CN111133220A

CN111133220A - Suspension device

Info

Publication number: CN111133220A
Application number: CN201880060556.6A
Authority: CN
Inventors: 秋本政信; 高桥启介
Original assignee: Yamaha Motor Co Ltd; KYB Motorcycle Suspension Co Ltd
Current assignee: Yamaha Motor Co Ltd; KYB Motorcycle Suspension Co Ltd
Priority date: 2017-09-26
Filing date: 2018-07-19
Publication date: 2020-05-08
Anticipated expiration: 2038-07-19
Also published as: JP7002266B2; CN111133220B; WO2019064838A1; JP2019060386A; TW201914845A; TWI785107B

Abstract

A suspension device of the present invention includes: a ring-shaped spring seat (11) which is rotatably mounted on the outer periphery of the outer tube (1) in the circumferential direction and supports one end of the suspension spring (3); an annular restricting member (10) that is attached to the outer periphery of the outer tube (1) on the side opposite the suspension spring of the spring seat (11) and that restricts the movement of the spring seat (11) on the side opposite the suspension spring; a plurality of cam portions (22A, 22B) that are provided on the restricting member (10) side of the spring seat (11) and that have a plurality of contact surfaces (23, 24, 25) having different axial heights; and a plurality of protrusions (17A, 17B) provided in the restriction member (10), arranged at positions corresponding to the cam portions (22A, 22B), and abutting against the abutment surfaces (23, 24, 25).

Description

Suspension device

Technical Field

The present invention relates to a suspension device.

Background

A conventional suspension device is mounted between a vehicle body and a wheel of a two-wheeled vehicle, and includes: an outer tube; a rod movably inserted in an axial direction into the outer tube; and a suspension spring disposed on an outer periphery of the outer tube and urging the rod in an extending direction.

Further, JP2007-085378A discloses a suspension device including: a spring seat provided with a cam portion that is rotatably attached to an outer periphery of a cylindrical cover body disposed on an outer periphery of the rod in a circumferential direction, supports one end of the suspension spring, and has a plurality of cam surfaces having different heights on a side opposite to the suspension spring; and an initial load adjusting device composed of a restricting member having a protrusion protruding toward the spring seat side.

According to this configuration, if the spring seat is rotated to bring the projection into contact with the cam surface of any height, the initial load acting on the suspension spring can be adjusted.

Disclosure of Invention

In addition, in the conventional suspension device, since the projection and the cam surface are only in one-point contact, the spring force of the suspension spring acts on the cam surface contact portion in a concentrated manner. Therefore, in order to ensure the strength of the cam portion and the protrusion, the spring seat and the restricting member are formed of a high-strength metal such as iron, and the restricting member is welded and fixed to the cover body.

However, if the spring seat and the restricting member are formed using iron or the like as in the conventional method, the weight of the spring seat and the restricting member increases.

In addition, the initial load adjusting device may be provided on the outer periphery of the outer pipe. However, in order to avoid occurrence of welding deformation on the outer pipe as in the case of the conventional welding fixing of the restricting member, it is necessary to take measures such as mounting a protector between the outer pipe and the restricting member as disclosed in japanese patent JP2013-036520a, which is very time-consuming and labor-consuming.

Accordingly, an object of the present invention is to provide a suspension device in which a spring seat and a restricting member can be formed of materials having lower strength and lighter weight than those of the conventional suspension device, and the restricting member does not need to be welded.

The method for solving the problem is characterized by comprising the following steps: a rod movably inserted into the outer tube in an axial direction; a suspension spring provided on an outer periphery of the outer tube and urging the rod in an extending direction; an annular spring seat which is rotatably attached to an outer periphery of either the outer tube or the rod in a circumferential direction and supports one end of the suspension spring; an annular restricting member that is attached to the spring seat on the outer periphery of either the outer tube or the rod on the side opposite to the suspension spring and restricts movement of the spring seat on the side opposite to the suspension spring; a plurality of cam portions provided on the other side of either the spring seat or the restricting member, and having a plurality of contact surfaces having different axial heights; and a plurality of protrusions provided on either one of the spring seat and the regulating member, arranged at positions corresponding to the respective cam portions, and abutting against the abutment surface.

