WO2013063997A1 - Boucle d'asservissement hydraulique - Google Patents

Boucle d'asservissement hydraulique Download PDF

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Publication number
WO2013063997A1
WO2013063997A1 PCT/CN2012/082285 CN2012082285W WO2013063997A1 WO 2013063997 A1 WO2013063997 A1 WO 2013063997A1 CN 2012082285 W CN2012082285 W CN 2012082285W WO 2013063997 A1 WO2013063997 A1 WO 2013063997A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
control valve
bypass
port
flow
Prior art date
Application number
PCT/CN2012/082285
Other languages
English (en)
Chinese (zh)
Inventor
左春庚
李美香
张劲
魏星
Original Assignee
中联重科股份有限公司
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 中联重科股份有限公司, 湖南中联重科专用车有限责任公司 filed Critical 中联重科股份有限公司
Publication of WO2013063997A1 publication Critical patent/WO2013063997A1/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
    • F15B11/0406—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed during starting or stopping
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/85—Control during special operating conditions
    • F15B2211/851—Control during special operating conditions during starting

Definitions

  • the present invention relates to the field of hydraulic control and, in particular, to a hydraulic control circuit having a bypass throttle circuit. Background technique
  • a speed control loop is usually also provided to meet the control requirements for the speed of movement of the actuator.
  • there are various ways to control the movement speed of the actuator for example, by changing the flow cross section of the flow control valve to control and regulate the flow into or out of the actuator, thereby realizing the throttle speed regulation loop of the speed regulation;
  • a variable speed control loop that achieves speed regulation by changing the displacement of a hydraulic pump or a hydraulic motor. Since variable-pressure hydraulic pumps are usually required for volumetric speed-regulating circuits, the cost is increased. Therefore, more throttling speed-regulating circuits are used, such as bypass throttle circuits using throttle valves or commutation Valve reversing valve speed control loop.
  • Figure 1 shows a conventional hydraulic control circuit.
  • the hydraulic control circuit includes a directional control valve 10 and an actuator 20 (such as a hydraulic motor) connected to the directional control valve 10, the directional control valve 10 including a bypass inlet P' and a bypass outlet.
  • a bypass throttle circuit of C wherein the bypass inlet P' communicates with the oil inlet port P (ie, the working hydraulic oil of the hydraulic pump is supplied to the oil inlet port P and the bypass inlet port P' of the directional control valve 10), bypassing
  • the outlet C communicates with the fuel tank, and the flow passage section of the bypass throttle circuit changes with the opening degree of the directional control valve 10.
  • 11-16 denote the respective throttle grooves at the respective ends of the spool of the directional control valve 10.
  • Figure 1 shows the working state of the hydraulic control circuit when the directional control valve 10 is in the neutral position.
  • the working oil ports (A port and B port) of the directional control valve 10 the oil inlet port P and the back are shown.
  • the oil ports T are all closed, and the bypass inlet P' and the bypass outlet C are connected, and the bypass throttle circuit (substantially) does not throttle the flow of oil flowing through the bypass inlet P' and the bypass outlet C.
  • execute Element 20 does not operate and hydraulic oil from a hydraulic pump (not shown) flows back to the tank through bypass inlet P' and bypass outlet C.
  • the opening degree of the directional control valve 10 gradually increases, the oil inlet port P communicates with the A port, and the B port communicates with the oil return port T.
  • the through-flow section of the bypass throttle circuit formed by the bypass inlet P' and the bypass outlet C is gradually reduced.
  • most of the hydraulic oil from the hydraulic pump sequentially flows through the oil inlet P, the oil inlet throttle groove 13, and the A port, passes through the actuator 20 and performs work on the actuator, and then returns oil from the port B.
  • the throttle groove 11 and the oil return port T flow back to the oil tank.
  • a small portion of the hydraulic oil from the hydraulic pump flows through the bypass inlet P', the bypass throttle 12, and the bypass outlet C to flow back to the tank after throttling.
