Hydraulic control valve group, hydraulic system and operating machinery

Abstract

The present invention provides a hydraulic control valve group, a hydraulic system and an operating machine, including a proportional valve and a pressure regulating valve. The pressure regulating valve includes an oil inlet connected to the main oil circuit of the main valve, an oil outlet for returning oil and a remote pressure regulating port connected to the oil outlet of the proportional valve. According to the main oil circuit pressure of the main valve, the oil outlet of the proportional valve outputs a corresponding control flow. The pressure regulating valve adjusts the valve port opening according to the control flow output by the proportional valve. In this way, the pressure regulating valve pre-sets a safety pressure value. When working, the control flow of the oil outlet of the proportional valve is controlled according to the main oil circuit pressure of the main valve, and is transmitted to the remote pressure regulating port. Then, the real-time pilot control pressure required by the pressure regulating valve is calculated based on the control flow, and the valve port opening of the pressure regulating valve is adjusted, so that the control pressure of the pressure regulating valve is proportionally reduced, so that the pressure peak of the system during switching can be reduced, the system impact is reduced, and the jitter caused by the impact is mitigated without losing the pumping efficiency and pumping continuity.

Description

Technical Field

[0001] The present invention relates to the technical field of engineering machinery, and in particular to a hydraulic control valve group, a hydraulic system and an operating machine. Background Art

[0002] At present, the overload protection scheme of 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 each switching moment will also reach the set system overflow pressure. Such a high pressure shock not only increases the noise generated by the switching, seriously affecting the stability and service life of the system components, but also brings greater vibration to the whole machine.

[0003] In order to reduce the switching shock, the existing technical solution is to reduce the shock pressure by reducing the oil pump displacement or instantaneously opening the unloading valve when the main valve is switched. However, this will reduce the pumping efficiency and also cause a gap in the system pumping pressure, which will have a negative impact on the pumping continuity. Summary of the invention

[0004] The purpose of the present invention is to provide a hydraulic control valve group, a hydraulic system and an operating machine to solve the problems existing in the prior art.

[0005] The present invention provides a hydraulic control valve group, comprising:

[0006] A proportional valve, used to output a corresponding control flow at the oil outlet of the proportional valve according to the pressure of the main oil circuit of the main valve;

[0007] The pressure regulating valve comprises an oil inlet connected to the main oil circuit of the main valve, an oil outlet for returning oil, and a remote pressure regulating port connected to the oil outlet of the proportional valve. The pressure regulating valve can adjust the valve opening size of the pressure regulating valve according to the control flow output by the proportional valve.

[0008] The hydraulic control valve group provided by the present invention further comprises a cartridge valve and a control valve, wherein the oil inlet of the cartridge valve is connected to the main oil circuit of the main valve, the control oil port of the cartridge valve 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.

[0009] Wherein, when the first working oil port of the control valve is communicated 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.

[0010] The hydraulic control valve group provided by the present invention further includes:

[0011] a first oil circuit and a second oil circuit, wherein 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 other ends of the first oil circuit and the second oil circuit are both connected to the oil inlet of the control valve through a third oil circuit;

[0012] A first one-way valve, arranged on the first oil circuit and conducting along the flow direction from the main oil circuit of the main valve to the oil inlet of the control valve;

[0013] A second one-way valve is arranged on the second oil circuit and is connected along the flow direction of the main valve high-pressure control oil circuit to the oil inlet of the control valve;

[0014] Wherein, when the first working oil port of the control valve is connected to the oil inlet of the control valve, the control oil port of the cartridge valve is connected to the third oil circuit via the control valve.

[0015] According to the hydraulic control valve group provided by the present invention, the control valve is configured as a solenoid valve.

[0016] Among them, when the control valve is in a power-off state, the first working oil port of the control valve is connected to the oil outlet of the control valve; when the control valve is in a power-on state, the control valve is connected to the first working oil port of the control valve.

[0017] According to the hydraulic control valve group provided by the present invention, the solenoid valve is configured as a unloading solenoid valve or a proportional solenoid valve.

[0018] According to the hydraulic control valve group provided by the present invention, the pressure regulating valve is configured as a relief valve.

[0019] The hydraulic control valve group provided according to the present invention further comprises a throttle valve, one end of which is connected to the first working oil port of the control valve, and the other end of which is connected to the control oil port of the cartridge valve.

[0020] The present invention also provides a hydraulic system, comprising the hydraulic control valve group as described in any one of the above items.

[0021] According to the hydraulic system provided by the present invention, the hydraulic control valve group is configured as a plate-type mounting structure.