Drawings

Fig. 1 is a side view showing a motorcycle to which a suspension device according to the present embodiment is applied.

Fig. 2 is a front cross-sectional view showing the entire suspension device according to the present embodiment.

Fig. 3 is a longitudinal sectional view of the initial load adjusting apparatus according to the present embodiment.

Fig. 4(a) is an expanded view of the projection and the cam according to the present embodiment, and shows a state at stage 1. Fig. 4(B) is an expanded view of the projection and the cam according to the present embodiment, and shows a state in the second stage. Fig. 4(C) is an expanded view of the projection and the cam according to the present embodiment, and shows a state at the third stage.

Fig. 5 is an X-X sectional view of fig. 2.

Fig. 6 is a front view of the initial load adjusting apparatus according to the present embodiment.

Detailed Description

The present embodiment will be described below with reference to the drawings. Like reference numerals designate like parts throughout the several views.

As shown in fig. 1, the suspension device S is mounted on the motorcycle 100. The motorcycle 100 includes a body frame 101; a front wheel 103 connected to the front side of the vehicle body frame 101 in the traveling direction via a front fork 102; and a rear wheel 104 connected to the rear of the vehicle body frame 101 in the traveling direction via a suspension device S.

Specifically, the vehicle body frame 101 includes: a head pipe 110 located at the vehicle center in the vehicle width direction; a lower frame 111 connected to the head pipe 110 and extending downward in the drawing; a bottom frame 112 connected to a lower end portion of the lower frame 111 and extending rearward in the traveling direction; and a rear frame 113 connected to a rear end of the bottom frame 112. Also, the rear frame 113 supports the seat 105 on which the driver sits.

The front frame 102 includes: a fork main body 120 having a lower end coupled to an axle of the front wheel 103; and a steering shaft 121 coupled to an upper end of the fork main body 120 and inserted into the head pipe 110. The handle 106 is supported by the upper end of the steering shaft 121.

A foot board 107 for putting both feet of a driver seated in the seat 105 during driving is provided below the vehicle body frame 101. Further, a center cover 108 surrounding the lower frame 111, the bottom frame 112, and the rear frame 113 is disposed at a center position in the vehicle width direction of the foot plate 107. Further, a front cover 109 surrounding the head pipe 110 and the steering shaft 121 is disposed below the handlebar 106.

The motorcycle B includes an engine 130, which is an internal combustion engine generating a driving force, and a power transmission device 131 connected to an axle of the rear wheel 104 and transmitting the driving force generated by the engine 130 to the rear wheel 104.

The suspension device S is mounted between the power transmission device 131 coupled to the axle of the rear wheel 104 and the rear frame 113.

In return, as shown in fig. 2, the suspension device S includes: an outer tube 1; a damper body D having a rod 2 inserted into the outer tube 1 movably in the axial direction; a suspension spring 3 which is provided on the outer periphery of the outer tube 1 and biases the rod 2 in the extending direction; and an initial load adjusting device 4 for adjusting the initial load of the suspension spring 3.

Specifically, as shown in fig. 2, the damper body D is configured to include a rod 2 inserted into a bottomed cylindrical outer tube 1 so as to be movable in the axial direction; a rod guide 5 mounted on an open end of the outer tube 1 and supporting the rod 2 by a shaft; a free piston 6 inserted slidably into the inner periphery of the outer tube 1 to divide the interior of the outer tube 1 into a liquid chamber R filled with a working liquid and a gas chamber G filled with a gas; and a piston 7 provided at the front end of the rod 2 and dividing the inside of the liquid chamber R into two chambers, an extension side chamber R1 and a compression side chamber R2.

Further, the piston 7 is formed with an extension side passage 7a and a compression side passage 7b that communicate the extension side chamber R1 and the compression side chamber R2. In addition, the piston 7 is provided with: an extension-side valve 9 which is laminated on the compression-side chamber side of the piston 7 and which applies resistance to the flow of the working fluid through the extension-side passage 7 a; and a compression-side valve 8 which is laminated on the extension-side chamber side of the piston 7 and which applies resistance to the flow of the working fluid through the compression-side passage 7 b. Therefore, if the shock absorber body D expands and contracts, when the working fluid moves from the compressed-side room to the expanded-side room in the outer tube 1 through the expansion-side passage 7a or the compression-side passage 7b, resistance is applied to the flow of the working fluid by the expansion-side valve 9 or the compression-side valve 8, so that a damping force is generated.

