WO2011057542A1 - 多路阀、液压装置及混凝土泵车 - Google Patents
多路阀、液压装置及混凝土泵车 Download PDFInfo
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- WO2011057542A1 WO2011057542A1 PCT/CN2010/078428 CN2010078428W WO2011057542A1 WO 2011057542 A1 WO2011057542 A1 WO 2011057542A1 CN 2010078428 W CN2010078428 W CN 2010078428W WO 2011057542 A1 WO2011057542 A1 WO 2011057542A1
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- Prior art keywords
- valve
- oil
- way
- hydraulic
- port
- Prior art date
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Classifications
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
-
- 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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
-
- 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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- 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
- F15B2211/3138—Directional control characterised by the positions of the valve element the positions being discrete
-
- 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
- F15B2211/41—Flow control characterised by the positions of the valve element
- F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
- 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
- F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
-
- 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
- F15B2211/455—Control of flow in the feed line, i.e. meter-in control
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/877—With flow control means for branched passages
- Y10T137/87885—Sectional block structure
Definitions
- a multi-way valve is an engineering machine, such as The core control element in the concrete pump truck boom hydraulic device, located between the hydraulic pump and the actuator, is used to control the flow rate and flow direction of the hydraulic oil, thereby centrally controlling the direction and speed of movement of the actuator in the hydraulic device, and thus controlling The movement direction and movement speed of the concrete pump truck boom.
- the existing concrete pump truck mainly uses the manual control multi-way valve and the electro-hydraulic proportional multi-way valve to control the movement of the boom.
- the manual control multi-way valve is operated manually.
- the force of the lever pushes the movement of the spool of the reversing valve, thereby achieving the on/off or switching of the oil passage.
- This multi-way valve cannot realize the electric power.
- the automatic control is subject to a large limitation in the application.
- the electro-hydraulic proportional multi-way valve has a proportional electromagnet, the command electric signal is converted into a current, and the proportional electromagnet is proportionally input, and the proportional electromagnet controls the proportional movement of the spool of the reversing valve.
- the number of circuits of the multi-way valve can be increased or decreased according to the actual movement needs.
- the valve body has at least two oil chambers and The oil port causes the structure of the valve body to be complicated and the manufacturing cost is high.
- the Chinese utility model patent entitled "Multi-way valve and hydraulic device having the multi-way valve, concrete pump truck” discloses a multi-channel a valve for centrally controlling at least two actuators, including a plurality of combination valves mounted on an integrated oil block, the combination valve including a proportional throttle 2 and a reversing valve 3; Having a total oil inlet P and a total oil return port T, the proportional throttle inlet port is in communication with the total oil inlet port, and the oil outlet port is in communication with the oil inlet port of the reversing valve, The oil outlet of the reversing valve is in communication with the total oil return port, and has a working port for connecting the ports of the two actuators; since the multi-way valve is throttled by a simple integrated oil block
- the valve and the reversing valve constitute at least two parallel combined valves, and the control of the movement of the actuator is realized by the proportional throttle valve and the reversing valve, so that the multi-way valve has the advantages of simple structure and low manufacturing cost.
- the disadvantage of the above multi-way valve scheme is that it does not have a load-sensing function.
- the oil pump 6 in the multi-way valve always operates at the relief pressure set by the relief valve 5, and can operate at a maximum of four, and cannot be executed with the actual operation.
- the load of component 4 matches the required flow rate, resulting in a large amount of energy was wasted, and the hydraulic system generates a large amount of heat.
- the technical problem to be solved by the present invention is to provide a multi-way valve and a hydraulic device having a load-sensing function so that the flow rate can be matched with the actual load of the actuator, and the multi-way valve and the hydraulic device can be used to minimize energy loss. , the heat is small.
- a multi-way valve comprising a plurality of parallel combined valves for controlling respective actuators, each of the combination valves including a series of proportional sections a flow valve and a reversing valve, wherein the oil inlet of the proportional throttle valve is connected to the total oil inlet port and the oil outlet port is connected to the oil inlet of the reversing valve, and the oil outlet of the reversing valve and the total
- the oil return port connection is characterized in that: each of the combination valves further includes a one-way type control valve for acquiring a load pressure of the corresponding actuator, and one side of the one-way type control valve is connected to a ratio a conduit between the throttle valve and the actuator, the multi-way valve further comprising a control element, the control element receiving a load pressure fed back by each one-way type control valve, and controlling the load in response to the load pressure Hydraulic oil supply to the actuator.
- the actual load of the plurality of actuators can be transmitted to the control component, and the control component provides the matched flow rate and pressure according to the actual load, so that the energy loss is small and the heat generation amount is small.
- one side of the one-way type control valve in each combination valve is connected to the line between the proportional throttle valve and the reversing valve or between the reversing valve and the corresponding actuator. These lines provide the possibility of collecting actual load pressure.
- the one-way type control valve is a one-way valve, and the oil inlet side of the one-way valve is an access side. Through each one-way valve, the actual pressure oil pressure driving the respective actuator can be transmitted to the control element.
- the one-way type control valve is a shuttle valve
- the first oil inlet side of the shuttle valve is an access side
- the first of the plurality of combination valves The oil outlet of the shuttle valve of the combined valve is connected to the control element
- the second oil inlet of the shuttle valve of the last combined valve is connected to a return port
- the shuttle valve of the adjacent two-two combination valve passes the former combined valve
- the second oil inlet of the shuttle valve is connected to the oil outlet of the shuttle valve of the latter combination valve and connected to each other.
- the shuttle valves of each of the combination valves are connected to each other, and finally the actual load pressure of each of the actuators can be transmitted to the control elements.
