WO2023070969A1

WO2023070969A1 - Hydraulic control valve group, hydraulic system, and operation machine

Info

Publication number: WO2023070969A1
Application number: PCT/CN2022/073535
Authority: WO
Inventors: 李俊; 杨敏; 胡涛
Original assignee: 三一汽车制造有限公司
Priority date: 2021-10-31
Filing date: 2022-01-24
Publication date: 2023-05-04
Also published as: CN113898633A

Abstract

A hydraulic control valve group, a hydraulic system, and an operation machine. The hydraulic control valve group comprises a proportional valve (1) and a pressure regulating valve (2), wherein the pressure regulating valve (2) comprises an oil inlet connected to a main oil circuit of a main valve, an oil outlet for returning oil, and a remote pressure regulating port connected to an oil outlet of the proportional valve (1); a corresponding control flow is output from the oil outlet of the proportional valve (1) according to the pressure of the main oil circuit of the main valve; and the pressure regulating valve (2) adjusts the opening degree of a valve port thereof according to the control flow that is output by the proportional valve (1). A safe pressure value is preset for the pressure regulating valve, and during operation, the control flow at the oil outlet of the proportional valve is controlled according to the pressure of the main oil circuit of the main valve, and is transmitted to the remote pressure regulating port. A real-time pilot control pressure required by the pressure regulating valve is then calculated according to the control flow, and the opening degree of the valve port of the pressure regulating valve is adjusted, such that the control pressure of the pressure regulating valve is proportionally reduced, and a pressure peak value of a system is reduced during reversing, thereby reducing the system impact, and alleviating the shaking caused by the impact without losing the pumping efficiency and pumping continuity.

Description

Hydraulic control valve group, hydraulic system and working machinery

Cross References to Related Applications

This application claims the priority of Chinese patent application No. 202111278863.1, filed on October 31, 2021, entitled "Hydraulic control valve group, hydraulic system and working machinery", which is incorporated herein by reference in its entirety.

technical field

The present application relates to the technical field of engineering machinery, in particular to a hydraulic control valve group, a hydraulic system and an operating machine.

Background technique

The current overload protection scheme for the concrete pumping hydraulic system is to set a system overflow pressure higher than the cut-off pressure of the main oil pump in the system, and the pressure value is as high as 35MPa and above. Therefore, the system often works under high pressure and large flow, and the peak value of the pressure shock at the moment of each reversing will also reach the set system overflow pressure. Such a high pressure shock not only increases the noise generated by the commutation, seriously affects the stability and service life of the system components, but also brings greater vibration to the whole machine.

In order to reduce the impact of reversing, the existing technical solution is to reduce the impact pressure by reducing the displacement of the oil pump or opening the unloading valve instantaneously when the main valve is reversing. However, this will reduce the pumping efficiency and will also cause a gap in the system pumping pressure, which will negatively affect the pumping continuity.

Contents of the invention

The purpose of this application is to provide a hydraulic control valve group, a hydraulic system and a working machine to solve the problems existing in the prior art.

The application provides a hydraulic control valve group, including:

The proportional valve is used to output a corresponding control flow from the oil outlet of the proportional valve according to the pressure of the main oil circuit of the main valve;

A pressure regulating valve, including an oil inlet connected to the main oil circuit of the main valve, an oil outlet for oil return, and a remote pressure regulating port connected to the oil outlet of the proportional valve, the pressure regulating valve The valve port opening of the pressure regulating valve can be adjusted according to the control flow output by the proportional valve.

According to the hydraulic control valve group provided in this application, it also includes a cartridge valve and a control valve, the oil inlet of the cartridge valve is connected to the main oil circuit of the main valve, and the control oil port of the cartridge valve is connected to the main oil circuit of the main valve. The first working oil port of the control valve is connected, and the oil outlet of the control valve is used for oil return,

Wherein, when the first working oil port of the control valve is connected with the oil outlet of the control valve, the control oil port of the cartridge valve is connected with the oil outlet of the control valve.