Further, the gas chamber G expands and compresses by the axial movement of the free piston 6, and it is possible to compensate for a change in the volume of the working fluid due to a change in the volume of the cylinder corresponding to the rod inlet/outlet volume portion and a change in the volume of the working fluid due to a change in the temperature, which are caused by the expansion and contraction operation of the shock absorber main body D.

In the present embodiment, the damper body D is of a single cylinder type, but may be of a double cylinder type in which a cylinder is provided in the outer tube 1 and the piston 7 or the base valve (base valve) is inserted into the cylinder. In the case of the double cylinder type, the reservoir formed between the outer tube 1 and the cylinder compensates for a change in volume in the cylinder corresponding to the rod in-and-out volume portion accompanying the expansion and contraction operation of the damper body D.

As shown in fig. 2, a vehicle body side bracket 35 connectable to the vehicle body side of the motorcycle is provided at one rod opposite side end of the outer tube 1, and a wheel side bracket 36 connectable to the wheel side of the motorcycle is provided at each base end as one piston opposite side end of the rod 2. Thus, the shock absorber main body D can be attached in an inverted state between the vehicle body and the wheel by connecting the outer tube 1 to the vehicle body via the vehicle-body-side bracket 35, and connecting the rod 2 to the wheel via the wheel-side bracket 36. However, the damper body D may be attached upright between the vehicle body and the wheel by connecting the outer tube 1 side of the damper body D to the wheel, connecting the rod 2 side to the vehicle body, and connecting the damper body D to the wheel.

Further, an insertion member 38 attached to the bracket 35 on the vehicle side is provided at the opposite rod-side end of the outer tube 1. As shown in fig. 2, the portion of the insertion member 38 connected to the outer tube 1 is formed as an annular flange portion 38a having a larger outer diameter than the outer tube 1, and the flange portion 38a protrudes outward when viewed from the axial direction.

As shown in fig. 2, the annular restricting member 10 and the annular upper spring bearing 11 are laminated in this order on the outer periphery of the opposite rod end of the outer tube 1 and are attached to the flange portion 38 a. A suspension spring 3 that biases the rod 2 in the extending direction and elastically supports the vehicle body is mounted between an annular lower spring seat 37 and an annular upper spring seat 11 provided on the outer periphery of the rod 2. Thus, the suspension device S can absorb the impact from the road surface when the vehicle travels by the suspension spring 3, and suppress the vertical vibration of the suspension spring 3 by the damping force generated when the shock absorber body D expands and contracts, thereby providing the riding vehicle with a comfortable feeling.

Next, the initial load adjusting apparatus 4 will be explained. The initial load adjusting device 4 is configured to include the upper spring seat 11 and the regulating member 10.

As shown in fig. 2 and 3, the upper spring bearing 11 includes: a cylindrical portion 20 which is attached to the outer periphery of the outer tube 1 so as to be movable in the axial direction and is rotatable in the circumferential direction; and a support portion 21 that is provided in the circumferential direction of the outer periphery of the cylindrical portion 20 and supports one end of the suspension spring 3.

As shown in fig. 3, a plurality of ribs 41 extending in the axial direction of the cylindrical portion 20 are provided on the inner periphery of the cylindrical portion 20 in the circumferential direction, and the axial movement of the upper spring bearing 11 is guided by these ribs 41.

As shown in fig. 6, the support portion 21 is formed of a plurality of projections 21a, and the plurality of projections 21a are provided in the circumferential direction of the outer periphery of the tube portion 20 and project outward from the outer periphery of the tube portion 20. As shown in fig. 3, the inner side of the projection 21a is thinned, and the material of the upper spring bearing 11 can be reduced.

The support portion 21 is a plurality of projections 21a provided in the circumferential direction of the tube portion 20, but may be provided with a flange on the outer periphery of the tube portion 20, for example, and one end of the suspension spring 3 may be supported by the flange.

