JPS58211040A - Spring load adjusting device in hydraulic damper - Google Patents

Abstract

PURPOSE:To make the operationability of a hydraulic damper satisfactory and as well to eliminate an unnecessary stroke of an adjusting member, by attaching, to a cylinder, a housing provided with a pressure chamber, and as well by inserting a piston in the pressure chamber so that the piston is opposed to an adjusting cam and a spring seat. CONSTITUTION:There are provided a piston 10 vertically movably arranged between a cylinder 2 and a housing 7 fixed to the outer periphery of the cylinder 2, an adjusting cam 18 rotatably disposed around the outer periphery of the housing 7, for receiving the load of a suspension spring 5, a torsion spring P disposed between the adjusting cam 18 and the housing 7 or a vehicle body, the adjusting cam 18 being associated with a control section 24 through an wire or gears, positioning and detecting means disposed in the control section, and a cam surface or a locking part 16 disposed between the housing 7 and one side of the adjusting cam 18, the piston 10 pushing up a spring seat 4 for the suspension spring 5 prior to the adjusting cam 18.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a spring load adjusting device for a hydraulic shock absorber such as a front fork for a two-wheeled vehicle, which can be set to an appropriate value depending on the situation.

Generally, a front fork or rear cushion unit for a motorcycle is formed of an oil damper/mer and a coil spring in order to alleviate the vibrations and shocks that the vehicle body receives from the road surface while driving. It must be set to an appropriate value depending on the weight of the vehicle body, road surface conditions, etc. There is also a coil spring load adjustment device that adjusts the initial pressing force according to the weight of the person riding on the vehicle body and the weight of luggage. It is also required.

For this reason, various spring load adjustment devices have been developed, but all of them have complicated structures and poor operability.
This method has drawbacks such as the need to stroke the operating member more than the amount of adjustment during adjustment, or the inability to accurately confirm the adjustment position.

Therefore, an object of the present invention is to provide a spring load adjusting device for a hydraulic shock absorber that has good operability, does not require an extra stroke of the adjusting member, and allows the initial set position to be confirmed at a glance.

In order to achieve this objective, the present invention fixes a housing to the outer periphery of a cylinder, inserts a piston between the cylinder and the housing so that it can move up and down, and rotatably disposes an adjustment cam that supports the load of a suspension spring on the outer periphery of the housing. A torsion spring is interposed between the adjusting cam and the housing or the vehicle body, and the adjusting cam is linked with an operating section via a wire or gear, and this operating section is provided with a positioning detection means. A cam surface or a locking part is provided on one side of the
The piston is characterized in that it pushes up the spring seat of the suspension spring before the adjustment cam.

Embodiments of the present invention will be described below with reference to the drawings.

Figures 1 to 6 show an adjustment device according to an embodiment of the present invention.

The hydraulic shock absorber (1) has a piston rod slidably inserted into the cylinder (2) via a piston.
) It is interposed between the vehicle body such as a motorcycle and the wheel side via the lower end bracket (3) and the upper bracket of the piston rod. Spring seat (4) on the outer periphery of the cylinder (2)
is inserted so that it can move up and down, and this spring seat (4
) and a spring seat on the upper part of the piston rod, and a suspension spring (5) is interposed between the piston rod and the spring seat, and this suspension spring (5) always urges the piston rod in the direction of extension.

The spring load adjusting device of the present invention adjusts the initial of this suspension spring (5).

A stopper (6) is fixed to the outer periphery of the cylinder (2), and the upper limit of the stroke of the spring seat (4) is regulated by this stopper (6).

A housing (7) is fixed to the lower outer periphery of the cylinder (2) via a snap ring (8), and a pressure chamber (9) is defined between the cylinder (2) and the housing (7). ) is inserted into the annular piston 00) so as to be able to move up and down, and the pressure chamber (9) is sealed with a seal 0υtl2+(13).
sealed through.

The housing has a passage (14) opening into the pressure chamber (9).
) is formed, and this passage 04) is connected to a hydraulic or pneumatic pressure source via a hose or the like connected to a port 15).

