WO2012019498A1 - Circuit et procédé de commande hydraulique - Google Patents

Circuit et procédé de commande hydraulique Download PDF

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Publication number
WO2012019498A1
WO2012019498A1 PCT/CN2011/076878 CN2011076878W WO2012019498A1 WO 2012019498 A1 WO2012019498 A1 WO 2012019498A1 CN 2011076878 W CN2011076878 W CN 2011076878W WO 2012019498 A1 WO2012019498 A1 WO 2012019498A1
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WO
WIPO (PCT)
Prior art keywords
valve
actuator
hydraulic
main
oil
Prior art date
Application number
PCT/CN2011/076878
Other languages
English (en)
Chinese (zh)
Inventor
郭海保
左春庚
魏星
薛长久
李美香
简桃凤
Original Assignee
长沙中联重工科技发展股份有限公司
湖南中联重科专用车有限责任公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 长沙中联重工科技发展股份有限公司, 湖南中联重科专用车有限责任公司 filed Critical 长沙中联重工科技发展股份有限公司
Publication of WO2012019498A1 publication Critical patent/WO2012019498A1/fr

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Classifications

    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line

Definitions

  • the present invention relates to the field of hydraulic control, and in particular to a hydraulic control circuit and method. Background technique
  • Pressure control in hydraulic systems or hydraulic circuits is often involved in the field of hydraulic control.
  • a hydraulic control check valve, a hydraulically controlled directional control valve, a balancing valve, etc. in a hydraulic system the control port is connected with an oil passage (hereinafter referred to as a main oil passage) in the hydraulic system to control the hydraulic control unit Actions on components such as valves, pilot operated directional valves, and balancing valves.
  • the pressure of the main oil line is usually affected by other parts of the hydraulic system, so that the operation of the above-mentioned liquid control check valve, hydraulically controlled directional valve, balance valve and the like are undesirably affected.
  • the pressure of the main oil passage is controlled by an additional pressure valve (for example, an electromagnetic proportional pressure reducing valve, etc.), thereby complicating the control methods of the above-mentioned liquid control check valve, hydraulically controlled directional valve, balance valve, and the like. It even increases the complexity of the entire hydraulic system.
  • an additional pressure valve for example, an electromagnetic proportional pressure reducing valve, etc.
  • the down load is a common implementation condition.
  • the balance valve is used to reduce the speed limit of the heavy object to ensure the safety of the operation process.
  • the weight can be lowered according to different speeds under different working conditions, and the balancing valve needs to have an internal control signal or an external control signal for control.
  • the electronic control system is limited in application scope due to various reasons such as cost and impact. Therefore, in some constructions where cost control is required and operation requirements are not very strict.
  • the hydraulic control system is used. In general, the hydraulic control pilot pressure of the hydraulic system is low, and the output value is single.
  • the balance valve has different control pressures for different load conditions. Therefore, the hydraulic control signals of the balance valve are taken from the system itself. Non-pilot control pressure signal.
  • the conventional down load hydraulic control circuit usually includes a main valve 8', a balancing valve 9', a hydraulic cylinder 71' and a relief valve 10', and the first working port A8' of the main valve 8' is balanced.
  • the valve 9' is connected to, for example, a rodless chamber 71' of the hydraulic cylinder 7'', and the second working port B8' of the main valve 8' is connected to the rod-shaped chamber 712' of the hydraulic cylinder 71', the relief valve 10' and the balancing valve 9'
  • the control port 91' is connected to the line between the rod chamber 712' of the hydraulic cylinder 7'' and the second working port B8' of the main valve 8'.
  • the main valve 8' operates in the right position, and the system oil supply port P8' flows through the second working oil port B8' to the second chamber 712' of the hydraulic cylinder 71'; the rodless chamber of the hydraulic cylinder 71'
  • the 71 ⁇ oil passes through the balancing valve 9' and flows back to the tank through the first working port A8' and the return port T8' of the main valve 8'.
  • the control pressure of the balancing valve 9' comes from the pressure of the rod chamber 712', that is, the pressure generated by the load, and the highest control pressure is the relief valve 10' Set the pressure value.
