastic pad and the inner edge 81, respectively, the anti-slip patterns 52 are provided to increase the friction force between each elastic pad 5 and the disk surface 14, between each elastic pad and the inner face 720 and between each elastic pad and the inner edge 81.

Regarding the roller set 9, the present invention is not limited to the structure and arrangement of the roller set 9, but in the present embodiment, two rollers 91 are included as an example, and the two rollers 91 of each roller set 9 are respectively adjacent to or respectively in soft contact with the two soft edges 51 of each elastic pad 5, and the two rollers 91 of each roller set 9 are specifically correspondingly disposed at positions between each passive tooth 72 and each rounded corner. In detail, each roller set 9 is pushed by the driving disc 1 or pushed back by the elastic pad 5 to perform the following actions: the brake is blocked between the outer edge 710 and the inner edge 81, or the brake is released by loosening between the outer edge 710 and the inner edge 81.

One surface of the driving disc 1 is provided with a plurality of driving teeth 15, and each driving tooth 15 extends into a space between any two adjacent roller groups 9, so that each driving tooth 15 can push the roller 91 and push each driven convex tooth 72 to move through the roller 91, and further drive the output part 7 to rotate. Preferably, each driving tooth 15 has two inclined sides 151 disposed at a distance from each other and inclined to each other, and the inclined angles of the two inclined sides 151 of each driving tooth 15 correspond to the diameter of the driving disc 1 (refer to fig. 6), that is, are parallel to the diameter of the driving disc 1, so as to facilitate the driving of the roller 91 to move in a specific direction.

Therefore, when the drive disk 1 is operated, each drive tooth 15 moves in such a manner that the inclined side 151 pushes the roller 91 of each roller group 9, and moves in such a manner that the adjacent hard joint sides 721 of each driven tooth 72 are respectively moved.

The fixing frame 6 covers the other surface of the ring body 8 and is clamped on the ring body 8 and the outer cover 4 to form the seat height adjusting device. The seat height adjusting device can be fixed on the chair by using the fixing frame 6, so that the fixing frame 6, the ring body 8 clamped by the fixing frame 6 and the outer cover 4 can not rotate, and the driving ratchet 73 of the output part 7 can be meshed with a lifting mechanism arranged in the chair to drive the chair.

As shown in fig. 6, is in a stationary braking state. At this time, each roller 91 is engaged between the inner edge 81 and the outer edge 710 to brake, a first gap S1a exists between the end edge 723 of each driven tooth 72 and the inner edge 81, and each first gap S1a is greater than zero in the rest state (i.e. the rest braking state), and a second gap S2a exists between each roller 91 and the outer edge 710, and each second gap S2a is equal to zero in the rest state.

As shown in fig. 7, the initial operation control lever (not shown) rotates the drive disk 1 and the output member 7 is then slightly moved by an external load. When the driving disk 1 rotates together with each driving tooth 15, the bevel edge 151 of each driving tooth 15 will contact one roller 91 of each roller group 9 to generate a contact point A; each driving tooth 15 then pushes each roller 91 with each contact point a, each roller 91 after being driven will start to push one of the soft edges 51 of each elastic pad 5 to indent, and each roller 91 after being driven will separate from the outer edge 710, the second gap S2b is greater than zero at this time to release the brake, and the second gap S2b is greater than the first gap S1a and the first gap S1a is still greater than zero at this time (not shown in fig. 6 and 7).

Next, as shown in fig. 7, when the second gap S2b is released and the brake is released as above, or when each roller 91 after being actuated continues to push each soft contact edge 51 to indent, at this time, a load direction L is generated in the seat height adjusting device due to an external load (weight from the seat itself or weight of the occupant, etc.), at least one actuated tooth 72 located below the axis (not labeled with a reference numeral) of the output member 7 after releasing the brake is slightly moved in the load direction L due to the external load, such that the end edge 723 thereof directly contacts the inner edge 81 to make the first gap S1b equal to zero, that is, at this time, there will be an end edge 723 of at least one actuated tooth 72 that contacts the inner edge 81, and therefore, the second gap S2b is also larger than the first gap S1b (at this time s1b=0); as for the end edges 723 of the other driven teeth 72 (for example, the two driven teeth 72 located above the axial center), the first gap S1c becomes slightly larger (S1 c > S1 a) than the inner edge 81.

When the roller 91 is pressed to start pressing the soft joint edge 51 to indent, the roller 91 is in soft contact with the soft joint edge 51; when the roller 91 after being driven continues to push the soft contact edge 51 to concave to the bottom, the roller 91 will be in hard contact with the hard contact edge 721 to push the driven convex teeth 72.

