Vehicle height adjustment device

Abstract

To provide a vehicle height adjustment device which can secure a long vehicle height adjustment length without being limited by specifications of a suspension spring and a shock absorber and achieve reduction of costs.SOLUTION: A vehicle height adjustment device 1 of the invention includes: a link 2 which is attached to a vehicle body B of a saddle-riding type vehicle V so as to be rotatable around a lateral direction of the vehicle body B and attached to a shock absorber D connected to the vehicle body 2 so as to be rotatable around the lateral direction of the vehicle body B; and an actuator 3 which is rotatably connected at one end to the link 2 and rotatably attached at the other end to a swing arm A, which is swingably attached to the vehicle body B, and may expand or contract.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a vehicle height adjusting device. [Background technology]

[0002] Some straddle-type vehicles are equipped with a vehicle height adjustment device that adjusts the height of the vehicle body to improve foot reach when the vehicle is stopped. Conventionally, the vehicle height adjustment device has been integrated with a shock absorber called a rear cushion unit that is interposed between the vehicle body and a swing arm that supports the rear wheel so that it can swing relative to the vehicle body.

[0003] The vehicle height control device integrated with the shock absorber in this manner is attached to the outer periphery of the cylinder of the shock absorber, which has a cylinder, a piston movably inserted into the cylinder, and a piston rod movably inserted into the cylinder and connected to the piston. More specifically, the vehicle height control device includes a cylindrical housing disposed on the outer periphery of the cylinder and forming an annular gap between it and the cylinder, an annular jack piston that slides against the outer periphery of the cylinder and the inner periphery of the housing and moves in and out of the annular gap to define a jack chamber between the cylinder and the housing, and a pump unit that supplies and discharges hydraulic oil to and from the jack chamber to drive the jack piston.

[0004] A vehicle height adjustment device configured in this manner supports one end of the suspension spring with a jack piston, and by driving the jack piston axially relative to the cylinder, the support position of the suspension spring can be moved vertically, thereby adjusting the height of the vehicle body elastically supported by the suspension spring (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Japanese Patent Application Laid-Open No. 2017-180478 Summary of the Invention [Problem to be solved by the invention]

[0006] As described above, conventional vehicle height adjustment devices are integrated into the shock absorber and use a jack to change the support position of the suspension spring, so the vehicle height cannot be lowered beyond the spring load generated by the suspension spring.Furthermore, when the vehicle height is adjusted, the piston position in the cylinder of the shock absorber also moves up and down, so the length over which the vehicle height can be adjusted is limited by the specifications of the suspension spring and shock absorber, making it difficult to increase the vehicle height adjustment length even if desired.

[0007] Furthermore, the jack piston for changing the support position of the suspension spring must be in sliding contact with both the cylinder and the housing of the shock absorber, which requires high machining precision and requires sealing at two locations: between the cylinder and the jack piston and between the housing and the jack piston, which increases costs.

[0008] SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a vehicle height adjusting device that can ensure a long vehicle height adjustment length without being restricted by the specifications of suspension springs and shock absorbers, and that can reduce costs. [Means for solving the problem]

[0009] In order to solve the above problem, the vehicle height adjustment device of the present invention comprises a link that is rotatably attached to the body of a saddle-ride vehicle around an axis in the left-right direction of the body and is rotatably attached to a shock absorber connected to the body around an axis in the left-right direction of the body, and an actuator that has one end rotatably connected to the link and the other end rotatably attached to a swing arm that is swingably attached to the body and can extend and retract by itself.

[0010] With a vehicle height adjustment device configured in this manner, the vehicle height is adjusted by rotating the link with an actuator to change the support position of the lower end of the shock absorber, so there is no need to expand or contract the shock absorber or suspension spring. This means that the vehicle height can be adjusted without being restricted by the specifications of the shock absorber and suspension spring, and a longer vehicle height adjustment length can be ensured compared to conventional vehicle height adjustment devices.

[0011] In addition, the actuator in the vehicle height adjustment device may have a screw shaft and a nut attached to the screw shaft, an expandable / contractible body that expands and contracts when one of the screw shaft and the nut rotates, and a motor that drives one of the screw shaft and the nut, and the screw shaft and the nut may be capable of self-locking so that one of the screw shaft and the nut does not rotate when the other of the screw shaft and the nut moves in the axial direction.

[0012] With this vehicle height adjustment device configured in this manner, the vehicle height can be easily adjusted using an electric actuator, and the vehicle height can be maintained by self-locking between the screw shaft and the nut, which saves energy because no power is consumed to maintain the vehicle height.

[0013] Furthermore, the actuator in the vehicle height adjustment device may have a link rod cylinder having a cylinder, a piston inserted into the cylinder so as to be axially movable, and a rod inserted into the cylinder so as to be axially movable and connected to the piston, a tank for storing liquid, a pump, and a pump unit having a hydraulic circuit that can be switched between a state in which the pump supplies liquid from the tank to the link rod cylinder, a state in which the pump discharges liquid from the link rod cylinder to the tank, and a state in which the connection between the link rod cylinder and the tank is cut off.

[0014] With a vehicle height adjustment device configured in this manner, vehicle height can be easily adjusted using an actuator that hydraulically drives a link rod cylinder with a simple structure, and vehicle height can be maintained by disconnecting the link rod cylinder from the tank, which saves energy because no power is consumed to maintain vehicle height.

[0015] In addition, the vehicle height adjustment device may be configured so that the vehicle body rises when the link rotates counterclockwise relative to the vehicle body when viewed from the left side, and the actuator may be configured so that when liquid is supplied by the pump unit to an extension chamber defined by a piston within the cylinder, the link rod cylinder is contracted, causing the link to rotate forward counterclockwise when viewed from the left side of the vehicle body.

[0016] With a vehicle height adjustment device configured in this manner, the pump unit can adjust the vehicle height by supplying and discharging fluid to the extension-side chamber of the link rod cylinder, which simplifies the structure of the link rod cylinder and the configuration of the hydraulic circuit in the pump unit, thereby reducing manufacturing costs.

[0017] Furthermore, the vehicle height adjustment device may be configured so that the vehicle body rises when the link rotates clockwise relative to the vehicle body as viewed from the left side of the vehicle body, and the actuator may be configured so that when liquid is supplied by the pump unit to a compression side chamber defined by a piston in the cylinder, the link rod cylinder is extended, causing the link to rotate clockwise as viewed from the left side of the vehicle body.