- control element is a three-way flow valve
- the oil inlet is connected to the total oil inlet
- the oil return port is connected to the total oil return port
- the control oil port is connected to the one-way valve
- the oil outlet of the oil outlet or the shuttle valve of the first combined valve By providing a three-way flow valve, a load-sensitive network of one-way valves or shuttle valves and three-way flow valves is formed, so that the load-sensitive function can be realized in a simple implementation.
- the integrated oil circuit block further includes the total oil inlet port and the total oil return port, and the combined valve and the three-way flow valve are installed on the integrated oil circuit block.
- the integrated oil block is on the block.
- a solution for providing a hydraulic device according to the present invention is: a hydraulic device including a hydraulic pump, a plurality of actuators, and a multi-way valve disposed between the hydraulic pump and the actuator,
- the road valve comprises a plurality of parallel combined valves, each combined valve being arranged for controlling a corresponding actuator, each of the combined valves comprising a proportional throttle valve and a reversing valve in series, and the inlet port of the proportional throttle valve Connected to the total oil inlet, the oil outlet of the directional valve is connected to the total oil return port.
- each of the combination valves further includes a device for acquiring the corresponding actuator a one-way type control valve of load pressure, one side of the one-way type control valve is connected to a pipeline between a proportional throttle valve and an actuator, and the hydraulic pump is a variable pump with a load-sensitive control mechanism
- the load sensitive control mechanism receives a load pressure fed back by each one-way type control valve, and the variable pump controls the supply of hydraulic oil to the actuator in response to the load pressure.
- the design of the one-way control valve can be similar to the design of the one-way control valve in the multi-way valve solution. The difference is that in the design of the check valve, the oil outlet side of the check valve is connected to the The load sensitive control mechanism. In the design of the shuttle valve, the oil outlet of the shuttle valve of the first of the plurality of combined valves is connected to the load sensitive control mechanism.
- the multi-way valve and hydraulic device of the present invention have load-sensing functions, which effectively reduce energy loss and system heat generation. ⁇ The multi-way valve or hydraulic device provided by the above technical solution controls the movement of the concrete pump truck boom, can meet the movement requirements of the boom, and has the advantages of simple structure, low manufacturing cost, less energy loss, and small system heat generation.
- FIG 1 is a schematic view of a first embodiment of a multi-way valve of the present invention
- FIG. 2 is a front view of a first embodiment of a multi-way valve of the present invention
- Figure 4 is a schematic view of a second embodiment of a multi-way valve of the present invention
- Figure 5 is a schematic view of a third embodiment of the multi-way valve of the present invention
- FIG. 1 it is a multi-way valve for controlling a concrete pump truck boom according to a first embodiment of the present invention.
- the one-way type control valves that acquire the load pressures of the respective actuators are check valves 9-1 - 9-5, receive the load pressure fed back by each one-way type control valve, and respond to the The load pressure is used to control the supply of hydraulic oil to the actuator through the total inlet port as a three-way flow valve 8, which together implements a load sensing function.
- the multi-way valve includes a first combined valve composed of a first electro-hydraulic proportional throttle valve 2-1, a first electromagnetic reversing valve 3-1, and a first one-way valve 9-1, and a second electro-hydraulic a second combination valve composed of a proportional throttle valve 2-2, a second electromagnetic reversing valve 3-2 and a second one-way valve 9-2, a third electro-hydraulic proportional throttle valve 2-3, and a third electromagnetic reversing valve a third combination valve composed of a valve 3-3 and a third check valve 9-3, a fourth electro-hydraulic proportional throttle valve 2-4, a fourth electromagnetic reversing valve 3-4, and a fourth check valve 9-4
- the combination valve and the three-way flow valve 8 are screwed to the integrated oil passage block 1, and the integrated oil passage block has a rectangular parallelepiped structure and has a total oil inlet port P and a total oil return port. T.
- the three-way flow valve 8 has an inlet port ⁇ , a return port Et and a control port Ec, and the three-way flow valve 8 inlet port Ep is in communication with the total inlet port P, and the three-way port 3 valve is returned to the oil port 8
- the port Et is connected to the total oil return port T.
- the first electro-hydraulic proportional throttle valve 2-1 has an oil inlet port A-1 and an oil outlet port B-1, and the first electro-hydraulic proportional throttle valve 2-1 is connected to the oil inlet A-1 and the total oil inlet port. P connected.
- the first electromagnetic reversing valve 3-1 is specifically a three-position four-way electromagnetic reversing valve having an oil inlet port P1, an oil outlet port T1, a first working port C-1 and a first a working port D-1, the oil inlet P-1 of the first electromagnetic reversing valve 3-1 is connected to the oil outlet B-1 of the first electro-hydraulic proportional throttle valve 2-1,
- the oil outlet T-1 of the first electromagnetic reversing valve 3-1 is in communication with the total oil return port ⁇ .
- the first check valve 9-1 has an oil inlet F-1 and an oil outlet G-1, and the oil inlet F-1 of the first one-way valve 9-1 and the first electro-hydraulic ratio are throttled
- the oil outlet B-1 of the valve 2-1 is in communication, and the oil outlet G-1 of the first check valve 9-1 is in communication with the control port Ec of the three-way flow valve 8.
- the second electro-hydraulic proportional throttle valve 2-2 has an oil inlet port A-2 and an oil outlet port B-2, and the second electro-hydraulic proportional throttle valve 2-2 inlet port A-2 and the total oil inlet port P connected.
