CN113898633A - Hydraulic control valve group, hydraulic system and operation machine - Google Patents
Hydraulic control valve group, hydraulic system and operation machine Download PDFInfo
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- CN113898633A CN113898633A CN202111278863.1A CN202111278863A CN113898633A CN 113898633 A CN113898633 A CN 113898633A CN 202111278863 A CN202111278863 A CN 202111278863A CN 113898633 A CN113898633 A CN 113898633A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/007—Overload
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/008—Reduction of noise or vibration
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
- F15B2013/004—Cartridge valves
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a hydraulic control valve group, a hydraulic system and a working machine. The pressure regulating valve comprises an oil inlet connected with a main valve main oil way, an oil outlet used for returning oil and a remote pressure regulating port connected with an oil outlet of the proportional valve. And according to the pressure of the main valve main oil way, the oil outlet of the proportional valve outputs corresponding control flow. The pressure regulating valve regulates the opening of the valve port according to the control flow output by the proportional valve. The pressure regulating valve presets a safe pressure value, and when it is working, the control flow of oil outlet of proportional valve can be controlled according to main valve main oil circuit pressure, and transferred into remote pressure-regulating port. Then, the real-time pilot control pressure required by the pressure regulating valve is calculated according to the control flow, and the opening degree of the valve port of the pressure regulating valve is adjusted, so that the control pressure of the pressure regulating valve is reduced in proportion, the pressure peak value of the system during reversing is reduced, the system impact is reduced, the vibration caused by the impact is relieved, and the pumping efficiency and the pumping continuity are not lost.
Description
Technical Field
The invention relates to the technical field of engineering machinery, in particular to a hydraulic control valve group, a hydraulic system and an operating machine.
Background
The current overload protection scheme of a concrete pumping hydraulic system is to set a system overflow pressure higher than the cut-off pressure of a main oil pump in the system, and the pressure value is as high as 35MPa or more. Therefore, the system is usually operated under high pressure and large flow, and the pressure impact peak value at each reversing moment can reach the set system overflow pressure. The high pressure impact not only increases the noise generated by reversing, seriously influences the stability and the service life of system elements, but also brings great vibration to the whole machine.
In order to reduce the reversing impact, the prior art scheme is to reduce the impact pressure by reducing the displacement of an oil pump or instantaneously opening an unloading valve when a main valve is reversed. This, however, reduces the pumping efficiency and also causes a gap in the system pumping pressure, which negatively affects the pumping continuity.
Disclosure of Invention
The invention aims to provide a hydraulic control valve group, a hydraulic system and a working machine, which are used for solving the problems in the prior art.
The invention provides a hydraulic control valve group, comprising:
the proportional valve is used for outputting corresponding control flow according to the pressure of the main valve main oil circuit;
the pressure regulating valve comprises an oil inlet connected with the main valve main oil way, an oil outlet used for returning oil and a remote pressure regulating port connected with the oil outlet of the proportional valve, and the opening degree of a valve port of the pressure regulating valve can be regulated according to the control flow output by the proportional valve.
The hydraulic control valve group provided by the invention also comprises a cartridge valve and a control valve, wherein an oil inlet of the cartridge valve is connected with the main oil circuit of the main valve, a control oil port of the cartridge valve is connected with a first working oil port of the control valve, an oil outlet of the control valve is used for returning oil,
and under the condition that 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.
According to the hydraulic control valve group provided by the invention, the hydraulic control valve group further comprises:
one end of the first oil way is connected with the main valve main oil way, one end of the second oil way is connected with the main valve high-pressure control oil way, and the other end of the first oil way and the other end of the second oil way are both connected with an oil inlet of the control valve through a third oil way;
the first check valve is arranged on the first oil path and communicated along the flowing direction from the main valve main oil path to the oil inlet of the control valve;
the second check valve is arranged on the second oil path and communicated along the flowing direction from the main valve high-pressure control oil path to the oil inlet of the control valve;
and under the condition that the first working oil port of the control valve is communicated with the oil inlet of the control valve, the control oil port of the cartridge valve is connected with the third oil way through the control valve.