[0018] With a vehicle height control device configured in this manner, the pump unit can adjust the vehicle height by simply supplying and discharging fluid to the compression-side chamber of the link rod cylinder, which simplifies the structure of the link rod cylinder and the configuration of the hydraulic circuit in the pump unit and reduces manufacturing costs. Also, since a seal to seal the extension-side chamber of the link rod cylinder is not required, the link rod cylinder can be manufactured more inexpensively, and since the entire cross-sectional area of ​​the piston is used as a pressure-receiving area to generate a large thrust, the pump discharge pressure can be lowered accordingly, allowing the motor that drives the pump to be made smaller.

[0019] Furthermore, the pump unit in the vehicle height adjustment device may be attached to the vehicle body, in which case it becomes easier to route the wiring for supplying electricity to the pump, and the vehicle height adjustment device can be easily installed on the saddle-type vehicle V. [Effects of the Invention]

[0020] According to the vehicle height adjusting device of the present invention, a long vehicle height adjustment length can be ensured without being restricted by the specifications of the suspension springs and shock absorbers. [Brief explanation of the drawings]

[0021] [Figure 1]1 is a side view of a saddle-ride type vehicle equipped with a vehicle height adjusting device according to an embodiment. [Figure 2] 1 is a cross-sectional view of an actuator of a vehicle height control device according to an embodiment. [Figure 3] 5A to 5C are diagrams illustrating the operation of the vehicle height adjusting device according to the embodiment. [Figure 4] FIG. 4 is a hydraulic circuit diagram of an actuator of a vehicle height control device according to a first modified example of the embodiment. [Figure 5] FIG. 10 is a side view of a vehicle height adjusting device according to a second modified example of the embodiment. [Figure 6] FIG. 10 is a hydraulic circuit diagram of an actuator of a vehicle height control device according to a second modified example of the embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0022] The present invention will be described based on the embodiment shown in the drawings. As shown in Fig. 1, a vehicle height adjusting device 1 in one embodiment is applied to a saddle-riding type vehicle V, and is configured to include a link 2 rotatably attached to a body B of the saddle-riding type vehicle V, and an actuator 3 attached between a swing arm A of the saddle-riding type vehicle V and the link 2.

[0023] The vehicle height adjusting device 1 will be described in detail below. As shown in Fig. 1, the link 2 is attached to the body B of the saddle-riding type vehicle V so as to be rotatable around an axis extending in the left-right direction of the body B of the saddle-riding type vehicle V. The link 2 is specifically triangular in shape, and the vicinity of the uppermost of its three vertices in Fig. 1 is hingedly connected to the body B, so that the link 2 can rotate around an axis extending in the left-right direction of the body B relative to the body B.

[0024] The saddle-ride type vehicle V also includes a shock absorber D whose upper end is hinged to the vehicle body B and whose lower end is hinged near the apex located at the lowest position of the link 2. The shock absorber D is a telescopic type shock absorber, and although not shown in detail, it includes a cylindrical damper cylinder, a piston inserted into the damper cylinder so as to be movable in the axial direction, and a piston rod inserted into the damper cylinder so as to be movable in the axial direction and connected to the piston, and when the piston rod moves axially relative to the damper cylinder, it generates a damping force that prevents the expansion and contraction of the piston rod. A suspension spring S is interposed between a spring bearing provided on the outer periphery of the damper cylinder of the shock absorber D and a spring bearing provided on the piston rod.

[0025] As mentioned above, shock absorber D is rotatably connected to vehicle body B and link 2, so when shock absorber D expands, link 2 is pushed down against vehicle body B, causing it to rotate clockwise when viewed from the left side of the vehicle body B's direction of travel, with the hinge connection point to vehicle body B as the fulcrum; and when shock absorber D contracts, it is pushed up against vehicle body B, causing it to rotate counterclockwise when viewed from the left side of vehicle body B, with the hinge connection point to vehicle body B as the center.

[0026] Further, a swing arm A is provided on a vehicle body B of the saddle-ride type vehicle V. The swing arm A rotatably holds a rear wheel W, is hinged to the vehicle body B, and is swingable up and down relative to the vehicle body B. As shown in FIG. 1 , one end of the actuator 3 is hinged to the link 2 near a vertex other than the two vertices to which the vehicle body B and the shock absorber D are hingedly connected, and the other end is hinged to the swing arm A. In this way, the actuator 3 is rotatable relative to the link 2 and the swing arm A.

[0027] When swing arm A rotates upward relative to vehicle body B, the other end of actuator 3 is pulled upward by swing arm A, causing link 2 to rotate counterclockwise around the connection point to vehicle body B in FIG. 1 when vehicle body B is viewed from the left side in the direction of travel, and shock absorber D contracts together with the suspension spring. The upward rotation of swing arm A also means that vehicle body B and wheel W move closer to each other, and in such a case, the displacement of swing arm A relative to vehicle body B is transmitted to shock absorber D by link 2, causing it to contract and exert a damping force that prevents wheel W from approaching vehicle body B.

[0028] Furthermore, when the swing arm A rotates downward relative to the vehicle body B, the other end of the actuator 3 is pulled downward by the swing arm A, causing the link 2 to rotate clockwise around the connection point to the vehicle body B in FIG. 1 when the vehicle body B is viewed from the left side in the direction of travel, and the shock absorber D extends together with the suspension spring. The downward rotation of the swing arm A also causes the vehicle body B and the wheel W to separate in the vertical direction, and in such a case, the displacement of the swing arm A relative to the vehicle body B is transmitted to the shock absorber D by the link 2, causing the shock absorber D to extend and exert a damping force that prevents the wheel W from separating from the vehicle body B. The link 2 is provided to transmit the swing of the swing arm A to the shock absorber D at a predetermined lever ratio, and its shape is not limited to a triangular shape, but may also be an L-shape or a straight line.

[0029] In the above-described mode of connection of shock absorber D and actuator 3 to link 2, the distance from the rotation center of link 2 relative to vehicle body B to the connection point of shock absorber D is longer than the distance from the rotation center of link 2 relative to vehicle body B to the connection point of actuator 3, so the swing of swing arm A is amplified and transmitted to shock absorber D. However, the connection points of shock absorber D and actuator 3 to link 2 may be interchanged, in which case the swing of swing arm A can be attenuated and transmitted to shock absorber D. The lever ratio of link 2 can be changed as desired by setting the distance from the connection point to vehicle body B to each of the connection points of shock absorber D and actuator 3.