- the second electromagnetic reversing valve 3-2 is specifically a three-position four-way electromagnetic reversing valve, and the three-position four-way electromagnetic reversing valve has an oil inlet port P-2, an oil outlet port T-2, and a first working oil port C. -2 and the second working port D-2, the oil inlet port ⁇ -2 of the second electromagnetic directional control valve 3-2 and the oil outlet port ⁇ of the second electro-hydraulic proportional throttle valve 2-2 2 communicating, the oil outlet port ⁇ -2 of the second electromagnetic reversing valve 3-2 is in communication with the total oil return port ⁇ .
- the second check valve 9-2 has an oil inlet F-2 and an oil outlet G-2, and the oil inlet F-2 of the second one-way valve 9-2 and the second electro-hydraulic proportional throttle
- the oil outlet port ⁇ -2 of the valve 2-2 is in communication, and the oil outlet port G-2 of the second check valve 9-2 is in communication with the control port Ec of the three-way flow valve 8.
- the third electro-hydraulic proportional throttle valve 2-3 has an oil inlet port A-3 and an oil outlet port B-3, and the third electro-hydraulic proportional throttle valve 2-3 inlet port A-3 and the total oil inlet port P connected.
- the third electromagnetic reversing valve 3-3 is specifically a three-position four-way electromagnetic reversing valve, and the three-position four-way electromagnetic reversing valve has an oil inlet port P-3, an oil outlet port T-3, and a first working oil port C. -3 and the second working port D-3, the oil inlet P-3 of the third electromagnetic reversing valve 3-3 and the oil outlet B- of the third electro-hydraulic proportional throttle valve 2-3 3 is connected, and the oil outlet T-3 of the third electromagnetic reversing valve 3-3 is in communication with the total oil return port T.
- the third check valve 9-3 has an oil inlet F-3 and an oil outlet G-3, and the oil inlet F-3 of the third one-way valve 9-3 is throttled by the third electro-hydraulic ratio
- the oil outlet B-3 of the valve 2-3 is in communication, and the oil outlet G-3 of the third check valve 9-3 is in communication with the control port Ec of the three-way flow valve 8.
- the fourth electro-hydraulic proportional throttle valve 2-4 has an oil inlet port A-4 and an oil outlet port B-4, and the fourth electro-hydraulic proportional throttle valve 2-4 inlet port A-4 and the total oil inlet port P connected.
- the fourth electromagnetic reversing valve 3-4 is specifically a three-position four-way electromagnetic reversing valve, and the three-position four-way electromagnetic reversing valve has an oil inlet port P-4, an oil outlet port T-4, and a first working oil port C. -4 and the second working port D-4, the oil inlet port ⁇ -4 of the fourth electromagnetic reversing valve 3-4 and the oil outlet port of the fourth electro-hydraulic proportional throttle valve 2-4 - 4 communicating, the oil outlet port ⁇ -4 of the fourth electromagnetic reversing valve 3-4 is in communication with the total oil return port ⁇ .
- the fourth check valve 9-4 has an oil inlet F-4 and an oil outlet G-4, and the oil inlet F-4 of the fourth one-way valve 9-4 and the fourth electro-hydraulic proportional throttle
- the oil outlet port ⁇ -4 of the valve 2-4 is in communication, and the oil outlet port G-4 of the fourth check valve 9-4 is in communication with the control port Ec of the three-way flow valve 8.
- the fifth electro-hydraulic proportional throttle valve 2-5 has an oil inlet port A-5 and an oil outlet port B-5, and the fifth electro-hydraulic proportional throttle valve 2-5 inlet port A-5 and the total oil inlet port P connected.
- the fifth electromagnetic reversing valve 3-5 is specifically a three-position four-way electromagnetic reversing valve, and the three-position four-way electromagnetic reversing valve has an oil inlet port P-5, an oil outlet port T-5, and a first working oil port C. -5 and the second working port D-5, the oil inlet port ⁇ -5 of the fifth electromagnetic reversing valve 3-5 and the oil outlet port of the fifth electro-hydraulic proportional throttle valve 2-5 - 5 communicating, the oil outlet port ⁇ -5 of the fifth electromagnetic reversing valve 3-5 is in communication with the total oil return port ⁇ .
- the fifth check valve 9-5 has an oil inlet F-5 and an oil outlet G-5, and the oil inlet F-5 of the fifth one-way valve 9-5 is throttled by the fifth electro-hydraulic ratio
- the oil outlet B-1 of the valve 2-5 is in communication, and the oil outlet G-5 of the fifth check valve 9-5 is in communication with the control port Ec of the three-way flow valve 8.
- the first working port C1 and the second working port D-1 of the first electromagnetic reversing valve 3-1 are connected to the two ports of the hydraulic motor 4-1 through the oil pipe; the second electromagnetic reversing valve 3-2
- the first working port C-2, the second working port D-2 and the two ports of the first hydraulic red 4-2 are connected by the oil pipe;
- the oil port is connected through the oil pipe;
- the first working port C-4, the second working port D-4 of the fourth electromagnetic reversing valve 3-4 and the two ports of the third hydraulic red 4-4 are connected by the oil pipe;
- the two ports of the first working port C-5, the second working port D-5 and the fourth hydraulic port 4-5 of the fifth electromagnetic reversing valve 3-5 are connected by a tubing.
- the working principle of the multi-way valve according to the first embodiment will be specifically described below:
- the first electro-hydraulic proportional throttle valve 2-1 controls the flow area of the valve port by the input electric signal, and thus can be continuous,
- the flow rate of the hydraulic oil flowing through the first electro-hydraulic proportional throttle valve 2-1 is proportionally adjusted, so that the rotational speed of the hydraulic motor 4-1 can be controlled.
