KR100259715B1 - Velocity control device of out-trigger system - Google Patents

Abstract

PURPOSE: A speed controller is provided to control the speed by regulating flux supplied to an outrigger device and to decrease loss of engine output. CONSTITUTION: Signal pressure supplied to a solenoid valve(8) variably controls discharge flux from a primary pump(1) through a pump flux control signal passageway(23). As a stroke of a main control valve(21) is enlarged, discharge flux of the primary pump is increased. In case of driving an outrigger device separately, a solenoid valve is operated. Upon switching downward a solenoid valve(9), electric signals(S1,S3) are fed to solenoid valves(6,8). So, flow of hydraulic pressure oil is supplied to each solenoid valve, and simultaneously, the solenoid valve(8) is switched downward and a pump signal pressure input to a primary pump(10) is changed from a main control valve(21) into a decompression valve(5). And decompressed signal pressure is fed to the primary pump(1). Speed of expansion cylinders and jack cylinders of outrigger device is decreased with spring pressure regulated equipped with the decompression valve. Therefore, for increasing speed of the outrigger device, an engine acceleration pedal is not needed and system efficiency is enhanced without loss of engine output.

Description

Hydraulic oil distribution device of the hydraulic circuit

The present invention, in the outrigger industrial vehicle, for example, hydraulic cranes, hydraulic telescopic boom forklifts, etc., to control the speed by controlling the flow rate supplied to the outrigger device to reduce the loss of engine output The present invention relates to a speed control device of an outrigger device which focuses on making it possible.

Operate at least two hydraulic pumps by means of engine power as a power converter to discharge hydraulic oil, drive at least two actuators through the discharged hydraulic oil, In an industrial vehicle equipped with an upper swing structure, an hydraulic crane and a boom forklift for lifting and unloading loads are provided with an outrigger device (ground support device) for leveling and fixing the vehicle at a predetermined height on the ground. .

1 is a schematic external view of a general vehicle out trigger device, and FIG. 2 is a hydraulic circuit diagram for controlling an outrigger device of a conventional vehicle.

In FIG. 1, 50 is an upper turning agent, 51 is a lower traveling body.

In addition, four expansion cylinders 14-1, 14-2, 14-3 and 14-4 are provided in both front and rear sides of the lower traveling body 51 as shown in FIG. Each of the expansion cylinders is provided with jack cylinders 15-1, 15-2, 15-3, and 15-4 for horizontally adjusting the vehicle while supporting the vehicle on the ground.

The expansion cylinder and the jack cylinder are provided with the same number of control valves 100 for controlling the movement direction of these cylinders, respectively, and the control valve 100 of the outrigger device for operating the expansion cylinder and the jack cylinder. A dedicated fixed displacement pump 53 is connected via a flow path.

Reference numerals 16-1, 16-2, 16-3, and 16-4 are pilot check valves, 41 is a main relief valve, and T is an oil tank.

The hydraulic oil discharged from the fixed displacement pump 53 passes through the output port of the control valve 100 according to the switching position of the selected control valve 100, and extends through an oil passage connected to the corresponding control valve 100. It is supposed to operate the jack cylinder at a constant speed.

Therefore, in order to raise the expansion cylinder and jack cylinder more than a certain speed, it is necessary to manually operate the engine acceleration / deceleration pedal lever separately installed outside the vehicle.

When the speed is increased by operating the engine acceleration / deceleration pedal lever, the discharge flow rate of the pump 53 is increased, but more energy than necessary is entered into the system of the entire vehicle operated by obtaining the proper driving energy of the engine, so that the loss of engine output is greatly increased. appear.

And since the operating speed of the expansion cylinder and the jack cylinder is kept constant by the discharge pressure of the pump 53 there is a disadvantage that the operator can not be adjusted to the desired high speed or low speed can not be quickly and precise control.

The present invention is to solve the problems of the prior art as described above, by adjusting the flow rate supplied to the outrigger device to control the speed and at the same time to reduce the loss of the engine output of the outrigger device The object is to provide a control device.