  • the operating speed of the actuator 20 is the linear moving speed of the piston rod of the hydraulic cylinder; if the actuator 20 is a hydraulic motor, the operating speed of the actuator 20 is the rotational speed of the hydraulic motor.
  • the opening degree of the directional control valve 10 when the load is constant, if the opening degree of the directional control valve 10 is increased, the flow cross section of the bypass throttle circuit formed by the bypass inlet P' and the bypass outlet C is reduced, and therefore, The flow rate of the hydraulic oil acting on the actuator 20 is increased, and the flow rate of the hydraulic oil flowing through the bypass throttle circuit is decreased, thereby accelerating the operating speed of the actuator 20; conversely, if the load is constant, if the direction is controlled
  • the opening degree of the valve 10 is decreased, the flow cross section of the bypass throttle circuit is increased, so that the flow rate of the hydraulic oil acting on the actuator 20 is decreased, and the flow rate of the hydraulic oil flowing through the bypass throttle circuit is increased. Large, thereby slowing the operating speed of the actuator 20.
  • the speed control of the actuator 20 is achieved by the bypass throttle circuit of the directional control valve 10.
  • the main factor affecting the operating speed of the actuator 20 is the opening degree of the system load and the directional control valve 10, in other words, the main influencing factor of the flow rate of the hydraulic oil acting on the actuator 20 is the system load and direction.
  • the opening of the control valve 10 is controlled.
  • the spool of the directional control valve 10 When the system is in the idle state, the spool of the directional control valve 10 is in the neutral position, and the system hydraulic oil flows back to the oil tank through the bypass circuit. Since the throttle groove is designed according to the idle speed, the hydraulic oil in the bypass circuit is The flow rate is equal to the system flow (ie, the oil flow capacity of the bypass return is equal to the system oil supply).
  • the excess hydraulic oil is caused by the rapid increase of the system flow rate, thereby causing the bypass circuit to have less oil flow than the system oil supply.
  • the flow will flow to the actuator 20, causing a sudden increase in the flow of hydraulic oil entering the actuator 20 (i.e., when the actuator 20 is actuated, the flow of hydraulic oil entering the actuator 20 is not zero-based).
  • the present invention provides a hydraulic control circuit including a directional control valve having a bypass throttle circuit and an actuator coupled to the directional control valve, the hydraulic control circuit further including a valve, a valve is connected in series in the bypass throttle circuit to enable The flow rate of hydraulic oil flowing through the bypass throttle circuit can be equal to the system flow supplied to the directional control valve when the actuator is activated.
  • the valve is capable of maintaining a constant flow rate of hydraulic oil flowing through the actuator when the system flow rate supplied to the directional control valve is constant.
  • the valve when the load on the actuator is increased, the valve correspondingly reduces the flow cross section of the valve port of the valve; when the load on the actuator is reduced, the valve correspondingly The flow cross section of the valve port of the valve is increased such that the flow rate of the hydraulic oil flowing through the bypass throttle circuit does not change if the directional control valve has a constant opening.
  • the hydraulic control circuit further includes a fuel tank
  • the valve is a hydraulic flow control valve including an inlet, an outlet, and a first control port and a second control port, the inlet and the direction control of the pilot flow control valve a bypass outlet of the valve is communicated, an outlet of the pilot flow control valve is in communication with the oil tank, and a first control port of the pilot flow control valve is directly or indirectly connected to a system pressure of the hydraulic control circuit,
  • the second control port is in communication with the bypass throttle circuit and is connected to a hydraulic control device acting on the spool of the pilot flow control valve.
  • the first control port of the pilot flow control valve is in direct communication with the oil inlet of the directional control valve.