- the first electromagnetic reversing valve 3-1 has three working positions, namely an intermediate first phase as shown in FIG. 1, a second phase on the left side, and a third phase on the right side.
- the spool of the first electromagnetic reversing valve 3-1 When the spool of the first electromagnetic reversing valve 3-1 is in the first phase, the spool will enter the oil inlet P1, the oil outlet T1, and the first working port C of the first electromagnetic reversing valve 3-1. -1 and the second working port D-1 are closed, the hydraulic oil does not flow through the first electromagnetic reversing valve 3-1 and the hydraulic motor 4-1, and the hydraulic motor 4-1 is stationary.
- the hydraulic oil enters the oil of the first electromagnetic reversing valve 3-1 through the oil inlet P-1 of the first electromagnetic reversing valve 3-1.
- the moonlight enters the hydraulic motor 4-1 through the second working port D-1 of the first electromagnetic reversing valve 3-1, and the hydraulic oil in the hydraulic motor 4-1 passes through the first electromagnetic reversing valve
- the first working port C-1 of 3-1 enters the oil moon space of the first electromagnetic reversing valve 3-1, and then passes through the oil outlet T-1:; the main oil return port ⁇ 3 ⁇ 4 ⁇ returns to the hydraulic oil tank In the middle, a control loop is formed.
- the hydraulic oil enters the oil of the first electromagnetic reversing valve 3-1 through the oil inlet P-1 of the first electromagnetic reversing valve 3-1.
- the moonlight enters the hydraulic motor 4-1 through the first working port C-1 of the first electromagnetic reversing valve 3-1, and the hydraulic oil in the hydraulic motor 4-1 passes through the first electromagnetic reversing valve
- the second working port D-1 of 3-1 enters the oil moon space of the first electromagnetic reversing valve 3-1, and then flows back to the hydraulic oil tank through the total oil return port T through the oil outlet T-1. Further, a control loop is formed. Through the above hydraulic control process, the flow direction of the hydraulic oil flowing through the hydraulic motor 4-1 is changed, thereby changing the direction of rotation of the hydraulic motor 4-1.
- the oil inlet F-1 of the first check valve 9-1 is in communication with the oil outlet B-1 of the first electro-hydraulic proportional throttle valve 2-1, and the valve of the first electromagnetic reversing valve 3-1
- the oil inlet F-1 of the first check valve 9-1 is in vacant communication with the hydraulic pressure of the hydraulic motor 4-1, that is, the first check valve 9-1 can be in real time.
- the oil outlet G-1 of the first check valve 9-1 communicates with the control port Ec of the three-way flow valve 8, so that the three-way flow valve 8
- the control pressure is equal to the load pressure of the hydraulic motor 4-1.
- the oil inlet Ep of the three-way flow valve 8 is in communication with the total oil inlet port P, and the oil return port Et of the three-way flow valve 8 is in communication with the total oil return port T, and the three-way flow valve 8 is actually driven by the hydraulic motor 4-1.
- Demand ⁇ 1 excess 3 ⁇ 4 ⁇ is returned to the tank through the return port Et, and the total inlet port P operates under the control pressure of the hydraulic motor 4-1 plus the control pressure difference of the three-way flow valve 8, when the hydraulic motor 4-1
- the load pressure changes, the pressure at the total inlet port P changes accordingly, so that the hydraulic device having the multi-way valve has a load-sensing function, which can effectively reduce energy loss and system heat generation.
- the integrated throttle block with simple structure and low manufacturing cost constitutes a proportional throttle valve and a reversing valve to form at least two parallel combined valves, and the integrated oil passage block has a total oil inlet port.
- the proportional throttle valve 2 inlet port is in communication with the total oil inlet port P, the oil outlet port is connected with the oil inlet port of the reversing valve 3, and the oil outlet port and the total return valve of the reversing valve 3
- the oil ports T are connected, and the working ports C and D are connected with the oil ports of the two actuators.
- the proportional throttle valve 2 realizes the control of the moving speed of the actuator 4, and the movement of the actuator 4 is realized by the switching valve 3.
- the check valve and the three-way flow valve in each combination valve can also be mounted on the integrated oil block.
- FIG. 4 is a schematic diagram of a second embodiment of a multi-way valve of the present invention in which the one-way valves 9-1 - 9-5 and the three-way flow valve 8 together implement a load sensing function.
- the oil inlets F-1 - F-5 of the check valves 9-1 - 9-5 are not associated with the electro-hydraulic proportional throttle valve 2-1 - 2
- the oil outlets B-1 - B-5 of -5 are connected, that is, not connected between the proportional section 3 ⁇ 4 ⁇ valve and the reversing valve, but connected between the reversing valve and the actuator.
- FIG. 5 is a schematic view of a third embodiment of the multi-way valve of the present invention, in which the check valve 9-1 - 9-5 is not used, but the shuttle valve and the three-way flow valve 8 are used together to achieve load sensitivity.
- the second oil inlet of the third shuttle valve 10-3 communicates with the oil outlet of the fourth shuttle valve 10-4, and the second oil inlet of the fourth shuttle valve 10-4 and the fifth shuttle valve 10-5
- the oil port is connected, and the second oil inlet of the fifth shuttle valve 10-5 is connected to a return port, which may be a total oil return port or any other oil return port that can be connected to the return oil tank.
- a specific embodiment of the multi-way valve of the present invention is given by taking five sets of combined valves as an example. Those skilled in the art can understand that the multi-way valve of the present invention can also be composed of three groups, four groups or six groups.
- the combination valve is constructed to constitute the multi-way valve of the present invention.
- FIG. 6 is a schematic diagram of a first embodiment of a hydraulic device of the present invention.
