JPS6056621A - Adjusting device of hydraulic buffer for suspension of motor-cycle or the like - Google Patents

Abstract

PURPOSE:To attain compactness and reduce misadjustment by adjusting the performance of a hydraulic buffer using the centrifugal force that is actuated on a heavy weight provided on a shaft that rotates following the rotation of an engine. CONSTITUTION:A rotary shaft 45 that is driven by engaging with the crank shaft of an engine and a centrifugal force extraction section (A) is formed on the rotary shaft 45. When an accel grip is actuated and the number of engine revolutions is increased, the number of revolutions of the rotary shaft 45 is increased and the centrifugal force of a steel ball 52 arranged between retainers 46 and 47 is also increased. The movable retainer 47 is moved against the energizing force of a coil spring 48 by this centrifugal force and a fork 53 also swings centering around an axial fulcrum. As a result, a Bowden cable 8 is pulled and the pulley member of a hydraulic buffer is rotated and actuated, then the aperture area of a variable orifice is expanded and adjusted.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an adjustment device for suspension hydraulic pressure and a shock absorber for a motor vehicle, three-wheel motor vehicle, etc. (hereinafter referred to as motor vehicle = two-wheel vehicle, etc.).

Even if the unevenness of the road surface is constant, the magnitude of the impact applied to the vehicle's drawing rack device varies depending on the speed of the vehicle.
The higher the traveling speed, the greater the impact τ the suspension v-system will have to deal with.

From this point of view, attempts have also been made in motorcycles and the like to automatically adjust the performance of a vehicle's suspension hydraulic shock absorber in accordance with the traveling speed of the vehicle.

By the way, for motorcycles, etc., equipment, parts, etc. tower 21 x
Since the vehicle has a small footprint, all devices, parts, etc. are required to be as compact as possible. Therefore, the automatic adjustment device for the suspension hydraulic shock absorber in motorcycles, motorcycles, etc.
As shown in No. 18, a system has been proposed in which an accelerator grip and a hydraulic shock absorber are connected by a wire, and the performance of the hydraulic shock absorber is adjusted in accordance with the operation of the accelerator grip.

However, since the hydraulic shock absorber is adjusted in accordance with the operation of the accelerator grip in this way8, as stated in the same publication, the operation of the accelerator grip does not necessarily correspond to the vehicle speed. There is a possibility of incorrect adjustment of the hydraulic shock absorber.

This invention has been made based on this background, and has a relatively compact structure, but is capable of adjusting suspension hydraulic pressure projectors and shock absorbers for motorcycles, etc., with less risk of incorrect W@adjustment. The aim is to provide the equipment.

This objective can be achieved by providing a weight on the yuzu that rotates with the rotation of the engine and adjusting the performance FA of the hydraulic shock absorber using the centrifugal force of the weight.

An embodiment of the two-wheeled motor vehicle shown in the drawings will be described below.

1 is the vehicle body, and 2 is the rear arm. The rear arm 2 holds the rear wheel 3 at the rear, and connects the vehicle body 1 via the pivot 4 at the front.
A hydraulic shock absorber o5, which is pivotally supported so as to be swingable in the vertical direction, is a hydraulic shock absorber, which is comprised of a FIHIr spring 11 and a hydraulic damper 12, and is interposed between the vehicle body 1 and the rear arm 2.

6 is an engine, and a chain 7 is wound between the output cusp Oket 44 of the engine 6 and the drive sprocket of the rear wheel 3 to transmit driving force. 8 is a Bowden wire, as will be described later. It connects the centrifugal force extraction section A of the engine 6 and the adjustment section of the hydraulic shock absorber 5.

First, the outline of the hydraulic shock absorber 5 will be explained with reference to FIG. 2 as follows.