Further, a plurality of

cam portions

22A, 22B are provided on the restricting member side end of the cylindrical portion 20 on the side opposite to the suspension spring, and the

cam portions

22A, 22B have a plurality of

contact surfaces

23, 24, 25 having different axial heights.

Specifically, the upper spring seat 11 is provided with two

cam portions

22A and 22B in the circumferential direction of the upper end of the cylindrical portion 20 in the drawing. As shown in fig. 3, the thickness of the cylindrical portion 20 in the radial direction is set to be the same as the thickness of the

cam portions

22A and 22B provided at the upper end of the cylindrical portion 20 in the radial direction, and is formed to be relatively thick. The

cam portions

22A and 22B further include

cam ridges

26, 27, and 28 arranged at equal intervals in the counterclockwise direction, i.e., in the left direction in the drawing, in order of a first cam ridge 26, a second cam ridge 27 having a height greater than the first cam ridge 26 in the axial direction, and a third cam ridge 28 having a height greater than the second cam ridge 27 in the axial direction. As shown in fig. 4(a) to (C), the first cam lobe 26 includes: a first contact surface 23 which is an inclined surface connected to the adjacent third cam 28; and a first locking surface 29 which is an inclined surface connected to the adjacent second cam ridge 27. The second cam 27 includes: a second contact surface 24 which is an inclined surface connected to the adjacent first cam ridge 26 and has a higher axial height than the first contact surface 23; and a second locking surface 30 which is an inclined surface continuous with the adjacent third cam 28. The third cam lobe 28 includes: a third contact surface 25 which is an inclined surface connected to the adjacent second cam ridge 27 and has a higher axial height than the second contact surface 24; and a third locking surface 31 which is an inclined surface connected to the adjacent first cam 26.

As shown in fig. 4(a) to (C), the inclination angles of the contact surfaces 23, 24, and 25 of the

cam cams

26, 27, and 28 are all the same.

On the other hand, as shown in fig. 2 and 3, the regulating member 10 includes: an annular base 12 rotatably attached to the outer periphery of the outer tube 1 in the circumferential direction; and a plurality of

projections

17A, 17B provided at equal intervals in the circumferential direction at the lower end of the annular base 12 in the figure, arranged at positions corresponding to the

cam portions

22A, 22B, respectively, and coming into contact with the contact surfaces 23, 24, 25.

Specifically, the restricting member 10 is provided with two

protrusions

17A, 17B in the circumferential direction of the lower end of the annular base 12 in the drawing. The radial thickness of the

protrusions

17A and 17B is set to be thicker than the radial thickness of the

cam portions

22A and 22B. The first projection 13, the second projection 14, and the third projection 15 are provided in the counterclockwise direction (left direction in the drawing) in the

respective projection portions

17A and 17B. The inclination angle of the adjacent third projection 15 side of the first projection 13 is set to be the same as the inclination angle of the third locking surface 31, and the inclination angle of the adjacent second projection 14 side of the first projection 13 is set to be the same as the inclination angle of the first contact surface 23. The inclination angle of the adjacent first projection 13 side of the second projection 14 is set to be the same as the inclination angle of the first locking surface 29, and the inclination angle of the adjacent third projection 15 side of the second projection 14 is set to be the same as the inclination angle of the second contact surface 24. The inclination angle of the adjacent second projection 14 side of the third projection 15 is set to be the same as the inclination angle of the second locking surface 30, and the inclination angle of the adjacent first projection 13 side of the third projection 15 is set to be the same as the inclination angle of the third contact surface 25.

Thus, as shown in fig. 4A, the

projections

17A and 17B provided on the regulating member 10 are shaped to match the

cam portions

22A and 22B.

Further, as shown in fig. 3, the restricting member 10 includes a cylindrical cover 16 extending from the outer periphery of the annular base 12 toward the upper spring seat side. As shown in fig. 5, a plurality of projecting portions 40 extending in the axial direction of the cap 16 are provided on the outer periphery of the cap 16 at the same intervals in the circumferential direction as the plurality of projecting portions 21a provided on the outer periphery of the cylindrical portion 20.