According to the hydraulic control valve group provided by the invention, the control valve is arranged as an electromagnetic valve,
under the condition that the control valve is in a power-off state, a first working oil port of the control valve is communicated with an oil outlet of the control valve; and under the condition that the control valve is in an electrified state, the control valve is communicated with the first working oil port of the control valve.
According to the hydraulic control valve group provided by the invention, the electromagnetic valve is set to be an unloading electromagnetic valve or a proportional electromagnetic valve.
According to the hydraulic control valve group provided by the invention, the pressure regulating valve is arranged as an overflow valve.
The hydraulic control valve group provided by the invention further comprises a throttle valve, wherein one end of the throttle valve is connected with the first working oil port of the control valve, and the other end of the throttle valve is connected with the control oil port of the cartridge valve.
The invention also provides a hydraulic system comprising the hydraulic control valve group.
According to the hydraulic system provided by the invention, the hydraulic control valve group is arranged into a plate-type mounting structure.
The invention further provides a working machine, which comprises a vehicle body and a pumping hydraulic system arranged on the vehicle body, wherein the pumping hydraulic system is the hydraulic system in any one of the above aspects.
The invention provides a hydraulic control valve group, which comprises a proportional valve and a pressure regulating valve. And the oil outlet of the proportional valve outputs corresponding control flow according to the pressure of the main valve main oil circuit. The pressure regulating valve comprises an oil inlet connected with the main valve main oil way, an oil outlet used for returning oil and a remote pressure regulating port connected with the oil outlet of the proportional valve, and the opening degree of a valve port of the pressure regulating valve can be regulated by the pressure regulating valve according to the control flow output by the proportional valve. According to the arrangement, the pressure regulating valve presets a safe pressure value, and when the proportional valve works, the control flow of the oil outlet of the proportional valve is controlled according to the pressure of the main valve main oil way and is transmitted to the remote pressure regulating port. Then, the real-time pilot control pressure required by the pressure regulating valve is calculated according to the control flow, and the opening of the valve port of the pressure regulating valve is regulated, so that the control pressure of the pressure regulating valve is reduced in proportion, the pressure peak value of the system during reversing is reduced, the system impact is reduced, the vibration caused by the impact is relieved, and the pumping efficiency and the pumping continuity are not lost.
Drawings
In order to more clearly illustrate the technical solutions of the present invention or the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
FIG. 1 is a schematic diagram of a hydraulic control valve pack provided by the present invention;
reference numerals:
1: a proportional valve; 2: a pressure regulating valve; 3: a cartridge valve;
4: a diverter valve; 5: a first check valve; 6: a second one-way valve;
7: a throttle valve; 8: a first oil passage; 9: a second oil passage;
10: a third oil passage; 11: an oil tank; 12: an oil drainage port.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The hydraulic control valve assembly of the present invention is described below in conjunction with fig. 1.
As shown in fig. 1, an embodiment of the present invention provides a hydraulic control valve group including a proportional valve 1 and a pressure regulating valve 2. Specifically, the oil outlet (port 1) of the proportional valve 1 outputs a corresponding control flow rate in accordance with the main valve main line pressure. The pressure regulating valve 2 comprises an oil inlet (1 port) connected with a main valve main oil path (P1), an oil outlet (2 ports) for oil return and a remote pressure regulating port (3 port) connected with the oil outlet of the proportional valve 1. Wherein, the oil outlet (2 ports) can be directly connected with the oil tank 11. The pressure regulating valve 2 can regulate the opening degree of the valve port of the pressure regulating valve 2 according to the control flow rate output by the proportional valve 1.
