JP3311367B2 - Vehicle cushion unit - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a cushion unit applied to vehicles such as motorcycles and four-wheeled vehicles.

[0002]

2. Description of the Related Art Conventionally, some cushion units applied to vehicles such as motorcycles have means for setting and adjusting an initial load of a coil spring.

[0003] In a vehicle equipped with this kind of cushion unit, by changing the initial load of the coil spring as appropriate, a change in the attitude of the vehicle due to the difference in the presence or absence of a passenger or the presence or absence of a load can be prevented as much as possible. Therefore, required steering stability can be secured.

[0004]

By the way, in a normal cushion unit, by adjusting both the initial load of the coil spring and the damping force of the damper in relation to each other, it is possible to obtain an optimum operating characteristic for the vehicle. I have to.

[0005] Therefore, when only the initial load of the coil spring is changed in order to suppress the change in the attitude of the vehicle as described above, there is a possibility that its operating characteristics may not be optimal for the vehicle.

An object of the present invention is to provide a vehicular cushion unit that can always obtain optimum operating characteristics for a vehicle in view of the above-mentioned circumstances.

[0007]

A vehicle cushion unit according to the present invention is a vehicle cushion unit including a coil spring and a damper, wherein the vehicle cushion unit is disposed in series with the coil spring between a damper body and an operating rod. The initial load that sets the initial load of the coil spring by changing the installation length of the coil spring by expanding and contracting by the hydraulic oil supplied from the hydraulic chamber of the hydraulic jack that drives according to the initial load acting on the cushion unit Setting means, a plunger having a taper surface which moves forward and backward in response to a change in the pressure of the hydraulic pressure acting on the drive chamber, and a taper surface of the plunger. Control that changes the effective cross-sectional area of the orifice and changes the damping force And a damping force adjusting means, comprising: a hydraulic chamber for supplying hydraulic oil to the driving chamber and the initial load setting means. The hydraulic circuit that communicates with the chamber includes a free piston partitioned into two oil chambers, a drive hydraulic chamber side of the hydraulic jack and a drive chamber side of the damping force adjusting means, inside the hydraulic circuit. Is characterized in that a hydraulic cylinder actuator having a smaller piston diameter than the piston diameter on the drive chamber side is inserted.

[0008]

According to the above arrangement, when the initial load of the coil spring is changed, the damping force of the damper changes in accordance with the initial load.

[0009]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the drawings showing embodiments. FIG. 1 conceptually shows a vehicle cushion unit according to the present invention. As shown in FIG. 3, a cushion unit 10 interposed between a body frame F of a motorcycle B and a rear wheel R is shown in FIG. Is exemplified.

As shown in FIG. 1, the cushion unit 10 includes a hydraulic damper 11 having damping force adjusting means 20.
And a coil spring 12 interposed between the damper body 11a and the operating rod portion 11b of the hydraulic damper 11 via an initial load setting means 30. The operating rod side mounting end 10a serves as a link mechanism 40. The main body side mounting end 10 b is connected to the body frame F via a vehicle height adjusting means 50. Although not explicitly shown in the figure, the rear wheel cushion unit 10 is disposed substantially vertically in the left-right central portion of the vehicle body frame F in such a manner as to be inclined only forward.

The damping force adjusting means 20 includes a through hole 21 and a communication hole 2 in the operating rod portion 11b of the hydraulic damper 11.
2, 22. The through-hole 21 is formed along the axis of the operating rod 11b.
1b is opened at both end surfaces, and a control rod 23 is inserted through the inside. The control rod 23 has a tapered portion 23a whose base end is formed in a spherical shape and whose tip portion gradually decreases in diameter toward the tip end. It is movably disposed in the through hole 21 in a manner facing the main body side mounting end 10b. The control rod 23 is provided with a return spring 24 between the control rod 23 and the operating rod portion 11b, and is constantly pressed by the return spring 24 in the direction of the operating rod side mounting end 10a of the cushion unit 10.