  • the control pressure is generated by the load and is always affected by the load, and is liable to fluctuate due to changes in the load.
  • the relief valve 10' is always in the open state, which requires that the system oil supply flow rate must simultaneously satisfy the lowering of the hydraulic cylinder when the main valve 8' is at different opening degrees. Flow requirements and opening flow requirements for the relief valve 10'. Therefore, the output flow of the conventional down load hydraulic control circuit is large.
  • control pressure of the balancing valve 9' is always the opening pressure of the relief valve 10', and since the pressure is guaranteed to be balanced under extreme conditions (such as the top of the hydraulic cylinder to the top end, the pressure of the rodless chamber 71 ⁇ is high at this time)
  • the valve 9' can be opened, and the set pressure of the relief valve 10' tends to be relatively high, making the system pressure too high.
  • the system pressure is high and the output flow is large, which makes the system output power large, resulting in energy loss.
  • the falling speed of the load is determined by the opening degree of the balancing valve 9', and the opening degree of the balancing valve 9' is controlled by the balancing valve 9', the hydraulic pressure
  • the pressure of the rodless chamber 71' of the cylinder 71' and the back pressure generated by the oil return port of the main valve 8' (the first working port 8A') are determined.
  • the positive opening of the pressure control balance valve 9' is controlled, and the pressure of the rodless chamber 711' and the negative pressure of the back pressure control balance valve 9'.
  • the pressure of the rodless chamber 71 ⁇ is affected by the load.
  • the back oil must be changed by changing the oil returning capacity of the return port of the main valve 8'. Press to change the opening of the balancing valve 9'.
  • the main valve 8' has a certain opening degree and the back pressure is small so that the opening degree of the balancing valve 9' is large, the descending speed is fast; when the back pressure is large, the opening degree of the balancing valve 9' is small, and the descending speed is slow.
  • the main valve 8' is designed to have a good matching between the oil inlet and the oil return port, otherwise the load may be unstable.
  • the speed regulation characteristic of the balance valve 9' is realized by the back pressure. When the load changes greatly, the back pressure will generate a jitter, causing the opening degree of the balance valve 9' to change, causing the change of the descending speed to make the load drop unstable.
  • the present invention is directed to a hydraulic control circuit and a hydraulic control method that overcomes at least some of the above disadvantages existing in the prior art, or at least provides a useful alternative.
  • the present invention provides a hydraulic control circuit, wherein the hydraulic control circuit package The main oil circuit, the liquid resistance element and the oil tank are arranged, and the liquid resistance element is connected in series with the oil tank and bypassed on the main oil passage.
  • liquid resistance element is a fixed orifice, an adjustable orifice, a pressure reducing valve or a throttle valve.
  • main oil passage is connected to a control port of the pilot valve.
  • the main oil passage is connected to the control oil port of the hydraulic control valve through the electromagnetic reversing valve.
  • the electromagnetic reversing valve is a three-position four-way electromagnetic reversing valve
  • the hydraulically controlled reversing valve is a three-position four-way hydraulically controlled reversing valve
  • the main oil passage is connected to the three-position four-way The oil inlet of the electromagnetic reversing valve, the two working ports of the three-position four-way electromagnetic reversing valve are respectively connected to the two control ports of the three-position four-way hydraulic reversing valve.
  • the two working ports of the three-position four-way hydraulically controlled directional control valve are respectively connected to the actuator.
  • the actuator is a hydraulic cylinder, and the two working ports of the three-position four-way hydraulic directional control valve are respectively connected to the rodless cavity and the rod cavity of the hydraulic cylinder.
  • the actuator is a hydraulic motor, and the two working ports of the three-position four-way hydraulic directional control valve are respectively connected to the oil inlet and the oil outlet of the hydraulic motor.