- the hydraulic device differs from the aforementioned multi-way valve having a load-sensing function in that a three-way flow valve 8 is not provided as a control element in the multi-way valve, but a load-sensitive control mechanism 11 included in the hydraulic device is used.
- the variable pump 6 cooperates to achieve load sensing.
- the one-way type control valves 9-1 - 9-5 are similar to the specific embodiment of the multi-way valve, that is, a one-way valve or a shuttle valve, a one-way valve 9-1 - 9-5 or a shuttle valve 10-1 - 10-5 can be installed between the proportional throttle valve 2-1- 2-5 and the reversing valve 3-1 - 3-5, or can be installed in the reversing valve 3-1 - 3-5 and executed Between components 4-1 - 4-5. Accordingly, in the embodiment of Fig. 6, the load sensitive control mechanism 11 is coupled to the oil outlet 4 of the one-way valves 9-1 - 9-5. According to a further embodiment of the hydraulic device, corresponding to the embodiment of the multi-way valve according to Fig.
- the first oil inlet side of the shuttle valve 10-1 - 10-5 and the electro-hydraulic proportional section The oil outlets B-1 to B-5 of the flow valves 2-1 - 2-5 are in communication, and the oil outlet of the first shuttle valve 10-1 is in communication with the load sensing control mechanism 11.
- the second oil inlet of the first shuttle valve 10-1 is in communication with the oil outlet of the second shuttle valve 10-2.
- the second oil inlet of the second shuttle valve 10-2 is in communication with the oil outlet of the third shuttle valve 10-3.
- the second oil inlet of the third shuttle valve 10-3 communicates with the oil outlet of the fourth shuttle valve 10-4, and the second oil inlet of the fourth shuttle valve 10-4 and the fifth shuttle valve 10-5
- the oil port is connected, and the second oil inlet of the fifth shuttle valve 10-5 is connected to a return port, which may be a total oil return port or any other oil return port that can be connected to the return oil tank.
- the check valve 9 (or shuttle valve) is used to obtain the load pressure of the actuator 4 to the three-way flow valve 8 (or the load-sensitive control mechanism of the variable pump), and the three-way flow valve 8 (or variable pump) is based on the actuator
- the actual demand of 4 provides the required flow
- the oil pump 6 operates at the load pressure of the actuator 4 plus the control pressure differential of the three-way flow valve 8 (or the load-sensing control mechanism of the variable pump), thereby causing the hydraulic pressure of the hydraulic device