The communication holes 22, 22 extend radially outward from the through hole 21 to the outside of the operating rod portion 11b, and open to the peripheral surface of the operating rod portion 11b. These communication holes 22, 22 are each disposed closer to the base end of the operating rod portion 11b than the piston 14 of the damper body 11a, and cooperate with the distal end of the through hole 21 to form the damper body 11a. The first pressure chamber 15a and the second pressure chamber 15b which are separated from each other constitute an orifice.

The damping force adjusting means 20 is provided with a plunger 25 at the mounting rod side mounting end 10a of the cushion unit 10. The plunger 25 has a piston 25a at a base end thereof, and has a tapered surface 25b at a position facing the control rod 23 at a tip end thereof.
It is movably arranged in a mode perpendicular to the axis b.

The piston 25a of the plunger 25 is
The plunger 25 is housed in a drive chamber 27 formed on the operating rod side mounting end 10 a and connected to a hydraulic cylinder actuator 26, and moves the plunger 25 based on a pressure change in the drive chamber 27.

The hydraulic cylinder actuator 26 is provided in parallel with a hydraulic jack 31 of an initial load setting means 30 to be described later, and an operating pressure chamber 26a is connected to a driving pressure chamber 31a of the hydraulic jack 31 via a communication passage 28. Then, based on the pressure change in the driving pressure chamber 31a, the pressure oil flows into and out of the driving chamber 27 of the operating rod side mounting end 10a.

As is clear from the drawing, the tapered surface 25b of the plunger 25 is formed so as to be gradually separated from the control rod 23 toward the tip. Also,
Tip surface of plunger 25 and cushion unit 10
A control spring 29 is provided between the control spring 29 and the operating rod side mounting end 10a.
The plunger 25 is always in the driving room 2
It is pressed in seven directions.

In the damping force adjusting means 20, when the hydraulic cylinder actuator 26 is actuated to cause pressure oil to flow into and out of the drive chamber 27 of the operating rod side mounting end 10a,
The plunger 25 disposed at the operating rod side mounting end 10a is reciprocated, and the control rod 23 is reciprocated with respect to the operating rod 11b by the action of the tapered surface 25b (vertical direction in FIG. 1). ).

When the control rod 23 reciprocates with respect to the operating rod portion 11b, the effective cross-sectional area of the orifice is changed by the action of the tapered portion 23a provided at the distal end thereof, and the orifice is formed inside the damper body 11a. First
When the flow resistance of the oil changes between the pressure chamber 15a and the second pressure chamber 15b, the damping force of the hydraulic damper 11 changes.

The initial load setting means 30 is disposed movably on the outer peripheral area of the damper main body 11a, and has a coil spring 12 interposed between the initial load setting means 30 and a receiving seat 32 fixed to the operating rod portion 11b. A pressure receiving seat 33, an operating member 34, the tip of which abuts against the pressure adjusting seat 33 and is movably disposed on the outer peripheral surface of the damper main body 11 a, is fixed to the outer peripheral surface of the damper main body 11 a. A block member 36 that defines a pressure chamber 35 between the damper body 11a and the base end of the operating member 34, and a hydraulic jack 31 with a built-in motor that supplies pressure oil to the pressure chamber 35 are provided. . The hydraulic jack 31 has a limit switch 37, and the position of the piston 31b is always detected by the limit switch 37.

In the initial load setting means 30, when the hydraulic jack 31 is operated by the operation of the motor 38, pressure oil flows into and out of the pressure chamber 35, and the operating member 34
The initial load of the coil spring 12 is changed by changing the occupied position of the pressure adjustment seat 33 with respect to the damper body 11a with the movement of the spring.

At this time, in the damping force adjusting means 20, the hydraulic cylinder actuator 26 is operated in conjunction with the operation of the hydraulic jack 31, and the operating rod side mounting end 10a
As a result, the pressure oil flows into and out of the drive chamber 27, so that in the cushion unit 10, the damping force of the hydraulic damper 11 is adjusted according to the set initial load of the coil spring 12.

