JP2020118206A - Suspension device - Google Patents

Abstract

A suspension device having a mechanism for adjusting vehicle height is simplified. A suspension device includes a spring disposed between a vehicle body and a wheel, a spring support portion that supports the spring and moves the spring according to the liquid in a liquid storage chamber that stores the liquid, and a suspension device that stores the liquid. A cylinder to accommodate, a rod provided with a piston and moving in the axial direction of the cylinder, a moving part arranged on the side of the rod on which the piston is provided and moving together with the rod, and a moving part provided at the end of the cylinder and moved A compression chamber forming portion that forms a compression chamber in which liquid to be stored is compressed by the moving portion, and a circulation portion that circulates the liquid from the compression chamber to the liquid storage chamber. [Selection drawing] Fig. 1

Description

The present invention relates to a suspension device.

For example, in Patent Document 1, an upper spring seat having an upper end coupled to a jack-up piston is seated with an upper end of a suspension spring for supporting a vehicle body, and a hollow hole formed in a central portion of an upper end of a piston rod is disclosed. Disclosed is a vehicle height adjusting device having a self-level adjusting function, characterized in that an upper spring seat is pushed down via a jack-up piston when an inner rod is fitted.

JP, 9-133173, A

By the way, the height of the vehicle changes according to the load amount, which is the weight of the person riding in the vehicle, the luggage loaded, and the like. Therefore, for example, in order to maintain the vehicle height above a certain level, it is necessary to provide the suspension device with a mechanism for adjusting the vehicle height. However, if the suspension device is simply provided with a mechanism for adjusting the vehicle height, the number of parts is increased and the device is complicated.
An object of the present invention is to simplify a suspension device having a mechanism for adjusting a vehicle height.

Based on such an object, the present invention provides a spring arranged between a vehicle body and a wheel, a spring support portion that supports the spring and moves the spring according to the liquid in a liquid storage chamber that stores the liquid, A cylinder that contains liquid, a rod that is provided with a piston and moves in the axial direction of the cylinder, a moving portion that is arranged on the side of the rod where the piston is provided and that moves with the rod, and a moving portion that is provided at the end of the cylinder The suspension device includes a compression chamber forming portion that forms a compression chamber that compresses the liquid stored by the moving portion, and a circulation portion that circulates the liquid from the compression chamber to the liquid storage chamber.

According to the present invention, the suspension device having the mechanism for adjusting the vehicle height can be simplified.

1 is an overall view of a suspension device according to a first embodiment. It is a fragmentary sectional view of a damper part of a 1st embodiment. (A) And (B) is explanatory drawing of the adjustment valve part of 1st Embodiment. (A) And (B) is explanatory drawing of operation|movement of the damper part in a high vehicle height state. It is explanatory drawing of the oil lock state of the damper part of 1st Embodiment. (A) And (B) is explanatory drawing of operation|movement of the damper part in a low vehicle height state. It is explanatory drawing of operation|movement of a damper part when the oil pressure of a jack chamber becomes excessive. It is explanatory drawing of operation|movement of a damper part when the load capacity becomes small. It is a fragmentary sectional view of a damper part of a 2nd embodiment.

Hereinafter, this embodiment will be described in detail with reference to the accompanying drawings.

<First Embodiment>
FIG. 1 is an overall view of the suspension device 1 of the first embodiment.

As shown in FIG. 1, the suspension device 1 of the first embodiment absorbs relative vibration between a vehicle body such as a four-wheeled vehicle and wheels such as tires, and a vibration of the spring portion 1A. It has the damper part 1B which attenuates. Further, in the suspension device 1 of the first embodiment, the spring portion 1A and the damper portion 1B are arranged not on the same axis but on different axes in parallel.

In the following description, the longitudinal direction of each of the spring portion 1A and the damper portion 1B arranged in parallel is referred to as "axial direction". The lower side in the axial direction is referred to as "one end side", and the upper side is referred to as "the other end side". The left-right direction of each of the spring portion 1A and the damper portion 1B is referred to as "radial direction". Then, in the radial direction, the central axis side is referred to as “radial direction inner side”, and the side away from the central axis is referred to as “radial direction outer side”. Furthermore, the rotation direction centering on each axial direction of the spring portion 1A and the damper portion 1B is referred to as "circumferential direction".

Here, first, an outline of the suspension device 1 of the first embodiment will be described.
By the way, in the suspension device 1, the amplitude amount greatly changes depending on the condition of the road surface on which the vehicle travels. For example, when the wheel contacts a relatively large obstacle such as a curb, the suspension device 1 contracts greatly. When the suspension device 1 is greatly contracted, it is necessary to suppress the collision between the rod 30 of the damper portion 1B and the cylinder portion 20 (described later). The damper unit 1B of the first embodiment has an oil lock mechanism unit 50 (described later) that forms an oil lock state that suppresses collision between the rod 30 and the cylinder unit 20 by compressing oil.