Next, the operation of the initial load adjusting apparatus 4 of the present embodiment will be described. In the initial load adjusting device 4, the initial load of the suspension spring 3 can be adjusted in three stages. As shown in fig. 4(a), in the first stage where the initial load of the suspension spring 3 is minimum, the

first protrusions

13, 13 are brought into contact with the first contact surfaces 23, the

second protrusions

14, 14 are brought into contact with the second contact surfaces 24, and the

third protrusions

15, 15 are brought into contact with the third contact surfaces 25, 25.

At this time, the upper spring bearing 11 having the

cam portions

22A and 22B is biased toward the restricting member 10 by the suspension spring 3, and the contact surfaces 23, 24, and 25 contact the

protrusions

13, 14, and 15 at the inclined surfaces, so that a force is generated to relatively rotate the upper spring bearing 11 and the restricting member 10. However, even if the upper spring bearing 11 and the restricting member 10 attempt to rotate relative to each other, the

projections

13, 14, and 15 contact the locking surfaces 29, 30, and 31, and therefore the relative rotation of the upper spring bearing 11 and the restricting member 10 is prevented.

In a second stage in which the initial load of the suspension spring 3 is further increased than in the first stage, the upper spring bearing 11 is rotated while the abutment surfaces 23, 24, 25 with which the

projections

13, 14, 15 abut are shifted one by one in the counterclockwise direction (left direction in the drawing). Then, as shown in fig. 4(B), the

first projections

13, 13 abut against the second abutment surfaces 24, respectively, and the

second projections

14, 14 abut against the third abutment surfaces 25, respectively. In this way, the upper spring bearing 11 moves only by the distance of the axial height difference between the first contact surface 23 and the second contact surface 24 in the downward direction in fig. 2, so that the initial load of the suspension spring 3 mounted between the upper spring bearing 11 and the lower spring bearing 37 is greater than in the first stage.

At this time, too, since the

projections

13 and 14 are in contact with the locking surfaces 29 and 30, the relative rotation between the upper spring bearing 11 and the restricting member 10 is prevented.

In a third stage in which the initial load of the suspension spring 3 is further increased than in the second stage, the upper spring bearing 11 is rotated while shifting the abutment surfaces 24 and 25, with which the

projections

13 and 14 abut, counterclockwise (left direction in the drawing) by one from the state in the second stage. Then, as shown in fig. 4(C), the

first protrusions

13, 13 are brought into contact with the third contact surfaces 25, respectively. In this way, the upper spring bearing 11 moves only by the distance of the difference in axial height between the second contact surface 24 and the third contact surface 25 in the downward direction in fig. 2, so the initial load of the suspension spring 3 is greater than in the second stage.

At this time, too, since the

first projections

13 and 13 are in contact with the second locking surfaces 30 and 30, the relative rotation of the upper spring bearing 11 and the restricting member 10 is prevented.

When the initial load of the suspension spring 3 is reduced, the upper spring bearing 11 may be rotated in a direction opposite to the direction in which the initial load of the suspension spring 3 is increased.

In this way, in the initial load adjusting device 4, if the upper spring bearing 11 is rotated so that the

projections

13, 14, and 15 come into contact with any of the contact surfaces 23, 24, and 25, the magnitude of the initial load of the suspension spring 3 can be adjusted.

As described above, in the first stage of the initial load adjusting device 4, the first protrusions 13, the second protrusions 14, and the

third protrusions

15, 15 respectively contact the first contact surfaces 23, the second contact surfaces 24, and the third contact surfaces 25, 25. Therefore, as shown in fig. 4A, in the first stage of the initial load adjuster 4, the restricting member 10 and the upper spring seat 11 are in contact on all surfaces over the entire circumference.

In the second stage of the initial load adjusting apparatus 4, the

first projections

13 and 13, the

second projections

14 and 14, the first contact surfaces 23 and 23, and the second contact surfaces 24 and 24 contact each other, so that the restricting member 10 and the upper spring bearing 11 contact each other at 4 as shown in fig. 4 (B).

Further, in the third stage of the initial load adjusting device 4, the

first protrusions

13, 13 are in contact with the respective first contact surfaces 23, and therefore, as shown in fig. 4(C), the restricting member 10 is in contact with the upper spring seat 11 at two places.

Therefore, in the initial load adjuster 4, the restricting member 10 and the upper spring seat 11 are always in contact at two or more places.