The hydraulic control valve group provided according to this application also includes:

The first oil circuit and the second oil circuit, one end of the first oil circuit is connected to the main oil circuit of the main valve, one end of the second oil circuit is connected to the high pressure control oil circuit of the main valve, and the first oil circuit The other end of the passage and the other end of the second oil passage are both connected to the oil inlet of the control valve through the third oil passage;

a first one-way valve, arranged on the first oil passage, and conducting along the flow direction from the main oil passage of the main valve to the oil inlet of the control valve;

a second one-way valve, arranged on the second oil circuit, and conducting along the flow direction from the high-pressure control oil circuit of the main valve to the oil inlet of the control valve;

Wherein, when the first working oil port of the control valve is connected with the oil inlet port of the control valve, the control oil port of the cartridge valve is connected with the third oil passage via the control valve .

According to the hydraulic control valve group provided in this application, the control valve is configured as a solenoid valve,

Wherein, when the control valve is in the de-energized state, the first working oil port of the control valve is connected with the oil outlet of the control valve; when the control valve is in the energized state, The control valve communicates with the first working oil port of the control valve.

According to the hydraulic control valve group provided in the present application, the solenoid valve is configured as an unloading solenoid valve or a proportional solenoid valve.

According to the hydraulic control valve group provided in the present application, the pressure regulating valve is set as a relief valve.

The hydraulic control valve group provided according to the present application further includes a throttle valve, one end of the throttle valve is connected to the first working oil port of the control valve, and the other end is connected to the control oil port of the cartridge valve.

The present application also provides a hydraulic system, including the hydraulic control valve group described in any one of the above.

According to the hydraulic system provided in the present application, the hydraulic control valve group is arranged in a plate-mounted structure.

The present application further provides a work machine, comprising a vehicle body and a pumping hydraulic system arranged on the vehicle body, the pumping hydraulic system being the hydraulic system as described in any one of the above.

The hydraulic control valve group provided by this application includes a proportional valve and a pressure regulating valve. Among them, according to the pressure of the main oil circuit of the main valve, the oil outlet of the proportional valve outputs the corresponding control flow. The pressure regulating valve includes an oil inlet connected to the main oil circuit of the main valve, an oil outlet for oil return, and a remote pressure regulating port connected to the oil outlet of the proportional valve. The pressure regulating valve can be controlled according to the output of the proportional valve. The flow rate is used to adjust the valve port opening of the pressure regulating valve. With this setting, the pressure regulating valve presets a safe pressure value. When working, the control flow of the oil outlet of the proportional valve is controlled according to the pressure of the main oil circuit of the main valve, and is transmitted to the remote pressure regulating port. Then calculate the real-time pilot control pressure required by the pressure regulating valve based on the control flow, and adjust the opening of the pressure regulating valve, so that the control pressure of the pressure regulating valve will decrease proportionally, so that the peak pressure of the system can be reduced during the reversing. Cut, reduce the system impact, reduce the jitter caused by the impact, without losing pumping efficiency and pumping continuity.

Description of drawings

In order to more clearly illustrate the technical solutions in the present application or the prior art, the following will briefly introduce the accompanying drawings that need to be used in the description of the embodiments or the prior art. Obviously, the accompanying drawings in the following description are the For some embodiments of the present invention, those of ordinary skill in the art can also obtain other drawings based on these drawings on the premise of not paying creative efforts.

Fig. 1 is the schematic diagram of the principle of the hydraulic control valve group provided by the present application;

Reference signs:

1: Proportional valve; 2: Pressure regulating valve; 3: Cartridge valve;

4: Reversing valve; 5: The first one-way valve; 6: The second one-way valve;

7: throttle valve; 8: first oil circuit; 9: second oil circuit;

10: The third oil circuit; 11: Oil tank; 12: Oil drain port.