In addition, the height of the vehicle body changes depending on the number of passengers on the vehicle and the amount of loaded items such as luggage. For example, when the load capacity is large, the spring portion 1A and the damper portion 1B are in a contracted state, and the vehicle body sinks and the vehicle height becomes relatively low (hereinafter referred to as a low vehicle height state). On the other hand, when the load capacity is small, the spring portion 1A and the damper portion 1B are in an extended state, the vehicle body is raised, and the vehicle height is relatively high (hereinafter referred to as a high vehicle height state).
The suspension device 1 of the first embodiment has a vehicle height adjustment mechanism that lifts the vehicle body in the low vehicle height state to bring it into the high vehicle height state. In particular, the suspension device 1 of the first embodiment adjusts the vehicle height by pumping oil using the oil lock mechanism section 50 described above.

Specifically, as shown in FIG. 1, the suspension device 1 of the first embodiment supports a coil spring 11 (an example of a spring) arranged between a vehicle body and a wheel, and the coil spring 11, and A jack portion 14 (an example of a spring support portion) that moves the coil spring 11 according to oil in a jack chamber 130 (an example of a liquid storage chamber) that stores oil (an example of a liquid); a cylinder 21 that stores the oil; A rod 30 that is provided with a piston portion 40 (an example of a piston) and moves in the axial direction of the cylinder 21, and an oil lock piece 51 (moving portion) that is arranged on the side of the rod 30 where the piston portion 40 is provided and that moves with the rod 30. And an oil lock collar 54 (an example of a compression chamber) that is provided at the end of the cylinder 21 and forms an oil lock chamber 500 (an example of a compression chamber) in which the oil stored by the moving oil lock piece 51 is compressed. (An example of a portion) and a flow passage forming portion 55 (an example of a circulation portion) that allows oil to flow from the oil lock chamber 500 to the jack chamber 130.
Hereinafter, each configuration will be described in detail.

[Spring part 1A]
As shown in FIG. 1, the spring portion 1A includes a coil spring 11 that expands and contracts, a spring receiving portion 12 that receives the coil spring 11, a jack cylinder 13 that stores oil, and a jack portion 14 that moves the spring receiving portion 12. With.

The coil spring 11 is formed by spirally winding a metallic wire material such as iron. The coil spring 11 according to the first embodiment has one end contacting the spring receiving portion 12 and the other end contacting the vehicle body (not shown).
The spring receiving portion 12 has one end contacting the jack portion 14 and the other end receiving the coil spring 11.

The jack cylinder 13 has a bottomed cylindrical shape having a bottom portion on one end side and an opening on the other end side. The jack cylinder 13 also has a through hole 13H that allows oil to flow into and out of the jack cylinder 13, and a connecting portion 13J for connecting the through hole 13H and the oil pipe 100.

The jack portion 14 is provided inside the jack cylinder 13 so as to be movable in the axial direction of the jack cylinder 13. In the first embodiment, the jack cylinder 13 and the jack portion 14 form a jack chamber 130 that is a space for storing oil. Then, the jack portion 14 moves in accordance with the inflow and outflow of oil in the jack chamber 130, thereby moving the coil spring 11 in the axial direction via the spring receiving portion 12.

[Damper section 1B]
The damper portion 1B includes a cylinder portion 20 that contains oil, a rod 30 that is slidably inserted into the cylinder portion 20 at the other end side of the cylinder portion 20, and a piston that is provided at one end portion of the rod 30. And a section 40. In addition, the damper portion 1B is provided with an oil lock mechanism portion 50 that absorbs an impact when the damper portion 1B is compressed most, a bottom valve portion 60 provided at an end portion on one end side, and an excessive oil pressure in the jack chamber 130. It has a blow valve part 70 for letting it escape and an adjusting valve part 80 for adjusting the oil pressure in an oil lock chamber 500 (described later) of the oil lock mechanism part 50.

(Cylinder part 20)
The cylinder portion 20 includes a cylindrical cylinder 21, a damper case 22 provided on the outer side in the radial direction of the cylinder 21, another end side structure portion 23 provided at the other end of the cylinder portion 20, and a cylinder portion 20. One end side structure portion 24 provided at one end side end portion of the.