A housing (two locking parts (16) α6 at opposite positions on the lower part of the outer circumference of the force) is provided, and this locking part (16)
The upper surface αη of (16) is curved. (Fig. 4) Housing (On the outer periphery of the force, an adjustment cam 0 mallet is provided so that it can move freely in the upward and rotational directions. 5S adjustable cam (Japanese) A sheave (20) consisting of a plurality of curved surfaces α, b, C-----rules and an annular groove provided in the upper part of the cylindrical body (09).
), and any two of the opposing cam surfaces α, b, and c--rules engage the locking portion (
+6) It is adapted to selectively engage with the upper surface 07) of (16). (Fig. 3) Furthermore, a rotational driving member (22) such as a wire, rope, or string is wound around the annular groove (21) of the sheave f20), and one end of this rotational driving member (22) is connected to the sheave (20). In contrast, it is fixed to the sheave (20) side by a fixing member (22). (Fig. 2) Furthermore, a permanent member T is provided between the lower surface of the adjustment cam 0 mark and the outer periphery of the housing, and a coiled screw spring P is interposed between the stop member T. The adjustment cam (18) is constantly biased in the rotational direction, for example, pulling the rotational drive member (22) in the direction of winding it around the sheave (201).

However, it is also possible to use the rotary drive member by rotating it in the direction of rewinding.

There is usually a spring seat (4) on the top of the sheave (20).
The lower surface of the suspension spring (5) is carried by the spring seat (4), the adjustment cam 08), and the housing (force). A collar (23) is provided that protrudes in the direction.

A stepped portion is formed in the upper part of the piston α0), and the piston 0
When the spring seat (4) is in contact with the upper surface of the piston (00), a gap l is formed between this piston step and the collar (23), and when the piston (00) rises, the spring seat (4) is pushed up first. , after the gap E height piston 00) rises, the stepped part of the piston 00) contacts the collar (23) and pushes it up, and when the piston 00) further contacts the collar (23) and pushes it up, conversely. A gap l is formed between the spring seat (4) and the adjustment cam 08), so that the spring force of the suspension spring (5) does not act on the adjustment cam (18), so the adjustment cam (+8) can rotate freely. It has become.

A rotational drive member (22) such as a wire is connected to an operating section provided in the driver's seat of the motorcycle or the like. This operation part (24)
As shown in Figure 5 and Figure 6, the sheave (26) rotatably attached to the support plate (251) and the sheave (26)
), and the other end of the rotary drive member (22) such as a wire is wound around the annular groove (2G) of the sheave (+6), and a fixed member (2)
When the adjusting cam (18) rotates, the sheave (2
6) is pulled and rotated in the same direction, and in turn is twisted (27
) When the sheave (26) is rotated through the sheave (26), this rotational force causes the adjustment cam 08) to rotate by the same amount and in the same direction. Therefore, on the support plate C25) there is a mark corresponding to the cam surface α+b+'-'-'-le of the adjusting cam 08),
A position detection means (?8) such as numbers is provided, and a knob (27) is provided.
is rotated to a position facing one of the position detecting means (28), one of the cam surfaces α, b, c corresponding to the selected position detecting means (28) moves toward the housing (7).
) to face the locking portion (16) on the side.

Conversely, when the adjustment cam (08) rotates, the sheave (26) also rotates in conjunction with it, so the mark 128 on the operation unit (24) side indicates at what position the adjustment cam (18) has rotated. )
It can be detected by

A rotating shaft (29) is provided at the center of the lower end of the sheave (26), and this rotating shaft passes through a hole in the support plate (25) so as to be rotatable, and a washer (29) is provided at the other end of the rotating shaft (29). 30)
and nut C3υ are screwed together.

Next, we will discuss the operation.

In FIG. 1, it is assumed that the locking portion (16) is engaged with the cam surface d of the adjustment cam 08), and the initial of the suspension spring (5) is set according to the height of the cam surface d.

In order to increase the spring load from this state, for example, when adjusting it to the initial value corresponding to the cam surface a, the procedure is as follows.

