KR820002436Y1 - Fluid control valve system - Google Patents

Abstract

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Description

Fluid Control Valve

The accompanying drawings are a schematic diagram of a fluid control valve with a primary and fluid actuator and a control valve mechanism.

The present invention relates to a fluid control valve system having a directional control valve for measuring the flow of fluid from the supply tank to the supply cylinder of the primary actuator. The pressure compensating valve is configured to regulate the flow of fluid through the directional control valve and to supply excess fluid to the compensating valve outlet to power the secondary actuator.

The main relief valve is connected downstream of the supply passage of the primary actuator from the measuring section of the directional control valve to detect stall conditions of the primary actuator.

When the main relief valve is activated, it detects an overload condition and transfers fluid from the supply passage through the metering section of the directional control valve to the relief passage with the tank and the main relief valve. The fluid velocity through the relief passage is limited only by the metered portion of the directional valve.

The present invention is related to the inventors of the United States Patent Nos. 3,911,942 and 4,003,202, which are incorporated herein by reference to better understand the background of the present invention. Accordingly, the present invention relates to a fluid control valve used to control fluid power operation of a plurality of fluid actuators of the present invention, and particularly relates to an improvement in the use of a main relief valve in this system.

For example, in a fluid control valve system, the primary hydraulic actuator powers a linked vehicle and the secondary actuator is used to manipulate the vehicle's mechanism. Directional control valves, together with pressure compensation valves, are used to control power steering, which gives priority to power control when used to operate both power control and machinery using a single fluid source.

A common practice for systems that operate multiple fluidic devices from a single fluid source is the upstream flow of main relief valves from primary directional control valves, such as in Tennis Patent No. 3,722,543. In addition to controlling the supply, by controlling the pressure compensator for the primary actuator as disclosed in the inventor's patent No. 3,911,942, the secondary actuator can be operated in the case of stall of the primary actuator. In these systems, sudden changes in pressure, especially when used for power control, result in changes in the measuring range of the compensating spool, thus causing unnecessary sudden changes in fluid oil.

The object of the present invention is to manufacture a fluid control system that eliminates one or more of the limitations found in such a conventional system, as well as to eliminate the need for multiple fluid power sources to effectively and efficiently operate multiple actuators in a linked vehicle. Simplify the operable fluid control valve system.

A single fluid power source is used to create a fluid control valve that can be operated with fluid power for the primary and secondary actuators that can control the power control and mechanism of the connected vehicle, respectively. To control the flow of fluid from the supply passage to the primary supply passage, and to configure the pressure compensation valve to control the flow of fluid through the directional control valve and to send excess fluid to the outlet of the compensation valve. It allows the power operation of the secondary actuator. The main relief valve is connected to the downstream of the supply passage of the primary actuator from the measurement section of the directional control valve to detect the stall of the primary actuator. The main relief valve controls the flow of fluid from the supply passage through the metering section of the directional valve to the relief passage as it detects fluid movement and stall conditions.

The flow rate through the relief passage is limited only by the metered portion of the directional valve.

In order to better understand the present invention, it will be described in detail with reference to the accompanying drawings. In the figure, the fluid control valve device is composed of the primary and secondary fluid actuators 10 and 11 and the control valve mechanism 12 so that the fluid control valve device 1 is controlled from the supply passage 13 depending on the control direction by the direction control valve 16. The fluid movement to the supply passage 14 or 15 of the primary actuator is controlled.

The pressure compensation valve 17 is configured to control the flow of fluid through the directional control valve 16 and to send excess fluid power to the outlet 18 of the compensation valve to operate the secondary actuator 11.

When the directional control valve 16 is operated to the left operation position, the main relief valve 19 flows downwardly from the supply passage 14 of the primary actuator coming from the measurement section 20 of the directional control valve 16. Connected to the side.

When the main relief valve 19 is opened as the pressure in the supply passage 14 increases, the flow rate limited by the measurement section 20 of the directional control valve 16 supplies the fluid toward the tank T. Relax As the pressure difference occurs on the opposite side of the measurement control portion 20 of the directional control valve 16, the compensation valve 17 is operated, which is obtained through the angular passages 21 and 22 and the control portions 23 and 24. Same as

When the pressure in the passages 21 and 22 is applied to the opposite end of the spool of the compensation valve 17, the fluid movement is regulated through the measurement control portion 20 of the direction control valve 16 as usual.

Since it has such an operation method and a main element, it is necessary to detail the typical operation conditions of this system.