[0022] The present invention further provides a working machine, comprising a vehicle body and a pumping hydraulic system arranged on the vehicle body, wherein the pumping hydraulic system is a hydraulic system as described in any one of the above items.

[0023] The hydraulic control valve group provided by the present invention includes a proportional valve and a pressure regulating valve. According to the pressure of the main oil circuit of the main valve, the oil outlet of the proportional valve outputs a 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 returning oil, and a remote pressure regulating port connected to the oil outlet of the proportional valve. The pressure regulating valve can adjust the valve port opening size of the pressure regulating valve according to the control flow output by the proportional valve. In this way, the pressure regulating valve pre-sets a safety pressure value. When working, the control flow of the proportional valve oil outlet is controlled according to the main oil circuit pressure of the main valve, and is transmitted to the remote pressure regulating port. Then, the real-time pilot control pressure required by the pressure regulating valve is calculated based on this control flow, and the opening size of the valve port of the pressure regulating valve is adjusted, so that the control pressure of the pressure regulating valve is proportionally reduced, so that the pressure peak of the system can be reduced during switching, the system impact is reduced, and the jitter caused by the impact is mitigated without losing the pumping efficiency and pumping continuity. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the technical solutions in the present invention or the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0025] Figure 1 It is a schematic diagram of the principle of the hydraulic control valve group provided by the present invention;

[0026] Reference numerals:

[0027] 1: Proportional valve; 2: Pressure regulating valve; 3: Cartridge valve;

[0028] 4: reversing valve; 5: first check valve; 6: second check valve;

[0029] 7: throttle valve; 8: first oil circuit; 9: second oil circuit;

[0030] 10: The third oil circuit; 11: Oil tank; 12: Oil drain port. DETAILED DESCRIPTION

[0031] In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be clearly and completely described below in conjunction with the drawings of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0032] Combine the following Figure 1 The hydraulic control valve group of the present invention is described.

[0033] like Figure 1 As shown, an embodiment of the present invention 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 a corresponding control flow. The 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 returning oil, and a remote pressure regulating port (port 3) connected to the oil outlet of the proportional valve 1. Among them, the oil outlet (port 2) can be directly connected to the oil tank 11. The pressure regulating valve 2 can adjust the valve port opening size of the pressure regulating valve 2 according to the control flow output by the proportional valve 1.

[0034] Specifically, the proportional valve 1 adopts an electro-hydraulic proportional valve, and the electrical signal is easy to transmit, which can realize remote control. When working, the pressure sensor of the main oil circuit of the main valve detects the real-time pressure of the system and transmits the pressure signal to the proportional valve 1. According to the input signal, the oil outlet (1 port) of the proportional valve 1 outputs the control flow in proportion. For example, Figure 1 As shown, 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 main valve high-pressure control oil circuit (Gp), and the main valve high-pressure control oil circuit is connected to the accumulator, which 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. Figure 1 As shown, an oil drain port 12 connected to the oil tank 11 can be set on the hydraulic control valve group, and the oil return port (3) of the proportional valve 1 can be connected to the oil drain port 12. As can be seen from the above, the oil return port of the proportional valve 1 and the oil outlet of the pressure regulating valve 2 are both used for returning oil and flowing to the oil tank 11. One or more oil tanks 11 can be set, and the specific number 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 a power-off state, the proportional valve 1 is in the first working position ( Figure 1 At this time, the oil outlet (port 1) and the oil return port (port 3) of proportional valve 1 are connected, and the oil inlet (port 2) is cut off; then, the remote pressure regulating port of pressure regulating valve 2 is connected to the oil drain port 12 through proportional valve 1 to drain oil, and proportional valve 1 does not work, and does not regulate and control pressure regulating valve 2. When proportional valve 1 is in the energized state, proportional valve 1 is in the second working position ( Figure 1 At this time, the oil outlet (port 1) and the oil inlet (port 2) of the proportional valve 1 are connected, and the oil return port (port 3) is cut off; 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 decreases accordingly. It should be noted that, Figure 1 As for the position state of the hydraulic control valve group shown in the figure, the left and right directions in the figure refer to the upper and lower positions, the left side in the figure is the upper position, and the right side is the lower position.

[0035] The pressure regulating valve 2 adopts a large flow relief valve, and a basic safety relief pressure value can be pre-set, such as 35Mpa. During operation, the pressure regulating valve 2 reversely 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 is switched, a control oil with a certain pressure flows into the remote pressure regulating port of the pressure regulating valve 2, enters the spring chamber to push the control spring, so that the valve port opening ratio increases, thereby reducing the relief pressure required to open the relief valve, and realizing the adaptive adjustment of the relief pressure with the main system pressure. At this time, at the moment when a large flow rate requires rapid switching, part of the oil can be released through the pressure regulating valve 2 to return to the oil tank 11, effectively reducing the pressure shock peak at the moment of opening and closing the oil circuit, and reducing the pressure shock of the system.