[0030] 2, the actuator 3 in one embodiment includes an expandable body 3a having a screw shaft 3b and a nut 3c attached to the screw shaft 3b, and a motor 3d that drives the screw shaft 3b. More specifically, the actuator 3 includes a cylindrical outer cylinder 3e with a bottom that rotatably houses the screw shaft 3b therein and also houses the motor 3d, and a cylindrical inner cylinder 3f with a bottom that has the screw shaft 3b inserted therein and is connected to the nut 3c so that it can move axially relative to the outer cylinder 3e while its circumferential rotation is prevented within the outer cylinder 3e.

[0031] In the actuator 3 configured as described above, when the screw shaft 3b is driven by the motor 3d, the nut 3c attached to the outer periphery of the screw shaft 3b moves along the axis of the screw shaft 3b, expanding and contracting by moving the inner cylinder 3f in and out of the outer cylinder 3e. Furthermore, when the nut 3c is threadedly coupled to the outer periphery of the screw shaft 3b, driving the screw shaft 3b to rotate by the motor 3d can move the nut 3c in the axial direction, but the screw shaft 3b does not rotate even when an axial load is applied from the nut 3c side. In this way, the screw shaft 3b and the nut 3c constitute a screw mechanism that exhibits an irreversible self-locking function: the nut 3c can be moved in the axial direction by driving the screw shaft 3b alone, but conversely, driving the nut 3c in the axial direction cannot rotate the screw shaft 3b.

[0032] One of the outer tube 3e and the inner tube 3f is hingedly connected to the link 2, and the other of the outer tube 3e and the inner tube 3f is hingedly connected to the swing arm A. Therefore, when the actuator 3 is driven to retract the inner tube 3f from the outer tube 3e and extend the telescopic body 3a, as shown in FIG. 3, which shows the vehicle body B as viewed from the left, the link 2 rotates clockwise around the hinge connection point to the vehicle body B as indicated by the dashed line in FIG. 3, and the rotation of the link 2 causes the lower end of the shock absorber D to move downward. The shock absorber D and the suspension spring S are connected in parallel to the vehicle body B and the link 2, and the weight of the vehicle body B supported by the suspension spring S does not change even when the link 2 rotates. Therefore, the vehicle height of the vehicle body B is lowered by the amount that the connection point of the lower end of the shock absorber D to the link 2 is lowered due to the rotation of the link 2.

[0033] Conversely, when the actuator 3 is driven to retract the inner tube 3f into the outer tube 3e and contract the telescopic body 3a, as shown in Figure 3, which shows the vehicle body B viewed from the left side, the link 2 rotates counterclockwise around the hinge connection point to the vehicle body B as indicated by the solid line in Figure 3, and the lower end of the shock absorber D moves upward as the link 2 rotates. Therefore, the vehicle height of the vehicle body B also rises by the amount that the connection point of the upper end of the shock absorber D to the link 2 rises due to the rotation of the link 2. Furthermore, if the motor 3d is stopped, the screw shaft 3b and nut 3c exhibit a self-locking function, and the telescopic body 3a does not expand or contract, so the vehicle height can be maintained even if the vehicle weight acts on the nut 3c.

[0034] The actuator 3 is located between the link 2 and the swing arm A, and at low speeds, whether it extends or contracts, does not cause the shock absorber D or the suspension spring S to expand or contract. Therefore, when adjusting the vehicle height by expanding or contracting the actuator 3, the load generated by the suspension spring S does not change, and the damping force generated by the shock absorber D does not change.

[0035] The actuator 3 is controlled by a controller C. The controller C obtains the rotation speed of the motor 3d from a signal from a sensor mounted on the motor 3d, such as a resolver or a Hall element, that detects the rotational position of the motor 3d in order to drive the motor 3d, and controls the vehicle height while monitoring it by multiplying the rotation speed by the amount of change in vehicle height per rotation of the motor 3d. Furthermore, when the speed of the saddle-riding type vehicle V falls below a preset low speed, the controller C drives the actuator 3 to lower the vehicle height until it reaches a predetermined stationary vehicle height that ensures foot reach when stationary, and when the speed of the saddle-riding type vehicle V exceeds the low speed, the controller C controls the actuator 3 to raise the vehicle height from the stationary vehicle height to a running vehicle height suitable for running. Note that the controller C uses a sensor in the motor 3d to determine the vehicle height, but the vehicle height may also be determined using a stroke sensor that detects the displacement of the telescopic body 3a, or a sensor that directly detects the height of the vehicle body B relative to the road surface. In addition, a switch that can be operated by the vehicle occupant to selectively rotate the motor 3d forward and reverse or stop the motor 3d may be installed on the saddle-type vehicle V, so that the vehicle occupant can operate the actuator 3 to adjust the vehicle height to the desired height.

[0036] As described above, the vehicle height adjustment device 1 of this embodiment includes a link 2 that is rotatably attached to the body B of a saddle-ride type vehicle V around an axis extending in the left-right direction of the body B and is rotatably attached to a shock absorber D connected to the body B around an axis extending in the left-right direction of the body B, and an actuator 3 that has one end rotatably connected to the link 2 and the other end rotatably attached to a swing arm A that is swingably attached to the body B and is capable of extending and contracting by itself.

[0037] The vehicle height adjusting device 1 configured in this manner adjusts the vehicle height by rotating the link 2 with the actuator 3 to change the support position of the lower end of the shock absorber D, and therefore does not need to expand or contract the shock absorber D and the suspension spring S. This means that the vehicle height can be adjusted without being limited by the specifications of the shock absorber D and the suspension spring S, and a longer vehicle height adjustment length can be ensured compared to conventional vehicle height adjusting devices. Furthermore, since the vehicle height adjusting device 1 does not need to be provided integrally with the shock absorber D, neither high processing precision nor seals in multiple locations are required, thereby reducing costs. As described above, the vehicle height adjusting device 1 of this embodiment can ensure a longer vehicle height adjustment length without being limited by the specifications of the suspension spring S and the shock absorber D, and can also reduce costs. Furthermore, according to the vehicle height adjustment device 1 of this embodiment, the actuator 3 is disposed between the link 2 and the swing arm A, and so even if it extends or contracts at low speeds, the shock absorber D and the suspension spring S do not need to be expanded or contracted. Therefore, when adjusting the vehicle height, the load generated by the suspension spring S does not change, and the damping force generated by the shock absorber D does not change. Therefore, even if the vehicle height is adjusted while driving, the ride comfort of the saddle-type vehicle V does not suddenly change.