- the system can effectively reduce energy loss and system heating.
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Description
多路岡、 : 装置及;昆凝土泵车 本申请要求 2009年 11月 10 日向中国国家知识产权局提交的名称为 "多 路阀、 液压装置及混凝土泵车,, 的第 200920278542.X号专利申请的优先权, 其全部内容结合于此供参考。 技术领域 本发明涉及工程机械技术领域, 尤其涉及一种多路阀、 液压装置以及混 凝土泵车。 背景技术 多路阀是工程机械, 如混凝土泵车臂架液压装置中的核心控制元件, 其 位于液压泵和执行元件之间, 用于控制液压油流量大小和流向, 从而集中控 制液压装置中的执行元件的运动方向和速度, 进而控制混凝土泵车臂架的运 动方向和运动速度的大小。 目前现有的混凝土泵车主要釆用手动控制多路阀 和电液比例多路阀控制臂架的运动。 手动控制多路阀通过操作手动杠杆的作用力推动换向阀阀芯运动, 进而 实现油路通断或切换, 此多路阀不能实现电气自动控制, 在应用中受到 艮大 的限制。 电液比例多路阀具有比例电磁铁, 指令电信号转化成电流, 按比例输入 比例电磁铁, 比例电磁铁控制换向阀的阀芯比例移动, 实现液压油流量和流 向的控制, 进而控制执行元件的运动速度和运动方向的变化, 该多路阀的回 路数量可根据实际运动需要而增加或减少。 但其阀体内具有至少两个油腔和 油口, 导致阀体的结构复杂, 制造成本很高。 名称为 "多路阀及具有该多路阀的液压装置、 混凝土泵车 " 的 ZL200820003735.X号中国实用新型专利公开了一种多路阀,用于集中控制至 少两个执行元件, 包括若千个安装在集成油路块上的组合阀, 所述组合阀包 括比例节流阀 2和换向阀 3; 所述集成油路块上具有总进油口 P和总回油口 T, 所述比例节流阀进油口与所述总进油口连通, 其出油口与所述换向阀的 进油口连通, 所述换向阀的出油口与所述总回油口连通, 且具有两个执行元 件的油口连接的工作油口; 由于该多路阀釆用简单的集成油路块将比例节流
阀和换向阀组成至少两个并联的组合阀, 通过比例节流阀和换向阀实现对执 行元件运动的控制, 因而该多路阀具有结构简单, 制造成本低的优点。 釆用上述多路阀方案的缺点是不具备负载敏感功能, 该多路阀中的油泵 6总是在溢流阀 5设定的溢流压力、 以最大 4 量进行工作, 不能够与实际执 行元件 4的负载和所需流量匹配, 造成能量大量浪费, 液压***发热量大。 发明内容 本发明所要解决的技术问题是提供一种具有负载敏感功能、 使得流量能 够与执行元件的实际负载匹配的多路阀和液压装置, 使用该多路阀和液压装 置, 可以使得能量损失少, 发热量小。 才艮据本发明的在多路阀方面的提供解决方案是: 一种多路阀, 包括多个 并联的组合阀, 用于控制相应的执行元件, 所述每一个组合阀包括串联的比 例节流阀和换向阀, 所述比例节流阀的进油口与总进油口连接并且出油口与 所述换向阀的进油口连接, 所述换向阀的出油口与总回油口连接, 其特征在 于: 所述每一个组合阀还包括用于获取所述相应的执行元件的负载压力的单 向型控制阀, 所述单向型控制阀的一侧接入到比例节流阀与执行元件之间的 管路上, 所述多路阀还包括控制元件, 所述控制元件接收每一个单向型控制 阀反馈的负载压力, 并响应所述负载压力来控制对所述执行元件的液压油供 给。 通过上述方案, 可以将多个执行元件的实际的负载传递给控制元件, 控 制元件根据实际的负载来提供匹配的流量以及压力, 从而使得能量损失少, 发热量小。 进一步地, 每一个组合阀中的单向型控制阀一侧接入比例节流阀和所述 换向阀之间或所述换向阀和相应的执行元件之间的管路上。 这些管路上都提 供了釆集实际负载压力的可能性。 进一步地, 所述单向型控制阀为单向阀, 所述单向阀的进油口侧为接入 的一侧。 通过每一个单向阀, 可以使得驱动相应执行元件的实际的压力油压 力均传递至控制元件。 在单向阀的进油口侧接入在所述换向阀和相应的执行 元件之间的管路上时, 可以考虑在换向阀的二个工作油口和执行元件之间的 两根管路中的每一根管路上均连接一个单向阀。 当然, 此时, 也相当于安装 一个梭阀, 该梭阀的两个进油口分别接通到这两根管路上, 而出油口则连接 到控制元件上。
才艮据本发明的一个可替换方案, 所述单向型控制阀为梭阀, 所述梭阀的 第一进油口侧为接入的一侧, 所述多个组合阀中的第一个组合阀的梭阀的出 油口连接至控制元件 ,最后一个组合阀的梭阀的第二进油口连接至一回油口 , 相邻两两组合阀的梭阀通过前一个组合阀的梭阀的第二进油口连通至后一个 组合阀的梭阀的出油口而彼此连接。 通过每一个组合阀的梭阀相互连接, 最 终也可以将每一个执行元件的实际负载压力传递到控制元件。 进一步地, 所述控制元件为三通流量阀, 其进油口连接至所述总进油口, 其回油口连接至所述总回油口,其控制油口连接至所述单向阀的出油口或第 一个组合阀的梭阀的出油口。 通过设置三通流量阀, 形成了单向阀或梭阀和 三通流量阀构成的负载敏感网络, 从而可以使得负载敏感功能以简单的实施 方式实现。 才艮据本发明的一个改进方案, 还包括集成油路块, 所述集成油路块上具 有所述总进油口和所述总回油口, 所述组合阀和三通流量阀安装在所述集成 油路块上。 因而该多路阀具有结构简单, 制造成本低的优点。 