In the cylinder 21, the opening on the other end side is closed by the other end side structure portion 23, and the one end side opening part is closed by the one end side structure portion 24. The cylinder 21 contains oil inside. Further, the cylinder 21 accommodates the piston portion 40 slidably in the axial direction on the inner side in the radial direction.
The damper case 22 forms a reservoir chamber R with the cylinder 21. The reservoir chamber R stores the oil in the cylinder 21 and discharges the accumulated oil into the cylinder 21.

The other end side structure portion 23 includes a rod guide 231 held by the damper case 22, a bush 232 that slidably supports the rod 30, and an oil seal 233 that seals between the damper case 22 and the rod 30. With.

The one end side structure portion 24 closes one end side of the damper case 22. Further, in the first embodiment, the wheel-side connecting portion 25 for connecting to the wheel-side component is attached to one end side of the one-end side structure portion 24. Further, the one end side structure portion 24 accommodates the bottom valve portion 60, the blow valve portion 70, and the adjustment valve portion 80 on the inner side in the radial direction.
In the first embodiment, the oil storage space between the blow valve portion 70 and the adjustment valve portion 80 on the radially inner side of the one end side structure portion 24 is referred to as a first bottom chamber 241. Further, in the first embodiment, the oil storage space between the inner side in the radial direction of the one end side structure portion 24 and the adjustment valve portion 80 is referred to as a second bottom chamber 242.

Further, the one end side structure portion 24 has a through hole 24H that allows oil to flow in and out between the jack chamber 130 and the second bottom chamber 242, and a connection portion for connecting the through hole 24H and the oil pipe 100. 24J. Then, the spring portion 1A and the damper portion 1B of the first embodiment can mutually pass oil through the oil pipe 100.

(Rod 30)
The rod 30 is a rod-shaped member that uses a metal such as iron as a material and extends in the axial direction. Further, the rod 30 of the first embodiment may be hollow or solid. However, the rod 30 of the present embodiment is formed solid and is not machined radially inward (inside).
The rod 30 has one end-side mounting portion 31 for mounting the piston portion 40 at one end-side end, and the other end-side mounting portion 32 for mounting at the other end-side end in the vehicle body-side connecting portion 26. have.

(Piston part 40)
FIG. 2 is a partial cross-sectional view of the damper portion 1B of the first embodiment.
As shown in FIG. 2, the piston portion 40 includes a piston body 42 having a compression side piston flow passage 411 and an expansion side piston flow passage 412, a compression side damping valve portion 43 provided on the other end side of the piston body 42, and a piston body. An expansion-side damping valve portion 44 provided on one end side of 42.
The piston portion 40 divides the oil in the cylinder 21 into a first oil chamber Y1 on one end side and a second oil chamber Y2 on the other end side.

The compression-side piston flow passage 411 and the expansion-side piston flow passage 412 can be connected to the first oil chamber Y1 at one end side and can be connected to the second oil chamber Y2 at the other end side, respectively.
The compression side damping valve portion 43 and the expansion side damping valve portion 44 can be configured by using a plurality of thin disc-shaped metal plates. Then, the compression side damping valve portion 43 always opens the other end side of the expansion side piston flow channel 412 and opens and closes the other end side of the compression side piston flow channel 411. Further, the expansion side damping valve portion 44 opens and closes one end side of the expansion side piston flow channel 412 and always opens one end side of the compression side piston flow channel 411.

(Oil lock mechanism section 50)
The oil lock mechanism portion 50 is provided on an end portion of the rod 30 on one end side, a check valve 52 provided on the inner side in the radial direction of the oil lock piece 51, and an outer side in the radial direction of the oil lock piece 51. And a seal member 53 that is provided. Further, the oil lock mechanism section 50 includes an oil lock collar 54 fixed to one end of the cylinder section 20 and a flow passage forming section 55 forming a flow path communicating with the jack chamber 130.

The oil lock piece 51 is fixed to one end of the rod 30 by screwing. Therefore, the oil lock piece 51 moves together with the rod 30 when the rod 30 moves in the axial direction. Then, the oil lock piece 51 enters the oil lock collar 54 when the rod 30 comes closest to the end portion on the one end side of the cylinder portion 20. In the first embodiment, the space formed by the oil lock piece 51 and the oil lock collar 54 with the oil lock piece 51 inserted inside the oil lock collar 54 in the radial direction is called an oil lock chamber 500. The oil lock chamber 500 is not always formed, such as when the oil lock piece 51 is located on the other end side, but is formed by moving the oil lock piece 51 to the end portion on the one end side.