[0038] Furthermore, the actuator 3 in the vehicle height adjusting device 1 of this embodiment includes a screw shaft 3b and a nut 3c attached to the screw shaft 3b, an expandable / contractable body 3a that expands and contracts as the screw shaft 3b rotates, and a motor 3d that drives the screw shaft 3b. In the vehicle height adjusting device 1 configured in this manner, the vehicle height can be easily adjusted using the electric actuator 3, and the vehicle height can be maintained by self-locking between the screw shaft 3b and the nut 3c, and energy is saved because no power is consumed to maintain the vehicle height.

[0039] The actuator 3 may employ a structure in which the rotation of the screw shaft 3b in the circumferential direction is restricted and the nut 3c is rotationally driven by the motor 3d to extend and retract the extendable body 3a. If the motor 3d is a motor with a reducer, the reducer on the motor 3d side may provide self-locking.

[0040] While the actuator 3 has been described above as an electric actuator, it may also be an actuator 10 that uses hydraulic pressure, as in the vehicle height control device 1 of a first modified example of one embodiment, as shown in Fig. 4. Specifically, the actuator 10 is configured to include a link rod cylinder 20 that includes a cylinder 21, a piston 22 inserted into the cylinder 21 so as to be axially movable, and a rod 23 inserted into the cylinder 21 so as to be axially movable and connected to the piston 22, a tank 31 that stores liquid, a pump 32, and a pump unit 30 that has a hydraulic circuit 33 that can be switched by the pump 32 among a state in which the liquid is supplied from the tank 31 to the link rod cylinder 20, a state in which the liquid is discharged from the link rod cylinder 20 to the tank 31, and a state in which the connection between the link rod cylinder 20 and the tank 31 is cut off.

[0041] First, we will explain each part of link rod cylinder 20. Cylinder 21 is a cylindrical cylinder with a bottom, and has bottom 21a equipped with eye-shaped bracket 21b that can be connected to swing arm A. In addition, an annular rod guide 24 is attached to the open end of cylinder 21, which is the right end in FIG. 4.

[0042] The piston 22 is inserted into the cylinder 21 so as to be movable in the axial direction, and divides the interior of the cylinder 21 into an extension-side chamber R1 and a compression-side chamber R2. The rod 23 is inserted into the cylinder 21 so as to be movable in the axial direction, and its base end, which is the left end in FIG. 4, is connected to the piston 22. The rod 23 is inserted into the inner periphery of a rod guide 24 fixed to the inner periphery of the open end of the cylinder 21, and its tip, which is the right end in FIG. 4, protrudes outward from the cylinder 21. The rod 23 is guided by the rod guide 24 so as to be movable in the axial direction without axial wobble, and can move in and out of the cylinder 21.

[0043] In this embodiment, when the link 2 rotates counterclockwise as viewed from the left side of the vehicle body B, the vehicle height increases, and therefore, in order to increase the vehicle height, the link rod cylinder 20 must be contracted. To contract the link rod cylinder 20, liquid is supplied to the extension-side chamber R1. Meanwhile, since the link rod cylinder 20 is constantly biased to extend by the weight of the vehicle body B, discharging liquid from the extension-side chamber R1 causes the link rod cylinder 20 to extend, thereby lowering the vehicle height. Therefore, in this embodiment, there is no need to supply or discharge liquid to or from the compression-side chamber R2 of the link rod cylinder 20. Therefore, the compression-side chamber R2 may be filled with gas at approximately atmospheric pressure when the link rod cylinder 20 is fully extended, or a hole may be provided in the cylinder 21 to open the compression-side chamber R2 to the atmosphere. When the compression side chamber R2 is open to the atmosphere, it is preferable to fill the compression side chamber R2 with gas and seal it from the viewpoint of protecting the seal ring (not shown) attached to the outer periphery of the piston 22 to seal between the cylinder 21 and the piston 22 from water or dust entering the compression side chamber R2.

[0044] The pump unit 30 includes a tank 31, a pump 32, and a hydraulic circuit 33. The hydraulic circuit 33 includes a main passage 34 connecting the tank 31 and the extension-side chamber R1 of the link rod cylinder 20, a cylinder relief passage 35 that is in communication with the tank 31 and is in communication with the extension-side chamber R1 through the main passage 34, pump relief passages 36 and 37 that are connected to the tank 31 and the main passage 34, a direction switching valve 38 provided in the main passage 34, an operate check valve 39, a check valve 40, and an orifice 41 that are provided in series in the main passage 34 and closer to the extension-side chamber R1 than the direction switching valve 38, a cylinder-side relief valve 42 provided in the cylinder relief passage 35, pump-side relief valves 43 and 44 that are provided in the pump relief passages 36 and 37, respectively, and a discharge passage 45.

[0045] One end of the main passage 34 is connected to the tank 31, and the other end is connected to the extension-side chamber R1 of the link rod cylinder 20. Along the main passage 34, there are provided, in this order from the tank 31 side, a directional control valve 38, a pump 32, an operable check valve 39, and a check valve 40 and an orifice 41, which are arranged in parallel with each other. For ease of understanding, the portion of the main passage 34 closer to the tank 31 than the directional control valve 38 will be referred to as a tank-side passage 34a, and the portion of the main passage 34 closer to the extension-side chamber R1 than the directional control valve 38 will be referred to as a cylinder-side passage 34b.

[0046] The discharge passage 45 has one end connected to the directional control valve 38 and the other end connected to the cylinder side passage 34b of the main passage 34, between the operated check valve 39 and the directional control valve 38.

[0047] Pump 32 is a pump capable of bidirectional discharge. When pump 32 rotates in the forward direction, it switches directional control valve 38 to connect tank 31 with extension-side chamber R1 of link rod cylinder 20, thereby sucking liquid from tank 31 and supplying the liquid to extension-side chamber R1. When pump 32 rotates in the reverse direction, it opens operate check valve 39 and switches directional control valve 38 to connect extension-side chamber R1 of link rod cylinder 20 with tank 31.