Specific means of the present invention for achieving the above object, the engine output is driven by two or more actuators using a hydraulic device, provided with a lower traveling device and the swinging body, lifting the load. In the outrigger device of a vehicle having a hydraulic outrigger device to be firmly fixed and supported at

A variable first pump 1 for varying the flow rate is provided, and the discharge port of the first pump 1 has an actuator control main control valve 21 and an outrigger control solenoid valve 9 for ground support disposed under the vehicle. Flow rate distribution valve (3) is installed to selectively supply the main supply flow rate of the first pump (10) to (10, 11, 12), and the flow rate is supplied to the outrigger control solenoid valve even when the vehicle upper swing structure is turning. A small capacity pump 2 is provided as a control means for connecting the supply passage 26 to the pivot joint 17 so as to reduce the discharge variable flow rate of the first pump 1, and the discharge port of the small capacity pump 2 is provided. A pressure reducing valve (5) for sending a pump control signal pressure to the first pump (1) is provided on the side, and between the pressure reducing valve (5) and the first pump (1) is reduced in pressure. Pump that selectively supplies the signal pressure to the signal pressure of the first pump (1) It is characterized in that the solenoid valve for signal pressure selection (8) is arranged so that only the required flow rate can be discharged during the operation of the outrigger device.

1 is a schematic external view of a typical vehicle out trigger device.

2 is a hydraulic circuit diagram for controlling an outrigger device of a conventional vehicle.

3 is a hydraulic circuit diagram for speed control of an outrigger device according to an embodiment of the present invention.

4 is an operation control flowchart according to an embodiment of the present invention.

5 is a schematic diagram of flow cut-up control according to an embodiment of the present invention.

<Explanation of symbols for the main parts of the drawings>

DESCRIPTION OF SYMBOLS 1st pump 2 Small capacity pump 3 Flow distribution valve

5: Pressure reducing valve 6,7: Solenoid valve 8: Solenoid valve for pump signal pressure selection

9,10,11,12: Solenoid valve 13-1 ~ 13-4: Jack selection valve

14-1 ~ 14-4: Expansion cylinder 15-1 ~ 15-4: Jack cylinder

17: Swivel Joint 21: Main Control Valve

Hereinafter, with reference to the accompanying drawings will be described an embodiment of the present invention;

The engine output is driven by two or more actuators using a hydraulic system, provided with a lower traveling device and a swinging structure, and a hydraulic outrigger device so that the vehicle body can be firmly fixed and supported on the ground when lifting or unloading loads. In the outrigger device of the vehicle,

4 pairs of expansion cylinders and jack cylinders 14-1, 15-1, 14-2, 15-2, 14-3, 15-3, and 14-4 constituting the outrigger device as shown in FIG. The jack selection valves 13-1, 13-2, 13-3, and 13-4 are connected to .15-4.

The jack selection valves 13-1, 13-2, 13-3, and 13-4 are connected to respective outrigger control solenoid valves 9, 10, 11, and 12, respectively. By operating any of these solenoid valves 9, 10, 11 and 12, the electrical signals S1 and S3 are respectively provided to the solenoid valve 6 and the pump signal pressure selection solenoid valve 8 which will be described later. Is supposed to be applied.

Reference numeral 1 is a large-capacity variable type first pump for driving a hydraulic actuator and an outrigger, wherein the discharge port of the first pump 1 is provided with a main control valve 21 for controlling the actuator and the outrigger control disposed at the vehicle undercarriage. A solenoid valve 3 for flow distribution is installed through the pump supply pressure passage 25 to selectively supply the main supply flow rate of the first pump 10 to the solenoid valves 9, 10, 11, and 12. .

The solenoid valve 3 and the solenoid valves 9, 10, 11, and 12 are connected to each other so that the flow rate can be supplied to the outrigger control solenoid valves 9, 10, 11, and 12 even while the vehicle upper swing body is turning. It is connected to the supply passage 26 through the joint 17.

In addition, a small capacity pump 2 is provided to control the discharge variable flow rate of the first pump 1, and in order to send a pump control signal pressure to the first pump 1 on the discharge port side of the small capacity pump 2. The pressure reducing valve 5 is connected through the pilot supply pressure passage 27.