The oil lock piece 51 also has an axial flow passage 511 formed in the axial direction and a radial flow passage 512 formed in the radial direction. The axial flow passage 511 communicates with the radial flow passage 512 at the other end side, and one end side is open toward the oil lock collar 54. The radial passage 512 communicates with the first oil chamber Y1 on the outer side in the radial direction, and communicates with the axial passage 511 on the inner side in the radial direction. Further, the radial passage 512 is arranged so as to be located outside the oil lock collar 54 even when the oil lock piece 51 enters the oil lock collar 54.

The oil lock piece 51 of the first embodiment also has a function of fixing the piston portion 40 to the rod 30.

The check valve 52 includes a lift valve 521 arranged on one end side of the axial flow path 511 and a coil spring 522 arranged on one end side of the lift valve 521. The check valve 52 allows the flow of oil from the other end of the axial flow passage 511 where the radial passage 512 is provided to the one end where the oil lock collar 54 is provided.
On the other hand, the check valve 52 limits the flow of oil from one end side to the other end side in the axial flow path 511. Therefore, when the oil lock piece 51 is inserted into the oil lock collar 54, the oil in the oil lock chamber 500 is separated from the oil contained in the cylinder 21.

The seal member 53 is a ring-shaped component. Then, the seal member 53 seals between the oil lock piece 51 and the oil lock collar 54 in a state where the oil lock piece 51 enters the oil lock collar 54 (see FIG. 5 described later).

The oil lock collar 54 has an inner diameter slightly larger than the outer diameter of the oil lock piece 51. The oil lock collar 54 is open toward the other end so that the oil lock piece 51 can enter. The oil lock collar 54 of the first embodiment is formed such that the inner diameter at the end portion on the other end side gradually increases toward the other end side on which the oil lock piece 51 is provided.
Further, the oil lock collar 54 communicates with the flow passage forming portion 55 at one end side.

A flange portion 55F formed on the other end side of the flow passage forming portion 55 is hooked on the oil lock collar 54, and is screwed to the blow valve portion 70 at one end side. The flow passage forming portion 55 has a flow passage 551 extending in the axial direction. The flow passage 551 communicates with the oil lock chamber 500 of the oil lock collar 54 on the other end side and communicates with the first bottom chamber 241 on the one end side.

(Bottom valve part 60)
The bottom valve part 60 includes a valve seat 61, a first valve part 62 provided on one end side of the valve seat 61, and a second valve part 63 provided on the other end side of the valve seat 61.

The valve seat 61 is a disk-shaped member. The valve seat 61 has a compression-side flow passage 611 that penetrates in the axial direction and an expansion-side flow passage 612 that is formed outside the compression-side flow passage 611 in the radial direction and penetrates in the axial direction. The pressure side flow passage 611 has one end facing the first valve portion 62 and the other end communicating with the first oil chamber Y1. Further, one end of the extension side flow channel 612 communicates with the reservoir chamber R and the other end thereof faces the second valve portion 63.

Each of the first valve portion 62 and the second valve portion 63 can be configured by using a plurality of thin disc-shaped metal plates. The first valve portion 62 opens and closes one end side of the compression side flow channel 611 and always opens one end side of the expansion side flow channel 612. Further, the second valve portion 63 has a flow passage port 63Y penetrating in the axial direction at a position facing the pressure side flow passage 611. Then, the second valve portion 63 opens and closes the other end side of the expansion side flow passage 612 and always opens the other end side of the compression side flow passage 611.

(Blow valve part 70)
The blow valve portion 70 has a valve seat 71 and a blow valve 72 provided on the other end side of the valve seat 71.
Then, the blow valve unit 70 sets the oil pressure in the jack chamber 130 to a pressure that enables the jack unit 14 to be lifted when pumping the oil into the jack chamber 130 by pumping in the oil lock chamber 500, and also the jack chamber 130. It prevents the oil pressure from rising excessively.

The valve seat 71 is a disk-shaped member. The valve seat 71 has a flow passage 711 that penetrates in the axial direction. One end side of the flow path 711 communicates with the first bottom chamber 241, and the other end side faces the blow valve 72.

The blow valve 72 can be configured by using a plurality of thin disk-shaped metal plates. Then, the blow valve 72 opens and closes the other end side of the flow path 711. In the first embodiment, the blow valve 72 is set so that the flow that opens the flow path 711 does not occur until the oil pressure in the jack chamber 130 lifts the jack portion 14 and compresses the coil spring 11. On the other hand, when the oil pressure in the jack chamber 130 sufficiently lifts the jack portion 14 and the coil spring 11 is in the most compressed state, the blow valve 72 has a flow that opens the flow passage 711 so that the oil pressure does not rise any further. Is set to occur. As a result, the blow valve 72 is adapted to release the oil pressure above the predetermined pressure of the oil in the jack chamber 130.