As shown in fig. 8, the control is rotated in the same direction to the bottom state for continued operation. When the driving teeth 15 continue to push the rollers 91, the driven rollers 91 continue to push the soft edges 51 to recess to the bottom and hard contact the hard edges 721, the second gap (not labeled with a reference numeral) is greater than or equal to the second gap S2b, and the rollers 91 start to push the driven teeth 72 to rotate until the control handle operationally touches the stop point. Of course, the second gap S2b is still larger than the first gap S1b at this time (see fig. 7).

As shown in fig. 9, the reaction state is a state when the control knob is released. When the user releases the control handle, the originally concave soft joint edge 51 of each elastic pad 5 will be elastically restored to be flat and push the roller 91 back, so that the roller 91 is clamped between the inner edge 81 and the outer edge 710 again, and at this time, the braking action is started. At the same time, the rollers 91 of each roller set 9 will also push the clutch mechanism 100 back to its original position (not shown).

The single adjustment of the seat up or down can be completed through the operations shown in fig. 6 to 9, and of course, the multiple adjustment operations of fig. 6 to 9 can be repeated until the seat is adjusted to the required height.

In addition, it should be noted that, referring to fig. 6, the output member 7 defines a rotation path (not labeled with a reference numeral) formed when each driven tooth 72 rotates about the center of the cam 71, and the protruding length center of each driven tooth 72 and the axle center of each roller 91 are located on the rotation path, so that each roller 91 is beneficial to push each driven tooth 72 in a manner of not generating a component force or reducing a component force.

The first embodiment of the present invention has the following effects compared with the prior art:

1. wear is reduced, and durability is improved: when the brake is released, at least one driven convex tooth 72 directly contacts the inner edge 81 by the end edge 723 thereof in the loading direction L, so as to share the external load borne by the roller 91, thus reducing the stress of the roller 91 and reducing the abrasion, further improving the durability and ensuring smooth action without failure.

2. Labor-saving operation effect: the protruding length center of each driven convex tooth 72 and the axle center of each roller 91 are located on the above-mentioned rotating path, so that the force component generated by each roller 91 when pushing each driven convex tooth 72 is not reduced, thereby achieving the labor-saving operation effect. Preferably, the end edge 723 of each driven tooth 72 is adjacent to the inner edge 81 to further reduce the generation of force components; preferably, the driving teeth 15 have two inclined sides 151 corresponding to the cam diameter, so that the driving teeth 15 can smoothly push the roller 91 to move in a specific direction without or with reduced component force.

3. Easy to process and easy to integrally form: the shape of the driven tooth 72 is changed into a simplified rectangular shape (or a rectangular thick sheet shape), so that the processing is easy, and the integrated forming is easy, so that the cost effect of the integrated part is achieved. In addition, as for the processing, press processing including forging, for example, can be adopted, so that the processing cost can be reduced. Preferably, the shape of the elastic pad 5 can be changed into a simplified rectangular body shape (or a rectangular thick sheet shape).

4. Has comfortable operation hand feeling: the two soft edges 51 of the elastic pad 5 are respectively protruded from the two hard edges 721 of the driven convex teeth 72, so that the comfortable operation hand feeling of soft contact and then hard contact is provided during the height adjustment operation.

A second embodiment of a brake mechanism 500 according to the present invention is shown in fig. 10. The second embodiment is substantially identical to the first embodiment described above, with the differences only being in the resilient pad 5a and the passive teeth 72a, as described in detail below.

Each of the driven teeth 72a has a convex shape and includes the two hard joint sides 721a and two concave portions 722a which are inwardly contracted with respect to the two hard joint sides 721a. Preferably, the driven tooth 72a includes a first rectangular body 75 and a second rectangular body 76 (the shape is easy to process and easy to integrally form) stacked one above the other, the first rectangular body 75 has two rigid edges 721a, and two sides of the second rectangular body 76 are retracted relative to the two rigid edges 721a to form two concave portions 722a. Specifically, the two hard edges 721a of each driven tooth 72a protrude from the outer edge 710, and the end edge 723a of each driven tooth 72a is correspondingly connected between the two concave portions 722a, and the first gap (S1 a in fig. 6) similar to the first embodiment exists between each end edge 723a and the inner edge 81 in the rest state.

Each elastic pad 5a includes two supporting pad bodies 53 which may be cylindrical or elliptic cylindrical, the two supporting pad bodies 53 are respectively accommodated in the two concave portions 722a, and opposite outer sides of the two supporting pad bodies 53 of each elastic pad 5a are respectively provided with one of the two soft connection edges 531, and the two soft connection edges 531 also respectively protrude from the two hard connection edges 721a.

Thereby, the second embodiment of the present invention also has all the effects of the foregoing first embodiment.

