JPH01226411A - Suspension device - Google Patents

Abstract

PURPOSE:To enable improvement of the degree of freedom of the mounting positions of a valve and the other parts by a method wherein, in the suspension device of an automobile, by using a single coil type electromagnetic plural port 2-position switching valve and an on-off valve to effect intermittent passage of oil liquid through a line, control is made by a control device. CONSTITUTION:A single type electromagnetic plural port 2-position switching valve 32 and an on-off valve 33 are disposed, in order, from the hydraulic source side in each of lines 27a and 27b for connecting hydraulic cylinders 12a and 12b to a hydraulic source 16. The switching valve 32 and the on-off valve 33 are controlled by a control device 18. Namely, in a given motion position of the switching valve 32, the on-off valve 33 is opened to feed and discharge oil liquid to and from the hydraulic cylinders 12a and 12b. After completion of the feed and discharge, the on-off valve 33 is closed, and the switching valve 32 is restored to its initial position. The use of a small valve enables elimination of limitation of the mounting position of the valve and the mounting position of other part.

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention is directed to controlling the attitude of an automobile body by supplying and discharging oil to a hydraulic cylinder interposed between the automobile body and each wheel. This invention relates to a suspension device that allows the user to ride.

(Prior Art) In recent years, various suspension devices have been proposed for automatically suppressing the rolling and pitching that occurs in the vehicle body of an automobile or the like while the vehicle is running, thereby stabilizing the posture of the vehicle body.

Conventionally, this suspension device has one type, for example, a first suspension device.
There is something shown in Figure 1.

To explain this, the double-acting hydraulic cylinder 1 is attached to the cylinder 2 side or the wheel 3, and is attached to the piston loft 4 side or the car body 5, and between the cylinder 2 and the car body 5 there is a ring 6. Or there is an intervention. Further, both pressure chambers A and B of the hydraulic cylinder 1 are connected to a hydraulic power source 8 constituted by a hydraulic pump or the like via a four-bottom, three-position switching valve 7.

This switching valve 7 is of a multi-coil type electromagnetic type, and a spool moves according to the current value, during which the flow rate is adjusted by the valve degree.

A vehicle height sensor 9 for detecting displacement is provided between the vehicle body 5 and the wheels 3, and the detected value from the vehicle height sensor 9 is sent to a control device M.
10 is input.

Then, the control device IO controls the switching valve 7 based on the vehicle height detected by the vehicle height sensor 9, so that oil is optimally supplied and discharged to both pressure chambers A and B of the hydraulic cylinder 1, and the vehicle body 5 and the wheels 3 to control the attitude of the vehicle body.

(Problem to be Solved by the Invention) However, in the above-mentioned conventional suspension device, the multi-coil type electromagnetic 4-port 3-position switching valve 7 that constitutes the device is relatively large. There were problems such as requiring a large installation space, restricting the installation position, and restricting the installation position of other parts.

In addition, the solenoid of the switching valve 7 uses a proportional solenoid that moves the spool proportionally according to the current to control the flow rate, so it is expensive and has the problem of increasing the cost of the entire device. there were.

The present invention has been made in view of one or more problems, and an object of the present invention is to provide a suspension device in which a switching valve for controlling oil supply and discharge is inexpensive and the mounting position is not restricted. There is a particular thing.

(Means for Solving the Problems) As a means to achieve the above object, a hydraulic power source is connected to a hydraulic cylinder interposed between the vehicle body side and the wheel side, and oil is supplied and discharged to the hydraulic cylinder. In a suspension control device that can control the posture of a hydraulic cylinder, a valve body is moved from the hydraulic source side to a pipe line connecting the hydraulic cylinder and the hydraulic source to an oil supply side position or an oil drain side position according to a current value. A single-coil electromagnetic multi-port two-position switching valve is provided to adjust the flow rate of the oil fluid, and an on/off valve is provided to interrupt the flow of the oil fluid in the pipeline. At a predetermined operating position of the valve body, the on-off valve is opened to start supplying and discharging oil to the hydraulic cylinder, and when the supply and discharging is completed, the on-off valve is closed and then the on-off valve is opened. A control device is provided for controlling the valve body of the switching valve to return to its initial position.