Detailed ways

In order to make the purpose, technical solutions and advantages of this application clearer, the technical solutions in this application will be clearly and completely described below in conjunction with the accompanying drawings in this application. Obviously, the described embodiments are part of the embodiments of this application , but not all examples. Based on the embodiments in this application, all other embodiments obtained by persons of ordinary skill in the art without creative efforts fall within the protection scope of this application.

The hydraulic control valve group of the present application will be described below with reference to FIG. 1 .

As shown in FIG. 1 , the embodiment of the present application provides a hydraulic control valve group, including a proportional valve 1 and a pressure regulating valve 2 . Specifically, according to the pressure of the main oil circuit of the main valve, the oil outlet (port 1) of the proportional valve 1 outputs the corresponding control flow. Pressure regulating valve 2 includes an oil inlet (port 1) connected to the main oil circuit (P1) of the main valve, an oil outlet (port 2) for oil return, and a remote regulator connected to the oil outlet of proportional valve 1. Pressure port (3 ports). Wherein, the oil outlet (2 ports) can be directly connected to the oil tank 11 . The pressure regulating valve 2 can adjust the valve port opening of the pressure regulating valve 2 according to the control flow output by the proportional valve 1 .

Specifically, the proportional valve 1 adopts an electro-hydraulic proportional valve, the electric signal is convenient to transmit, and remote control can be realized. When working, the pressure sensor in the main oil circuit of the main valve detects the real-time pressure of the system, and sends the pressure signal to the proportional valve 1. According to the input signal, the oil outlet (port 1) of the proportional valve 1 outputs the control flow in proportion. For example, as shown in Figure 1, a two-position three-way proportional valve is used, and its oil outlet (port 1) is connected to the remote pressure regulating port of the pressure regulating valve 2. Its oil inlet (port 2) is connected to the high-pressure control oil circuit (Gp) of the main valve, and the high-pressure control oil circuit of the main valve is connected to the accumulator, and the accumulator provides high-pressure control oil. Its oil return port (port 3) is connected to the control oil return oil circuit of the main valve, and then flows back to the oil tank 11 for oil return. As shown in FIG. 1 , an oil drain port 12 connected to an oil tank 11 can be provided on the hydraulic control valve group, and the oil return port (3 ports) of the proportional valve 1 can be connected to the oil drain port 12 . It can be seen from the above that the oil return port of the proportional valve 1 and the oil outlet port of the pressure regulating valve 2 are both used for oil return and flow to the oil tank 11 . Wherein the oil tank 11 can be provided with one or more, and its specific quantity can be determined according to actual conditions. Specifically, the proportional valve 1 has a first working position and a second working position. When the proportional valve 1 is in the de-energized state, the proportional valve 1 is in the first working position (the lower position in Figure 1), at this time, the oil outlet (1 port) and the oil return port (3 port) of the proportional valve 1 are connected, and the The oil port (2 ports) is closed; then, the remote pressure regulating port of the pressure regulating valve 2 is connected to the oil drain port 12 via the proportional valve 1 to discharge oil, then the proportional valve 1 does not work, and the pressure regulating valve 2 is not adjusted and controlled. When the proportional valve 1 is in the energized state, the proportional valve 1 is in the second working position (upper position in Fig. 1). The oil port (port 3) is closed; then, based on the input electrical signal, the proportional valve 1 outputs the corresponding control flow in proportion, and the control pressure of the pressure regulating valve 2 drops accordingly. It should be noted that, in terms of the position and state of the hydraulic control valve group as shown in Figure 1, the left and right directions in the figure refer to the up and down positions, the left side in the figure is the upper position, and the right side is the lower position.