  • the hydraulic control circuit further includes a main valve, a balancing valve and an actuator disposed on the main oil passage, and the first working port of the main valve passes the first operation of the balancing valve and the actuator
  • the second working port of the main valve is in communication with the second working end of the actuator
  • the liquid resisting element is disposed at the second working port of the main valve and the second working element
  • a control port of the balance valve is connected to a line between the second working port of the main valve and the liquid resistance element
  • the second working end of the actuator is A conduit between the fluid blocking elements is in communication with the fuel tank.
  • the hydraulic control circuit further includes a first one-way valve and a second one-way valve, the first one-way valve allowing oil to flow from the second working end of the actuator to the second of the main valve a working port, the second check valve allowing oil to flow from the tank to the second operation of the actuator
  • first one-way valve is located on a pipeline between the second working end of the actuator and the second working port of the main valve, and is connected in parallel with the liquid resistance element;
  • a one-way valve is located on the line between the fuel tank and the second working end of the actuator and is in series with the fluid resistance element.
  • the hydraulic control circuit further includes a relief valve bypassing the line between the second working port of the main valve and the control port of the balancing valve.
  • the actuator is a hydraulic cylinder, and the first working end and the second working end of the actuator are respectively a rodless cavity and a rod cavity of the hydraulic cylinder; or the actuator is a hydraulic motor.
  • the first working end and the second working end of the actuator are respectively an oil inlet and an oil outlet of the hydraulic motor.
  • the main valve is a reversing valve.
  • liquid resistance element is integrated in the main valve or the balancing valve.
  • the present invention also provides a hydraulic control method in which a flow control element can be controlled by controlling a flow rate of the main oil passage by bypassing a liquid resistance element on a main oil passage and bringing the liquid resistance element back to the oil tank. The pressure of the main oil passage.
  • main oil passage is used to control a hydraulically controlled check valve or a hydraulically controlled directional control valve.
  • the hydraulic control method further includes: providing a main valve, a balancing valve, and an actuator disposed on the main oil passage; causing hydraulic oil in the first working end of the actuator to flow into the valve through the balancing valve a first working port of the main valve; causing a hydraulic pressure flowing from the second working port of the main valve to generate a pressure drop through the liquid resisting element, flowing into the oil tank, and a pressure drop value generated by the liquid resisting element
  • the flow rate of the hydraulic oil flowing out of the second working port of the main valve is proportional; the pressure of the hydraulic oil in the line between the second working port of the main valve and the liquid blocking element is Controlling a pressure of the balancing valve; communicating a second working end of the actuator with the fuel tank; controlling a speed of actuation of the actuator by controlling a flow of hydraulic oil flowing from a second working port of the main valve, and / or controlling the speed of the action of the actuator by adjusting the fluid resistance element.
  • the liquid resistance element includes a fixed damping hole, an adjustable damping hole, a pressure reducing valve or a throttling provided on a pipeline between a second working oil port of the main valve and a second working end of the actuator valve.
  • the liquid resistance element includes an adjustable orifice or a throttle valve disposed on a pipeline between a second working port of the main valve and a second working end of the actuator to achieve adjustment by
  • the flow area of the orifice or the throttle valve is adjustable to control the speed at which the actuator is actuated.
  • the actuator is a hydraulic cylinder, and the first working end and the second working end of the actuator are respectively a rodless cavity and a rod cavity of the hydraulic cylinder; or the actuator is a hydraulic motor.
  • the first working end and the second working end of the actuator are respectively an oil inlet and an oil outlet of the hydraulic motor.
  • the method further controls an upper limit of the control pressure of the balancing valve by providing a relief valve between the second working port of the main valve and the control port of the balancing valve.
  • the pressure in the main oil passage can be controlled by controlling the flow rate in the main oil passage, so that the pressure in the main oil passage is not easily affected by other parts of the hydraulic system, and there is no need to provide an additional pressure valve.
  • the entire hydraulic system is simplified.
  • Figure 1 is a schematic view of a conventional down load hydraulic control circuit
  • FIG. 2 is a schematic diagram of a hydraulic control circuit in accordance with an embodiment of the present invention.
  • FIG. 3 is a schematic view of a hydraulic control circuit according to another embodiment of the present invention
  • FIGS. 4 to 6 are schematic views of a hydraulic control circuit according to still another embodiment of the present invention
  • FIGS. 7 to 9 are diagrams according to the present invention.