That is, first, when pressure oil is supplied from the pump to the lower part of the piston in the pressure chamber (9), the piston 00) rises, and at this time, the upper end of the piston 00) resists the spring force of the suspension spring (5) and pushes against the spring seat (4). ) is pushed up and then stroked for 1 minute, the stepped part of the piston 00) moves into the flange (of the adjustment cam θ8).
23), and then the adjusting cam 08)
0).

When the adjusting cam (18) rises to a height where the locking part 06) of the housing (7) can move from the cam surface d to the cam surface α, the supply of pressure oil is stopped, and at this position the piston α0) is moved to the spring seat (4). hold. At this time, a gap l is formed between the spring seat 14) and the adjustment cam (1~), and the spring force of the suspension spring (5) does not act on the adjustment cam 08), so the adjustment cam 0al is connected to the torsion spring P. The cam surface a automatically faces the locking portion (1G). This position corresponds to the adjustment cam (18), rotation, and operation part (24) interlocked via the drive member (22).
It can be detected by coming to the position 7), for example, the number 2 position.

In this state, when the pressure oil in the pressure chamber (9) is removed, the suspension spring (
The restoring force of 5) pushes the piston 00) and the adjustment cam 08) downward, and the cam surface α of the adjustment cam (18) is pressed against the housing (
The adjustment cam (the height of the adjustment cam is installed at a position corresponding to the height of the cam surface a), thereby reducing the initial spring load of the suspension spring (5). It is set corresponding to the cam surface a.

Incidentally, the above method may be used to shift the spring load from weak to strong, but conversely, it may be shifted from a strong position to a weak position. At this time, with the adjusting cam 08) free, manually rotate the knob (27) of the operating section 04) to the desired position, or set it to the weakest position and then 08) may be sent automatically.

Furthermore, the operating part e4) is equipped with a sheave (2G) to prevent the rotational drive member (22) from loosening and to prevent play in the adjustment cam (IgI).
A screw spring Pa is interposed between the support plate (c) and the support plate (c). The spring force of this torsion spring PcL is made weaker than the spring force of the screw spring P on the adjusting cam (18) side. However, it can be used without this screw spring Pa.

Since the cam surfaces α, b, c----- are curved, the upper surface o'7) of the locking part 06) is also curved, and when the two are engaged, positional displacement is prevented, but the curve is not necessarily the same. You don't have to.

Although two locking portions (16) are provided facing each other as shown in FIG. 4, one or two or more locking portions (16) may be provided depending on the number of cam surfaces.

Although the spring seat (4) and the piston tlO) are separated, these two members can be used even if they are integrally molded.

Furthermore, it is also possible to provide a detent mechanism in the operating section (24) to prevent positional displacement.

Since the locking part (16) is provided at the lower part of the outer side of the housing (force), the diameter of the housing (7) in the radial direction becomes thicker, but conversely, the length in the axial direction can be shortened.

However, what happens when you conversely reduce the radial diameter? A locking portion may be provided at the upper end of the housing as shown in Figures 7 and 8.

That is, Fig. 7 and Fig. 8 relate to other embodiments of the present invention.
This is done by providing two opposing locking parts (16α016(Z)) protruding from the upper end of the cylindrical body of the housing (7), and reducing the axial length of the cylindrical body (19) of the other adjusting cam 08. There is a locking part (16a) f16a) at the bottom of this cylindrical body α9).
cam surfaces α, b, c---n facing each other are provided. Further, a stop member Ta for receiving a spring is provided on the outer periphery of the housing (7), and a screw spring P is interposed between the stop member Ta and the adjustment cam (18).

The operation is the same as in Figure 1, so the explanation will be omitted.

Next, Figure 9 shows another embodiment of the present invention, in which the cam surface is a smooth surface.

That is, a locking part (16b) with a smooth upper surface is provided at the outer lower part of the housing (7), and a cylindrical hole is formed for the adjustment cam α, and a locking part [16b] is provided on either of the cam surfaces. ) are brought into contact with each other.