(Adjustment valve section 80)
FIG. 3 is an explanatory diagram of the adjusting valve unit 80 of the first embodiment.
As shown in FIG. 3A, the adjusting valve portion 80 has a valve seat 81 and an adjusting valve 82 provided on one end side of the valve seat 81.
Then, the adjustment valve unit 80 maintains the oil pressure in the oil lock chamber 500 of the oil lock mechanism unit 50 at or above a predetermined level. The adjusting valve unit 80 allows the oil lock mechanism unit 50 to realize an oil lock function described later. Further, the adjusting valve portion 80 acts so that pumping is performed after the oil lock function is realized.

The valve seat 81 is a disk-shaped member. The valve seat 81 has a channel 811 penetrating in the axial direction. The other end of the flow path 811 communicates with the first bottom chamber 241, and one end of the flow path 811 faces the adjustment valve 82.

The adjusting valve 82 can be configured by using a plurality of thin disk-shaped metal plates. Then, the adjustment valve 82 opens and closes the one end side of the flow path 811. In the first embodiment, the adjusting valve 82 allows the reaction pressure toward the other end of the rod 30 due to the oil pressure in the oil lock chamber 500 to be generated, and the flow path 811 is maintained until the collision of the rod 30 with the cylinder portion 20 is suppressed. It is set so that there is no flow of opening. On the other hand, the adjusting valve 82 is set to open the flow path 811 when the oil pressure in the oil lock chamber 500 becomes equal to or higher than a predetermined pressure.

As described above, in the damper portion 1B of the first embodiment, the adjustment valve 82 acts so that the oil pressure in the oil lock chamber 500 becomes equal to or higher than a predetermined pressure, thereby ensuring that the oil lock state is formed. doing. Further, the adjustment valve 82 can be easily adjusted for the oil lock such as the speed at which the oil lock state is exhibited by changing the design such as the rigidity.

Further, the adjusting valve 82 has a slit valve 821 at a position in contact with the valve seat 81. As shown in FIG. 3(B), the slit valve 821 is formed in a disc shape.
The slit valve 821 has a slit 82S (an example of a flow path hole) cut from the outside in the radial direction toward the inside in the radial direction. The slit 82S enables the oil to flow between the slit valve 821 and the flow path 811 without the slit valve 821 being deformed in the direction away from the valve seat 81. That is, the slit 82S is connected to the flow passage port of the flow passage 811 opened and closed by the slit valve 821, and the slit valve 821 does not open the flow passage port of the flow passage 811. Enable the flow of. The oil flow through the slit 82S of the slit valve 821 will be described later in detail.

In the first embodiment, the flow passage 551, the first bottom chamber 241, the flow path 811, the second bottom chamber 242, the through hole 24H, the connecting portion 24J, the oil pipe 100, the connecting portion 13J, and the through hole 13H are respectively It has a function of circulating oil from the oil lock chamber 500 to the jack chamber 130.

<Operation of suspension device 1>
Next, the operation of the suspension device 1 will be specifically described.
First, the flow of oil in the damper portion 1B in the high vehicle height state will be described.

FIG. 4 is an explanatory diagram of the operation of the damper unit 1B in the high vehicle height state.
It should be noted that FIG. 4A shows the oil flow in the extension stroke in the high vehicle height state, and FIG. 4B shows the oil flow in the compression stroke in the high vehicle height state.

In the high vehicle height state and the extension stroke, the rod 30 relatively moves in a direction away from the cylinder 21, as shown in FIG. In the example shown in FIG. 4A, the rod 30 moves toward the other end side. Then, as the piston portion 40 moves to the other end side along with the rod 30, the oil pressure in the second oil chamber Y2 increases.
In the piston part 40, the expansion side damping valve part 44, which has closed one end side of the expansion side piston flow path 412, opens the expansion side piston flow path 412. Then, the oil in the second oil chamber Y2 flows out into the first oil chamber Y1 through the expansion side piston flow path 412. The oil flow generated by the movement of the rod 30 and the piston portion 40 is throttled by the extension side piston flow path 412 and the extension side damping valve portion 44, so that a damping force is generated in the extension stroke.

Further, the piston portion 40 moves to the other end side along with the rod 30, so that the oil pressure in the second oil chamber Y2 increases and the oil pressure in the first oil chamber Y1 decreases. Further, in the extension stroke, the oil flowing from the second oil chamber Y2 into the first oil chamber Y1 is insufficient by the advancing volume of the rod 30 from the second oil chamber Y2. Therefore, in the bottom valve portion 60, the second valve portion 63 that closes the other end side of the expansion side flow passage 612 opens the expansion side flow passage 612. Then, the oil in the reservoir chamber R flows out into the first oil chamber Y1 through the expansion side flow path 612.