In this way, in the initial load adjuster 4, since the restricting member 10 and the upper spring seat 11 are always in contact at two or more places, a larger contact area can be always ensured between the restricting member 10 and the upper spring seat 11 as compared with the conventional one-point contact. In addition, since the restricting member 10 and the upper spring seat 11 are always in contact at two or more places, even if the upper spring seat 11 is pressed by the suspension spring 3, it is difficult to incline and to keep stable as compared with the conventional one.

In addition, in the present embodiment, since the radial thickness of the

cam portions

22A and 22B and the

projection portions

17A and 17B is formed to be relatively thick, the contact area between the restricting member 10 and the upper spring seat 11 can be secured more, and the pressure acting on the restricting member 10 and the upper spring seat 11 can be reduced.

In addition, in the present embodiment, since the inclination angles of the abutment surfaces 23, 24, and 25 are the same as the inclination angles of the abutment sides of the

projections

13, 14, and 15 with the abutment surfaces 23, 24, and 25, the abutment surfaces 23, 24, and 25 are in surface contact with the

projections

13, 14, and 15, not at a point, and therefore, the contact area between the restricting member 10 and the upper spring seat 11 can be ensured to be larger.

Since the inclination angles of the contact surfaces 23, 24, and 25 are the same, even when the upper spring seat 11 is rotated, the contact surfaces 23, 24, and 25 with which the

protrusions

13, 14, and 15 contact change, but the

protrusions

13, 14, and 15 come into surface contact with the contact surfaces 23, 24, and 25.

Therefore, in the present embodiment, the pressure acting on the upper spring bearing 11 and the restriction member 10 can be reduced by the spring force of the suspension spring 3 more than in the conventional case. Thus, the upper spring seat 11 and the restricting member 10 can be formed of a material having lower strength and lighter weight than conventional ones, and therefore, the material selectivity is improved. In addition, the strength of the material forming the upper spring bearing 11 and the restricting member 10 may be ensured so long as the strength can withstand the maximum pressure applied when the initial load adjusting apparatus 4 is set to the third stage, at least when the contact area is reduced, that is, in the present embodiment.

In addition, in the present embodiment, since it is not necessary to weld and fix the upper spring bearing 11 and the restricting member 10 to the outer periphery of the outer tube 1, the process of the welding operation can be omitted, and a protector or the like that prevents the welding deformation of the outer tube 1 can be omitted, thereby reducing the number of components.

In addition, three

cam portions

26, 27, 28 are provided in the

cam portions

22A, 22B, respectively, and the number of cam portions is not limited to three, and may be any number as long as the number of stages of the initial load of the suspension spring 3 is adjusted as necessary.

The first cam ridges 26, the second cam ridges 27, and the

third cam ridges

28, 28 provided on the

cam portions

22A, 22B may have different axial heights from each other. In this case, the axial height of each of the

projections

13, 14, 15 of the

projections

17A, 17B may be set so that the fitting height of the cam portion 22A and the projection 17A is equal to the fitting height of the cam portion 22B and the projection 17B.

In the present embodiment, the two

cam portions

22A and 22B are provided in the upper spring bearing 11, but the number of cam portions is not limited to two, and three or more cam portions may be provided.

Further, a plurality of cam portions may be provided at arbitrary positions in the circumferential direction of the cylindrical portion 20. Further, the plurality of cam portions may be provided at intervals.

However, if the number of the cam portions is increased or a portion without the cam portions is provided, the circumferential length of each cam portion becomes shorter and the inclination angle of each

cam ridge

26, 27, 28 becomes steeper. Then, when the upper spring bearing 11 is rotated, the resistance generated between the upper spring bearing and the

projections

13, 14, and 15 increases, and therefore the operability of the initial load adjuster 4 is degraded. Therefore, as in the present embodiment, when the number of the

cam portions

22A and 22B is two and the

cam portions

22A and 22B are continuously provided without interruption, the inclination angles of the

cam ridges

26, 27, and 28 can be made gentle, and the operability of the initial load adjusting device 4 can be improved.

In the present embodiment, the

projections

17A and 17B are formed in shapes matching the

cam portions

22A and 22B, but if the projections are arranged at positions corresponding to the

cam portions

22A and 22B, the number and shape of the projections provided on the

projections

17A and 17B are not particularly limited, and there may be at least one projection for each corresponding cam portion.