The system illustrated in the figure is in a non-operational state in which no fluid pressure is applied and the directional control valve 16 is in the center position. In this position, the spring chamber at the right end of the compensation valve 17 is routed through the control section 24, the passages 22 and 31, the directional control valve 16 and the tank passage 25 in the center position. Connect to tank (T). The spring 26 actuates the sprue of the compensating valve 17 to the left position as illustrated in the figure.

When pressure is applied to this system by the pump P, the chamber at the left end of the compensation valve 17 is pressurized at the pressure at which the passage 21 is supplied through the control part 23.

In this case, the compensation valve 17 immediately moves to the right position to apply pressure from the supply passage 13 to the closed central portion of the direction control valve 16 through the control portion 27 and the passage 28.

Bypass of the fluid to be supplied is exerted through the passage 29 of the valve 17 toward the outlet 18 and fed through the passage 30 toward the actuation valve and the actuator 11.

This of course causes one or both of the steering actuator 10 and the actuator 11 to be operated. It can be assumed here that when the driver turns the direction control valve 16 to the left, the driver controls the operation of the steering actuator 10.

This connects the supply passage 28 to the supply passage 14 via the measurement control portion 20.

The supply passage 14 also passes through the passage 31 to the main relief valve 19 and passes through the passages 31 and 22 and the control portion 24 to the spring chamber at the right end of the compensation valve 17. do. The chamber at the left end of the compensation valve 17 is subjected to a high pressure applied through the passage 17, the control portion 27, the passage 21 and the control portion 23. In this case, the compensation valve 17 operates due to a slight difference between the input pressure and the output pressure generated through the measurement portion 20 of the directional control valve 16, thereby controlling the supply of the fluid to the control actuator 10. do.

The overload relief valves 32 and 33 are connected in various passages between the power control supplies 14 and 15 and the tank T via the direction control valve 16 and the passage 25 in the center position. For example, they are opened at a pressure of about 500 psi depending on the fixing of the main relief valve 19.

These overload relief valves 32 and 33 relieve the pressure returned from the cylinder 10 when the direction control valve 16 is centered when the vehicle passes through the irregular area.

These overload relief valves become ineffective if the directional control valves 16 operate out of the center position. However, when the direction control valve 16 is out of the center position, the main relief valve 19 operates only in the open position through the measurement control portion 20.

The anti-cavity vortex valves 34 and 35 are connected in combination with the overload relief valves 32 and 33 but are connected in opposite directions to the normal valves 32 and 33.

In view of the operation method of operating the power steering mechanism 10 in one direction by applying pressure to the supply passage 14 as described above, it is obvious that the direction control valve 16 is operated by operating the direction control valve 16 to the right position. The same operation is effectively applied in operating the actuator 10 in the opposite direction by the fluid pressure in the supply passage 15.

Allows the male relief valve 19 to maintain fluid through the metering section 20 and also the position of the compensation valve 17 relative to the rapid pressure change in the actuator 10 and the water spring position of the given directional control valve 16. By not changing the range rapidly, unnecessary flow rate changes in the fluid control valves do not occur. The fluid is supplied from the supply passageway 28 when the main relief valve 19 is in the operating position, and the fluid is supplied when the main control valve 20, the passage 31, and the main relief valve 19 are in the operating position. It flows from the passage 28 through the measurement control part 20, the passage 31, the main relief valve 19, the passage 350, the low pressure relief valve 36 and the passage 37.

The use of the low pressure relief valve 36 in this circuit ensures that at least some pressure is maintained in the system in the event of a malfunction of the main relief valve 19 which ensures that the valve is in the operating position.

Claims (1)

A directional control valve device for measurement is configured to control fluid movement from the supply passage to the supply passage 14 of the primary actuator 10, and a pressure compensation valve 17 is configured to control the flow through the directional control valve 16. To control the fluid power operation of the primary and secondary actuators 10 and 11 to regulate the fluid and direct excess fluid to the outlet 18 of the compensating valve 17 for power operation of the secondary actuator 11. In the fluid control valve device, the primary actuator is connected by connecting the main relief valve 19 to the downstream of the supply passage 14 of the primary actuator 10 coming from the measurement portion 20 of the directional valve 16. To detect the stall state of the primary relief valve 19 and constitute a device controlled by the main relief valve 19 so that the supply passage through the measuring portion 20 of the direction control valve 16 immediately after the stall state of the primary actuator is detected. Supply fluid from the tank 14 to the tank T, and also including a main relief valve 19 A fluid control valve apparatus, characterized in that, and to supply the fluid into the loop path, so as to limit the flow rate through the relief passage only by the measurement portion 20 of the direction control valve 16.