In the high vehicle height state and in the compression stroke, as shown in FIG. 4(B), the rod 30 relatively moves toward the cylinder 21. In the example shown in FIG. 4B, the rod 30 moves toward the one end side. Then, as the piston portion 40 moves to the one end side along with the rod 30, the oil pressure in the first oil chamber Y1 increases.
In the piston portion 40, the compression side damping valve portion 43, which has closed the other end side of the compression side piston flow passage 411, opens the compression side piston flow passage 411. Then, the oil in the first oil chamber Y1 flows out to the second oil chamber Y2 through the pressure side piston flow channel 411. The oil flow generated by the movements of the rod 30 and the piston portion 40 is throttled by the pressure side piston flow path 411 and the pressure side damping valve portion 43, so that a damping force in the compression stroke is generated.

Further, as described above, the piston portion 40 moves to the one end side along with the rod 30, so that the oil pressure in the first oil chamber Y1 increases. Further, in the compression stroke, the amount of oil that has entered the rod 30 flows out from the first oil chamber Y1 to the reservoir chamber R. A damping force in the compression stroke is also generated by restricting the oil flow generated by the movement of the rod 30 and the piston portion 40 to the pressure side flow passage 611 and the first valve portion 62.

FIG. 5: is explanatory drawing of the oil lock state of the damper part 1B of 1st Embodiment.
Next, the flow of oil when the damper portion 1B is greatly contracted in a high vehicle height state will be described.

As shown in FIG. 5, the rod 30 and the cylinder 21 relatively approach each other, and the rod 30 moves toward the end portion on the one end side of the cylinder 21. Then, the oil lock piece 51 provided at the one end of the rod 30 enters the oil lock collar 54 provided at the one end of the cylinder 21. The axial flow path 511 of the oil lock piece 51 is closed by the check valve 52. Further, the space between the oil lock piece 51 and the oil lock collar 54 is hermetically sealed by the seal member 53. As a result, the oil lock chamber 500 is formed. Furthermore, when the oil lock chamber 500 is formed, the oil lock piece 51 is pushed into the oil lock collar 54, so that the oil pressure in the oil lock chamber 500 rises at once. Then, the oil pressure of the oil lock chamber 500 acts on the end surface of the rod 30 on one end side, so that a reaction force toward the other end side is generated on the rod 30. Further, since the oil lock chamber 500 is filled with oil, the impact applied to the rod 30 is alleviated.
As described above, in the damper portion 1B of the first embodiment, by including the oil lock mechanism portion 50, even when the damper portion 1B is greatly contracted, the rod 30 is provided at the end portion on the one end side of the cylinder portion 20. Collisions are suppressed.

Next, the flow of oil in the damper portion 1B in the low vehicle height state will be described.
FIG. 6 is an explanatory diagram of the operation of the damper unit 1B in the low vehicle height state.
It should be noted that FIG. 6A shows the oil flow in the extension stroke in the low vehicle height state, and FIG. 6B shows the oil flow in the compression stroke in the low vehicle height state.

In the low vehicle height state, as shown in FIG. 6(A), the rod 30 and the cylinder 21 relatively approach each other, and the rod 30 moves toward the end portion on the one end side of the cylinder 21. Then, similarly to the oil lock state, the oil lock piece 51 provided at the one end side end portion of the rod 30 enters the oil lock collar 54 provided at the one end side end portion of the cylinder 21.

When the vehicle height is low, the rod 30 and the cylinder 21 relatively expand and contract with the oil lock piece 51 entering the oil lock collar 54. In this case, the flow of oil in the piston portion 40 and the bottom valve portion 60 is the same as that in the high vehicle height state (see FIGS. 4A and 4B) in both the extension stroke and the compression step.

Then, in the low vehicle height state and in the extension stroke, as shown in FIG. 6(A), the oil in the first oil chamber Y1 flows from the radial passage 512 into the axial passage 511, and the lift valve 521 is opened. It opens and flows into the oil lock chamber 500. After that, in the low vehicle height state and in the compression step, as shown in FIG. 6B, the oil lock piece 51 moves toward the one end side. At this time, the lift valve 521 is in a state where the axial flow path 511 is closed. Then, the oil in the oil lock chamber 500 is pressure-fed by the oil lock piece 51 and flows into the flow passage 551 and the first bottom chamber 241. Further, the oil in the first bottom chamber 241 flows through the flow path 811, the second bottom chamber 242, the through hole 24H, and the connecting portion 24J while opening the adjustment valve 82. Then, the oil flows into the jack chamber 130 through the oil pipe 100 (see FIG. 1). The jack portion 14 lifts the coil spring 11 as the amount of oil in the jack chamber 130 increases. As a result, in the first embodiment, the vehicle is lifted by the spring portion 1A and the vehicle height is increased.