  • the hydraulic control device comprises a throttle valve and a flow-sensitive piston cylinder, the throttle valve being connected in series in an oil inlet path of the directional control valve, the flow-sensitive piston cylinder comprising a closed piston cylinder and an axially axial direction a piston reciprocally disposed in the cylinder, the piston being coupled to a first piston rod extending from a first end wall of the cylinder, the first piston rod and a spool of the pilot flow control valve a spring connection, a first cavity is defined between the piston and the first end wall, and a second cavity is defined between the piston and the second end wall, the first cavity and the directional control valve
  • the downstream portion of the throttle valve of the oil inlet passage is connected, and the second chamber is connected to the upstream portion of the throttle valve of the oil inlet passage of the directional control valve.
  • the piston of the flow sensitive piston cylinder is further coupled with a second piston rod extending in a direction opposite to the first piston rod to a second end wall of the piston barrel.
  • the hydraulic control device comprises a controller and an electric control valve electrically connected to the controller, the output end of the electric control valve is connected to the second control port, thereby acting on the liquid control flow control valve a spool, the controller controlling a pressure of an output of the electronically controlled valve based on a flow signal of a system flow supplied to the directional control valve.
  • the directional control valve has an oil inlet P, a return port T, and two working ports ⁇ ,
  • a valve constituting the bypass inlet P' and the bypass outlet C of the bypass throttle circuit, and a bypass throttle groove 15 is disposed between the bypass inlet P' and the bypass outlet C,
  • the oil inlet port and the bypass inlet P' are both in pressure communication with the system, and the working port ports ⁇ , ⁇ are respectively in communication with the actuator 11, and the bypass outlet C is in communication with the valve 30.
  • the actuator is a hydraulic motor
  • the hydraulic control circuit is a swing control loop.
  • the actuator when the actuator is started, that is, when the spool of the directional control valve starts to move from the neutral position to the left or right position, the system flow rate is increased, and the valve is used to control the hydraulic oil in the bypass throttle circuit, thereby
  • the flow rate of the hydraulic oil flowing through the bypass throttle circuit can be equal to the system flow supplied to the directional control valve, that is, the system flow supplied to the directional control valve flows substantially all through the bypass throttle circuit to the fuel tank, thus No hydraulic oil flows to the actuator to achieve a zero flow of hydraulic oil entering the actuator when the actuator is activated. Further, it is possible to avoid violent jitter of the actuator and achieve the object of the present invention.
  • Figure 1 is a schematic view of a conventional hydraulic control circuit
  • FIG. 2 is a schematic view of a hydraulic control circuit in accordance with a preferred embodiment of the present invention
  • Figure 3 is a detailed schematic view showing the connection relationship between the liquid control flow control valve and the flow sensitive piston cylinder of Figure 1;
  • Figure 4 is a schematic view showing the structure of the flow sensitive piston rod of Figure 3;
  • FIG. 5 is a schematic illustration of a hydraulic control circuit in accordance with another preferred embodiment of the present invention. detailed description
  • the hydraulic control circuit includes a directional control valve 10 having a bypass throttle circuit and an actuator 20 coupled to the directional control valve 10, the hydraulic control circuit further including a valve 30, the valve 30 is connected in series in the bypass throttle circuit so that the flow rate of the hydraulic oil flowing through the bypass throttle circuit can be equal to that supplied to the directional control valve 10 when the actuator 20 is activated System traffic.
  • the actuator 20 when the actuator 20 is started, that is, when the spool of the directional control valve 10 starts to move from the neutral position to the left or right position, the system flow rate Q is increased, and the valve 30 is used to bypass the hydraulic oil in the throttle circuit.
  • the circuit flows to the fuel tank so that no hydraulic oil flows to the actuator 20 to achieve a zero flow of hydraulic oil entering the actuator 20 when the actuator 20 is activated. Further, it is possible to avoid the violent jitter of the actuator 20, and the object of the present invention is achieved.
  • the valve 30 can have various forms as long as the flow passage area of the bypass throttle circuit can be adjusted and controlled when the actuator 20 is started, so that the hydraulic pressure oil flows into the system when the actuator 20 is started.
  • the bypass throttle circuit can be used.