[0048] The directional control valve 38 has three positions and three ports, is provided midway through the main passage 34 and is connected to one end of a discharge passage 45 . Specifically, the direction switching valve 38 is provided with a valve element 38a having a blocking position 38b that closes the tank-side passage 34a and the cylinder-side passage 34b to block the main passage 34 and also blocks the discharge passage 45, a supply position 38c that connects the tank-side passage 34a and the cylinder-side passage 34b to open the main passage 34 and closes one end of the discharge passage 45, and a discharge position 38d that blocks the tank-side passage 34a to connect the cylinder-side passage 34b and the discharge passage 45, a pair of springs 38e and 38f that sandwich and urge the valve element 38a to position the valve element 38a at the blocking position 38b, which is a neutral position, a pilot passage 38g that is located midway through the cylinder-side passage 34b and that applies pressure on the extension-side chamber R1 side relative to the pump 32 to the valve element 38a, and a pilot passage 38h that is located midway through the cylinder-side passage 34b and that applies pressure on the tank 31 side relative to the pump 32 to the valve element 38a. The pilot passage 38g applies pressure from the cylinder-side passage 34b on the expansion-side chamber R1 side relative to the pump 32 to the valve element 38a so as to switch the valve element 38a to the supply position 38c. On the other hand, the pilot passage 38h applies pressure from the cylinder-side passage 34b on the tank 31 side relative to the pump 32 to the valve element 38a so as to switch the valve element 38a to the discharge position 38d.

[0049] The direction switching valve 38 configured as described above is switched as follows by the operation of the pump 32. First, when the pump 32 is not driven and is stopped, the pressure inside the cylinder-side passage 34b is low, and sufficient pressure cannot be applied to the valve element 38a of the direction switching valve 38 to switch the valve element 38a from the shut-off position 38b, which is the neutral position, to another position, so the direction switching valve 38 takes the shut-off position 38b, shuts off the main passage 34, and closes one end of the discharge passage 45.

[0050] When the pump 32 is driven to rotate in the forward direction, the pump 32 discharges fluid toward the extension-side chamber R1, so that the pressure in the cylinder-side passage 34b on the extension-side chamber R1 side becomes higher than the pressure in the pump 32, while the pressure in the cylinder-side passage 34b on the tank 31 side becomes lower than the pressure in the pump 32. As a result, the valve body 38a is pushed leftward in FIG. 4, and the direction switching valve 38 is switched to the supply position 38c, connecting the tank-side passage 34a and the cylinder-side passage 34b to each other, connecting the tank 31 to the extension-side chamber R1 through the main passage 34, and closing one end of the discharge passage 45.

[0051] When the pump 32 is driven to rotate in the reverse direction, the pump 32 discharges fluid toward the tank 31, so that the pressure in the cylinder-side passage 34b on the tank 31 side becomes higher than the pressure in the pump 32, while the pressure in the cylinder-side passage 34b on the extension-side chamber R1 side becomes lower than the pressure in the pump 32. As a result, the valve element 38a is pushed to the right in Figure 4, and the direction switching valve 38 switches to the discharge position 38d, connecting the tank-side passage 34a and the discharge passage 45 and closing the cylinder-side passage 34b.

[0052] When the pressure on the tank 31 side of the cylinder-side passage 34b is higher than the pressure on the pump 32 side of the cylinder-side passage 34b, the operated check valve 39 is forcibly opened by the pressure to allow bidirectional flow of liquid between the tank 31 and the extension-side chamber R1, but when the pressure on the tank 31 side of the cylinder-side passage 34b is lower than the pressure on the pump 32 side of the cylinder-side passage 34b, the operated check valve 39 functions as a normal check valve that allows liquid to flow from the tank 31 to the extension-side chamber R1 through the cylinder-side passage 34b in the main passage 34, but blocks liquid from the extension-side chamber R1 to the tank 31. Thus, the operated check valve 39 functions as a normal check valve when the pump 32 is rotated forward, but when the pump 32 is rotated reversely, the pressure on the tank 31 side of the cylinder-side passage 34b is higher than the pressure on the pump 32 side of the cylinder-side passage 34b, so the operated check valve 39 opens to allow bidirectional flow of liquid.

[0053] A check valve 40 and an orifice 41 are provided in parallel in the cylinder-side passage 34b of the main passage 34, closer to the extension-side chamber R1 than the operated check valve 39. The check valve 40 allows liquid to flow through the cylinder-side passage 34b only in the direction from the tank 31 to the extension-side chamber R1, and prevents liquid from flowing in the opposite direction. The orifice 41 provides resistance to the flow of liquid passing through it.

[0054] One end of the cylinder relief passage 35 is connected to the tank 31, and the other end is connected to the cylinder-side passage 34b of the main passage 34, between the operated check valve 39 and the check valve 40. Therefore, the cylinder relief passage 35 is always connected to the expansion-side chamber R1 through the orifice 41 of the cylinder-side passage 34b, and connects the tank 31 and the expansion-side chamber R1. In addition, a cylinder-side relief valve 42 is provided in the cylinder relief passage 35. When the pressure in the expansion-side chamber R1 exceeds a normally allowable pressure range and becomes abnormally high, the cylinder-side relief valve 42 opens to allow fluid to flow from the expansion-side chamber R1 to the tank 31, thereby preventing the pressure in the expansion-side chamber R1 from becoming abnormally high.

[0055] One end of the pump relief passage 36 is connected to the tank 31, and the other end is connected to the cylinder-side passage 34b of the main passage 34, on the directional control valve 38 side relative to the operate check valve 39. A pump-side relief valve 43 is provided midway through the pump relief passage 36. When the pump 32 rotates forward and the pressure on the expansion-side chamber R1 side of the cylinder-side passage 34b increases and exceeds a normally allowable pressure range, the pump-side relief valve 43 opens to allow fluid to flow from the pump 32 toward the tank 31, thereby preventing the pressure in the cylinder-side passage 34b from becoming abnormally high.

[0056] One end of the pump relief passage 37 is connected to the tank 31, and the other end is connected to a portion of the cylinder-side passage 34b between the directional control valve 38 and the pump 32. A pump-side relief valve 44 is provided midway through the pump relief passage 37. When the pump 32 rotates in reverse and the pressure in the cylinder-side passage 34b on the tank 31 side of the pump 32 rises and exceeds a normally allowable pressure range, the pump-side relief valve 44 opens to allow the flow of liquid from the pump 32 to the tank 31, thereby preventing the pressure in the cylinder-side passage 34b from becoming abnormally high.

[0057] The pump unit 30 configured in this manner is connected to the link rod cylinder 20 by a flexible hose (not shown) that forms the main passage 34, and is installed in the vehicle body B of the saddle-riding type vehicle V. By installing the pump unit 30, which requires a drive source, in the vehicle body B in this manner, it becomes easy to route the wiring for supplying electricity to the pump 32, and the vehicle height control device 1A can be easily installed in the saddle-riding type vehicle V.