Specifically, the proportional valve 1 adopts an electro-hydraulic proportional valve, the electric signals are convenient to transmit, and remote control can be realized. When the system works, the pressure sensor of the main valve main oil circuit detects the real-time pressure of the system and transmits a pressure signal to the proportional valve 1. According to the input signal, the oil outlet (1 port) of the proportional valve 1 proportionally outputs the control flow. For example, as shown in fig. 1, a two-position three-way proportional valve is adopted, and an oil outlet (port 1) of the two-position three-way proportional valve is connected with a remote pressure regulating port of a pressure regulating valve 2. The oil inlet (2 ports) of the oil pump is connected with a main valve high-pressure control oil way (Gp), the main valve high-pressure control oil way is connected with an energy accumulator, and the energy accumulator provides high-pressure control oil. The oil return port (3 ports) is connected with a control oil return oil way of a main valve and then flows back to the oil return tank 11 for oil return. As shown in fig. 1, a drain port 12 connected to an oil tank 11 may be provided on the hydraulic control valve block, and a drain port 12 may be connected to an oil return port (port 3) of the proportional valve 1. 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 to the oil tank 11. One or more oil tanks 11 can be arranged, and the specific number can be determined according to actual conditions. In particular, the proportional valve 1 has a first operating position and a second operating position. When the proportional valve 1 is in a power-off state, the proportional valve 1 is located at a first working position (lower position in fig. 1), at the moment, an oil outlet (port 1) of the proportional valve 1 is communicated with an oil return port (port 3), and an oil inlet (port 2) is cut off; then, when the remote pressure adjusting port of the pressure regulating valve 2 is connected to the drain port 12 via the proportional valve 1 and drain is performed, the proportional valve 1 does not operate and the pressure regulating valve 2 is not subjected to regulation control. When the proportional valve 1 is in an electrified state, the proportional valve 1 is located at a second working position (upper position in fig. 1), at the moment, an oil outlet (port 1) of the proportional valve 1 is communicated with an oil inlet (port 2), and an oil return port (port 3) is cut off; then, based on the inputted electric signal, the proportional valve 1 proportionally outputs the corresponding control flow rate, whereby the control pressure of the pressure regulating valve 2 is decreased. In the positional state of the hydraulic control valve group shown in fig. 1, the left-right direction in the drawing is the vertical direction, the left side in the drawing is the upper position, and the right side is the lower position.
The pressure regulating valve 2 is a large-flow overflow valve, and a basic safe overflow pressure value, such as 35Mpa, can be preset. When the pressure regulating valve 2 works, the real-time pilot control pressure required by the external control port of the pressure regulating valve 2 is inversely calculated according to the control flow obtained by the remote pressure regulating port, so that the control pressure of the pressure regulating valve 2 is proportionally reduced. Therefore, when the system is reversed, control oil with certain pressure flows into the remote pressure regulating port of the pressure regulating valve 2 and enters the spring cavity to push the control spring, so that the opening ratio of the valve port is increased, the overflow pressure required by opening the overflow valve is reduced, and the adaptive adjustment of the overflow pressure along with the pressure of the main system is realized. At the moment of large flow requiring quick reversing, part of oil can be released by the pressure regulating valve 2 and returns to the oil tank 11, so that the pressure impact peak value at the moment of opening and closing the oil way is effectively reduced, and the pressure impact of the system is reduced.
According to the arrangement, the pressure regulating valve 2 is preset with a safe pressure value, and when the pressure regulating valve works, the control flow of the oil outlet of the proportional valve 1 is controlled according to the pressure of the main valve main oil way and is transmitted to the remote pressure regulating port. Then, the real-time pilot control pressure required by the pressure regulating valve 2 is calculated according to the control flow, and the opening degree of the valve port of the pressure regulating valve 2 is adjusted, so that the control pressure of the pressure regulating valve 2 is reduced proportionally. When the system is reversed, the pressure regulating valve 2 can be opened temporarily, so that the pressure peak value of the system is reduced during the reversing, the system impact is reduced, the vibration caused by the impact is reduced, and the pumping efficiency and the pumping continuity cannot be lost.