  • FIG. 10 is a schematic illustration of a hydraulic control circuit in accordance with yet another embodiment of the present invention. Description of the reference numerals
  • the present invention provides a hydraulic control circuit, wherein the hydraulic control circuit includes a main oil circuit 1, a liquid resistance element 2, and a fuel tank 3, and the liquid resistance element 2 and the oil tank 3 Connected in series and bypassed on the main oil passage 1.
  • the oil pressure p in the main oil passage 1, the flow passage area A of the liquid resisting member 2, and the oil flow rate in the main oil passage 1 are obtained by the following formula (1):
  • Q is the oil flow rate
  • C d is the flow coefficient
  • A is the flow area of the liquid resistance element 2
  • ⁇ ⁇ is the pressure drop generated by the liquid passing through the liquid resistance element 2
  • ⁇ is the oil density.
  • the oil pressure ⁇ in the main oil passage 1 is equal to the above formula (1). ⁇ ⁇ plus the oil pressure in the tank as a fixed value. It can be concluded from the formula (1) that the oil pressure ⁇ is proportional to the square of the oil flow rate Q, and inversely proportional to the square of the flow area ⁇ of the liquid resistive element 2.
  • the oil pressure p in the main oil passage 1 depends on the flow rate 0. gP, the oil pressure p increases proportionally with the increase of the oil flow rate Q.
  • the pressure in the main oil passage 1 can be controlled by controlling the flow rate in the main oil passage 1, so that the pressure in the main oil passage 1 is not easily affected by other portions of the hydraulic system, and it is not necessary
  • An additional pressure valve is provided to control the pressure in the main line 1, which simplifies the entire hydraulic system.
  • the above formula (1) is only a general flow calculation formula.
  • the formula (1) can be applied, if selected.
  • Different liquid resistance elements for example, when the liquid resistance element is a plurality of series or parallel damping holes or other more complex liquid resistance elements, the specific flow calculation method may also be different, but still can be achieved.
  • the purpose of controlling the flow in the main oil passage 1 to control the pressure in the main oil passage 1 is controlled.
  • the liquid resistance element 2 may be a fixed orifice, an adjustable orifice, a pressure reducing valve or a throttle valve or the like.
  • the liquid resistance element 2 is an adjustable orifice or a throttle valve, thereby adjusting the flow area of the adjustable orifice or the throttle valve by adjusting the flow rate in the main oil passage 1 The pressure in the main oil circuit 1.
  • the main oil passage 1 can be connected to various hydraulic components or hydraulic circuits that require control of pressure, thereby controlling the pressure thereof.
  • the main oil passage 1 can be connected to the control port 41 of the pilot valve 4 to control the conduction or closing of the pilot valve 4.
  • the main oil passage 1 may pass through the control ports 61, 62 of the pilot-operated directional control valve 6 to which the electromagnetic reversing valve 5 is connected. Therefore, the hydraulic oil in the main oil passage 1 serves as the pilot control oil of the pilot-operated directional control valve 6 for controlling the pilot-operated directional control valve 6 to perform the commutation. More specifically, as shown in FIG.
  • the electromagnetic reversing valve 5 may be a three-position four-way electromagnetic reversing valve
  • the hydraulic reversing valve 6 may be a three-position four-way hydraulically controlled reversing valve.
  • the main oil passage 1 is connected to the oil inlet port P5 of the three-position four-way electromagnetic reversing valve, and the two working oil ports A5 and B5 of the three-position four-way electromagnetic reversing valve are respectively connected to the three-position four-way Two control ports 61, 62 of the hydraulically controlled directional control valve.
  • the two working ports A6, B6 of the three-position four-way hydraulically controlled directional control valve can be respectively connected to the actuator 7.
  • the action of the actuator 7 is further controlled by the commutation of the pilot-operated reversing valve 6, and the speed at which the actuator 7 is actuated can be adjusted by controlling the flow rate of the main oil passage 1.