In the present embodiment, the

projections

17A and 17B are provided in the restricting member 10 and the

cam portions

22A and 22B are provided in the upper spring seat 11, respectively, but the

projections

17A and 17B may be provided in the upper spring seat 11 and the

cam portions

22A and 22B may be provided in the restricting member 10.

In addition, in the present embodiment, the upper spring seat 11 and the restricting member 10 are formed of synthetic resin. In this way, when the upper spring seat 11 and the restricting member 10 are formed of synthetic resin, the upper spring seat 11 and the restricting member 10 can be made lighter and the upper spring seat 11 and the restricting member 10 can be easily formed, as compared with the case where they are formed of metal such as iron.

In addition, in the case where the same number of

cam ridges

26, 27, 28 are provided in the cylindrical portion 20 of the upper spring bearing 11, if the circumferential length of the cylindrical portion 20 is long, the inclination angles of the respective abutment surfaces 23, 24, 25 in the

respective cam ridges

26, 27, 28 can be reduced. Here, since the upper spring bearing 11 is made of a lightweight synthetic resin which is easy to mold, even if the thickness of the cylindrical portion 20 in the radial direction is increased and the outer diameter is increased in order to increase the circumferential length of the cylindrical portion 20, the upper spring bearing is not heavy as compared with the case where it is made of metal.

Therefore, if the upper spring bearing 11 is formed of synthetic resin, the operability of the initial load adjuster 4 can be improved if the radial thickness of the cylindrical portion 20 is increased and the outer diameter is increased.

The type of synthetic resin is not particularly limited, but when the pressure acting on the upper spring seat 11 and the restricting member 10 is extremely high, such as when the spring force of the suspension spring 3 is set to be extremely high, a reinforcing resin added as a reinforcing material, such as glass fiber, may be selected.

As shown in fig. 3, a cover 16 that covers the

projections

17A and 17B and the

cam portions

22A and 22B is provided on the outer periphery of the annular base 12 of the restriction member 10. Thus, foreign matter is not caught between the

cam portions

22A, 22B and the

projection portions

17A, 17B. The axial length of the cover 16 may be set to a length enough to cover the

cam portions

22A and 22B at least in the third stage where the initial load of the suspension spring 3 is the highest in the initial load adjusting device 4.

As shown in fig. 3, the

cam ridges

26, 27, 28 and the contact surfaces 23, 24, 25 of the

cam portions

22A, 22B are inclined from the axial side toward the outer peripheral side toward the side opposite to the restricting member. Thus, even if foreign matter is caught in the

cam portions

22A and 22B and the

projection portions

17A and 17B by any chance that the cover 16 cannot be completely protected, the foreign matter can be naturally discharged to the outside by the inclination.

The initial load adjusting device 4 is provided with a stopper for restricting the movement of the

projections

13, 14, and 15 from the third contact surface 25, which is the contact surface having the highest axial height, to the opposite direction to the second contact surface 24 side having a one-step lower axial height than the third contact surface 25.

Further, the initial load adjusting device 4 is provided with a stopper for restricting the movement of the

respective protrusions

17A, 17B from the terminal end to the opposite side of the starting end to the movement to the non-opposing positions of the

respective cam portions

22A, 22B corresponding to the

respective protrusions

17A, 17B, when the first contact surface 23 side having the lowest axial height among the plurality of contact surfaces 23, 24, 25 is the starting end and the third contact surface 25 side having the highest axial height is the terminal end.

Specifically, as shown in fig. 5, the stopper is configured to include: a pair of inner

circumferential protrusions

50, 50 provided at mutually opposing positions on the inner circumference of the cover 16 of the restriction member 10, respectively; and a pair of outer

peripheral projections

51, 51 provided on the outer periphery of the upper spring seat 11 at positions opposite to 180 degrees. The inner

circumferential protrusions

50, 50 are provided at positions corresponding to the first protrusions 13, respectively, and the outer

circumferential protrusions

51, 51 are provided at positions corresponding to the third cam cams 28, respectively. Thus, even when the

protrusions

17A and 17B are moved leftward in the drawing from the third stage shown in fig. 4(C), the inner protrusions 50 and the

outer protrusions

51 and 51 abut against each other, respectivelyPrevent fromAnd (4) rotating. Therefore, if such a stopper is provided, the first projection 13 cannot be suddenly moved from the third abutment surface 25 having the highest axial height to the first abutment surface 23 having the lowest axial height, and therefore the upper spring seat 11 can be prevented from being pressed by the suspension spring 3, which causes the

cam portions

22A, 22B and the

projection portions

17A, 17B to violently collide.