As shown in FIG. 3, the link mechanism 40 is swingable to the lower part of the vehicle body frame F via a base end thereof in a mode along the vehicle traveling direction (left side in FIG. 3). A first rod 41 is supported, and a pair of second rods 42, 42 each having one end pivotally fixed to an intermediate portion of the first rod 41, and the distal end of the first rod 41 is The pair of second rods 42, which are pivotally fixed to the operating rod-side mounting end 10 a of the cushion unit 10,
The other end of each 42 is pivoted to the swing arm 13.

The vehicle height adjusting means 50 is shown in FIGS.
As shown in FIG. 1, a vane motor 51 is provided. The vane motor 51 includes a casing 52 and the casing 52.
And a vane 53 accommodated in the inside of the vehicle body F, and is attached to an upper portion of the vehicle body frame F via the casing 52.

The vane 53 has a base end fixed to a rotating shaft 54 and is disposed so as to be swingable around the axis of the rotating shaft 54. Chambers 55a and 55b are defined. These two pressure chambers 55a, 55b are respectively provided with oil passages 56a, 56b.
b, the upper pressure chamber 55a is connected to one discharge port 57a of the gear pump 57 via the upper oil passage 56a, and the lower pressure chamber 55b is connected to the other of the gear pump 57 via the lower oil passage 56b. It is connected to the discharge port 57b. The gear pump 57 includes a drive motor 58 therein.
, And is rotated by the driving motor 58 in the forward and reverse directions.

As is apparent from the drawing, a reservoir tank 59 is interposed in the upper oil passage 56a connecting the upper pressure chamber 55a of the vane motor 51 and the gear pump 57. A cylinder actuator 60 is interposed in the lower oil passage 56b connecting the lower pressure chamber 55b and the gear pump 57 to the lower oil passage 56b.

The reservoir tank 59 stores hydraulic oil (not shown) therein, and is connected to the upper oil passage 56a via a check valve 61.

In the cylinder actuator 60, the distal end of the operating rod 62 functions as a lock pin 63. An operating rod side pressure chamber 65a divided by a piston 64 is connected to the lower oil passage 56b through a throttle passage 66. It is connected. The cylinder actuator 60 has a built-in pressure spring 67 for urging the lock pin 63 outward in the other pressure chamber 65b.
Further, a limit switch 68 is attached to the cylinder actuator 60, and the occupied position of the piston 64, that is, the occupied position of the lock pin 63 is constantly detected.

The vehicle height adjusting means 50 has a lever member 69 on the vane motor 51. The base end of the lever member 69 has a pivot shaft 54 of the vane motor 51.
And is pivotably supported around the axis of the rotating shaft 54, and is arranged in such a manner that the swinging direction is along the vehicle traveling direction (left side in FIG. 3).

One end of the lever member 69 is supported by the mounting end 10b of the cushion unit 10 on the main body side, and a lock hole 70 is formed at an intermediate portion thereof. The lock hole 70 is formed and arranged at a position corresponding to the lock pin 63 formed at the tip of the operating rod 62 in the cylinder actuator 60,
When the lever member 69 swings down most, the axial center with the lock pin 63 is aligned.

In the vehicle height adjusting means 50, the drive motor 5
When the gear pump 57 is operated by the rotation of the gear 8,
Hydraulic oil flows into and out of the two pressure chambers 55a and 55b of the vane motor 51, and the vane 53 swings around the axis of the rotating shaft 54.

When the vane 53 swings, the rotating shaft 54
The lever member 69 connected via the lever is pivoted, and the body-side mounting end 10b of the cushion unit 10 is moved with respect to the vehicle body frame F to change its mounting position.