In the embodiment of the invention, the hydraulic control valve group further comprises a cartridge valve 3 and a control valve 4, and the control valve 4 can select a two-position four-way valve. An oil inlet (port A) of the cartridge valve 3 is connected with a main valve main oil way (P1), a control oil port (port X) of the cartridge valve 3 is connected with a first working oil port (port A) of the control valve 4, and an oil outlet (port B) of the cartridge valve 3 is connected with an oil tank 11. An oil outlet (a T port) of the control valve 4 is used for oil return and can be connected with the oil drainage port 12, and a second working oil port (a B port) of the control valve 4 is cut off and sealed.
Wherein, the first working oil port (port a) of the control valve 4 is communicated with the oil outlet (port T) of the control valve 4, that is, under the condition of the left position in fig. 1, the control oil port (port X) of the cartridge valve 3 is connected with the oil outlet (port T) 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 via the control valve 4 to the tank 11, and the control oil pressure is almost zero. As long as the main valve main oil passage (P1) has a slight pressure acting on the inlet port (port a) of the cartridge valve 3, the cartridge valve 3 can be easily opened to return the oil to the oil tank 11, so that the pressure of the entire system is low. Therefore, the cartridge valve 3 and the control valve 4 work in a matched mode, the system has an unloading function under the standby working condition, and the standby power consumption of the system is reduced.
Further, the hydraulic control valve group further comprises a first oil path 8, a first check valve 5, a second oil path 9 and a second check valve 6. Specifically, one end of the first oil passage 8 is connected to the main valve main oil passage (P1), one end of the second oil passage 9 is connected to the main valve high-pressure control oil passage (Gp), and the other end of the first oil passage 8 and the other end of the second oil passage 9 are both connected to the oil inlet (port P) of the control valve 4 via the third oil passage 10. The first check valve 5 is provided on the first oil passage 8, and the first check valve 5 is in a conducting state in a flow direction of the main valve main oil passage to the oil inlet of the control valve 4, i.e., from left to right. The second check valve 6 is provided on the second oil passage 9, and the second check valve 6 is in a conducting state in the flow direction of the main valve high-pressure control oil passage to the oil inlet of the control valve 4, i.e., from right to left. In the positional state of the hydraulic control valve group shown in fig. 1, the vertical direction in the drawing is the left-right direction, the vertical direction in the drawing is the left side, and the vertical direction is the right side.
Wherein, when the first working oil port (port a) of the control valve 4 is communicated with the oil inlet (port P) of the control valve 4, i.e. in the right position in fig. 1, the control oil port of the cartridge valve 3 is connected with the third oil passage 10 via the control valve 4. When the pressure of the main valve main oil way is higher than that of the main valve high-pressure control oil way, the first one-way valve 5 is conducted, the second one-way valve 6 is stopped, and the hydraulic oil from the main valve main oil way finally flows to the spring control cavity 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 valve high-pressure control oil way is higher than that of the main valve main oil way, the second one-way valve 6 is communicated, the first one-way valve 5 is closed, and the hydraulic oil from the main valve high-pressure control oil way finally flows to the spring control cavity of the cartridge valve 3, so that the cartridge valve is in a closed state, and the system enters a working state. Therefore, after the pressures of the main valve high-pressure control oil way and the main valve main oil way are compared, only one path of hydraulic oil with higher pressure acts on the spring control cavity of the cartridge valve 3, so that when the high-pressure pumping and the 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 can not be opened during reversing, and oil return impact can be reduced.
In the embodiment of the invention, the control valve 4 is set to be an electromagnetic valve, for example, a two-position four-way electromagnetic valve, so that the power-off and power-on states of the electromagnetic valve can be controlled by the controller. The controller can be arranged independently, and a controller for controlling the main valve can also be adopted. Under the condition that the control valve 4 is in a power-off state, the first working oil port of the control valve 4 is communicated with the oil outlet of the control valve 4, namely, the first working oil port is in the left position in fig. 1. Under the condition that the control valve 4 is in an electrified state, the oil inlet of the control valve 4 is communicated with the first working oil port of the control valve 4, namely, the oil inlet is in the right position in fig. 1. Specifically, the electromagnetic valve may adopt an unloading electromagnetic valve or a proportional electromagnetic valve.