The foregoing description is only illustrative of the preferred embodiments of the present invention and is not to be construed as limiting the scope of the invention, as all changes which come within the meaning and range of equivalency of the description and drawings are intended to be embraced therein.

Claims

1. An improved braking mechanism for a seat height adjustment device, comprising:

a ring body having an inner edge;

the output component is arranged in the ring body in a penetrating way and comprises a cam, the outer edge of the cam is provided with a plurality of driven convex teeth which are respectively provided with two hard-connected edges and one end edge connected between the two hard-connected edges, a first gap exists between each end edge and the inner edge, and the first gap is larger than zero in a static state;

the elastic pads are overlapped on the inner surface of the driven convex teeth face to face, each elastic pad is provided with two soft joint edges which are respectively protruded out of the two hard joint edges, each roller group comprises two rollers which are respectively adjacent to the two soft joint edges of each elastic pad, a second gap exists between each roller and the outer edge, and the second gap is equal to zero in a static state;

the driving disc corresponds to the ring body cover; and

a housing corresponding to the drive plate housing;

wherein when the roller is driven to start to push the soft joint edge to indent, the second gap between the driven roller and the outer edge is larger than zero; when the roller after being driven continues to push the soft joint edge to indent or continues to push the soft joint edge to indent to the bottom and hard contact the hard joint edge, at least one end edge of the driven convex tooth directly contacts the inner edge in the loading direction so that the first gap is equal to zero, and the second gap is larger than the first gap which is equal to zero.

2. The improved brake mechanism of claim 1, wherein each of said resilient pads and corresponding said driven lugs are rectangular.

3. The improved brake mechanism of claim 2, wherein said two soft edges of each said resilient pad are straight and spaced apart from each other, and said two hard edges of each said driven tooth are also straight and spaced apart from each other.

4. The improved brake mechanism of claim 1, wherein each of said resilient pads is in face-to-face engagement between an inner face of each of said driven lugs and a face of said drive plate.

5. The improved brake mechanism of claim 4, wherein the sum of the thicknesses of each of said resilient pads and corresponding said driven teeth after being stacked one upon another is greater than or equal to the thickness of said cam.

6. The improved brake mechanism of claim 4, wherein said drive plate has a plurality of drive teeth extending between any two adjacent roller sets, each of said drive teeth having two beveled edges spaced apart from each other and disposed obliquely relative to each other, said drive teeth pushing said rollers with said beveled edges toward said hard edges adjacent to each other.

7. The improved brake mechanism of claim 4, wherein at least one anti-slip feature is provided between each of said resilient pads and said disc surface of said drive disc, said inner faces of said corresponding driven teeth, and said inner edges of said ring body, respectively.

8. The improved brake mechanism of claim 1, wherein each of the plurality of driven lugs has two recesses that are inwardly tapered relative to the two hard edges, each of the plurality of resilient pads includes two support pads received in the two recesses, and each of the two support pads of the plurality of resilient pads has one of the two soft edges protruding from the two hard edges.

9. The improved brake mechanism of claim 8, wherein the two hard edges of each of the driven teeth protrude from the outer edge of the cam, the end edge of each of the driven teeth is correspondingly connected between the two recesses, the first gap exists between each of the end edges and the inner edge, and the first gap is greater than zero in a rest state.

10. The improved brake mechanism of claim 8, wherein each of said driven lugs comprises a first rectangular body and a second rectangular body stacked one above the other, said first rectangular body having said two hard edges, said second rectangular body having said two recesses formed on opposite sides thereof by being retracted relative to said two hard edges.

11. The improved brake mechanism of claim 1 or 8, wherein when the roller is actuated to begin to push against the soft flange recess, the second gap between the actuated roller and the outer edge is greater than the first gap and the first gap is still greater than zero.

12. The improved brake mechanism of the seat height adjusting device according to claim 1 or 8, wherein when the roller is pressed to start pressing the soft joint edge inward, the roller after being pressed is in soft contact with the soft joint edge first; when the roller after being driven continuously pushes the soft joint edge to concave inwards to the bottom, the roller after being driven is in hard contact with the hard joint edge to push the driven convex teeth.

13. The improved brake mechanism of claim 1 or 8, wherein each of the driven teeth has a rotation path formed around the center of the cam, the center of the protruding length of each of the driven teeth and the axis of each of the rollers are located on the rotation path.

14. An improved brake mechanism for a seat height adjustment assembly as set forth in claim 13 wherein said end edge of each said driven tooth is adjacent said inner edge.

15. The improved brake mechanism of claim 1 or 8, wherein the cam is a rectangular body and has four sides, any two adjacent sides are connected by a rounded corner, each of the driven teeth protrudes from between two adjacent rounded corners of the four sides, and each of the rollers is disposed at a position between each of the driven teeth and each of the rounded corners.