In this case, since the cam surfaces α, b, and c are smooth surfaces, the locking portion (16b) is connected from one cam surface to another.
), the adjustment amount and cylinder stroke are almost the same, and cylinder (2) and adjustment cam 0
8), there is no need to stroke it unnecessarily, and since it is a flat surface, the curvature is the same, increasing the pressure-receiving area and reducing the surface pressure. Furthermore, it becomes possible to shorten the axial dimension. The locking portion (16b) may also be formed at the upper end of the housing (7). The locking part can also be used as a housing (one that protrudes from the upper end surface of the force).

Other configurations, functions, and effects are the same as in the case of Fang 1.

In addition, 10 fangs~! FIG. 12 shows another embodiment of the present invention, in which a gear mechanism is used instead of a wire, rope, etc. as the rotational drive member.

That is, teeth (36) are carved on the outer periphery of the cylindrical body (19 (Z)) of the adjustment cam f18a), and the teeth (36) of the teeth (: small gear 07) are
The small gear (37) is rotatably engaged with the adjustment cam (
18iz) rotates, one of the desired cam surfaces a, A, c-1--n engages with the engaging portion (16) of the housing (7), and at the same time, the small gear (37 ), the operating section is linked to allow the position of the cam surface to be detected.

A locking part Q6)06), a bracket side, and a pressure boat (401) are provided on the outside of the housing (7), and the bracket 0
A small gear 07) is rotatably fitted into the hole (41) of 9, and a cylindrical tube holding part (421) is screwed into the lower part of the bracket (39).

The tube holding part (421 has a flexible tube (4
3 are screwed together, and a rotation transmission member (44) such as a wire or rope rotatably inserted into this tube j43) is inserted into the central hole (49) of the small gear (37), and when the wire etc. rotates. The small gear 07) also rotates by the same amount at the same time.

A screw spring P is interposed between the adjustment cam (18α) and the housing (7) to urge the adjustment cam (18α) to rotate in one direction.

On the other hand, the operating section on the driver's seat side is connected to the gear (29+2) through the hole in the support plate ρω, as shown in Figures 13 to 14.
26a) is rotatably supported, and this gear! 26(Z)
Teeth (26A) are engraved on the outer periphery of the gear (2kl), and the gear (2kl) is rotated via a knob (27α).
o) and a nut (31), and is also held by a gear (26 (Z)
) and the support plate (29) are provided with a positioning mechanism consisting of a screw spring Pa and, if necessary, a spring and a pawl.

Furthermore, a small gear (46) is rotatably supported on the support plate (2), and teeth (471) are carved on the outer periphery of this small gear (46).

These teeth (471) are rotatably meshed with the teeth (26A) of the gear (26α).

A box (48) is fixed to the lower surface of the support plate (25) by welding or the like, and a tube holding member (49) is attached to this box decoy.
A flexible tube 50) is screwed to this holding member (49), and one end of a rotation transmission member (44) such as a wire rotatably inserted into this flexible tube 50) is connected to a small gear. When the rotation transmission member (44) rotates, the small gear (46)
It is designed so that it rotates as one. The rotation transmission member 6+4) is integrally connected to the rotation transmission member (44) shown in the fang 10.

Therefore, when the adjustment cam (18a) rotates due to the torsion spring P, the small gear (37) and the rotation transmission member (44) rotate,
As a result, the operating section side is connected to the gear (2) via the small gear (37).
64) rotates, and the knob (27α) faces the mark at the position corresponding to the selected cam surface.

Other functions and effects are the same as in the case of Fang 1. As for the cam side! As shown in Figure 9, the smooth surface may be provided in a stepped manner.
The engaging portion may be provided at the upper end of the housing (7).

As can be seen from the embodiments described above, the present invention is characterized by: (1) Compressing the suspension spring with hydraulic or pneumatic pressure and selecting one of the cam surfaces, so no spring load acts on the adjustment cam, resulting in good operability. .