Between the pressure reducing valve 5 and the first pump 1, the solenoid valve for pump signal pressure selection for supplying the reduced pressure signal of the pressure reducing valve 5 to the signal pressure of the first pump 1 selectively. (8) is excreted.

The pressure reducing valve 5 and the solenoid valve 8 are connected to the pump flow control signal passage 24, and the solenoid valve 8 and the first pump 1 to the pump flow control signal passage 23. The solenoid valve 8 and the main control valve 21 are connected to the pump flow control signal passage 22.

On the other hand, on the discharge port side of the small capacity pump 2, the flow rate distribution solenoid valve 3 is switched through the pilot signal pressure passage 28 by the application of the electrical signal S1 to discharge the first pump 1. A solenoid valve 6 for supplying a flow rate to the solenoid valves 9, 10, 11, 12 from the main control valve 21 side is connected.

In addition, the pilot signal pressure passages 32 and 33 branched to both sides through the pilot signal pressure passage 29 and the branch block 31 by the application of the electric signal S2 to the discharge port side of the small capacity pump 2. The hydraulic fluid is extended to the jack selection valves 13-1, 13-2, 13-3, and 13-4 through the expansion cylinders 14-1, 14-2, 14-3, 14 A jack selection solenoid valve (7) which is supplied from -4) to the jack cylinders 15-1, 15-2, 15-3 and 15-4 is connected.

Reference numeral 4 is a relief valve, 16-1, 16-2, 16-3, 16-4 are pilot check valves, 18, 19, 20 are oil tanks, and 35, 36, 37, 38 are actuator hydraulic pressures. 44 is the wheel, 45 is the axle.

The operation state of this embodiment configured as described above will be described with reference to the operation control flowchart of FIG.

First, in the apparatus of the present invention, the hydraulic oil discharged from the first pump 1 is normally supplied to the main control valve 21 for controlling the system actuator (not shown) through the flow distribution valve 3, wherein the hydraulic oil supplied is The signal pressure decompressed according to the operation of the main control valve 21 is transmitted to the pump signal pressure selection solenoid valve 8 through the pump flow control signal passage 22.

The signal pressure transmitted to the solenoid valve 8 variably controls the discharge flow rate of the first pump 1 through the pump flow control signal passage 23.

That is, as shown in FIG. 5, as the stroke of the main control valve 21 increases, the pump signal pressure decreases, and at the same time, the discharge flow rate of the first pump 1 increases.

Therefore, when controlling the system actuator, the flow rate of the first pump 1 is variably controlled between the maximum and the minimum according to the signal pressure decompressed through the main control valve 21.

On the other hand, when the outrigger device is to be individually driven, any one of the solenoid valves 9, 10, 11 and 12 may be selected.

For example, when the solenoid valve 9 is switched downward, electrical signals S1 and S3 are applied to the solenoid valves 6 and 8, respectively.

Accordingly, the solenoid valve 6 is switched downward, and the hydraulic oil discharged from the small capacity pump 2 passes through the solenoid valve 6, so that the pilot signal pressure generated through the pilot signal pressure passage 28 passes through the flow distribution valve ( Switch 3) downward.

As a result, the flow of hydraulic oil discharged from the first pump 1 flows from the main control valve 21 to the solenoid valves 9, 10, 11, 12 through the hydraulic supply passage 26 and the pivot joint 17. Are simultaneously supplied through the parallel passage 42.

At the same time, the pump signal pressure selection solenoid valve 8 is also switched downward by the electric signal S3, so that the pump signal pressure input to the first pump 1 is reduced by the pressure reducing valve 5 at the main control valve 21. Is changed to).

Then, the decompressed signal pressure p ₀ through the pressure reducing valve 5 is transmitted to the first pump 1 through the pump flow control signal passages 24 and 23, and eventually the discharge flow rate of the first pump 1 is reduced. As shown in FIG. 5, the proper flow rate is cut-up to become the required flow rate Q _{0 for} driving the outrigger device.

In this manner, the expansion cylinders 14-1, 14-2, 14-3, 14-4, or jack cylinders 15-1, 15-2, 15-3, and 15-4 are the first. Although driven at the required discharge flow rate of the pump 1, control of the flow rate discharged from the first pump 1 is made by the pressure reducing valve 5.