Then, due to the amplitude of the damper portion 1B accompanying the traveling of the vehicle, the oil is sucked into the oil lock chamber 500 during the extension stroke in the above-described low vehicle height state, and the oil is sucked into the jack chamber 130 from the oil lock chamber 500 during the compression process. Pumping of pumping oil is repeated. As a result, the amount of oil in the jack chamber 130 increases, and the vehicle finally attains a high vehicle height state.

In the low vehicle height state, the damper portion 1B according to the first embodiment can reduce the oil even if the damper portion 1B is greatly contracted due to, for example, a wheel contacting a relatively large obstacle such as a curb. Since the locked state is formed, the collision between the rod 30 and the cylinder portion 20 is suppressed.

As described above, in the suspension device 1 according to the first embodiment, for example, the pumping operation is not performed using the compression pump having another power source, but the operation of the damper unit 1B accompanying the traveling of the vehicle in the low vehicle height state. The vehicle height is automatically adjusted by.
In particular, in the suspension device 1 of the first embodiment, by using the oil lock mechanism section 50 to perform pumping for vehicle height adjustment, an increase in the number of parts and complication of the device are suppressed, and a simple configuration is achieved. Has been realized.

Further, in the suspension device 1 according to the first embodiment, the oil in the oil lock chamber 500 divided in the cylinder 21 is not directly compressed, but the oil is compressed in the oil lock chamber 500 divided in the cylinder 21 to the jack chamber 130. Pumping. Therefore, in the first embodiment, the oil pressure in the cylinder 21 is prevented from increasing due to pumping.

Here, consider a case where the oil lock chamber 500 of the first embodiment is not provided and a configuration is adopted in which, for example, the oil of the cylinder 21 is compressed to perform pumping. In this case, the constraining force of the oil seal 233 of the cylinder 21 is set high for pumping in which the oil pressure is relatively high, or the rod 30 is moved by the oil seal 233 due to the increase of the oil pressure of the cylinder 21. The frictional force may increase. Then, the rod 30 may affect the amplitude operation of the damper portion 1B due to the frictional force received from the oil seal 233.

On the other hand, in the suspension device 1 of the first embodiment, pumping is performed on the jack chamber 130 in the oil lock chamber 500 that is separated from the cylinder 21, so that the influence of frictional force on the rod 30 due to pumping is suppressed. It

Next, the case where the oil pressure in the jack chamber 130 becomes excessive by increasing the amount of oil in the jack chamber 130 by pumping in the oil lock mechanism unit 50 will be described.

FIG. 7 is an explanatory diagram of the operation of the damper portion 1B when the oil pressure in the jack chamber 130 becomes excessive.
As described above, pumping using the oil lock mechanism unit 50 is performed in the low vehicle height state. However, as a result of the oil being continuously pumped to the jack chamber 130 by pumping, the amount of oil pumped to the jack chamber 130 may become unnecessarily large.

In this case, as shown in FIG. 7, when the oil pressure in the jack chamber 130 becomes excessive with the oil lock piece 51 entering the oil lock collar 54, the blow valve 72 of the blow valve unit 70 causes the flow path 711 to flow. open. Then, a part of the oil pressure-fed from the oil lock chamber 500 flows out into the reservoir chamber R. As a result, in the damper portion 1B of the first embodiment, excessive oil pressure in the jack chamber 130 is suppressed. Then, in the damper portion 1B of the first embodiment, for example, the load on the jack cylinder 13 and the oil lock mechanism portion 50 is reduced.

Next, a description will be given of the oil flow when the vehicle load is reduced in a state where the oil amount in the jack chamber 130 is increased by pumping in the oil lock mechanism unit 50.

FIG. 8 is an explanatory diagram of the operation of the damper unit 1B when the loaded amount is small.
As shown in FIG. 8, as the vehicle load decreases, the rod portion 30 and the cylinder portion 20 relatively move away from each other in the damper portion 1B, and the rod 30 moves toward the other end side. As a result, the oil lock piece 51 provided on the rod 30 advances from the oil lock collar 54. Then, the jack portion 14 is pushed down by the coil spring 11, and the oil in the jack chamber 130 flows from the oil pipe 100 into the second bottom chamber 242. Further, the oil in the second bottom chamber 242 passes through the slit 82S of the slit valve 821 and returns from the flow passage 811 and the flow passage 551 to the first oil chamber Y1.
Then, as the oil in the jack chamber 130 returns to the first oil chamber Y1, the spring portion 1A is in a state before pumping is performed.