■The piston is pushed up by hydraulic or pneumatic pressure, and the adjustment cam is rotated by a torsion spring, so adjustment is automatic and easy to operate. ■Since the spring load is carried on the cylinder side via the spring seat, adjustment cam, housing, and snap ring, it has high strength and durability. ■Since the cylinder stroke is the same or almost the same as the initial adjustment width, there is no need to make an extra stroke of the cylinder.
Not only is it easy to operate, but the length in the longitudinal direction can be shortened. ■
The operating section is interlocked with the adjustment cam, and the operating section is provided with a position detecting means such as a scale, so that the initial position can be accurately confirmed.

[Brief explanation of the drawing]

Fig. 1 is a partially cutaway longitudinal sectional front view of a hydraulic shock absorber using a spring load adjustment device according to an embodiment of the present invention, Fig. 2 is a schematic cross-sectional plan view of Fig. 1 taken along the line ■-■; Figure 3 is a perspective view of the adjustment cam in Figure 1, Figure 4 is a perspective view of the housing in Figure 1, Figure 5 is a plan view of the operating section, and Figure 6 is a longitudinal cross-sectional side view of Figure 5. Fig. 7 is a partially cutaway longitudinal sectional front view of a hydraulic shock absorber according to another embodiment, Fig. 8 is a partially cutaway perspective view of the housing of Fig. 7, and Fig. 9 is a hydraulic shock absorber according to another embodiment. FIG. 10 is a partially cutaway vertical front view of a hydraulic shock absorber according to another embodiment, and FIG.
Figure 12 is a side view of the housing shown in Figure 10, Figure 13 is a plan view of the operating section according to the embodiment, Figure 14 is a vertical sectional side view of Figure 13; Figure 15 is Fang 13
FIG. 3 is a longitudinal cross-sectional side view of the small gear portion shown in the figure. (2)...Cylinder, (4)...Spring seat, (5)...Suspension spring, (7)...Housing, (
9)...Pressure chamber, 00)...Piston, C6) (1
6α) C16h)...Locking part, (18) (18α)
... Adjustment cam, (22... Rotation drive member, (2)
...Operation unit, track...Position detection means, (3)...Positioning mechanism, (37) (26a) (46)...Gear, Q
, a', b, h', C, C----n, n...Cam surface, l...Gap, P, Pα...Torsion spring. Representative Patent Attorney Izumi Amano Figure 2 7j $1 Figure [II '( \--- -1\ Figure 5 Figure 6 Figure 7 Figure 9 Figure 10

Claims (9)

[Claims] (1) In a hydraulic shock absorber in which a piston rod is slidably inserted into a cylinder via a piston and a suspension spring is interposed between the cylinder and the piston rod, a nozzing is attached to the cylinder, and this housing A piston is inserted into the inner pressure chamber so as to be able to move up and down, and an adjustment cam is rotatably disposed on the housing, and a torsion spring is inserted in the adjustment cam to urge the adjustment cam in the rotational direction. , the piston is arranged to face the spring seat and the adjustment cam, and the piston pushes up the spring seat in advance of the adjustment cam, and a plurality of cam surfaces are formed on either the nozzing or the adjustment cam, A spring load adjusting device for a hydraulic shock absorber, wherein the other side is provided with a locking portion that selectively engages with one of the cam surfaces, and the adjusting cam is remotely connected to an operating portion via a rotational drive member. (2) A spring load adjustment device for a hydraulic shock absorber according to claim 1, wherein the rotational drive member is a wire, rope, or string. (3) A spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein the rotational drive member is a gear. (4) The spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein the cam surface and the upper surface of the locking portion are curved. (5) The spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein the cam surface and the top of the locking portion are smooth surfaces. (6) A step is provided on the piston, and when the piston is in a compressed state where the upper end is in contact with the spring seat, a gap is formed between the adjusting cam and the step, and when the piston is extended, a gap is formed between the adjusting cam and the spring seat by the same amount. A spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein a gap is formed. (7) A spring load adjustment device for a hydraulic shock absorber according to claim 1, wherein the operating portion is provided with a position detection means. (8) A spring load adjusting device for a hydraulic shock absorber according to claim 1, wherein the operating portion is provided with a positioning mechanism. (9) Claim 1 in which the operating part is provided with a torsion spring
A spring load adjustment device for a hydraulic shock absorber as described in 2.