WO2023070969A1 - Groupe de soupapes de commande hydraulique, système hydraulique et machine d'exploitation - Google Patents

Groupe de soupapes de commande hydraulique, système hydraulique et machine d'exploitation Download PDF

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Publication number
WO2023070969A1
WO2023070969A1 PCT/CN2022/073535 CN2022073535W WO2023070969A1 WO 2023070969 A1 WO2023070969 A1 WO 2023070969A1 CN 2022073535 W CN2022073535 W CN 2022073535W WO 2023070969 A1 WO2023070969 A1 WO 2023070969A1
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WO
WIPO (PCT)
Prior art keywords
valve
oil
control valve
port
control
Prior art date
Application number
PCT/CN2022/073535
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English (en)
Chinese (zh)
Inventor
李俊
杨敏
胡涛
Original Assignee
三一汽车制造有限公司
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Filing date
Publication date
Application filed by 三一汽车制造有限公司 filed Critical 三一汽车制造有限公司
Publication of WO2023070969A1 publication Critical patent/WO2023070969A1/fr

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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
    • 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
    • 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
    • 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
    • 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
    • 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

Definitions

  • 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.
  • 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.
  • 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.
  • this will reduce the pumping efficiency and will also cause a gap in the system pumping pressure, which will negatively affect the pumping continuity.
  • 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.
  • 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,
  • 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;
  • the control oil port of the cartridge valve is connected with the third oil passage via the control valve .
  • control valve is configured as a solenoid valve
  • the first working oil port of the control valve 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.
  • the solenoid valve is configured as an unloading solenoid valve or a proportional solenoid valve.
  • 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.
  • 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.
  • 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.
  • Fig. 1 is the schematic diagram of the principle of the hydraulic control valve group provided by the present application.
  • the embodiment of the present application provides a hydraulic control valve group, including a proportional valve 1 and a pressure regulating valve 2 .
  • 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 .
  • the proportional valve 1 adopts an electro-hydraulic proportional valve, the electric signal is convenient to transmit, and remote control can be realized.
  • 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.
  • the oil outlet (port 1) of the proportional valve 1 outputs the control flow in proportion.
  • 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.
  • 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 .
  • 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 .
  • the oil tank 11 can be provided with one or more, and its specific quantity can be determined according to actual conditions.
  • the proportional valve 1 has a first working position and a second working position.
  • the proportional valve 1 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.
  • the proportional valve 1 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 pressure regulating valve 2 adopts a large-flow relief valve, which can preset a basic safe relief pressure value, such as 35Mpa.
  • 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.
  • 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.
  • the pressure regulating valve 2 presets a safe pressure value.
  • 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.
  • 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.
  • 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.
  • 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 .
  • 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
  • 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 .
  • the control oil port of the cartridge valve 3 It is connected to the third oil passage 10 via the control valve 4 .
  • 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.
  • 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.
  • 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 .
  • 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 .
  • the solenoid valve can be an unloading solenoid valve or a proportional solenoid valve.
  • 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 .
  • 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 embodiment of the present application also provides a hydraulic system, including the hydraulic control valve group in the above embodiments.
  • 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.
  • 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.
  • the hydraulic control valve group is arranged as a board-type installation structure.
  • 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 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.
  • 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.
  • 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.

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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

L'invention concerne un groupe de soupapes de commande hydraulique, un système hydraulique et une machine d'exploitation. Le groupe de soupapes de commande hydraulique comprend une vanne proportionnelle (1) et une soupape de régulation de pression (2), la soupape de régulation de pression (2) comprenant une entrée d'huile reliée à un circuit d'huile principal d'une soupape principale, une sortie d'huile pour renvoyer de l'huile, et un orifice de régulation de pression à distance relié à une sortie d'huile de la vanne proportionnelle (1) ; un flux de commande correspondant est fourni par la sortie d'huile de la vanne proportionnelle (1) en fonction de la pression du circuit d'huile principal de la soupape principale ; et la soupape de régulation de pression (2) règle le degré d'ouverture d'un orifice de soupape associé en fonction du flux de commande qui est fourni par la vanne proportionnelle (1). Une valeur de pression sûre est prédéfinie pour la soupape de régulation de pression, et pendant le fonctionnement, le flux de commande au niveau de la sortie d'huile de la vanne proportionnelle est commandé en fonction de la pression du circuit d'huile principal de la soupape principale, et est transmis à l'orifice de régulation de pression à distance. Une pression de commande pilote en temps réel requise par la soupape de régulation de pression est ensuite calculée en fonction du flux de commande, et le degré d'ouverture de l'orifice de soupape de la soupape de régulation de pression est ajusté, de telle sorte que la pression de commande de la soupape de régulation de pression soit proportionnellement réduite, et qu'une valeur de pic de pression d'un système soit réduite pendant l'inversion, réduisant ainsi l'impact du système, et atténuant le tremblement provoqué par l'impact sans perdre l'efficacité de pompage et la continuité de pompage.
PCT/CN2022/073535 2021-10-31 2022-01-24 Groupe de soupapes de commande hydraulique, système hydraulique et machine d'exploitation WO2023070969A1 (fr)

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CN202111278863.1A CN113898633A (zh) 2021-10-31 2021-10-31 液压控制阀组、液压系统及作业机械
CN202111278863.1 2021-10-31

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113898633A (zh) * 2021-10-31 2022-01-07 三一汽车制造有限公司 液压控制阀组、液压系统及作业机械

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000045340A (ja) * 1998-07-29 2000-02-15 Yutani Heavy Ind Ltd 油圧作業機械の油圧回路
CN103603840A (zh) * 2013-11-26 2014-02-26 三一汽车制造有限公司 集成液压阀组及液压驱动系统及混凝土泵
CN204677522U (zh) * 2014-12-09 2015-09-30 新乡平原航空技术工程有限公司 一种液压马达驱动油源的供压系统
CN113898633A (zh) * 2021-10-31 2022-01-07 三一汽车制造有限公司 液压控制阀组、液压系统及作业机械
CN216430099U (zh) * 2021-10-31 2022-05-03 三一汽车制造有限公司 液压控制阀组、液压系统及作业机械

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000045340A (ja) * 1998-07-29 2000-02-15 Yutani Heavy Ind Ltd 油圧作業機械の油圧回路
CN103603840A (zh) * 2013-11-26 2014-02-26 三一汽车制造有限公司 集成液压阀组及液压驱动系统及混凝土泵
CN204677522U (zh) * 2014-12-09 2015-09-30 新乡平原航空技术工程有限公司 一种液压马达驱动油源的供压系统
CN113898633A (zh) * 2021-10-31 2022-01-07 三一汽车制造有限公司 液压控制阀组、液压系统及作业机械
CN216430099U (zh) * 2021-10-31 2022-05-03 三一汽车制造有限公司 液压控制阀组、液压系统及作业机械

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