In the embodiment of the invention, the hydraulic control valve group further comprises a throttle valve 7, and the flow of the throttle valve 7 can be adjusted, so that the flow rate of oil can be controlled. One end of the throttle valve 7 is connected with a first working oil port (port A) of the control valve 4, and the other end is connected with a control oil port (port X) of the cartridge valve 3. Therefore, the oil pressure flowing to the spring control cavity of the cartridge valve 3 is controlled through the throttle valve 7, the impact on the cartridge valve 3 is relieved, the excessive vibration of the cartridge valve is prevented, and the system safety is improved.
The hydraulic system provided by the invention is described below, and the hydraulic system described below and the hydraulic control valve group described above can be referred to correspondingly.
The embodiment of the invention also provides a hydraulic system which comprises the hydraulic control valve group in the above embodiments. By the arrangement, the proportional overflow valve group functional module assembly formed by combining the proportional valve 1 and the pressure regulating valve 2 with the remote pressure regulating port can realize the self-adaptive regulation of the overflow pressure along with the pressure of the main oil way of the main valve. When the system is reversed, the pressure regulating valve 2 can be opened temporarily, so that the pressure peak value of the system can be reduced, the system impact is reduced, the shaking caused by the impact is further reduced, and the pumping efficiency and the pumping continuity cannot be lost. The derivation process of the beneficial effect is substantially similar to the derivation process of the beneficial effect of the hydraulic control valve group, and therefore, the description is omitted here.
Further, the hydraulic control valve group is arranged to be a plate-type mounting structure. Therefore, the valve is manufactured into a standard plate type installation form, so that the valve is convenient to install and can be conveniently applied to different hydraulic systems.
The present disclosure provides a work machine, which may be referred to with respect to the hydraulic system described above.
The embodiment of the invention also provides a working machine, in particular to a concrete pump truck and the like. The working machine includes a vehicle body and a pumping hydraulic system provided on the vehicle body, the pumping hydraulic system being the hydraulic system in each of the above embodiments. By the arrangement, the proportional overflow valve group functional module assembly formed by combining the proportional valve 1 and the pressure regulating valve 2 with the remote pressure regulating port can realize the self-adaptive regulation of the overflow pressure along with the pressure of the main oil way of the main valve. When the system is reversed, the pressure regulating valve 2 can be opened temporarily, so that the pressure peak value of the system can be reduced, the system impact is reduced, the shaking caused by the impact is further reduced, and the pumping efficiency and the pumping continuity cannot be lost. The derivation process of the beneficial effect is substantially similar to the derivation process of the beneficial effect of the hydraulic system, and therefore, the description is omitted here.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (10)
1. A hydraulic control valve group, comprising:
the proportional valve is used for outputting corresponding control flow according to the pressure of the main valve main oil circuit;
the pressure regulating valve comprises an oil inlet connected with the main valve main oil way, an oil outlet used for returning oil and a remote pressure regulating port connected with the oil outlet of the proportional valve, and the opening degree of a valve port of the pressure regulating valve can be regulated according to the control flow output by the proportional valve.
2. The hydraulic control valve group as claimed in claim 1, further comprising a cartridge valve and a control valve, wherein an oil inlet of the cartridge valve is connected to the main valve main oil path, a control oil port of the cartridge valve is connected to the first working oil port of the control valve, an oil outlet of the control valve is used for oil return,
and under the condition that 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.