Accordingly, when the spring pressure provided in the pressure reducing valve 5 is adjusted, the expansion cylinders 14-1, 14-2, 14-3, 14-4 and the jack cylinder 15-1 of the outrigger device are adjusted. The speed of (15-2) (15-3) (15-4) can be increased or decreased.

That is, when the pump signal pressure of the pressure reducing valve 5 is smaller than the initial pump signal pressure p ₀ as shown in FIG. 5, the discharge flow rate of the first pump 1 increases and increases at the outrigger required flow rate Q ₀ . Cylinders and jack cylinders operate at high speed.

On the contrary, when the pump signal pressure of the pressure reducing valve 5 is greater than the initial pump signal pressure p ₀ , the discharge flow rate of the first pump 1 decreases at the outrigger required flow rate Q ₀ , so that the expansion cylinder and the jack cylinder have a low speed. Works.

In order to increase the speed of the expansion cylinder or the jack cylinder, there is no need to operate the engine acceleration / deceleration pedal or lever as in the prior art, and to increase the speed of the outrigger device as in the prior art by supplying only the required flow rate when controlling the outrigger device. There is no need to use an engine acceleration / deceleration pedal, thus improving the efficiency of the system without losing engine power.

In addition, the single actuator 1 allows the system actuator and the outrigger to be individually controlled, thereby reducing the cost.

As described above, according to the present invention, it is possible to improve the system efficiency by supplying only the required flow rate when controlling the working speed and the outrigger actuator by adjusting the speed of the outrigger actuator.

In addition, there is an energy saving effect induced by sending the total flow rate to the system actuator when not using the outrigger device, and a cost reduction effect obtained by enabling the control of the system actuator and the outrigger device with one pump.

Claims (3)

The variable pump 1 and the small capacity pump 2 for discharging the pressure oil and the pressure oil supplied from the variable pump 1 are selectively selected to the outrigger working machines 14-1 to 14-4 and 15-1 to 15-4. The outrigger control valve device 48 for supplying the gas to the work device, the main control valve 21 for selectively supplying the hydraulic oil supplied from the variable pump 1 to the work device, the small capacity pump 2 and the variable pump. Pressure reducing means for reducing the pressure oil of the small capacity pump 2 provided on the pump flow control signal passages 23 and 24 connecting the discharge flow rate control mechanism of (1) and the pump flow control signal passages 23 and 24. In the outrigger hydraulic system of an industrial vehicle consisting of a valve (5), The first flow path is installed on the pump supply pressure passage 25 of the variable pump 1 and supplies the pressure oil of the variable pump 1 to the outrigger control valve device 48 and the variable pump 1. A flow rate distribution valve (3) having a second flow path for supplying the pressurized oil to the main control valve (21), wherein the first and second flow paths are selectively switched; A pilot signal pressure passage (28) connecting one side pressure receiving portion (3) of the flow rate distribution valve (3) to the small capacity pump (2) and selectively switching the first and second flow paths of the flow rate distribution valve (3); An outrigger disposed on the pilot signal pressure passage 28 and including a solenoid valve 6 for communicating the oil pressure of the small capacity pump 2 to the signal pressure passage 28 by an outrigger operation signal S1. Hydraulic oil distribution device for the hydraulic circuit. The solenoid valve 8 of claim 1, wherein the solenoid valve 8 is switched on the pump flow control signal passages 23 and 24, and the solenoid valve 8 is switched according to the outrigger operation signal S3. The pump flow rate control signal passage 22 of the variable pump 1 supplied via the main flow valve and the pump flow rate control signal passage 24 of the small capacity pump (2) supplied via the Hydraulic fluid distribution device of the outrigger hydraulic circuit, characterized in that configured to be connected. 3. The third flow passage according to claim 1 or 2, wherein an orifice is placed on the first flow passage supplied to the outrigger control valve device 48 of the flow rate distribution valve 3 and supplied to the main control valve 21. Hydraulic fluid distribution device of the outrigger hydraulic circuit characterized in that it further comprises.

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