(Function) With this configuration, when the oil supply/drainage operation is not performed, a constant oil pressure is maintained in the hydraulic cylinder by blocking the pipe line with the on/off valve. Furthermore, when starting the oil supply/drain operation, the on/off valve is opened at a predetermined operating position of the valve body of the switching valve, so that supply/drain of oil to the hydraulic cylinder is promptly started. Furthermore, when the oil supply/drain operation is completed, the on/off valve is closed to shut off the pipeline, and then returned to the initial position of the valve body of the switching valve. This prevents unnecessary oil from flowing in and out of the cylinder, and keeps the oil pressure in the hydraulic cylinder in one chamber.

By combining the 2-position switching valve and the on/off valve and controlling them appropriately using the control device, oil supply and drainage operations can be performed in the same way as the conventional multi-coil electromagnetic 4-port 3-position switching valve. I can make you do it.

Since the switching valve is a two-position switching valve, which is smaller than the conventional three-position switching valve, the installation space is small, and the switching valve and on/off valve can be installed separately to avoid interference with other parts. It can be freely installed in any position that does not occur.

(Example) Next, embodiments of the present invention will be described based on the drawings.

First, the overall configuration of this embodiment will be described based on FIG. 2. The front wheels 11a, llb and the rear wheel 11c.

Piston rods l:la, 13b, 1:lc, 1:ld of hydraulic cylinders 12a, 12b, 12c, 12d attached to the vehicle body are attached to each wheel of the hydraulic cylinder 11d. 12b, 12
c, Supply and discharge oil to +2d and piston lot 1: la
By expanding and contracting the wheels 11a, llb, llc, and lid, the vehicle height can be raised or lowered by moving the wheels 11a, llb, llc, and lid relative to the vehicle body.

Each hydraulic cylinder 12a, 12b, 12c, 12d includes
Accumulator 1, which is the spring element of the suspension device
4a, 14b, 14c, and 14d are connected to throttle valves +5a, 15b, +5c, and 15d that generate damping force.

Further, the hydraulic cylinders 12a, 12b, 12c, and 12d are connected to a hydraulic power source 16, which will be described later, via oil supply/discharge means 17a, 17b, 17c, and 17d, which are essential parts of this embodiment. And oil supply and drainage means 17a, 17b, 17c, 17d
is controlled by a control device 18. In addition, 19a, 19
b, 19c, +9d are hydraulic cylinders +2a, 12b, 1
2c, 12d and its piston lot I:la, 13b,
A vehicle height sensor is attached to 1:lc and 1:Id to detect expansion and contraction, 20 is a vehicle speed sensor that measures vehicle speed, and 21 is a steering angle sensor that detects the rotation angle of the steering shaft. The detected detection signal is
It is input to the control device 18.

Next, the hydraulic power source 16 and the oil supply/drainage means 17a.

17b, 17c, and +7d will be explained based on FIG.

Note that FIG. 1 only shows the oil supply/drainage means 17a, 17b on the front wheel side, or the rear wheel side has a similar configuration.

First, the hydraulic pressure 916 will be explained. The hydraulic pump 22 is driven by a drive source 23 such as an engine or an electric motor. On the suction side of the hydraulic pump 22, there is a conduit 25 for sucking oil stored in the reservoir tank 24.
is connected, and a filter 26 is attached to the suction port of the conduit 25. Further, a pipe line 27 for supplying oil to the hydraulic cylinders 12a, 12b, 12c, and 12d is connected to the discharge port of the hydraulic pump 22, and a check valve 28 and an accumulator 29 are connected in the middle of the pipe line 27. It is set up.

Further, a pipe line 30 connected to the reservoir tank 24 is branched in the middle of the pipe line 27, and an unload valve 31 which is operated by the pressure inside the pipe line 27 is provided in this pipe line 30.

According to this configuration, the high pressure oil generated by the driven hydraulic pump 22 is accumulated in the accumulator 29, and when the pressure in the pipe line 27 rises above a set value, the unload valve 31 is switched by the pilot pressure to The oil discharged from the pump 22 is returned to the reservoir tank 24, so that the oil pressure source 16 can supply oil at a constant pressure.