[0058] Furthermore, in this embodiment, the extension-side chamber R1 of the link rod cylinder 20 and the tank 31 are connected by a main passage 34, and a flexible hose is connected to a passage 23a that is provided in the rod 23 of the link rod cylinder 20 and that communicates with the extension-side chamber R1. By providing the passage 23a in the rod 23 in this way, the flexible hose can be connected to the tip side of the rod 23 that does not interfere with the rod guide 24 when the link rod cylinder 20 strokes, so the flexible hose does not get in the way when the link rod cylinder 20 strokes, and the stroke length is not sacrificed. Note that a flexible hose may be connected to the outer periphery of the extension-side chamber R1 of the cylinder 21 to supply or discharge liquid into the extension-side chamber R1, but since it is necessary to avoid the range in which the piston 22 slides, the overall length of the link rod cylinder 20 would be longer to ensure the stroke length of the link rod cylinder 20.

[0059] The operation of the actuator 10 configured as described above will now be described. When the pump 32 is driven to rotate in the forward direction, the pump 32 discharges fluid toward the extension-side chamber R1, increasing the pressure on the extension-side chamber R1 side of the cylinder-side passage 34b and switching the directional control valve 38 to the supply position 38c. This connects the tank-side passage 34a and the cylinder-side passage 34b and closes the discharge passage 45, causing the pump 32 to suck fluid from the tank 31 and discharge it into the extension-side chamber R1. The fluid discharged from the pump 32 pushes open the operated check valve 39 and the check valve 40 and moves into the extension-side chamber R1. This supply of fluid to the extension-side chamber R1 pushes the piston 22 to move leftward in FIG. 4, expanding the extension-side chamber R1, and the rod 23 enters the cylinder 21, causing the link rod cylinder 20 to contract.

[0060] When the link rod cylinder 20 contracts, the link 2 rotates counterclockwise when viewed from the left side of the vehicle body B, pushing up the lower end of the shock absorber D and increasing the vehicle height. When increasing the vehicle height, if an excessive amount of liquid is supplied from the pump 32 to the expansion-side chamber R1 and the pressure in the expansion-side chamber R1 becomes excessive, the pump-side relief valve 43 opens and allows the excess liquid to be returned to the tank 31 via the pump relief passage 36. Therefore, when the pump 32 is rotated forward, the expansion-side chamber R1 does not become abnormally high pressure, and the actuator 10 is protected.

[0061] When the drive of pump 32 in the forward rotation direction is stopped, the pressure pressing valve element 38a to assume supply position 38c decreases, causing directional control valve 38 to assume shutoff position 38b, and main passage 34 and discharge passage 45 are shut off. The vehicle weight acts on link rod cylinder 20 via shock absorber D and link 2, urging it in the extension direction, but the liquid in extension-side chamber R1 cannot move to tank 31 via main passage 34 because operate check valve 39 is closed, and link rod cylinder 20 enters a locked state in which it cannot extend or retract. When link rod cylinder 20 enters a state in which it cannot extend or retract, the vehicle height of saddle-ride type vehicle V is maintained.

[0062] When the directional control valve 38 is in the shutoff position 38b and the link rod cylinder 20 is in a locked state, if the pressure in the extension-side chamber R1 of the link rod cylinder 20 becomes high above the normal range due to a rise in temperature or excessive vibration being input to the wheel W while the saddle-riding type vehicle V is traveling, the cylinder-side relief valve 42 opens and the cylinder relief passage 35 is opened, so that the liquid in the extension-side chamber R1 passes through the orifice 41 and the cylinder-side relief valve 42 and moves to the tank 31. Therefore, the pressure in the extension-side chamber R1 of the link rod cylinder 20 does not become abnormally high, and the actuator 10 is protected. Even when the cylinder-side relief valve 42 opens, the liquid in the extension-side chamber R1 moves to the tank 31 through the resistance of the orifice 41. This slows the extension of the link rod cylinder 20, preventing a sudden drop in vehicle height and mitigating sudden changes in the posture of the saddle-riding type vehicle V, preventing interference with traveling.

[0063] Next, when the pump 32 is driven to rotate in the reverse direction, the pump 32 discharges liquid toward the tank 31, causing the pressure on the tank 31 side of the cylinder-side passage 34b to rise, causing the directional control valve 38 to switch to the discharge position 38d and forcibly opening the operate check valve 39. This then connects the tank-side passage 34a to the discharge passage 45, and the extension-side chamber R1 is connected to the tank 31 through the discharge passage 45 and the tank-side passage 34a. The link rod cylinder 20 is always biased in the extension direction by the vehicle weight via the shock absorber D and the link 2, so that liquid pushed out from the extension-side chamber R1 by the movement of the piston 22 to the right in FIG. 4 relative to the cylinder 21 passes through the orifice 41, the operate check valve 39, and the directional control valve 38 and moves to the tank 31, causing the link rod cylinder 20 to perform an extension operation.

[0064] When the link rod cylinder 20 extends, the link 2 rotates clockwise when viewed from the left side of the vehicle body B, lowering the bottom end of the shock absorber D and therefore lowering the vehicle height. When lowering the vehicle height, fluid is discharged from the pump 32 to the directional control valve 38 side of the cylinder-side passage 34b, and if the pressure in the cylinder-side passage 34b becomes excessive, the pump-side relief valve 44 opens and allows the fluid to be returned to the tank 31 via the pump relief passage 37. Therefore, when the pump 32 is rotated in the reverse direction, the pressure in the cylinder-side passage 34b does not become abnormally high, and the actuator 10 is protected.

[0065] When the drive of pump 32 in the reverse direction is stopped, the pressure pressing valve element 38a to assume shut-off position 38b decreases, causing directional control valve 38 to assume shut-off position 38b and shutting off main passage 34. Therefore, actuator 10 can maintain vehicle height by locking link rod cylinder 20 so that it cannot extend or retract.