The hydraulic shock absorber 5 consists of a buffer spring 11 and a hydraulic damper 12. The hydraulic damper 12 includes a cylinder 13 filled with hydraulic oil, a piston 14 that reciprocates within the cylinder 13, and a piston rod 15 that holds the piston 14 at one end and projects outside the cylinder 13 at the other end. Be equipped. Is there a beam inside cylinder 13? -7117 is in communication with the inside of the cylinder 16, and the adjustment of the oil amount due to the volume fluctuation that the piston rod 15 occupies in the cylinder 13 is performed by filling high pressure nitrogen gas between the t:xz and the oil chamber. Free piston 19 that partitions
This is achieved by

The hydraulic oil sealed in the cylinder is divided into three oil chambers shown in the second figure by the piston, the base pulp 17, and the crest 918. 18 is oil chamber o2 empty oil chamber o
A damping force is generated for the flow from 03 to 02, but on the contrary, since the base pulp 17 has a large opening, no damping force is generated for the flow from 03 to 02. 17 and ridges 18 do not produce a damping force for the extension movement of the hydraulic damper 12.

In the hydraulic damper 5 of this embodiment, its damping performance U
Since the adjustment is performed by adjusting the damping force accompanying the extension operation of the hydraulic damper 12, the performance adjustment section and extension operation of the hydraulic damper in this embodiment will be explained below using Fig. 3. explain.

Due to the extension action of the hydraulic damper 12, the piston 14 moves to the right at S as shown in Fig.
The hydraulic oil in the piston expands the annular plate valve 21 and reaches the oil chamber 02 through the through hole 22 provided in the piston. The flow path 24 also produces a flow of hydraulic oil that reaches the oil chambers 01 and 02. Difficulty in the flow of these hydraulic oils causes a damping force during the extension operation. In this hydraulic damper 12, a variable orifice is created by the step part and the needle valve 25, which is movable with respect to the latter flow. 26 is configured so that the damping force accompanying the extension operation can be adjusted.
Bushing rod 27 (F
)-4 is located, and the other end of this push rod F27 is the piston port? It protrudes from the rear end of P15.

Since oil pressure is always acting on the needle valve 25, the rear end of the needle valve 25 is supported by the bush rod 27 to determine its position. An end fitting 2 is attached to the rear end of the piston rod 15.
8 is fixed, and a via 31 is provided passing through the through hole 29 of this end portion A28.The rear end of the bushing rod 27 abuts against the central portion of this bin 31, so that the position of the bushing rod 27 is regulated. Ru.

A holder 32 is fixed on the outer periphery of the end fitting 28, and a stopper fitting 33 is provided. A cylindrical portion 32a is integrally formed in the holder 32, and a folding member 34 is slidably fitted on the outer circumferential surface of the cylindrical portion 32a.This pulley member 34 supports the pin 31 described above. Therefore, a thin stepped sheet made of sheet metal is placed on the support surface of the pin 31 of the fist pulley member 34 whose rear end surface abuts against the end surface of the abutting fitting 33 to counteract the hydraulic pressure acting on the needle valve 25. 35 is attached, and the surface that contacts the bottle 31 is formed in a step shape, so the rotational displacement of the pulley member 34 causes the position of the bit 31 to be h<1 (C1?). F27 is displaced in the axial direction, so that the opening area of the variable orifice 26 is adjusted.

The abutment fitting 33 is composed of a main body 33& and an auxiliary ring 33b, and the main body 33& is movable on the screw of the end fitting 28, and the auxiliary IJ ring 33b is fixed on the same screw. Several grooves extending in the axial direction are formed at predetermined intervals on the outer circumference of this auxiliary ring 331), and on the other hand, a spring-loaded pole is provided on the main body 33, and the pawl serves as an auxiliary link. It engages with the groove of 33b to prevent movement of the main body 33a.

Therefore, this damping force can be adjusted by manually adjusting the rotation of the main body 33111 as necessary. During this manual adjustment, the main body 33& moves with moderation.

At around 7, the pulley member 34 is next connected to the centrifugal force take-off section A of the engine, which will be explained in FIG.

The engine 6 is a U-cycle engine, and the power generated by the piston and cylinder is 41 degrees and 5 times 42 degrees.
．． It passes through the transmission 1243 and reaches the output sprocket 44, which drives the rear wheel 3 via the chain 7.

In this engine 6, a rotating shaft (corresponding to the shaft in the present invention) 4 that is engaged with and driven by the glaze 41
5 is provided, and a centrifugal force extraction portion A is formed at this oe=aa5.