Subsequently, the oil supply and drainage means 17a, 17b, 17c, and 17d connect the hydraulic power source 16 and each wheel 11a, Ilb, llc, and lld.
Hydraulic cylinder 12 immersed in (2 not shown)
a, +2b, 12c.

Respective conduits 27a, 27b, 27 connecting +2d
c.

27d, and is composed of a single-coil electromagnetic type switching valve 32 with three ports and two positions, and an electromagnetic type switching valve 33 with two ports and two positions.

Single coil type 'Itiji type 3 port 2 position switching valve 32
The spool as a valve body moves to the oil supply side position or the oil drain side position according to the current, adjusts the valve opening by 13J, and controls flow 1. In this case, the cylinder port A and the tank port T are in communication, and the oil fluid of the hydraulic cylinders 12a, 12b, 12c, and 12d is returned to the reservoir tank 24 via the return pipe 34, and in the oil supply side. is pump port P
and cylinder port A, and a constant oil pressure is supplied from the hydraulic source I6 to the hydraulic cylinders 12a, +2b, 12c, 12.
It is now ready to supply to d.

As shown in Fig. 4, the operating characteristics of this switching valve 32 are such that the flow rate of oil supply and drainage changes continuously in approximately proportion to the current value, and by setting the current value, it is possible to Once the flow rate is determined, flow rate control can be performed. In addition, in the initial position when the power is not energized, the force of the spring places it in the oil drain side position (or the oil supply side position as required), and the range where the flow rate is O in the figure is the neutral position, and the 'If flow value I,
By energizing, the neutral position can be achieved.

The 2-bot, 2-position switching valve 33 switches between the pipes 27a, 27b, 27c, and 27d by applying current. It switches from a blocking position to a position allowing oil to flow, and functions as an on/off valve to allow or shut off the flow of oil in the pipe. Hereinafter, the single-coil electromagnetic three-port, two-position switching valve 32 will be referred to as a flow control valve, and the electromagnetic two-port, two-position switching valve 33 will be referred to as an on-off valve.

Next, using FIG. 3, the oil supply/drainage means 17a.

The control device 18 that controls 17b, +7c, and 17d will be explained. In this embodiment, the rolling state during turning is estimated based on the vehicle speed and the steering angle, and each hydraulic cylinder 12a, 12b is adjusted based on the estimation.

A case will be described in which control is performed to supply and discharge oil to and from 12c and 12d.

As mentioned above, the control device 18 includes a vehicle height sensor 19a.
, 19b, 19c, 19d, vehicle speed sensor 20. A detection signal detected by the steering angle sensor 21 is input.

A lateral acceleration estimation stage 34 is provided for estimating the lateral acceleration expected to occur in the vehicle body at each fixed steering angle based on the input speed and steering angle detection signals. Note that this estimation is performed based on the fact that the lateral acceleration is proportional to the steering angle and proportional to the vehicle speed.

Also,! There is a proportional relationship between the lateral acceleration generated on the V body and the roll angle, and a calculation means 35 is provided for calculating the roll angle based on the lateral acceleration based on this relationship. Further, once the roll angle is calculated, the amount of change in the length of each hydraulic cylinder 12a, ]2b, 12c, 12d due to the roll angle is also calculated.

The hydraulic cylinder 12a calculated in this way.

Each hydraulic cylinder 12a, 12b, 12c, 1 is arranged so as to suppress the change in length of 12b, +2c, +2d.
A logic calculation means 36 is also provided for determining the amount of oil to be supplied and discharged to and from the oil tank 2d (target amount of oil to be supplied and discharged).

Valve opening amount calculation means 37 is provided for setting the opening amount of the flow rate control valve 32 based on the target oil supply/drainage amount calculated by the logical calculation means 36.

Based on the set valve opening amount, the oil supply/drainage means 17
Also provided is an oil supply/drainage control means 38 for properly controlling the flow rate control valves 32 and on/off valves 33 of a, 17b, 17c, and 17d. Multi-valve 3 by this oil supply/drainage control means 38
2.33 switching control is performed by switching the on/off valve 33 at a predetermined operating position of the spool (not shown) of the flow control valve 32.
to open the hydraulic cylinders 12a, 12b, 1.
At 2c and 12d, supply and discharge of oil based on the target oil supply and discharge amount is started, and when the supply and discharge is completed, the on/off valve 33 is closed, and then the spool of the flow control valve 32 is returned to the initial position. It is intended to do so.