The stopper is not limited to the structure of the present embodiment, and may be a mechanism that prevents the

protrusions

17A and 17B from moving from the end to the opposite side of the start end and moving to the non-opposing positions of the

cam portions

22A and 22B corresponding to the

protrusions

17A and 17B.

As shown in fig. 6, a plurality of convex portions 40 provided at equal intervals in the circumferential direction on the outer periphery of the cover 16 and a plurality of protrusions 21a provided on the outer periphery of the tube portion 20 function as jaws (grip) that can be gripped by a human hand. Thereby, the upper spring seat 11 and the restricting member 10 can be rotated by hand while gripping the jaw. The shape of the jaw is not limited to the shape of the present embodiment, and the jaw may be grasped only by a human hand.

As shown in fig. 6, the number of 1 to 3 is described at equal intervals on the outer circumference of the upper spring bearing 11 of the present embodiment. In addition, the mark 60 is described in each of the pair of projecting

portions

40, 40 facing each other in each projecting portion 40 of the cover 16.

The number and the mark 60 are described in the position where the first load adjustment device 4 switches from the first stage to the third stage in accordance with the number to which the mark 60 is opposed.

Thus, the initial load adjusting device 4 of the present embodiment can easily perform the adjustment work of the initial load.

In the suspension device S of the present embodiment, the initial load adjusting device 4 is provided on the outer periphery of the outer tube 1, but may be provided on the outer periphery of the rod 2.

In fig. 1, the suspension device S is used for a rear suspension mounted between the rear wheel 104 and the body frame 101 of the motorcycle 100, but may be used for a front fork 102 mounted between the front wheel 103 and the body frame 101.

While the preferred embodiments of the present invention have been described in detail, it is to be understood that modifications, variations and changes may be made without departing from the scope of the appended claims.

The present application claims priority based on patent application 2017, 26.9.2017 to the native patent office, the entire contents of which are incorporated herein by reference.

Claims

1. A suspension device is characterized by comprising:

an outer tube;

a rod movably inserted into the outer tube in an axial direction;

a suspension spring provided on an outer periphery of the outer tube and urging the rod in an extending direction;

an annular spring seat which is rotatably attached to an outer periphery of either the outer tube or the rod in a circumferential direction and supports one end of the suspension spring;

an annular restricting member that is attached to the spring seat on the outer periphery of either the outer tube or the rod on the side opposite to the suspension spring and restricts movement of the spring seat on the side opposite to the suspension spring;

a plurality of cam portions provided on the other side of either the spring seat or the restricting member, and having a plurality of contact surfaces having different axial heights;

and a plurality of protrusions provided on either one of the spring seat and the regulating member, arranged at positions corresponding to the respective cam portions, and abutting against the abutment surface.

2. The suspension arrangement according to claim 1, wherein the protrusion is formed in a shape that matches the cam portion.

3. The suspension arrangement according to claim 1, wherein a cover is provided on either one of the spring seat or the restricting member and encloses the protrusion and the cam.

4. The suspension arrangement according to claim 1,

the plurality of contact surfaces provided on the respective cam portions are arranged such that the axial heights thereof gradually increase,

and a stopper for preventing the protrusions from moving from a terminal end to a side opposite to the starting end and moving to non-facing positions of the cams corresponding to the protrusions, when the contact surface side having the lowest axial height is a starting end and the contact surface side having the highest axial height is a terminal end, of the plurality of contact surfaces.

5. The suspension arrangement of claim 1 wherein said spring seat is provided with said cam portion,

the cam portion is inclined from the axial side to the outer peripheral side toward the opposite side of the restriction member.

6. The suspension arrangement according to claim 1,

the spring seat and the restricting member are formed of synthetic resin.