[0066] The actuator 10 configured as described above is controlled by a controller C1. The controller C1 has a sensor that monitors the stroke of the link rod cylinder 20, and controls the vehicle height while monitoring the stroke displacement of the link rod cylinder 20. When the speed of the saddle riding type vehicle V falls below a preset low speed, the controller C1 drives the actuator 10 to lower the vehicle height until it reaches a predetermined stationary vehicle height that ensures easy foot reach when the vehicle is stopped, and when the speed of the saddle riding type vehicle V exceeds the low speed, the controller C1 drives the actuator 10 to raise the vehicle height from the stationary vehicle height to a running vehicle height that is suitable for driving. Note that a switch that can be operated by a vehicle occupant and that can selectively rotate the pump 32 forward, reverse, or stop it may be provided on the saddle riding type vehicle V, so that the vehicle occupant can operate the actuator 10 to adjust the vehicle height to a desired vehicle height.

[0067] As described above, actuator 10 of vehicle height control device 1A in the first modified example of this embodiment includes link rod cylinder 20 having cylinder 21, piston 22 inserted into cylinder 21 so as to be axially movable, and rod 23 inserted into cylinder 21 so as to be axially movable and connected to piston 22, tank 31 for storing liquid, pump 32, and pump unit 30 having hydraulic circuit 33 that can be switched between a state in which pump 32 supplies liquid from tank 31 to link rod cylinder 20, a state in which liquid is discharged from link rod cylinder 20 to tank 31, and a state in which the connection between link rod cylinder 20 and tank 31 is cut off.

[0068] With vehicle height adjustment device 1A configured in this manner, vehicle height can be easily adjusted by utilizing actuator 10 that hydraulically drives link rod cylinder 20 of a simple structure, and vehicle height can be maintained by disconnecting link rod cylinder 20 from tank 31, which saves energy since no power is consumed to maintain vehicle height.

[0069] Furthermore, the vehicle height adjustment device 1A of this embodiment is set up so that when the link 2 rotates counterclockwise relative to the vehicle body B as viewed from the left side, the vehicle body B rises, and the actuator 10 is configured so that when liquid is supplied by the pump unit 30 to the extension side chamber R1 defined by the piston 22 within the cylinder 21, the link rod cylinder 20 is contracted, causing the link 2 to rotate counterclockwise as viewed from the left side of the vehicle body B.

[0070] According to the vehicle height control device 1A configured in this manner, the pump unit 30 can adjust the vehicle height by supplying and discharging fluid to the extension-side chamber R1 of the link rod cylinder 20, which simplifies the structure of the link rod cylinder 20 and the configuration of the hydraulic circuit 33 in the pump unit 30, thereby reducing manufacturing costs.

[0071] Furthermore, according to the vehicle height control device 1A of this embodiment, since the pump unit 30 is attached to the vehicle body B, it is easy to route the wiring for supplying electricity to the pump 32, and the vehicle height control device 1A can be easily installed on the saddle-type vehicle V.

[0072] The pump unit 30 of this embodiment includes a tank 31 that stores liquid, a pump 32, and a hydraulic circuit 33. The hydraulic circuit 33 includes a main passage 34 that connects the tank 31 and the link rod cylinder 20 and in which the pump 32 is installed, a direction switching valve 38 and an operated check valve 39 that are provided in series in the main passage 34 and closer to the extension-side chamber R1 than the pump 32, and a discharge passage 45 having one end connected to the direction switching valve 38 and the other end connected in the main passage 34 between the pump 32 and the operated check valve 39. The direction switching valve 38 is a three-position, three-port valve. The operated check valve 39 has a blocking position 38b that blocks the main passage 34 and the discharge passage 45 when the pump 32 is stopped, a supply position 38c that connects the main passage 34 and closes the discharge passage 45 when the pump 32 is rotating forward, and a discharge position 38d that connects the tank side of the main passage 34 and the discharge passage 45 when the pump 32 is rotating backward and blocks the cylinder side of the main passage 34. The operated check valve 39 only allows liquid to flow from the tank 31 to the extension-side chamber R1, but allows liquid to flow from the extension-side chamber R1 to the tank 31 only when the pump 32 is rotating backward.

[0073] With vehicle height control device 1A configured in this manner, the vehicle height can be adjusted by switching directional control valve 38 and operate check valve 39 depending on the drive state of pump 32 to supply fluid to link rod cylinder 20 and discharge fluid from link rod cylinder 20, eliminating the need for a drive source other than pump 32. Therefore, vehicle height control device 1A of the present embodiment is lightweight, compact, and can be manufactured at low cost.

[0074] In addition to the above configuration, hydraulic circuit 33 in vehicle height control device 1A of this embodiment further includes a check valve 40 and an orifice 41 in parallel on the link rod cylinder 20 side of operated check valve 39 in main passage 34, and check valve 40 allows only the flow of liquid from tank 31 to link rod cylinder 20.

[0075] With vehicle height control device 1A configured in this manner, when raising the vehicle height, liquid passes through check valve 40 and can be quickly supplied from pump 32 to link rod cylinder 20, allowing the vehicle height to be raised quickly, and when lowering the vehicle height, liquid passes through orifice 41 and moves from link rod cylinder 20 to tank 31, slowing the rate at which the vehicle height is lowered and preventing a sudden drop in vehicle height.

[0076] Furthermore, in addition to the above configuration, hydraulic circuit 33 in vehicle height control device 1A of the present embodiment further includes a cylinder relief passage 35 connecting link rod cylinder 20 and tank 31, and a cylinder-side relief valve 42 provided midway through cylinder relief passage 35. With vehicle height control device 1A configured in this manner, when the pressure in link rod cylinder 20 becomes high beyond the normal range due to a rise in temperature or excessive vibration being input to wheel W while saddle-ride type vehicle V is traveling, cylinder-side relief valve 42 opens to open cylinder relief passage 35, so that the pressure in link rod cylinder 20 does not become abnormally high and actuator 10 can be protected.

[0077] Furthermore, the hydraulic circuit 33 of the pump unit 30 is not limited to the above-described configuration as long as it is capable of supplying liquid from the pump 32 to the link rod cylinder 20 and discharging liquid from the link rod cylinder 20.

[0078] In the vehicle height adjustment device 1 and vehicle height adjustment device 1A described above, when the link 2 rotates counterclockwise around the connection point to the vehicle body B as viewed from the left side, the support position of the shock absorber D rises and the vehicle height increases. However, as in the vehicle height adjustment device 1B shown in Figure 5, when the link 2 rotates clockwise around the connection point to the vehicle body B, the support position of the shock absorber D rises and the vehicle height increases.