The lateral acceleration estimation means 34, the calculation means 35, the logic operation means 36, the valve opening amount calculation means 37, and the oil supply/drainage control means 38 are controlled by a CPU 39 provided in the control device 18 according to a predetermined program. Ru.

The operation of the above configuration will be explained using the flowchart of FIG.

First, the main routine will be explained with reference to FIG. 5. When the ignition switch is turned on, initial settings of each set value of the control device 18 are performed in step 1. Next, in step (2), the vehicle speed sensor 20 and the steering angle sensor 21 are
The detected value from is input to the control device 18, and in step (2), the lateral acceleration estimation means 34, the calculation means 35, and the logic operation means 35 of the control device m18 control the hydraulic cylinder 12a.

A target amount of oil to be supplied and discharged to and from 12b, 12c, and 12d is set. Then, in step (2), the opening amount of the flow rate control valve 32 is set by the opening amount calculating means 37 of the control device ta. Next, in step (2), the oil supply and discharge control means 38 of the control device R18 controls the oil supply and discharge means 17a.

Controls 17b, 17c, and 17d are performed, and a subroutine for this control is shown in FIG. 6 and will be explained.

In step (2), it is determined whether the opening amount required for the flow control valve 32 for adjusting the vehicle height is 0 or not, and if it is 0 (not required), the flow control valve 32 is opened in step (2). 32 is being energized. And when the power is not on.

Since vehicle attitude control is on standby, the process returns to the main routine.

In step (2), if the required valve opening amount is not 0 (if the valve opening amount is set in the main routine to perform attitude control), it is determined in step (2) whether the flow control valve 32 is energized; If the current is not being energized, in step 1, the current Il is energized to the flow rate control valve 32 so that the spool changes from the initial position to the neutral position, and the process returns to the main routine. Further, when it is determined in step (2) that the flow rate control valve 32 is energized, it is determined in step (2) whether the on/off valve 33 is open. Step ■ On/off valve 33
If it is determined that the valve is in the closed state, it is determined in step (2) whether the energization time of the flow control valve 32 or the time T until the spool of the flow control valve moves to the neutral position has elapsed. If not, the process returns to the main routine, and if the elapsed time has elapsed, the on/off valve 33 is energized to open the hydraulic cylinder 12a, 12b, 12c.
, 12d, supply and discharge of oil begins.

In addition, when it is determined that the on/off valve 33 is in the open state fE in step (2), the hydraulic cylinders +2a, 12 are
A current is applied to the flow rate control valve 32 according to the valve opening amount set so that the target amount of oil can be supplied or discharged to the valves b, 12c, and 12d.

When the supply/discharge operation is completed, the required valve opening amount of the flow rate control valve 32 is determined to be 0 in step G), and it is determined that the hydraulic pressure control valve 32 is energized in step (β), so that the flow rate in step G) is determined to be 0. passes flow 1. to the control valve 32 so that the spool returns to the neutral position.Next, in step (2), it is determined whether the on/off valve 33 is in the open state, and it is determined whether the on/off valve 33 is in the open state. If so, in step (2), it is determined whether the required opening amount of the flow rate control valve 32, the O state, or whether it has continued for T2 time, and if the T2 time jtI has not been maintained, the process returns to the main routine and continues. If so, step
A closing operation of the off valve 33 is performed.

In this way, the conduits 27a, 27b, 27c, 27d
In order to shut off the on/off valve 33, the on/off valve 33 is closed, and when it is determined in step (2) whether the on/off valve 33 is closed, the on/off valve 33 is closed in step [phase]. It is determined whether the flow rate has continued for T1 time or not, and if the flow rate has not been continued, the process returns to the main routine, and if the flow rate control valve 32 has been continued, the flow rate control valve 32 is de-energized in step (2). This 13 hours was set in consideration of the operating time of the on/off valve 33.