The pressure regulating valve 2 adopts a large-flow relief valve, which can preset a basic safe relief pressure value, such as 35Mpa. When working, the pressure regulating valve 2 calculates the real-time pilot control pressure required by the external control port of the pressure regulating valve 2 according to the control flow obtained from the remote pressure regulating port, so that the control pressure of the pressure regulating valve 2 decreases proportionally. Therefore, when the system changes direction, the remote pressure regulating port of the pressure regulating valve 2 has a certain pressure of control oil flowing in, entering the spring chamber to push the control spring, so that the opening ratio of the valve port is increased, so that the pressure required for the relief valve to open The overflow pressure becomes smaller, and the adaptive adjustment of the overflow pressure with the main system pressure is realized. At this time, at the moment when the large flow rate requires quick reversing, part of the oil can be released through the pressure regulating valve 2 and returned to the oil tank 11, effectively reducing the pressure shock peak value at the moment of oil circuit opening and closing, and reducing the pressure shock of the system.

In this way, the pressure regulating valve 2 presets a safe pressure value. When working, the control flow of the oil outlet of the proportional valve 1 is controlled according to the pressure of the main oil circuit of the main valve, and transmitted to the remote pressure regulating port. Then calculate the real-time pilot control pressure required by the pressure regulating valve 2 according to the control flow, and adjust the valve opening of the pressure regulating valve 2, so that the control pressure of the pressure regulating valve 2 will decrease proportionally. When the system is reversing, the pressure regulating valve 2 can be opened briefly, so that the pressure peak of the system can be reduced during the reversing, the system impact is reduced, and the jitter caused by the impact is reduced without losing pumping efficiency and pumping continuity.

In the embodiment of the present application, the hydraulic control valve group also includes a cartridge valve 3 and a control valve 4, and the control valve 4 can be a two-position four-way valve. The oil inlet (port A) of the cartridge valve 3 is connected to the main oil circuit (P1) of the main valve, and the control oil port (port X) of the cartridge valve 3 is connected to the first working oil port (port A) of the control valve 4 , The oil outlet (B port) of the cartridge valve 3 is connected with the oil tank 11. The oil outlet (T port) of the control valve 4 is used for oil return and can be connected with the oil drain port 12, and the second working oil port (B port) of the control valve 4 is blocked and closed.

Among them, when the first working oil port (A port) of the control valve 4 is connected with the oil outlet (T port) of the control valve 4, that is, in the left position in Fig. 1, the control oil port of the cartridge valve 3 (X port) is connected to the oil outlet (T port) of the control valve 4. In this way, in the standby state of the system, the oil in the spring control chamber of the cartridge valve 3 flows to the oil tank 11 through the control valve 4, and its control oil pressure is almost zero. As long as a slight pressure from the main oil circuit (P1) of the main valve acts on the oil inlet port (A port) of the cartridge valve 3, the cartridge valve 3 can be easily opened to allow the oil to flow back to the oil tank 11, so that the pressure of the whole system is very low. Low. Therefore, the cartridge valve 3 and the control valve 4 cooperate with each other, so that the system has an unloading function in the standby mode and reduces the standby power consumption of the system.

Further, the hydraulic control valve group also includes a first oil circuit 8 , a first one-way valve 5 , a second oil circuit 9 and a second one-way valve 6 . Specifically, one end of the first oil passage 8 is connected to the main oil passage (P1) of the main valve, one end of the second oil passage 9 is connected to the high pressure control oil passage (Gp) of the main valve, and the other end of the first oil passage 8 and the other end of the second oil passage 9 are connected to the oil inlet (port P) of the control valve 4 through the third oil passage 10 . The first one-way valve 5 is arranged on the first oil passage 8, and along the flow direction from the main oil passage of the main valve to the oil inlet of the control valve 4, that is, from left to right, the first one-way valve 5 is in a conduction state. The second one-way valve 6 is arranged on the second oil passage 9, and along the flow direction from the high-pressure control oil passage of the main valve to the oil inlet of the control valve 4, that is, from right to left, the second one-way valve 6 is in a conduction state . It should be noted that, in terms of the position and state of the hydraulic control valve group as shown in FIG. 1 , the up and down directions in the figure refer to the left and right directions, the lower part in the figure refers to the left side, and the upper part refers to the right side.