  • the actuator 7 may be a hydraulic cylinder 71, and the two working ports A6, B6 of the three-position four-way hydraulic reversing valve are respectively connected to the rodless chamber 711 of the hydraulic cylinder 71 and There is a rod cavity 712.
  • the actuator 7 may be a hydraulic motor 72, and the two working ports A6, B6 of the three-position four-way pilot valve are respectively connected to the oil inlet 721 of the hydraulic motor 72 and Oil outlet 722.
  • T5 and ⁇ 6 indicate the oil return port of the electromagnetic directional control valve 5 and the oil return port of the pilot directional control valve 6, respectively.
  • Figure 7 shows a hydraulic control circuit providing yet another embodiment of the present invention, the hydraulic control circuit comprising a main oil circuit 1, a liquid resistive element 2 and a fuel tank 3, the liquid resistive element 2 and the fuel tank 3 Connected in series and bypassed on the main oil passage 1, the control circuit further includes a main oil passage 1 disposed a main valve 8 , a balancing valve 9 and an actuator 7 , the first working port A8 of the main valve 8 being in communication with the first working end of the actuating element 7 via the balancing valve 9 , the main valve 8
  • the second working port B8 is in communication with the second working end of the actuator 7, wherein the liquid resisting element 2 is disposed at the second working port B8 of the main valve 8 and the third of the actuator 7 a control port 91 of the balance valve 9 is connected to a line between the second working port B8 of the main valve 8 and the liquid resistance element 2, the actuator A line between the second working end of the seventh working end and the liquid-repellent element 2 is in communication with the oil
  • the control pressure of the balancing valve 9 (ie, the line between the second working port B8 of the main valve 8 and the liquid resisting element 2 (corresponding to the main oil path 1 in the above hydraulic control circuit)
  • the pressure of the hydraulic oil in the ) is generated by the liquid resistive element 2, and the pressure drop value formed by the liquid resistive element 2 is proportional to the flow rate of the hydraulic oil flowing out from the second working port B8 of the main valve 8, ie It is only related to the opening degree of the main valve 8. Therefore, the control pressure of the balancing valve 9 is completely unaffected by the load applied to the actuator 7 (for example, the hydraulic cylinder in the background art), and thus is relatively stable.
  • control pressure of the balancing valve 9 is controlled by controlling the opening degree of the main valve 8, without being controlled by adjusting the back pressure, and therefore, the hydraulic control circuit according to the present invention does not require back pressure, thus reducing the system pressure a lot.
  • the hysteresis of the balance valve is eliminated. Therefore, the system pressure can be reduced, the oil flow rate can be reduced, and the energy loss can be reduced; and the matching between the oil inlet and the oil return port of the main valve 8 is not too high.
  • the actuator 7 may be a hydraulic cylinder 71, and the first working end and the second working end of the actuator 7 are respectively the hydraulic cylinder.
  • the rodless chamber 711 of the 71 and the rod chamber 712; or the actuator 7 is a hydraulic motor 72, the first working end and the second working end of the actuator 7 are respectively the oil inlet of the hydraulic motor 72 721 and oil outlet 722.
  • the actuator 7 can be a hydraulic cylinder 71, that is, corresponding to the down load hydraulic control circuit described in the background art, the scheme will be described in more detail below by way of example.
  • the liquid resistance element 2 may be a fixed orifice, an adjustable orifice, a pressure reducing valve or a throttle valve.
  • the liquid resistance element 2 is an adjustable orifice or a throttle valve, so that by adjusting the opening degree of the main valve 8, the flow area of the adjustable orifice or the throttle valve can be adjusted.
  • the control pressure of the balancing valve 9 is adjusted to adjust the speed of the falling load.
  • the liquid resistive element 2 can be mounted as a separate component on the oil passage between the second working port B of the main valve 1 and the rod chamber 712 of the hydraulic cylinder 71, the liquid resisting element 2 and also It can be integrated in the main valve 8 or the balancing valve 9.
  • the damper hole may be a single damper hole or may be formed by series and/or parallel connection through several damper holes.