居本发明的在液压装置方面的提供解决方案是: 一种液压装置, 包括 液压泵、 多个执行元件、 以及设置在所述液压泵和所述执行元件之间的多路 阀, 所述多路阀包括多个并联的组合阀, 每一个组合阀设置用于控制相应的 执行元件, 所述每一个组合阀包括串联的比例节流阀和换向阀, 比例节流阀 的进油口均连接至总进油口, 所述换向阀的出油口均连接至总回油口, 在本 发明的液压装置中, 所述每一个组合阀还包括用于获取所述相应的执行元件 的负载压力的单向型控制阀, 所述单向型控制阀的一侧连接到比例节流阀与 执行元件之间的管路上, 所述液压泵为带有负载敏感控制机构的变量泵, 所 述负载敏感控制机构接收每一个单向型控制阀反馈的负载压力, 所述变量泵 响应所述负载压力来控制对所述执行元件的液压油供给。 通过将液压泵设计 为变量泵, 结合其所具有的负载敏感机构, 可以根据各个执行元件的负载压 力提供与负载匹配的流量和压力。 单向型控制阀的设计可以与多路阀的解决方案中的单向型控制阀的设计 相似, 不同的是, 在单向阀的设计方案时, 单向阀的出油口侧连接至所述负 载敏感控制机构。 在釆用梭阀的设计方案时, 所述多个组合阀中的第一个组 合阀的梭阀的出油口连接至所述负载敏感控制机构。
本发明提拱的多路阀和液压装置具有负载敏感功能, 有效地减少了能量 损失和***发热。 釆用上述技术方案提供的多路阀或液压装置控制混凝土泵 车臂架的运动, 可满足臂架的运动要求, 并且具有结构简单、 制造成本低、 能量损失少、 ***发热小的优点。 附图说明 构成本说明书的一部分、 用于进一步理解本发明的附图示出了本发明的 具体实施方式, 并与说明书一起用来说明本发明的原理。 附图中: 图 1为本发明多路阀的第一种具体实施方式的原理图; 图 2为本发明多路阀第一种具体实施方式的主视图; 图 3为本发明多路阀第一种具体实施方式的俯视图; 图 4为本发明多路阀第二种具体实施方式的原理图; 图 5为本发明多路阀第三种具体实施方式的原理图; 以及 图 6为本发明所述液压装置第一种具体实施方式的原理图。 具体实施方式 下面结合附图和实施例对本发明故进一步说明。 需要说明的是, 在不冲 突的情况下, 本申请中的实施例及实施例中的特征可以相互组合。 如图 1所示, 为本发明第一具体实施方式的用于控制混凝土泵车臂架的 多路阀。 在该实施例中, 获取所述相应的执行元件的负载压力的单向型控制 阀为单向阀 9-1 - 9-5 , 接收每一个单向型控制阀反馈的负载压力、 并响应所 述负载压力来控制经过总进油口对所述执行元件的液压油供给的控制元件为 三通流量阀 8 , 二者共同实现了负载敏感功能。 具体而言, 该多路阀包括第一电液比例节流阀 2-1、 第一电磁换向阀 3-1 和第一单向阀 9-1构成的第一组合阀, 第二电液比例节流阀 2-2、 第二电磁换 向阀 3-2和第二单向阀 9-2构成的第二组合阀, 第三电液比例节流阀 2-3、 第 三电磁换向阀 3-3和第三单向阀 9-3构成的第三组合阀, 第四电液比例节流 阀 2-4、 第四电磁换向阀 3-4和第四单向阀 9-4构成的第四组合阀, 第五电液
比例节流阀 2-5、 第五电磁换向阀 3-5和第五单向阀 9-5构成的第五组合阀, 以及三通流量阀 8和集成油路块 1。 如图 2和图 3所示, 上述组合阀、 三通流量阀 8与所述集成油路块 1螺 紋连接, 所述集成油路块为长方体结构, 具有总进油口 P和总回油口 T。 三通流量阀 8具有进油口 Ερ、 回油口 Et和控制油口 Ec, 所述三通流量 阀 8进油口 Ep与总进油口 P连通, 所述三通 ¾ϊ量阀 8回油口 Et与总回油口 T连通。 第一电液比例节流阀 2-1具有进油口 A-1和出油口 B-1 , 所述第一电液 比例节流阀 2-1进油口 A-1与总进油口 P连通。 第一电磁换向阀 3-1具体为三位四通电磁换向阀, 该三位四通电磁换向 阀具有进油口 P-l、 出油口 T-l、 第一工作油口 C-1和第二工作油口 D-1 , 所 述第一电磁换向阀 3-1 的进油口 P-1与所述第一电液比例节流阀 2-1 的出油 口 B-1连通, 所述第一电磁换向阀 3-1的出油口 T-1与总回油口 Τ连通。 第一单向阀 9-1具有进油口 F-1和出油口 G-1 ,所述第一单向阀 9-1的进 油口 F-1与所述第一电液比例节流阀 2-1的出油口 B-1连通, 所述第一单向 阀 9-1的出油口 G-1与所述三通流量阀 8的控制油口 Ec连通。 第二电液比例节流阀 2-2具有进油口 A-2和出油口 B-2, 所述第二电液 比例节流阀 2-2进油口 A-2与总进油口 P连通。 第二电磁换向阀 3-2具体为三位四通电磁换向阀, 该三位四通电磁换向 阀具有进油口 P-2、 出油口 T-2、 第一工作油口 C-2和第二工作油口 D-2, 所 述第二电磁换向阀 3-2的进油口 Ρ-2与所述第二电液比例节流阀 2-2的出油 口 Β-2连通, 所述第二电磁换向阀 3-2的出油口 Τ-2与总回油口 Τ连通。 第二单向阀 9-2具有进油口 F-2和出油口 G-2,所述第二单向阀 9-2的进 油口 F-2与所述第二电液比例节流阀 2-2的出油口 Β-2连通, 所述第二单向 阀 9-2的出油口 G-2与所述三通流量阀 8的控制油口 Ec连通。 第三电液比例节流阀 2-3具有进油口 A-3和出油口 B-3 , 所述第三电液 比例节流阀 2-3进油口 A-3与总进油口 P连通。