Among them, when the first working oil port (A port) of the control valve 4 is connected with the oil inlet port (P port) of the control valve 4, that is, in the right position in Fig. 1, the control oil port of the cartridge valve 3 It is connected to the third oil passage 10 via the control valve 4 . When the pressure of the main oil circuit of the main valve is higher than the pressure of the high-pressure control oil circuit of the main valve, the first one-way valve 5 is turned on, the second one-way valve 6 is turned off, and the hydraulic oil from the main oil circuit of the main valve finally flows to the cartridge valve 3 of the spring control cavity, so that the cartridge valve is in the closed state, and the system enters the working state. When the pressure of the high-pressure control oil circuit of the main valve is higher than the pressure of the main oil circuit of the main valve, the second check valve 6 is turned on, the first check valve 5 is turned off, and the hydraulic oil from the high-pressure control oil circuit of the main valve finally flows to the cartridge The spring of the valve 3 controls the chamber so that the cartridge valve is in the closed state and the system enters the working state. In this way, after comparing the pressure of the high-pressure control oil circuit of the main valve and the main oil circuit of the main valve, only one high-pressure hydraulic oil acts on the spring control chamber of the cartridge valve 3, so that when the high-pressure and low-pressure pumping are switched, the cartridge Valve 3 is in the closed state, and the system enters the working state. Cartridge valve 3 will not open during reversing, which can reduce oil return impact.

In the embodiment of the present application, the control valve 4 is configured as a solenoid valve, such as a two-position four-way solenoid valve, so that the power-off and power-on states of the solenoid valve can also be controlled by the controller. The controller can be set independently, or the controller that controls the main valve can also be used. When the control valve 4 is in the power-off state, the first working oil port of the control valve 4 communicates with the oil outlet of the control valve 4, that is, it is in the left position in FIG. 1 . When the control valve 4 is in the electrified state, the oil inlet port of the control valve 4 communicates with the first working oil port of the control valve 4, that is, it is in the right position in FIG. 1 . Specifically, the solenoid valve can be an unloading solenoid valve or a proportional solenoid valve.

In the embodiment of the present application, the hydraulic control valve group further includes a throttle valve 7, and the flow rate of the throttle valve 7 can be adjusted, so that the flow rate of the oil can be controlled. One end of the throttle valve 7 is connected to the first working oil port (A port) of the control valve 4 , and the other end is connected to the control oil port (X port) of the cartridge valve 3 . In this way, the throttle valve 7 is used to control the oil pressure flowing to the spring control chamber of the cartridge valve 3, slow down the impact on the cartridge valve 3, prevent its vibration from being too large, and provide system security.

The hydraulic system provided by the present application is described below, and the hydraulic system described below and the hydraulic control valve group described above can be referred to in correspondence.

The embodiment of the present application also provides a hydraulic system, including the hydraulic control valve group in the above embodiments. In this way, the proportional relief valve group functional module assembly formed by the combination of the proportional valve 1 and the pressure regulating valve 2 with a remote pressure regulating port can realize the adaptive adjustment of the relief pressure with the pressure of the main oil circuit of the main valve. When the system changes direction, the pressure regulating valve 2 can be opened briefly, so that the peak pressure of the system can be reduced, the system impact can be reduced, and the vibration caused by the impact can be reduced without losing pumping efficiency and pumping continuity. The derivation process of this beneficial effect is roughly similar to the derivation process of the above-mentioned beneficial effect of the hydraulic control valve group, so it will not be repeated here.

Further, the hydraulic control valve group is arranged as a board-type installation structure. In this way, the valve group is made into a standard plate installation form, which is easy to install and can be easily applied to different hydraulic systems.

The working machine provided by the present application is described below, and the working machine described below and the hydraulic system described above can be referred to in correspondence.