As described above, when refueling and draining operations are required regarding the posture of the vehicle body, first, the flow control valve 32 is energized to displace its spool from the initial position to the neutral position, and then the on/off valve 33 is turned on. After opening the valves and preparing for attitude control, the flow control valves 32 are energized with a current corresponding to the valve opening amount set based on the target oil supply/drainage amount to start attitude control, and each hydraulic cylinder 12a, When the target amount of oil is supplied and discharged to 12b, 12c, and 12d, the on/off valve 33 is closed to cut off the pipes 27a, 27b, 27c, and 27d, and then the flow control valve 32 is de-energized. Then, attitude control ends. Here, the reason why the flow control valve 32 is de-energized is to prevent wasteful power consumption when attitude control is not performed, but if attitude control is frequently performed (for example, rolling while driving on a mountain road) Since a hold time of 12 hours is set from the closing of the on-off valve 33 to the de-energization of the flow control valve 32 for the control m), the de-energization of the flow control valve 32 is stopped within 12 hours. Control can be performed continuously without stopping. Furthermore, if it is necessary to perform continuous control reliably, turn on the ignition switch and energize the YT shop control valve 32 at the same time as 11, and then turn off the ignition switch to stop the energization. Instead, the above control may be performed. That is, by energizing the flow rate control valve 32 with a current of 11, when the vehicle height adjustment is required, the on/off valve 33 immediately opens and the oil supply/drain operation is immediately started. Even when rolling occurs frequently, such as when driving on mountain roads, the vehicle height can be adjusted continuously.

FIG. 8 specifically shows temporal changes in the target oil supply/drainage amount, the current supplied to the flow control valve 32, and the open/close state of the on/off valve 33 in the above control.

Oil supply and discharge means 17 by the oil supply and discharge control means 38 explained above
a, I7b, 17c, and 17d are controlled by the flow rate control valve 32.
The on/off valve 33 is opened and closed when the spool is in the neutral position. Next, another example of control will be shown using FIG.

In step ■, it is determined whether the opening amount required for the flow control valve 32 for adjusting the vehicle height is 0 or not, and if it is 0 (not required), step It is determined whether the flow rate control valve 32 is energized. If the power is not being applied, the vehicle attitude control is on standby, and the process returns to the main routine.

In step @, if the required valve opening amount is not 0 (if the valve opening amount is set).

In step (2), a current is applied to the flow rate control valve 32 in accordance with the target amount of oil to be supplied and discharged. Then, in step ■, on/off valve 3
It is determined whether the valve 32 is open or not, and if the valve is closed, the flow control valve 32 is energized in step
, 'time has elapsed and it is determined whether 7:l: or not. Incidentally, the time T1' is set in consideration of the time required for the spool of the flow rate control valve 32 to move from the initial position to the set valve open position.

If the time T1' has not elapsed, the process returns to the main routine, and if it has elapsed, the on/off valve 33 is energized and opened in step (3), and the pipes 27a, 27b,
27c and 27d are connected, and oil is supplied and drained.

Further, if it is determined that the on/off valve 33 is in the open state in step S1, the routine returns to the main routine and the target amount of oil to be supplied and discharged is supplied and discharged.

When the supply/discharge operation is completed, the opening amount of the flow control valve 32 is determined to be O in step (2), and it is determined in step (2) that the flow rate control valve 32 is energized. Then, the current 1. is applied so that the spool returns to the neutral position. energize. Next, in step (2), it is determined whether the on/off valve 33 is in an open state, and if it is in the open state, in step (2), the required opening amount of the flow rate control valve 32 is maintained at O for 12 hours. If it has not continued for 12 hours, the process returns to the main routine, and if it has continued, the on/off valve 33 is closed in step (2).

In this way, the conduits 27a, 27b, 27c, 27d
When the on-off valve 33 performs a valve closing operation to shut off the air, and it is determined in step (2) whether the on-off valve 33 is in the closed state, the on-off valve 33 is in the closed state in step (2). It is determined whether the time has continued, and if it has not continued, the process returns to the main routine, and if it has continued, the flow rate control valve 32 is de-energized in step (3).

In this way, in this control, after the flow rate control valve 32 is set to the set valve opening amount, the on/off valve 33 is opened to supply and drain oil, so the flow rate control start time is controlled. This can reduce the delay.