  • the oil supply of the rod chamber 712 of the hydraulic cylinder 71 comes directly from the oil tank 3, because the oil in the rodless chamber 711 of the hydraulic cylinder 71 passes through the oil return pipe (ie, through the balance valve 9, the main valve 8 The working port A8 and the return port T8) flow back to the tank 3, so that the system has sufficient oil to be replenished into the rod chamber 712 of the hydraulic cylinder 71 without generating a negative pressure.
  • the oil return pipe ie, through the balance valve 9, the main valve 8
  • the working port A8 and the return port T8 flow back to the tank 3, so that the system has sufficient oil to be replenished into the rod chamber 712 of the hydraulic cylinder 71 without generating a negative pressure.
  • the hydraulic control circuit may further include a first check valve 11 and a second check valve 12, the first check valve 11 allowing oil to be rodped from the hydraulic cylinder 71
  • the chamber 712 flows to a second working port B8 of the main valve 8, which allows oil to flow from the tank 3 to the rod chamber 712 of the hydraulic cylinder 71.
  • the first check valve 11 is located on a pipeline between the rod chamber 712 of the hydraulic cylinder 71 and the second working oil port B8 of the main valve 8, and is connected in parallel with the liquid resistance element 2;
  • the second check valve 12 is located on the line between the oil tank 3 and the rod chamber 712 of the hydraulic cylinder 71, and is connected in series with the liquid resistance element 2.
  • the first check valve 11 can further ensure that the oil in the rod chamber 712 of the hydraulic cylinder 71 flows to the second working port B8 of the main valve 8 without flowing directly back to the tank 3 , thus ensuring that other additional functions of the system are not affected.
  • the second check valve 12 can further ensure oil supply from the fuel tank 3 to the rod chamber 712 of the hydraulic cylinder 71. Since the oil in the rod chamber 711 flows back to the tank through the return pipe during the load drop, the system has sufficient replenishing effect without generating a negative pressure.
  • the hydraulic control circuit may further include a tube bypassing between the second working port B8 of the main valve 8 and the control port 91 of the balancing valve 9. Overflow valve 10 on the road.
  • the upper limit value of the control pressure of the balancing valve 9 can be further controlled by the relief valve 10.
  • the relief valve 10 can also be omitted.
  • the main valve 8 can be selected according to specific conditions.
  • the main valve 8 can be a three-position four-way reversing valve.
  • pilot operated check valve and the hydraulically controlled directional control valve may also be other hydraulic control components.
  • the present invention provides a hydraulic control method in which a liquid resistance element 2 is bypassed on the main oil passage 1 and the liquid resistance element 2 is brought back to the oil tank 3, thereby
  • the pressure of the main oil passage 1 can be controlled by controlling the flow rate of the main oil passage 1.
  • the pressure in the main oil passage 1 is not easily affected by other parts of the hydraulic system, and there is no need to provide an additional pressure valve to control the pressure in the main oil passage 1. This simplifies the entire hydraulic system.
  • the main oil passage 1 can be used to control the pilot operated check valve 4 or the pilot operated pilot valve 6, as described above with reference to Figs. 3 to 6.
  • the hydraulic control method may further include: providing a main valve 8, a balancing valve 9, and an actuator 7 disposed on the main oil passage 1, and making the first of the actuator 7
  • the hydraulic oil in the working end flows into the first working port A8 of the main valve 8 through the balancing valve 9; the hydraulic oil flowing out from the second working port B8 of the main valve 8 is generated through the liquid-resisting element 2
  • the oil tank 3 flows into the tank 3, and the pressure drop value generated by the liquid resisting element 2 is proportional to the flow rate of the hydraulic oil flowing out from the second working port B8 of the main valve 8;
  • the pressure of the hydraulic oil in the pipeline between the second working port B8 and the liquid resisting member 2 is used as the control pressure of the balancing valve 9; the second working end of the actuator 7 is communicated with the oil tank 3;
  • the speed at which the actuator 7 is actuated is controlled by controlling the flow of hydraulic oil flowing out of the second working port B8 of the main valve 8, and/or
  • the control pressure of the balancing valve 9 (ie, the line between the second working port B8 of the main valve 8 and the liquid resisting element 2 (corresponding to the main oil path 1 in the above hydraulic control circuit)
  • the pressure of the hydraulic oil in the ) is generated by the liquid resistive element 2, and the pressure drop value formed by the liquid resistive element 2 is proportional to the flow rate of the hydraulic oil flowing out from the second working port B8 of the main valve 8, ie It is only related to the opening degree of the main valve 8. Therefore, the control pressure of the balancing valve 9 is completely unaffected by the load applied to the actuator 7 (for example, the hydraulic cylinder in the background art), and thus is relatively stable.