3. The hydraulic control valve set of claim 2, further comprising:
one end of the first oil way is connected with the main valve main oil way, one end of the second oil way is connected with the main valve high-pressure control oil way, and the other end of the first oil way and the other end of the second oil way are both connected with an oil inlet of the control valve through a third oil way;
the first check valve is arranged on the first oil path and communicated along the flowing direction from the main valve main oil path to the oil inlet of the control valve;
the second check valve is arranged on the second oil path and communicated along the flowing direction from the main valve high-pressure control oil path to the oil inlet of the control valve;
and under the condition that the first working oil port of the control valve is communicated with the oil inlet of the control valve, the control oil port of the cartridge valve is connected with the third oil way through the control valve.
4. The set of hydraulic control valves according to claim 3, characterized in that the control valves are provided as solenoid valves,
under the condition that the control valve is in a power-off state, a first working oil port of the control valve is communicated with an oil outlet of the control valve; and under the condition that the control valve is in an electrified state, the oil inlet of the control valve is communicated with the first working oil port of the control valve.
5. The set of hydraulic control valves according to claim 4, characterized in that the solenoid valve is provided as an unloading solenoid valve or a proportional solenoid valve.
6. The set of hydraulic control valves according to claim 1, wherein the pressure regulating valve is provided as a relief valve.
7. The set of hydraulic control valves of any one of claims 2-6, further comprising a throttle valve having one end connected to the first working port of the control valve and the other end connected to the control port of the cartridge valve.
8. A hydraulic system comprising a hydraulic control valve assembly according to any one of claims 1 to 7.
9. The hydraulic system of claim 8, wherein the hydraulic control valve block is provided as a plate mount structure.
10. A working machine comprising a vehicle body and a pumping hydraulic system arranged on said vehicle body, characterized in that said pumping hydraulic system is a hydraulic system according to any one of claims 8-9.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111278863.1A CN113898633A (en) | 2021-10-31 | 2021-10-31 | Hydraulic control valve group, hydraulic system and operation machine |
| PCT/CN2022/073535 WO2023070969A1 (en) | 2021-10-31 | 2022-01-24 | Hydraulic control valve group, hydraulic system, and operation machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111278863.1A CN113898633A (en) | 2021-10-31 | 2021-10-31 | Hydraulic control valve group, hydraulic system and operation machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113898633A true CN113898633A (en) | 2022-01-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111278863.1A Pending CN113898633A (en) | 2021-10-31 | 2021-10-31 | Hydraulic control valve group, hydraulic system and operation machine |
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| Country | Link |
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| CN (1) | CN113898633A (en) |
| WO (1) | WO2023070969A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023070969A1 (en) * | 2021-10-31 | 2023-05-04 | 三一汽车制造有限公司 | Hydraulic control valve group, hydraulic system, and operation machine |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3961123B2 (en) * | 1998-07-29 | 2007-08-22 | コベルコ建機株式会社 | Hydraulic circuit of hydraulic work machine |
| CN103603840B (en) * | 2013-11-26 | 2016-03-23 | 三一汽车制造有限公司 | Integrated hydraulic valve group and hydraulic driving system and concrete pump |
| CN204677522U (en) * | 2014-12-09 | 2015-09-30 | 新乡平原航空技术工程有限公司 | A kind of confession pressing system of fluid motor-driven oil sources |
| CN113898633A (en) * | 2021-10-31 | 2022-01-07 | 三一汽车制造有限公司 | Hydraulic control valve group, hydraulic system and operation machine |
| CN216430099U (en) * | 2021-10-31 | 2022-05-03 | 三一汽车制造有限公司 | Hydraulic control valve group, hydraulic system and operation machine |
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2021
- 2021-10-31 CN CN202111278863.1A patent/CN113898633A/en active Pending
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2022
- 2022-01-24 WO PCT/CN2022/073535 patent/WO2023070969A1/en unknown
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023070969A1 (en) * | 2021-10-31 | 2023-05-04 | 三一汽车制造有限公司 | Hydraulic control valve group, hydraulic system, and operation machine |
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| Publication number | Publication date |
|---|---|
| WO2023070969A1 (en) | 2023-05-04 |
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