FIG. 9 specifically shows temporal changes in the target oil supply/drainage amount, the current supplied to the control valve 32, and the open/close state of the on/off valve 33 in the above control.

Next, two other embodiments of the present invention will be described using FIG. 10. In this embodiment, only the structure of the oil supply and discharge means is different from that shown in FIG. 1, so only the structure of the oil supply and discharge means will be explained.

In the middle of the pipes 27a, 27b, 27c, and 27d, a single-coil electromagnetic three-port two-position switching valve (hereinafter referred to as a flow control valve) 32 and a pilot-operated check valve 4 are installed from the hydraulic source side.
0 is arranged. Further, in the conduit 27 on the pressure source side of the flow rate control valve 32, an electromagnetic three-port, two-position switching valve 41 for supplying pilot pressure to the pilot-operated check valve 40 is provided. The switching valve 41 and the pilot-operated check valve 40 constitute an on-off valve.

This electromagnetic 3-port 2-position switching valve (hereinafter referred to as a pilot pressure control valve) 41 is used to control the left and right front wheels 11 as shown in the figure when actively suppressing pitching of the vehicle body.
One each for the a, llb side and the left and right rear wheels 11c, lld. When trying to suppress the rolling of the vehicle body, one each for the left front and rear wheels 11a, llc and the right front and rear wheels 11b, lld. When adjusting the upper height of the vehicle one by one, or the entire vehicle height, adjust the front and rear four wheels 11a, l.
lb, llc.

One is provided for +1d. In addition, when controlling the opening and closing of the on/off valves by turning the ignition switch on and off, each pilot operated check valve 40 for each of the four front and rear wheels is controlled to open and close using one pilot pressure control valve 41. You can.

According to this configuration, when the pilot pressure control valve 41 is in a de-energized state, the pilot pressure is 0, so the pilot-operated check valve 40 functions as a normal check valve, and the hydraulic cylinders 12a, 12b, 12c .

The oil pressure is kept constant within +2d.

When the pilot pressure control valve 41 is energized, the high pressure on the hydraulic power source 16 side acts on the pilot operated check valve 40 via the pilot pipe line 42, causing the pilot operated check valve 40 to open.

Note that the flow-2 control valve 32 and the pilot pressure control valve 4
1 is similar to the embodiment described in 1.1 above, when the spool of the flow rate control valve 32 is moved to a predetermined neutral position or the set valve opening amount position a) by the control device fi18, the pilot pressure control valve is activated. 41 to open the pilot operated check valve 40, and the hydraulic cylinders 12a, 12bj2c, +2
d, and when the supply and discharge are completed, the pilot pressure control valve 41 is de-energized and the pilot-operated check valve 40 is turned off.
After closing the flow rate control valve 32, the flow rate control valve 32 is controlled to be de-energized. This allows the vehicle height to be adjusted optimally. Further, in this embodiment, if high pressure oil is not stored on the hydraulic source 16 side, the pilot operated check valve 40 will not open even if the pilot pressure control valve 4I is energized, so the hydraulic cylinder 12a, +2b, +2c, +2
The oil in d will not flow backward through the flow rate control valve 32.

In the embodiment of the invention described hereinabove, the hydraulic cylinder 12a
, +2b, 12c, +2d side, electromagnetic 3-port 2-position switching valve 33. In addition, since the pilot-operated check valve 40 is provided, leakage can be significantly reduced compared to the conventional multi-coil electromagnetic 4-port 3-position switching valve 7, which has a lot of leakage due to its structure. It also has the unique effect of preventing the oil from leaking from the hydraulic cylinders 12a, 12b, 12c, +2d and causing the vehicle height to be extremely lowered when the vehicle is not in use.

In this embodiment, a case has been described in which the low link state is estimated from the vehicle speed and the steering angle, the amount of oil to be supplied and discharged is set, and the amount of oil to be supplied and discharged is performed based on this, but the present invention is not limited to this. For example, when braking, the vehicle speed sensor 19
a, 19b, 19C.