Here, the structure of this centrifugal force extraction portion A will be explained with reference to FIG. The rotary shaft 45 has fixed 1 retainer and 2 fixed retainer 46.
and a slidable movable retainer 47 are provided facing each other, and the movable retainer 47 is urged toward the fixed retainer by a coil spring 48.

An annular space 49 whose outer edge is thinner is formed above the rotation shaft 45 which serves as a latch for these retainers 46 and 47.

This annular space 49 is divided into four chambers by means of lips 51 provided on the fixed retainer 46 at intervals of 9011. Each chamber contains a steel ball (corresponding to the weight of the present invention) 52. It is arranged.

The movable retainer 47 is provided with a cylindrical portion that covers the outer periphery of the rotating shaft, and a fork 53 is slidably engaged with this portion.

The fork 53 has one end attached to the engine case and is swingably held, and the inner ear of the Bowden wire 8 is attached to the middle portion thereof, and is connected to the pulley member 34.

Therefore, if the rotation speed of the engine 6 increases by operating the axle clip, the rotation speed of the rotating shaft 45 will increase.
The centrifugal force of the steel ball 52 placed between 6.47 and 47 increases. Then, the retainer 47 moves against the biasing force of the coil spring 48 due to this centrifugal force. The movable retainer 47 swings around the glazed fork 536, and as a result, the Bowden wire 8 is pulled, the pulley member 34 of the hydraulic damper 12 is rotated, and the opening area of the variable orifice 26 is enlarged and adjusted. In this way, since the centrifugal force generated on the rotating shaft of the engine is directly used as the power for adjusting the hydraulic shock absorber, there is no need for a special power source for automatic adjustment, and the system can be made relatively compact.

Furthermore, since it operates when the rotational speed of zy2y actually increases, malfunctions are less likely than in the prior art.

Note 1: Although this embodiment is configured to reduce and adjust the damping force associated with the extension operation of the hydraulic damper as a performance adjustment of the hydraulic damper, the present invention is not limited to this, but can also be applied to the compression operation of the hydraulic damper. The accompanying damping force may be adjusted, and the spring force of the buffer spring v! It can also be used for 4th grade.

In addition, in this embodiment, the centrifugal force extraction portion A is connected to the clutch 42.
Although it is installed closer to the power source side, since the clutch is generally engaged and engaged instantaneously, it may be installed closer to the Q rear wheel 3 than the clutch 42, for example, on the output shaft of the transmission 43.

As explained above, in this invention, a heavy bell is provided on the glaze that rotates as the engine rotates, and the centrifugal force of the 11 spindles is transmitted to the performance adjustment section of the hydraulic shock absorber for adjustment.

Therefore, it is not necessary to use a special power source for adjusting one hydraulic shock absorber, and the structure can be made relatively compact. Furthermore, since the necessary centrifugal force is generated in the two parts where the engine rotational speed actually increases, the hydraulic shock absorber may be operated incorrectly.
There is little chance of a one-off situation.

[Brief explanation of the drawing]

The drawings relate to an embodiment of the present invention in a motorcycle, and FIG. 1 is a side view of the motorcycle. FIG. 2 is an overall explanatory diagram of a hydraulic shock absorber. FIG. is an explanatory diagram of the entire Nishijin, and Figure 5 is an explanatory diagram of the main parts of the engine.・5! Hydraulic shock absorber 6: Engine 45! Axis (rotating axis) 52: Jusho (p-ball) Figure 5 Procedural amendment (/i-eri0mei 359 2 swords 250 Commissioner of the Patent Office Kazuo Wakasugi-21. 1. Indication of the case etc.゛;゛Showa 5Showa 5Showa 5Showa 5 Adjustment device 3 for hydraulic shock absorbers for stealth racks of fraudulent motorcycles, relationship with the case of the person making the amendment Patent Applicant Address 2500 Shingai, Iwata City, Shizuoka Prefecture Name (AO?) Yamaha Motor Co., Ltd. Iseisha Spout
Hideto 4, agent 〒430 drawings, engraving (no changes in content)

Claims (1)

[Claims] Hydraulic shock absorbers such as automatic rotary shock absorbers are constructed in such a way that a weight is attached to the cylinder that rotates as the engine rotates, and the centrifugal force of the weight is transmitted to the performance adjustment section of the hydraulic shock absorber for one adjustment operation. Adjustment device/