  • valve 30 can be a hydraulic flow control valve or an electronically controlled flow control valve, the electronically controlled flow control
  • the valve or pilot flow control valve can act according to the signal of the system flow. Two preferred embodiments of the valve 30 will be described in detail below.
  • the valve 30 is also capable of maintaining a constant flow rate of hydraulic oil flowing through the actuator 20 while the hydraulic control system is operating, in the event that the system flow rate supplied to the directional control valve 10 is constant. Therefore, in the case where the flow rate of the hydraulic oil supplied to the directional control valve by the hydraulic pump (i.e., the system flow rate) is constant, the hydraulic oil flowing through the actuator 20 can be utilized by the valve 30 regardless of the change in the load on the actuator. The traffic (basically) remains the same. Thus, the actuator can be maintained at a relatively stable operating speed during operation, thereby achieving a stable operating state.
  • valve 30 connected in series in the bypass throttle circuit
  • the valve 30 when the load on the actuator 20 is increased, the valve 30 correspondingly reduces the flow cross section of the valve port of the valve;
  • the valve 30 When the load on the actuator 20 is reduced, the valve 30 correspondingly increases the flow cross section of the valve port of the valve so that the directional control valve 10 has a constant opening degree, flowing through
  • the flow rate (basic) of the hydraulic oil of the bypass throttle circuit does not change. This is because, for example, when the load on the actuator 20 is increased, the system pressure is increased, and an increase in the system pressure will push the spool of the valve 30 to decrease its flow area, so the pressure at the inlet of the valve 30 will rise.
  • the flow rate of the hydraulic oil of 10 is substantially constant, passing through the working port of the directional control valve 10 (port A or Port B) the flow rate of the hydraulic oil acting on the actuator 20 (this flow rate is equal to the system flow rate Q of the hydraulic oil supplied to the directional control valve 10 minus the flow rate Q2 of the hydraulic oil flowing through the bypass throttle circuit) It remains unchanged, so that the oil flow rate for the actuator can be made independent of the load change, and only by the opening of the spool of the directional control valve 10 (i.e., the flow area of the bypass outlet).
  • the valve 30 capable of realizing the technical solution of the present invention can have various forms.
  • the hydraulic control circuit further includes a fuel tank, and the valve 30 is a hydraulic flow including an inlet 301, an outlet 302, and a first control port 303 and a second control port 304.
  • a control valve, an inlet 301 of the pilot flow control valve is in communication with a bypass outlet C of the directional control valve 10, and an outlet 302 of the pilot flow control valve is in communication with the fuel tank, thereby causing the valve 30 to be connected in series In the fuel saving circuit.
  • the first control port 303 of the pilot flow control valve is directly or indirectly connected to the system pressure of the hydraulic control circuit, thereby regulating the flow area of the valve 30, so that the oil flow rate of the actuator is independent of the load change. the goal of.
  • the first control port 303 of the pilot flow control valve is in direct communication with the oil inlet of the directional control valve 10.
  • the second control port 304 is in communication with the bypass throttle circuit and is connected to a hydraulic control device serving as a spool of the pilot flow control valve. Therefore, the position of the spool of the pilot flow control valve is adaptively adjusted by the action of the spring, so that when the actuator 20 is started, the flow rate of the hydraulic oil entering the actuator 20 is zero. .
  • the hydraulic control device can have various forms, such as shown in Figures 2, 3 and 4, the hydraulic control device comprising a throttle valve 4 and a flow sensitive piston cylinder 32, the throttle valve 4 being connected in series
  • the flow sensitive piston cylinder 32 includes a closed piston cylinder 329 and a piston 328 axially reciprocally disposed in the piston cylinder 329.
  • the piston 328 is connected to the piston 328.