[0079] In this way, when the actuator 10 and shock absorber D are attached to the link 2, when the actuator 10 is extended, the link 2 rotates clockwise when viewed from the left side of the vehicle body B, raising the support position of the lower end of the shock absorber D and increasing the vehicle height, and when the actuator 10 is contracted, the link 2 rotates counterclockwise when viewed from the left side of the vehicle body B, lowering the support position of the lower end of the shock absorber D and decreasing the vehicle height.

[0080] Therefore, in this case, fluid is supplied from the pump unit 30 to the link rod cylinder 20 when the link rod cylinder 20 is extended, and fluid is discharged from the link rod cylinder 20 when the link rod cylinder 20 is retracted. To extend the link rod cylinder 20, fluid must be supplied to the compression-side chamber R2, so as shown in FIG. 6, the main passage 34 of the pump unit 30 can be connected to the compression-side chamber R2. In this case, if the main passage 34 communicates with the compression-side chamber R2 via a passage 23b that opens from the base end of the rod 23 and leads to the tip of the rod 23, it is easy to ensure the stroke length of the link rod cylinder 20 and the overall length of the link rod cylinder 20 does not need to be long. The main passage 34 may also be connected to the compression-side chamber R2 via a hole provided in the cylinder 21 of the link rod cylinder 20.

[0081] The configuration of the pump unit 30 is the same as that described above, and when the pump 32 is rotated forward, fluid is supplied to the compression-side chamber R2, causing the link rod cylinder 20 to extend, rotating the link 2 clockwise as viewed from the left side of the vehicle body B, and raising the vehicle height. In the mounted state shown in FIG. 5 , the link rod cylinder 20 is urged in the contraction direction by the vehicle weight via the link 2, so when the pump 32 is rotated backward, fluid is discharged from the compression-side chamber R2 to the tank 31, causing the link 2 to contract, rotating the link 2 counterclockwise as viewed from the left side of the vehicle body B, and lowering the vehicle height. Stopping the pump 32 also prevents fluid from flowing between the compression-side chamber R2 of the link rod cylinder 20 and the pump unit 30, allowing the vehicle height to be maintained. In this case, the extension-side chamber R1 of the link rod cylinder 20 may be left open to the atmosphere, and only a dust seal that slides against the outer periphery of the rod 23 to prevent water and dust from entering the extension-side chamber R1 may be installed in the rod guide 24.

[0082] As described above, the vehicle height adjustment device 1B of this embodiment is set up so that when the link 2 rotates clockwise relative to the vehicle body B as viewed from the left side, the vehicle body B rises, and the actuator 10 is configured so that when liquid is supplied by the pump unit 30 to the compression side chamber R2 defined by the piston 22 within the cylinder 21, the link rod cylinder 20 is extended, causing the link 2 to rotate clockwise as viewed from the left side of the vehicle body B.

[0083] According to vehicle height control device 1B configured in this manner, pump unit 30 can adjust vehicle height by supplying or discharging fluid to compression-side chamber R2 of link rod cylinder 20, which simplifies the structure of link rod cylinder 20 and the configuration of hydraulic circuit 33 in pump unit 30 and reduces manufacturing costs. Also, since a seal for sealing extension-side chamber R1 of link rod cylinder 20 is not required, link rod cylinder 20 can be manufactured more inexpensively, and since the entire cross-sectional area of ​​piston 22 is used as a pressure-receiving area to generate a large thrust, the discharge pressure of pump 32 can be lower accordingly, allowing the motor that drives pump 32 to be made smaller.

[0084] In the vehicle height control device 1B shown in FIG. 5, the vehicle height is adjusted by the actuator 10 that utilizes hydraulic pressure, but the actuator 10 may be replaced by an electric actuator 3.

[0085] Although the preferred embodiment of the present invention has been described in detail, modifications, variations and changes can be made thereto without departing from the scope of the appended claims. [Explanation of symbols]

[0086] 1, 1A, 1B... Vehicle height adjustment device, 2... Link, 3, 10... Actuator, 3a... Telescopic body, 3b... Screw shaft, 3c... Nut, 20... Link rod cylinder, 21... Cylinder, 22... Piston, 23... Rod, 30... Pump unit, 31... Tank, 32... Pump, 33... Hydraulic circuit, A... Swing arm, B... Vehicle body, R1... Extension side chamber, R2... Compression side chamber, V... Saddle-ride type vehicle

Claims

1. a link that is attached to a vehicle body of a saddle-ride type vehicle so as to be rotatable about an axis extending in the left-right direction of the vehicle body and that is attached to a shock absorber that is connected to the vehicle body so as to be rotatable about an axis extending in the left-right direction of the vehicle body; an actuator having one end rotatably connected to the link and the other end rotatably attached to a swing arm that is swingably attached to the vehicle body and is capable of expanding and contracting by itself; A vehicle height adjustment device characterized by:

2. The actuator is an expandable body including a screw shaft and a nut attached to the screw shaft, the expandable body expanding and contracting by rotation of either the screw shaft or the nut; a motor that drives one of the screw shaft and the nut, The screw shaft and the nut are capable of self-locking, in which one of the screw shaft and the nut does not rotate when the other of the screw shaft and the nut moves in the axial direction.

2. The vehicle height adjusting device according to claim 1.

3. The actuator is a link rod cylinder including a cylinder, a piston inserted into the cylinder so as to be axially movable, and a rod inserted into the cylinder so as to be axially movable and connected to the piston; The pump unit includes a tank for storing liquid, a pump, and a hydraulic circuit that can be switched among a state in which the pump supplies liquid from the tank to the link rod cylinder, a state in which the pump discharges liquid from the link rod cylinder to the tank, and a state in which the link rod cylinder is disconnected from the tank.

2. The vehicle height adjusting device according to claim 1.

4. When the link rotates counterclockwise relative to the vehicle body as viewed from the left side, the vehicle body is set to rise, When the pump unit supplies fluid to an extension-side chamber defined by the piston in the cylinder, the actuator contracts the link rod cylinder, thereby rotating the link forward counterclockwise when viewed from the left side of the vehicle body.

4. The vehicle height adjusting device according to claim 3.

5. When the link rotates clockwise relative to the vehicle body as viewed from the left side of the vehicle body, the vehicle body is set to rise, When the pump unit supplies fluid to a compression side chamber defined by the piston in the cylinder, the actuator extends the link rod cylinder, thereby rotating the link clockwise when viewed from the left side of the vehicle body.

4. The vehicle height adjusting device according to claim 3.

6. The pump unit is attached to the vehicle body.

4. The vehicle height adjusting device according to claim 3.

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