19d (If necessary, braking pressure sensor, deceleration sensor, etc.) may be used to adjust the distance between the vehicle body and wheels based on the actual change in vehicle body posture detected, and apply this to suspensions that control the vehicle body posture. can.

Further, although the flow control valve (switching valve) 32 has been described using an example of three ports, it is not limited to this, and may be one with four or more ports, in short, it is sufficient to have a plurality of ports.

(Effects of the Invention) As explained in detail above, the present invention includes a single coil electromagnetic three-port two-position switching valve and an on/off valve that connects the flow of oil in the pipeline. By using this system and having the control device control it, oil supply and drain operations can be performed to automatically suppress the rolling and pitching that occurs in the vehicle body while the vehicle is running and to stabilize the posture of the vehicle body, similar to conventional methods.

Furthermore, since the six valves are relatively small, there are fewer restrictions on the installation position of the six valves, or restrictions on the installation position t of the six valves or other parts.

Furthermore, while conventional multi-coil electromagnetic 4-port 3-position switching valves use two 2-proportional solenoids, the present invention uses a single-coil type, so only one proportional solenoid is used.
Since the on/off valve is a solenoid that only switches, the structure is cheaper than conventional ones, and the cost of the entire device can be reduced.

[Brief explanation of the drawing]

1U'A is a diagram showing an example of the configuration of an oil supply/drainage means which is a main part of the suspension device of the present invention, and FIG. 2 is a diagram showing the overall configuration of an example of the suspension device of the present invention. FIG. 3 is a diagram showing the configuration of an example of a control device provided in the suspension device of the present invention. FIG. 4 is a diagram showing the relationship between the current value applied to the flow rate control valve shown in FIG. 1 and the flow rate, FIG. 5 is a flow chart of control by the control device 18 shown in FIG. 3, and FIG. is a flowchart of oil supply and drainage control by the oil supply and drainage control means of the control device shown in FIG. 3, and FIG. Flowchart diagram of control. FIG. 8 is a diagram showing temporal changes in the target oil supply/drainage amount, the energization state of the flow control valve, and the energization state of the on/off valve when the oil supply/drainage control shown in FIG. 6 is performed. Figure 9 is a diagram showing temporal changes in the target oil supply and drainage amount, the energization state of the flow rate control valve, and the energization state of the on/off valve when the oil supply and drainage control shown in Fig. 7 is performed. The figure is a diagram showing the configuration of another example of the oil supply/drainage means which is a main part of the suspension device of the present invention. FIG. 11 is a diagram showing the configuration of a conventional suspension device capable of adjusting vehicle height. 12a, 12b, 12c, 12d - hydraulic cylinder 16
... Hydraulic power source 18 ... Control devices 27a, 27b, 27c, 27d --- Pipe line 32 ...
・Single-coil electromagnetic 3-port 2-position switching valve (flow control valve) 33...On-off valve patent applicant Tokico Co., Ltd.
Uchida Hydraulic Equipment Industry Co., Ltd. Fig. 1 27a, 27b ・It route 32 I71 criticism (1 Shido IFill Misaki valve) of Hanako-type electronic a-garment 2ai 33. O-off valve Fig. 2 Fig. 3 Fig. 4 Figure 5 Figure 6 Figure 7 Figure 10 Figure 11 Figure 1゜

Claims (1)

[Claims] (1) A suspension control device in which a hydraulic power source is connected to a hydraulic cylinder interposed between a vehicle body side and a wheel side, and the posture of the vehicle body can be controlled by supplying and discharging oil to and from the hydraulic cylinder, wherein the hydraulic pressure is as follows. Multiple single-coil electromagnetic type that adjusts the flow rate of oil by moving the valve body from the oil pressure source side to the oil supply side position or the oil drain side position according to the current value in the pipeline connecting the cylinder and the oil pressure source. A switching valve at the port 2 position and an on/off valve that cuts off the flow of oil in the pipe line are provided, and when the valve body of the switching valve is in a predetermined operating position, the on/off valve is disposed.
Control that opens an off valve to start supplying and discharging oil to the hydraulic cylinder, and when supply and discharging is completed, closing the on-off valve and returning the valve body of the switching valve to its initial position. A suspension device characterized in that it is provided with a control device that performs the following.