  • a first piston rod 327 of the first end wall 3281 of the piston barrel 329 the first piston rod 327 is coupled to a spring of the valve core of the pilot flow control valve, thereby adjusting the force acting on the spring Adjusting a position of a spool of the pilot flow control valve, a first cavity 322 is defined between the piston 328 and the first end wall 3281, the piston 328 and the second end A second cavity 321 is defined between the walls 3282, and the first cavity 322 is connected to a downstream portion of the throttle valve 4 of the oil inlet path of the directional control valve 10, the second cavity 321 and the directional control valve 10 The upstream portion of the throttle valve 4 of the inlet passage is connected.
  • the control pressure of the hydraulic oil is the system pressure P entering the directional control valve 10, and the control area is Al.
  • the control pressure of the hydraulic oil is the pressure P2 of the hydraulic oil entering the inlet 301 of the pilot flow control valve and the valve of the valve 30.
  • P-P2 is a constant. That is, after the throttling of the bypass throttling circuit, the pressure difference of the hydraulic oil is fixed. Specifically, the pressure difference of the hydraulic oil on both sides of the bypass throttle grooves 12 and 15 is fixed and is not affected by the load. Therefore, in the case where the flow rate of the system supplied to the directional control valve 10 is constant, the flow rate of the hydraulic oil flowing through the bypass throttle circuit remains unchanged, thereby maintaining the flow rate of the hydraulic oil flowing through the actuator 20. constant. The purpose of achieving the oil flow of the actuator is independent of the load change.
  • the first chamber 322 is connected to the downstream portion of the throttle valve 4 of the oil inlet passage of the directional control valve 10, the first chamber 322 is introduced into the pressure P of the oil inlet port of the directional control valve 10, and the control area is A5.
  • the second chamber 321 is connected to the upstream portion of the throttle valve 4 of the oil inlet path of the directional control valve 10, the second chamber 321 introduces a system pressure ⁇ , and the control area is ⁇ 4.
  • the above pressure ⁇ is the pressure of the system hydraulic oil upstream of the throttle valve 4
  • the pressure ⁇ is the pressure of the hydraulic oil after the (downstream) throttle valve 4.
  • the P-P2 is increased to increase the flow of hydraulic oil through the bypass throttle circuit.
  • the calculation process is as follows:
  • the flow rate of the hydraulic oil flowing through the bypass throttle circuit is Q2, wherein
  • A the force control area of the pressure compensating valve 31
  • A3 is decreased as the opening degree of the directional control valve 10 is increased. Therefore, as the opening degree of the directional control valve 10 is gradually increased, since the flow passage area of the bypass throttle groove 12 or 15 is gradually decreased, the flow rate through the bypass circuit is gradually decreased until the directional control valve 10 reaches the left Bit or right position (At this time, part of the hydraulic oil passes through the bypass circuit or there is no hydraulic oil as required).
  • the opening degree of the directional control valve 10 is constant and the system flow rate Q is constant, the flow rate Q2 of the hydraulic oil flowing through the bypass throttle circuit is also constant, so the flow rate of the hydraulic oil entering the actuator 20 is set.
  • Q1 is also a fixed value.
  • the flow rate Q when the system flow rate Q is constant, the flow rate of the hydraulic oil entering the actuator 20 is only related to the opening degree of the directional control valve 10; when the opening degree of the directional control valve 10 is a fixed value, A3 is a fixed value, and the system flow rate Q When increasing, the flow rate Q2 of the hydraulic oil flowing through the bypass throttle circuit is increased.
  • the flow rate Q2 of the hydraulic oil flowing through the bypass throttle circuit can be equalized when the actuator 20 is started.
  • the system flow Q that is, the flow rate Q1 entering the actuator 20 can start from zero.
  • the piston 328 of the flow-sensitive piston cylinder 32 is further coupled with a second end wall 3282 extending in a direction opposite to the first piston rod 327 from the piston barrel 329.
  • the second piston rod 326 is such that the control area A5 of the first chamber 322 coincides with the control area A4 of the second chamber 321 to reduce the presence of errors.
  • the hydraulic control device is not limited thereto.
  • the hydraulic control device may include a controller 50 and an electronically controlled valve 40 electrically connected to the controller 50.