When the body-side mounting end 10b of the cushion unit 10 moves with respect to the vehicle body frame F, the swing arm 13 swings via the link mechanism 40, so that the cushion unit 10 is in an equilibrium state, that is, the cushion unit 10 is expanded and contracted. The occupation position of the swing arm 13 in the non-existing state with respect to the body frame F is changed, and as a result, the occupation position of the body frame F with respect to the road surface, that is, the vehicle height is changed. At this time, since the gear pump 57 has a larger flow rate of hydraulic oil than other types of pumps, the operation time can be significantly reduced.

FIG. 2 shows a control system of the vehicle height adjusting means 50 and the initial load setting means 30 described above. Hereinafter, the actual operation of the present embodiment will be described based on the block diagram shown in FIG. The vehicle speed sensor 71 outputs a signal corresponding to the vehicle speed of the motorcycle B, and the signal is applied to the comparison unit 73 of the vehicle height control unit 72.

When the vehicle speed detected by the vehicle speed sensor 71 is higher than the range of 5 to 7 km / h, the comparator 73 outputs a signal "1" and adds it to one input of the AND circuit 74.

The gear position sensor 75 outputs a signal "1" when the gear selected by the transmission (not shown) is not "neutral", and applies this signal to the other input of the AND circuit 74.

The manual setting switch 76 is for manually setting the initial load of the coil spring 12 in the cushion unit 10 arbitrarily, and its signal is applied to the signal selecting section 77.

The rear vehicle height sensor 78 outputs a signal corresponding to the posture of the swing arm 13 in the equilibrium state with respect to the vehicle body frame F, that is, the inclination angle θ with respect to the vehicle body frame F. Added to section 80.

The comparison unit 80 of the initial load control unit 79 determines whether the tilt angle θ of the equilibrium swing arm 13 detected by the rear vehicle height sensor 78 is within the preset tilt angle θ0. Outputs a signal "00" and outputs a signal "01" when the tilt angle is smaller than the preset tilt angle θ0, and outputs a signal "10" when the tilt angle is larger than the preset tilt angle θ0. And outputs these output signals to the signal selection unit 77, respectively.

The signal selection section 77 performs “auto” based on the signal selected by the auto / manual selection switch 81.
Is selected, the signal from the comparison section 80 is output to the motor drive section 82, and if "manual" is selected, the signal from the manual set switch 76 is output to the motor drive section 82. .

Now, when the vehicle speed detected by the vehicle speed sensor 71 is 5-7 km / h or less, or the selected gear of the transmission (not shown) detected by the gear position sensor 75 is "neutral". The AND circuit 74 outputs a signal "0" to the motor drive unit 83 of the vehicle height control unit 72.

The motor driver 83 is provided with the AND circuit 74
The drive motor 58 of the gear pump 57 is rotated in an appropriate direction on the basis of the output signal “0” (hereinafter referred to as forward rotation).
Then, the operating oil is supplied to the upper pressure chamber 55a of the vane motor 51, and the vane 53 is pivoted to the lowermost position by increasing the internal pressure, and the lever member 69 for supporting the cushion unit 10 is pivoted to the uppermost position. Let it.

In this state, the cushion unit 10 occupies the uppermost position with respect to the body frame F,
Since the swing arm 13 in the parallel state is held in a state of being swung up most with respect to the body frame F, the height of the motorcycle B becomes the lowest, and the driver easily attaches the sole to the road surface. It becomes possible.

When the operation of the gear pump 57 is stopped in the above state, the vane motor 51 is stopped.
Although the pressure difference between the upper pressure chamber 55a and the lower pressure chamber 55b decreases, the weight of the motorcycle B and the driver causes the cushion unit 10 to occupy the uppermost position with respect to the body frame F. Will be kept as is.

Next, the motorcycle B is run, the vehicle speed detected by the vehicle speed sensor 71 becomes 5 to 7 km / h or more, and the transmission (not shown) detected by the gear position sensor 75 is selected. When the gear is no longer "neutral", the AND circuit 74 outputs a signal "1" to the motor drive unit 83 of the vehicle height control unit 72.