The embodiment of the present application further provides an operating machine, specifically, for example, a concrete pump truck. The working machine includes a vehicle body and a pumping hydraulic system arranged on the vehicle body, and the pumping hydraulic system is the hydraulic system in the above embodiments. In this way, the proportional relief valve group functional module assembly formed by the combination of the proportional valve 1 and the pressure regulating valve 2 with a remote pressure regulating port can realize the adaptive adjustment of the relief pressure with the pressure of the main oil circuit of the main valve. When the system changes direction, the pressure regulating valve 2 can be opened briefly, so that the peak pressure of the system can be reduced, the system impact can be reduced, and the vibration caused by the impact can be reduced without losing pumping efficiency and pumping continuity. The derivation process of the beneficial effect is roughly similar to the derivation process of the above-mentioned beneficial effect of the hydraulic system, so it will not be repeated here.

Finally, it should be noted that: the above embodiments are only used to illustrate the technical solutions of the present application, rather than limiting them; although the present application has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that: it can still Modifications are made to the technical solutions described in the foregoing embodiments, or equivalent replacements are made to some of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the various embodiments of the present application.

Claims

A hydraulic control valve group, characterized in that it comprises:

The proportional valve is used to output a corresponding control flow from the oil outlet of the proportional valve according to the pressure of the main oil circuit of the main valve;

A pressure regulating valve, including an oil inlet connected to the main oil circuit of the main valve, an oil outlet for oil return, and a remote pressure regulating port connected to the oil outlet of the proportional valve, the pressure regulating valve The valve port opening of the pressure regulating valve can be adjusted according to the control flow output by the proportional valve.
The hydraulic control valve group according to claim 1, further comprising a cartridge valve and a control valve, the oil inlet of the cartridge valve is connected to the main oil circuit of the main valve, and the oil inlet of the cartridge valve is The control oil port is connected to the first working oil port of the control valve, and the oil outlet of the control valve is used for oil return,

Wherein, when the first working oil port of the control valve is connected with the oil outlet of the control valve, the control oil port of the cartridge valve is connected with the oil outlet of the control valve.
The hydraulic control valve group according to claim 2, further comprising:

The first oil circuit and the second oil circuit, one end of the first oil circuit is connected to the main oil circuit of the main valve, one end of the second oil circuit is connected to the high pressure control oil circuit of the main valve, and the first oil circuit The other end of the passage and the other end of the second oil passage are both connected to the oil inlet of the control valve through the third oil passage;

a first one-way valve, arranged on the first oil passage, and conducting along the flow direction from the main oil passage of the main valve to the oil inlet of the control valve;

a second one-way valve, arranged on the second oil circuit, and conducting along the flow direction from the high-pressure control oil circuit of the main valve to the oil inlet of the control valve;

Wherein, when the first working oil port of the control valve is connected with the oil inlet port of the control valve, the control oil port of the cartridge valve is connected with the third oil passage via the control valve .
The hydraulic control valve group according to claim 3, wherein the control valve is configured as a solenoid valve,

Wherein, when the control valve is in the de-energized state, the first working oil port of the control valve is connected with the oil outlet of the control valve; when the control valve is in the energized state, The oil inlet port of the control valve communicates with the first working oil port of the control valve.
The hydraulic control valve group according to claim 4, wherein the solenoid valve is configured as an unloading solenoid valve or a proportional solenoid valve.
The hydraulic control valve group according to claim 1, wherein the pressure regulating valve is set as a relief valve.
The hydraulic control valve group according to any one of claims 2-6, further comprising a throttle valve, one end of the throttle valve is connected to the first working oil port of the control valve, and the other end is connected to the first working oil port of the control valve. The control port of the cartridge valve is connected.
A hydraulic system, characterized by comprising the hydraulic control valve group according to any one of claims 1-7.
The hydraulic system according to claim 8, characterized in that, the hydraulic control valve group is arranged as a board-type installation structure.
An operating machine, comprising a vehicle body and a pumping hydraulic system arranged on the vehicle body, characterized in that the pumping hydraulic system is the hydraulic system according to any one of claims 8-9.