<Second Embodiment>
Next, the suspension device 1 of the second embodiment will be described.
FIG. 9 is a partial cross-sectional view of the damper portion 1B of the second embodiment.
In the second embodiment, the same components as those in the first embodiment are designated by the same reference numerals and detailed description thereof will be omitted.

As shown in FIG. 9, the damper unit 1B to which the second embodiment is applied is different from the oil lock mechanism unit 50 of the first embodiment in the configuration of the oil lock mechanism unit 250.

(Oil lock mechanism part 250)
The oil lock mechanism portion 250 includes an oil lock piece 251 provided at the end portion on the one end side of the rod 30, and a check valve 52 provided inside the oil lock piece 251 in the radial direction. Further, the oil lock mechanism part 250 connects the oil lock collar 254 fixed to one end of the cylinder part 20, the seal member 253 provided outside the oil lock collar 254 in the radial direction, and the flow connecting to the jack chamber 130. And a flow passage forming portion 55 that forms a passage.

The oil lock piece 251 has a shape in which one end side opens toward the one end side.
The outer diameter of the oil lock collar 254 is slightly smaller than the inner diameter of the oil lock piece 251. The oil lock collar 254 can enter the inside of the oil lock piece 251 in the radial direction.

Also in the damper portion 1B of the second embodiment configured as described above, in the low vehicle height state, due to the amplitude of the damper portion 1B accompanying the traveling of the vehicle, the oil is sucked into the oil lock chamber 500 during the extension stroke. During the compression process, pumping is performed by pumping oil from the oil lock chamber 500 to the jack chamber 130 (see FIG. 1). As a result, the amount of oil in the jack chamber 130 increases, and the vehicle goes from the low vehicle height state to the high vehicle height state.

In addition, the suspension device 1 of the first and second embodiments adopts a configuration in which the spring portion 1A and the damper portion 1B are arranged in parallel to form separate bodies, but is not limited to this configuration. For example, the suspension device 1 may be a so-called strut type device in which the spring portion 1A is provided coaxially with the damper portion 1B.

Further, in the damper portion 1B of the first and second embodiments, if it is possible to allow the oil flow from the jack chamber 130 to the oil lock chamber 500 in a state where the slit valve 821 does not open the flow passage port of the flow passage 811. The slit 82S of the slit valve 821 is not an essential component. For example, the flow passage opening of the flow passage 811 may have a notch or a through hole as an example of the flow passage hole in a part in the radial direction.

Further, in the damper portion 1B of the first embodiment and the second embodiment, the piston portion 40 and the bottom valve portion 60 are not limited to the structures shown in the above-mentioned embodiments, but may be any one as long as they fulfill the function as a damping mechanism. Other shapes and configurations may be used.

DESCRIPTION OF SYMBOLS 1... Suspension device, 1A... Spring part, 1B... Damper part, 11... Coil spring, 20... Cylinder part, 30... Rod, 40... Piston part, 50... Oil lock mechanism part, 51... Oil lock piece, 54... Oil Lock collar, 60...bottom valve part, 70...blow valve part, 80...adjustment valve part, 130...jack chamber, 500...oil lock chamber

Claims (6)

A spring arranged between the vehicle body and the wheels,
A spring support portion that supports the spring and moves the spring according to the liquid in the liquid storage chamber that stores the liquid,
A cylinder containing the liquid,
A rod provided with a piston and moving in the axial direction of the cylinder,
A moving portion arranged on the side of the rod where the piston is provided, and moving together with the rod,
A compression chamber forming portion which is provided at an end portion of the cylinder and which forms a compression chamber in which the liquid stored by the moving portion is compressed.
A circulation unit for circulating a liquid from the compression chamber to the liquid storage chamber,
Suspension device. The suspension device according to claim 1, wherein the liquid in the compression chamber is separated from the liquid contained in the cylinder. The suspension device according to claim 1, wherein the moving portion is inserted inside a compression chamber forming portion in a radial direction. The suspension device according to claim 1, further comprising an adjusting valve that is provided on a liquid flow path in the flow section and adjusts a pressure of the fluid in the compression chamber. The adjustment valve is a flow path hole that allows a liquid to flow from the liquid storage chamber to the compression chamber between the adjustment valve and a flow path opening and closing the flow path opening. The suspension device according to claim 4, further comprising: The suspension device according to claim 1, further comprising a blow valve that is provided on a flow path of the liquid in the circulation portion and that releases a pressure of a fluid in the liquid storage chamber that is equal to or more than a predetermined pressure.