[0036] In this way, the pressure regulating valve 2 is pre-set with a safety pressure value. When working, the control flow of the oil outlet of the proportional valve 1 is controlled according to the main oil circuit pressure of the main valve, and transmitted to the remote pressure regulating port. Then, the real-time pilot control pressure required by the pressure regulating valve 2 is calculated based on this control flow, and the valve opening size of the pressure regulating valve 2 is adjusted, so that the control pressure of the pressure regulating valve 2 decreases proportionally. When the system is switched, the pressure regulating valve 2 can be opened briefly, so that the pressure peak of the system during the switching can be reduced, the system impact is reduced, and the jitter caused by the impact is mitigated without losing the pumping efficiency and pumping continuity.

[0037] In the embodiment of the present invention, the hydraulic control valve group further 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, 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, and the oil outlet (port B) of the cartridge valve 3 is connected to the oil tank 11. The oil outlet (port T) of the control valve 4 is used for oil return and can be connected to the oil drain port 12, and the second working oil port (port B) of the control valve 4 is cut off and closed.

[0038] Among them, 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, Figure 1 In the middle left position, the control oil port (X port) of the cartridge valve 3 is connected to the oil outlet (T port) of the control valve 4. In this way, when the system is in standby mode, 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 there is a slight pressure in the main oil circuit (P1) of the main valve acting on the oil inlet (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, making the pressure of the entire system very low. Therefore, the cartridge valve 3 and the control valve 4 work in coordination with each other, so that the system has the function of unloading in standby mode, reducing the system standby power consumption.

[0039] Furthermore, 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 circuit 8 is connected to the main oil circuit (P1) of the main valve, one end of the second oil circuit 9 is connected to the main valve high-pressure control oil circuit (Gp), and the other end of the first oil circuit 8 and the other end of the second oil circuit 9 are both connected to the oil inlet (P port) of the control valve 4 through the third oil circuit 10. The first one-way valve 5 is arranged on the first oil circuit 8, and the flow direction along the main oil circuit of the main valve to the oil inlet of the control valve 4 is from left to right, and the first one-way valve 5 is in a conducting state. The second one-way valve 6 is arranged on the second oil circuit 9, and the flow direction along the main valve high-pressure control oil circuit to the oil inlet of the control valve 4 is from right to left, and the second one-way valve 6 is in a conducting state. It should be noted that, as shown in the example Figure 1 As for the position state of the hydraulic control valve group shown in the figure, the up and down directions in the figure refer to the left and right directions, the bottom in the figure is the left side, and the top is the right side.

[0040] Among them, the first working oil port (A port) of the control valve 4 is connected to the oil inlet (P port) of the control valve 4, that is, Figure 1 In the middle right position, the control oil port of the cartridge valve 3 is connected to the third oil circuit 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 main 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 eventually flows to the spring control chamber of the cartridge valve 3, so that the cartridge valve is in a closed state, and the system enters a working state. When the pressure of the main 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 one-way valve 6 is turned on, the first one-way valve 5 is turned off, and the hydraulic oil from the main high-pressure control oil circuit of the main valve eventually flows to the spring control chamber of the cartridge valve 3, so that the cartridge valve is in a closed state, and the system enters a working state. In this way, after comparing the pressures of the main high-pressure control oil circuit of the main valve and the main oil circuit of the main valve, only one higher-pressure hydraulic oil acts on the spring control chamber of the cartridge valve 3, so that when high-pressure and low-pressure pumping are switched, the cartridge valve 3 is in a closed state, and the system enters a working state. The cartridge valve 3 will not open during reversing, which can reduce the impact of oil return.

[0041] In the embodiment of the present invention, the control valve 4 is configured as a solenoid valve, for example, a two-position four-way solenoid valve, so that the power-off and power-on states of the solenoid valve can be controlled by a controller. The controller can be configured separately, or the controller for controlling the main valve can be used. When the control valve 4 is in the power-off state, the first working oil port of the control valve 4 is connected to the oil outlet of the control valve 4, that is, in the power-off state. Figure 1 When the control valve 4 is in the energized state, the oil inlet of the control valve 4 is connected to the first working oil port of the control valve 4, that is, in the middle left position. Figure 1 Specifically, the solenoid valve can be a load relief solenoid valve or a proportional solenoid valve.