  • the output end of the electronic control valve 40 is connected to the a second control port 304 of the flow control flow control valve, thereby acting on the spool of the pilot flow control valve, the controller 50 controlling the flow according to the flow signal of the system pressure hydraulic oil (ie, the system flow rate Q)
  • the electronically controlled valve 40 is an electromagnetic proportional pressure reducing valve.
  • the controller 50 can activate the electronically controlled valve 40 to adjust the position of the spool of the pilot flow control valve, thereby making the flow
  • the flow rate Q2 of the hydraulic oil passing through the bypass throttle circuit is increased to a level equal to the system flow rate Q, achieving the object of the present invention.
  • the directional control valve 10 has the oil inlet port P, the oil return port T, two working oil ports A, B, and a bypass inlet constituting the bypass throttle circuit.
  • P' and a valve bypassing the outlet C (such as a three-position six-way valve), and a bypass throttle groove 12, 15 is disposed between the bypass inlet P and the bypass outlet C.
  • Both the port P and the bypass inlet P' are in communication with a system pressure (such as a system hydraulic oil pumped by the hydraulic pump), and the working ports A, B are respectively in communication with the actuator 11,
  • the oil return port T is in communication with the oil tank, and the bypass outlet C communicates with the valve 30 and further communicates with the oil tank.
  • the directional control valve 10 when the directional control valve 10 is in the first position (the left position in FIG. 1), the oil inlet port P communicates with a working oil port A, and the oil return port T is in communication with another working port B, the bypass throttle circuit is cut off (the flow area of the bypass throttle groove 12 is the smallest, that is, closed); in the directional control valve 10 is in the second position (Fig.
  • the oil inlet P is in communication with the other working port B, the oil return port T is in communication with the one port A, and the bypass throttle circuit is cut off (bypass section)
  • the flow passage area of the flow channel 15 is the smallest, that is, closed; when the directional control valve 10 is at the intermediate position, the oil inlet port P and the oil return port T are both closed, and the bypass inlet P' is adjacent to the side
  • the outlet port C communicates through the bypass throttle groove (at this time, the flow passage area of the bypass throttle groove is the largest).
  • the actuator 11 can be a hydraulic motor, and the hydraulic control circuit is a swing control loop.

Abstract

L'invention concerne une boucle d'asservissement hydraulique comportant un distributeur (10) doté d'une boucle d'étranglement de dérivation et un élément (20) d'exécution relié au distributeur. La boucle d'asservissement hydraulique comporte en outre une vanne (30). La vanne (30) est raccordée en série dans la boucle d'étranglement de dérivation, de telle façon que, lorsque l'élément (20) d'exécution est mis en marche, un débit d'huile hydraulique dans la boucle d'étranglement de dérivation soit égal à un débit du système fourni au distributeur (10). Lorsque l'élément (20) d'exécution est mis en marche, la vanne (30) régule l'huile hydraulique présente dans la boucle d'étranglement de dérivation, de telle façon que le débit d'huile hydraulique dans la boucle d'étranglement de dérivation soit égal au débit du système fourni au distributeur (10), c'est-à-dire que le débit du système fourni au distributeur (10) s'écoule entièrement dans un caisson à huile via la boucle d'étranglement de dérivation, de sorte qu'aucune huile hydraulique ne s'écoule vers l'élément (20) d'exécution, ce qui fait que, lorsque l'élément (20) d'exécution est mis en marche, le débit d'huile hydraulique entrant dans l'élément (20) d'exécution est initialement nul.
PCT/CN2012/082285 2011-10-31 2012-09-28 Boucle d'asservissement hydraulique WO2013063997A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201110338157.1 2011-10-31
CN 201110338157 CN102374203B (zh) 2011-10-31 2011-10-31 液压控制回路

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WO2013063997A1 true WO2013063997A1 (fr) 2013-05-10

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WO2013063749A1 (fr) * 2011-10-31 2013-05-10 中联重科股份有限公司 Circuit de commande hydraulique
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