The motor driving section 83 is provided with the AND circuit 74.
The drive motor 58 is rotated in the reverse direction (hereinafter, referred to as reverse rotation) based on the output signal “1” from the controller to supply hydraulic oil to the lower pressure chamber 55b of the vane motor 51, and the internal pressure is increased. This causes the vane 53 to swing upward and the lever member 69 to swing downward. At this time, the pressure P1 applied to the lower pressure chamber 55b
Is lower than the pressing force of the pressing spring 67 built in the cylinder actuator 60.

When the lever member 69 is occupied at the lowest position with respect to the body frame F, the axis of the lock hole 70 and the axis of the lock pin 63 of the cylinder actuator 60 coincide with each other. As a result, the lock pin 63 is inserted into the lock hole 70 of the lever member 69, and at this time, the limit switch 68 attached to the cylinder actuator 60 is operated.

When the lock pin 63 of the cylinder actuator 60 is inserted through the lock hole 70 of the lever member 69,
The swing of the lever member 69 is prevented, and the cushion unit 10 is held in a state where it is occupied at the lowest position relative to the vehicle body frame F.

The signal output from the limit switch 68 is input to the motor drive unit 83 of the vehicle height control unit 72 and the motor drive unit 82 of the initial load control unit 79, and as a result, the operation of the gear pump 57 is stopped. At the same time, the motor drive unit 82 of the initial load control unit 79 is in an operable state.

In the above-described state, the swing arm 13 in the equilibrium state is held in a state of swinging most downward with respect to the vehicle body frame F, so that the height of the motorcycle B is greatly increased. Its maneuverability is improved.

During these operations, in the cushion unit 10, only the attachment position of the body-side attachment end 10b to the vehicle body frame F is changed.
Regardless of the height of the vehicle, the equilibrium length of the hydraulic damper 11 and the coil spring 12 is always constant, and the operating characteristics do not change. Further, since the rocking of the lever member 69 is mechanically prevented by the lock pin 63 of the cylinder actuator 60 being inserted into the lock hole 70, even when the operation of the gear pump 57 is stopped, The unit 10 is held in a state of being occupied at the lowest position with respect to the vehicle body frame F, and the impact from the road surface or the like applied during the traveling of the motorcycle B is directly applied to the hydraulic system of the vehicle height adjusting means 50. There is no.

Further, the motorcycle B is decelerated so that the vehicle speed detected by the vehicle speed sensor 71 becomes 5-7 km / h or less, or a transmission (not shown) selection gear detected by the gear position sensor 75. Becomes "neutral", the AND circuit 74 sends a signal "" again to the motor drive unit 83 of the vehicle height control unit 72.
0 "is output.

The motor drive unit 83 is provided with the AND circuit 74.
, And the drive motor 58 of the gear pump 57 is once rotated in reverse to supply the working oil to the lower pressure chamber 55b of the vane motor 51 based on the output signal “0” from the cylinder switch 60 and the output signal from the limit switch 68 of the cylinder actuator 60. , The internal pressure of the cylinder actuator 60
Pressure P2 higher than the pressing force of the pressing spring 67 built in
To rise.

When the lower pressure chamber 55b of the vane motor 51 reaches the pressure P2, the lever member 69 is urged downward, so that the cushion unit 10 applied to the lock pin 63 of the cylinder actuator 60 is moved.
4 is removed, and the piston 64 moves rightward in FIG. 4 against the pressing force of the built-in pressing spring 67, so that the lock pin 63 moves the lever member 69.
From the lock hole 70.

When the lock pin 63 is removed from the lock hole 70 of the lever member 69, the output signal from the limit switch 68 is immediately stopped, and only the output signal "0" from the AND circuit 74 is sent to the motor drive unit 83. Will be added.

For this reason, the motor drive unit 83 rotates the drive motor 58 of the gear pump 57 in the forward direction, and holds the vane 53 of the vane motor 51 in the state of being swung to the lowermost position. Again to the lowest state.