[0042] In the embodiment of the present invention, the hydraulic control valve group further includes a throttle valve 7, the flow of which can be adjusted, so as to control the flow rate of the oil. One end of the throttle valve 7 is connected to the first working oil port (port A) of the control valve 4, and the other end is connected to the control oil port (port X) 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, so as to reduce the impact on the cartridge valve 3, prevent it from vibrating too much, and provide system safety.

[0043] The hydraulic system provided by the present invention is described below. The hydraulic system described below and the hydraulic control valve group described above can be referred to each other.

[0044] The embodiment of the present invention further provides a hydraulic system, including the hydraulic control valve group in the above embodiments. With such an arrangement, the proportional overflow 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 adaptive adjustment of the overflow pressure with the main oil circuit pressure of the main valve. When the system is switched, the pressure regulating valve 2 can be opened briefly, so that the system pressure peak can be reduced, the system shock can be reduced, and the jitter caused by the shock can be alleviated without losing the pumping efficiency and pumping continuity. The derivation process of this beneficial effect is roughly similar to the derivation process of the beneficial effect of the above-mentioned hydraulic control valve group, so it will not be repeated here.

[0045] Furthermore, the hydraulic control valve group is arranged as a plate-type installation structure, so that the valve group is made into a standard plate-type installation form, which is easy to install and can be conveniently applied to different hydraulic systems.

[0046] The working machine provided by the present invention is described below. The working machine described below and the hydraulic system described above can be referred to each other.

[0047] The embodiment of the present invention further provides an operating machine, specifically, for example, a concrete pump truck, etc. The operating 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. With such an arrangement, the proportional overflow valve group functional module component formed by the combination of the proportional valve 1 and the pressure regulating valve 2 with a remote pressure regulating port can realize adaptive adjustment of the overflow pressure with the main oil circuit pressure of the main valve. When the system is reversed, the pressure regulating valve 2 can be opened briefly, so that the system pressure peak can be reduced, the system shock can be reduced, and the jitter caused by the shock can be alleviated without losing the pumping efficiency and pumping continuity. The derivation process of this beneficial effect is roughly similar to the derivation process of the beneficial effect of the above-mentioned hydraulic system, so it will not be repeated here.

[0048] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A hydraulic control valve group, characterized in that: include: A proportional valve, used to output a corresponding control flow at the oil outlet of the proportional valve according to the pressure of the main oil circuit of the main valve; A pressure regulating valve, comprising an oil inlet connected to the main oil circuit of the main valve, an oil outlet for returning oil, and a remote pressure regulating port connected to the oil outlet of the proportional valve, wherein the pressure regulating valve can adjust the valve port opening size of the pressure regulating valve according to the control flow output by the proportional valve; It also includes a cartridge valve and a control valve, wherein the oil inlet of the cartridge valve is connected to the main oil circuit of the main valve, the control oil port of the cartridge valve 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 communicated 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.

2. The hydraulic control valve group according to claim 1, characterized in that: Also includes: a first oil circuit and a second oil circuit, wherein 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 other ends of the first oil circuit and the second oil circuit are both connected to the oil inlet of the control valve through a third oil circuit; A first one-way valve, arranged on the first oil circuit and conducting along the flow direction from the main oil circuit of the main valve to the oil inlet of the control valve; A second one-way valve is arranged on the second oil circuit and is connected along the flow direction of the main valve high-pressure control oil circuit to the oil inlet of the control valve; Wherein, when the first working oil port of the control valve is connected to the oil inlet of the control valve, the control oil port of the cartridge valve is connected to the third oil circuit via the control valve.

3. The hydraulic control valve group according to claim 2, characterized in that: The control valve is configured as a solenoid valve. Among them, when the control valve is in a power-off state, the first working oil port of the control valve is connected to the oil outlet of the control valve; when the control valve is in a power-on state, the oil inlet of the control valve is connected to the first working oil port of the control valve.

4. The hydraulic control valve assembly according to claim 3, characterized in that: The solenoid valve is configured as a load relief solenoid valve or a proportional solenoid valve.

5. The hydraulic control valve assembly according to claim 1, characterized in that: The pressure regulating valve is configured as a relief valve.

6. The hydraulic control valve group according to any one of claims 2 to 4, characterized in that: It also includes a throttle valve, one end of which is connected to the first working oil port of the control valve, and the other end of which is connected to the control oil port of the cartridge valve.

7. A hydraulic system, characterized in that: It comprises a hydraulic control valve group as described in any one of claims 1 to 6.

8. The hydraulic system according to claim 7, characterized in that: The hydraulic control valve group is arranged as a plate-type mounting structure.

9. A working machine, comprising a vehicle body and a pumping hydraulic system arranged on the vehicle body, characterized in that: The pumping hydraulic system is a hydraulic system as described in any one of claims 7-8.

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