  • control pressure of the balancing valve 9 is controlled by controlling the opening degree of the main valve 8, without being controlled by adjusting the back pressure, and therefore, the hydraulic control circuit according to the present invention does not require back pressure, thus reducing the system pressure a lot.
  • the hysteresis of the balance valve is eliminated. Therefore, the system pressure can be reduced, the oil flow rate can be reduced, and the energy loss can be reduced; and the matching between the oil inlet and the oil return port of the main valve 8 is not too high.
  • the liquid resistance element 2 in the hydraulic control method provided by the present invention may include the second working port B8 of the main valve 8 and the second operation of the actuator 7.
  • a damper hole, pressure reducing valve or throttle valve is provided on the pipe between the ends.
  • the liquid resisting element 2 may also include an adjustable orifice or a throttle valve disposed on a line between the second working port B8 of the main valve 8 and the second working end of the actuator 7 to achieve passage The flow area of the adjustable orifice or throttle is adjusted to control the speed at which the actuator 7 operates. As shown in FIG. 8 and FIG.
  • the actuator 7 may be a hydraulic cylinder 71, and the first working end and the second working end of the actuator 7 are respectively a rodless cavity 711 and a rod of the hydraulic cylinder 71.
  • the actuator 712; or the actuator 7 is a hydraulic motor 72.
  • the first working end and the second working end of the actuator 7 are the oil inlet 721 and the oil outlet 722 of the hydraulic motor 72, respectively.
  • the hydraulic control method according to the present invention can also control the installation by providing an overflow valve 10 between the second working port B8 of the main valve 8 and the control port 91 of the balancing valve 9.
  • the upper limit of the control pressure of the balancing valve 9 is described.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un circuit de commande hydraulique comprenant un chemin principal d'huile (1), une unité de résistance liquide (2) et un réservoir (3), laquelle unité de résistance liquide est alignée sur le réservoir et déviée du chemin principal d'huile. L'invention concerne aussi un procédé de commande hydraulique consistant à dévier l'unité de résistance liquide sur le chemin principal d'huile et retirer l'unité de résistance liquide du réservoir afin de commander la pression du chemin principal d'huile moyennant la commande du débit du chemin principal d'huile.
PCT/CN2011/076878 2010-08-13 2011-07-05 Circuit et procédé de commande hydraulique WO2012019498A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN 201010255962 CN102042273B (zh) 2010-08-13 2010-08-13 液压控制回路及方法
CN201010255962.3 2010-08-13

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Publication Number Publication Date
WO2012019498A1 true WO2012019498A1 (fr) 2012-02-16

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CN (1) CN102042273B (fr)
WO (1) WO2012019498A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
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CN102269190B (zh) * 2011-07-04 2013-06-05 中联重科股份有限公司 液压控制回路
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CN102374203B (zh) * 2011-10-31 2013-03-13 中联重科股份有限公司 液压控制回路
CN102583173B (zh) * 2011-12-19 2014-06-04 徐州重型机械有限公司 吊臂伸缩液控系统及具有液控系统的起重机
CN102758389A (zh) * 2012-06-28 2012-10-31 湖南海捷精密工业有限公司 移动装置液压平衡回路
CN103603839B (zh) * 2013-11-20 2016-08-10 长沙中联消防机械有限公司 防抖液压回路、臂架防抖液压回路、工程机械和工程车辆
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