At this time, the drive motor 58 of the gear pump 57
Rotates forward, the lower pressure chamber 5 in the vane motor 51
5b and the internal pressure of the lower oil passage 56b communicating therewith decrease rapidly, but the cylinder actuator 60b
Operating rod side pressure chamber 65a and the lower oil passage 56
The lock pin 63 is not erroneously inserted into the lock hole 70 of the lever member 69 by the action of the throttle passage 66 interposed between the lock member 63 and the lever member 69.

On the other hand, when the vehicle height of the motorcycle B is increased by the vehicle height control unit 72, the initial load control unit is controlled based on the operation signal of the limit switch 68 attached to the cylinder actuator 60 described above. 79 allows the initial load of the coil spring 12 to be adjusted.

When the auto / manual selection switch 81 of the initial load control section 79 is set to "auto" and the swing arm 13 has an angle smaller than the preset inclination angle θ0, The comparison unit 80 outputs the signal “01” to the signal selection unit 77.

The signal selecting section 77 is based on the signal from the auto / manual selection switch 81, and
The signal “01” output from 0 is directly applied to the motor drive unit 82.

The motor drive unit 82 controls the motor 3 of the hydraulic jack 31 based on the signal “01” from the comparison unit 80.
8 is rotated in an appropriate direction (hereinafter, referred to as forward rotation), and pressure oil flows into a pressure chamber 35 defined in an outer peripheral area of the damper main body 11a in the initial load setting means 30, thereby initializing the coil spring 12. In addition to increasing the load, the operating rod side mounting end 1 of the damping force adjusting means 20 is increased.
The damping force of the hydraulic damper 11 is increased by flowing the pressurized oil into the drive chamber 27a.

When the initial load of the coil spring 12 is increased, the operating rod portion 11b of the hydraulic damper 11 is extended with respect to the damper body 11a, that is, moved downward, and the swing arm 13 swings downward via the link mechanism 40. The tilt angle θ with respect to the vehicle body frame F in the equilibrium state increases by being moved.

Thereafter, the above-described operation is repeatedly performed, and the initial load of the coil spring 12 is adjusted so that the swing arm 13 occupies the preset inclination angle θ0. The damping force of the hydraulic damper 11 is adjusted according to the initial load 12.

Therefore, the motorcycle B is always kept at a constant posture even when its load weight changes, and the operating characteristics of the cushion unit 10 are always optimal for the vehicle.

When the swing arm 13 is at an angle larger than the preset inclination angle θ0, the signal “1” is sent from the comparing unit 80 to the motor driving unit 82.
By adding “0”, the initial load of the coil spring 12 is reduced, and thereafter, the operation opposite to the above-described operation is performed, whereby the swing arm 13 is occupied at the preset inclination angle θ0. At this time, the operation opposite to the above-described operation is performed in the damping force adjusting means 20, and the damping force of the hydraulic damper 11 is reduced by the coil spring 12.
Can be lowered according to the initial load.

When the auto / manual selection switch 81 is set to "manual", the signal output from the manual set switch 76 is directly applied to the motor drive section 82, and the initial state of the coil spring 12 is set. The load is set to an arbitrary value, and the damping force of the hydraulic damper 11 is adjusted according to the arbitrarily set initial load of the coil spring 12. In the case of this manual operation, the motor 38 of the hydraulic jack 31 is automatically stopped when the initial load of the coil spring 12 becomes maximum or minimum according to the output signal of the limit switch 37 provided on the hydraulic jack 31. .

In the above-described embodiment, the motorcycle cushion unit 10 interposed between the vehicle body frame F and the rear wheel R is illustrated. However, the present invention is not limited to this. Needless to say, the present invention can also be applied to vehicles other than motorcycles, and in that case, it can also be applied to other wheels such as front wheels. In addition, although the cushion unit 10 is disposed substantially vertically in such a manner as to tilt forward, it may be disposed substantially horizontally with respect to the vehicle body frame F. Further, the operating rod side mounting end 10a of the cushion unit 10 is connected to the link mechanism 40.
And is connected to the rear wheel R via the swing arm 13, but the present invention is not limited to this. Furthermore, although the motorcycle B having only one cushion unit 10 is illustrated, a plurality of cushion units 10 may be provided.

In the above embodiment, the vehicle height adjusting means 50 is used.
The cushion unit 10 is attached to the vehicle B via the vehicle height adjusting means 50 in the present invention.
Is not necessary. When the vehicle height adjusting means 50 is applied, in the embodiment, the cushion unit 1 is used.
Although it is disposed at the main body side mounting end 10b, it may be applied only to the operating rod side mounting end 10a, or may be applied to both. In the case where the vehicle height adjusting means 50 is applied, the embodiment illustrates the vane motor 51 operated by the gear pump 57 and the vehicle height adjusting means 50 employing the lever member 69 which swings by the operation of the vane motor 51. However, the present invention is not limited to these. Furthermore, although the vehicle height is automatically controlled based on the vehicle speed and the gear position, the vehicle height may be manually changed. When the vehicle height is controlled by the vehicle speed, the reference is set to 5 to 7 km / h in the embodiment, but other values may be used. Further, although the vehicle height is changed by only two steps, the vehicle height may be changed by a plurality of steps or may be changed steplessly. Further, the vehicle height adjusting means 50 is connected to the lever member 69 by the lock pin 63 and the lock hole 70.
Although there is provided a means for mechanically preventing the rocking motion, this means is not always necessary.

[0068]

[0069]

As described above, according to the vehicle cushion unit of the present invention, when the initial load of the coil spring is changed, the damping force of the damper changes in accordance with the initial load. Optimum operating characteristics can be obtained.

[Brief description of the drawings]

FIG. 1 is a partial side sectional view conceptually showing a vehicle cushion unit according to the present invention.

FIG. 2 is a block diagram showing a control system of the vehicle cushion unit according to the present invention.

FIG. 3 is a side view conceptually showing a main part of a motorcycle to which the vehicle cushion unit according to the present invention is applied.

FIG. 4 is a conceptual diagram showing a drive system of a vehicle height adjusting unit applied to the embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Cushion unit 11 Damper 12 Coil spring 20 Damping force adjusting means 30 Initial load setting means

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-60-44633 (JP, A) JP-A-60-88240 (JP, A) JP-A-60-56617 (JP, A) JP-A-1- 212686 (JP, A) JP-A-56-116936 (JP, A) JP-A-61-116248 (JP, U) JP-A-62-108094 (JP, U) (58) Fields investigated (Int. ⁷ , DB name) B60G 17/08 B60G 17/027 B62K 25/04 B62K 25/10 F16F 9/46

Claims (1)

(57) [Claims] 1. A vehicle cushion unit including a coil spring and a damper, wherein the vehicle cushion unit is disposed in series with the coil spring between the damper main body and an operating rod portion, according to an initial load acting on the vehicle cushion unit. An initial load setting unit that expands and contracts by hydraulic oil supplied from a driving hydraulic chamber of a driving hydraulic jack to change an installation length of the coil spring to set an initial load of the coil spring; and an operating rod of the damper. A plunger having a tapered surface that moves forward and backward in response to a change in hydraulic pressure acting on the driving chamber in a driving chamber disposed in the mounting-side end; and an operating rod of the damper pressed against the tapered surface of the plunger. Force adjustment consisting of a control rod that changes the effective area of the orifice by shifting the inside and changes the damping force A step, wherein the damping force adjusting means communicates the drive chamber with a drive hydraulic chamber of the hydraulic jack that supplies hydraulic oil to the initial load setting means, and communicates the drive chamber with the drive hydraulic chamber. The hydraulic circuit includes a free piston partitioned into two oil chambers, a drive hydraulic chamber side of the hydraulic jack and a drive chamber side of the damping force adjusting means, and a free piston on the drive hydraulic chamber side of the free piston. A cushion unit for a vehicle, wherein a hydraulic cylinder actuator having a piston diameter smaller than the piston diameter on the drive chamber side is inserted.