第三电磁换向阀 3-3具体为三位四通电磁换向阀, 该三位四通电磁换向 阀具有进油口 P-3、 出油口 T-3、 第一工作油口 C-3和第二工作油口 D-3 , 所 述第三电磁换向阀 3-3的进油口 P-3与所述第三电液比例节流阀 2-3的出油 口 B-3连通, 所述第三电磁换向阀 3-3的出油口 T-3与总回油口 T连通。 第三单向阀 9-3具有进油口 F-3和出油口 G-3 ,所述第三单向阀 9-3的进 油口 F-3与所述第三电液比例节流阀 2-3的出油口 B-3连通, 所述第三单向 阀 9-3的出油口 G-3与所述三通流量阀 8的控制油口 Ec连通。 第四电液比例节流阀 2-4具有进油口 A-4和出油口 B-4, 所述第四电液 比例节流阀 2-4进油口 A-4与总进油口 P连通。 第四电磁换向阀 3-4具体为三位四通电磁换向阀, 该三位四通电磁换向 阀具有进油口 P-4、 出油口 T-4、 第一工作油口 C-4和第二工作油口 D-4, 所 述第四电磁换向阀 3-4的进油口 Ρ-4与所述第四电液比例节流阀 2-4的出油 口 Β-4连通, 所述第四电磁换向阀 3-4的出油口 Τ-4与总回油口 Τ连通。 第四单向阀 9-4具有进油口 F-4和出油口 G-4,所述第四单向阀 9-4的进 油口 F-4与所述第四电液比例节流阀 2-4的出油口 Β-4连通, 所述第四单向 阀 9-4的出油口 G-4与所述三通流量阀 8的控制油口 Ec连通。 第五电液比例节流阀 2-5具有进油口 A-5和出油口 B-5 , 所述第五电液 比例节流阀 2-5进油口 A-5与总进油口 P连通。 第五电磁换向阀 3-5具体为三位四通电磁换向阀, 该三位四通电磁换向 阀具有进油口 P-5、 出油口 T-5、 第一工作油口 C-5和第二工作油口 D-5 , 所 述第五电磁换向阀 3-5的进油口 Ρ-5与所述第五电液比例节流阀 2-5的出油 口 Β-5连通, 所述第五电磁换向阀 3-5的出油口 Τ-5与总回油口 Τ连通。 第五单向阀 9-5具有进油口 F-5和出油口 G-5 ,所述第五单向阀 9-5的进 油口 F-5与所述第五电液比例节流阀 2-5的出油口 B-1连通, 所述第五单向 阀 9-5的出油口 G-5与所述三通流量阀 8的控制油口 Ec连通。 第一电磁换向阀 3-1 的第一工作油口 C-l、 第二工作油口 D-1与液压马 达 4-1的两个油口通过油管连接; 第二电磁换向阀 3-2的第一工作油口 C-2、 第二工作油口 D-2与第一液压紅 4-2的两个油口通过油管连接; 第三电磁换 向阀 3-3的第一工作油口 C-3、 第二工作油口 D-3与第二液压紅 4-3的两个
油口通过油管连接; 第四电磁换向阀 3-4 的第一工作油口 C-4、 第二工作油 口 D-4与第三液压紅 4-4的两个油口通过油管连接; 第五电磁换向阀 3-5的 第一工作油口 C-5、 第二工作油口 D-5与第四液压紅 4-5的两个油口通过油 管连接。 下面具体描述才艮据第一实施方式的多路阀的工作原理: 所述第一电液比例节流阀 2-1 通过输入的电信号控制其阀口的通流面 积, 进而可连续的、 按比例地调节流经所述第一电液比例节流阀 2-1 的液压 油流量, 从而可控制液压马达 4- 1的旋转速度。 所述第一电磁换向阀 3-1具有三个工作位置, 分别如图 1所示的中间的 第一相位、 左侧的第二相位和右侧的第三相位。 当第一电磁换向阀 3-1 的阀芯处于第一相位时, 所述阀芯将第一电磁换 向阀 3-1的进油口 P-l、 出油口 T-l、 第一工作油口 C-1和第二工作油口 D-1 封闭, 液压油不流经第一电磁换向阀 3-1和液压马达 4-1 , 液压马达 4-1静止 不动。 当第一电磁换向阀 3-1 的阀芯处于第二相位时, 液压油通过第一电磁换 向阀 3-1的进油口 P-1进入第一电磁换向阀 3-1 的油月空, 再通过第一电磁换 向阀 3-1的第二工作油口 D-1进入液压马达 4-1 ,所述液压马达 4-1内的液压 油通过所述第一电磁换向阀 3-1的第一工作油口 C-1进入第一电磁换向阀 3-1 的油月空内, 再通过出油口 T-1:;充经总回油口 Τ ¾ϊ回到液压油箱中, 进而形成 控制回路。 当第一电磁换向阀 3-1 的阀芯处于第三相位时, 液压油通过第一电磁换 向阀 3-1的进油口 P-1进入第一电磁换向阀 3-1 的油月空, 再通过第一电磁换 向阀 3-1的第一工作油口 C-1进入液压马达 4-1 ,所述液压马达 4-1内的液压 油通过所述第一电磁换向阀 3-1的第二工作油口 D-1进入第一电磁换向阀 3-1 的油月空内, 再通过出油口 T-1流经总回油口 T流回到液压油箱中, 进而形成 控制回路。 经过上述液压控制过程,实现流经所述液压马达 4-1的液压油流向改变, 进而改变液压马达 4-1的回转方向。
所述第一单向阀 9-1 的进油口 F-1与第一电液比例节流阀 2-1 的出油口 B-1 连通, 当第一电磁换向阀 3-1 的阀芯处于第二相位或第三相位时, 第一 单向阀 9-1 的进油口 F-1 即与液压马达 4-1工作压力油空连通, 即第一单向 阀 9-1 可以实时获得液压马达 4-1 的负载压力; 同时所述第一单向阀 9-1的 出油口 G-1与所述三通流量阀 8的控制油口 Ec连通, 使得三通流量阀 8的 控制压力与液压马达 4-1的负载压力相等。三通流量阀 8的进油口 Ep与总进 油口 P连通, 三通流量阀 8的回油口 Et与总回油口 T连通, 三通流量阀 8 才艮据液压马达 4-1实际需求^ 1多余的 ¾ϊ量通过回油口 Et返回油箱,总进油口 P 在液压马达 4-1的负载压力加上三通流量阀 8的控制压差下工作, 当液压马 达 4-1的负载压力变化时, 总进油口 P处的压力随之发生改变, 从而使得具 有该多路阀的液压装置具有负载敏感功能, 能有效地减少能量损失和***发 热。 同样, 其它电液比例节流阀、 电磁换向阀和单向阀可以实现控制第一液 压紅 4-2、 第二液压紅 4-3、 第三液压紅 4-4和第四液压紅 4-5的活塞运动方 向和速度, 同时具有负载敏感功能, 能有效地减少能量损失和***发热。 如图 2, 3 所示, 釆用结构简单、 制造成本低的集成油路块将比例节流 阀和换向阀组成至少两个并联的组合阀, 该集成油路块上具有总进油口 P和 总回油口 T, 比例节流阀 2进油口与总进油口 P连通, 其出油口与换向阀 3 的进油口连通, 换向阀 3的出油口与总回油口 T连通, 且具有两个执行元件 的油口连接的工作油口 C和 D, 通过比例节流阀 2实现对执行元件 4运动速 度的控制, 通过换向阀 3实现对执行元件 4运动方向的控制。 此外, 也可以 将每一个组合阀中的单向阀和三通流量阀安装在集成油路块上。 图 4为本发明的多路阀的第二种具体实施方式的原理图,其中单向阀 9-1 - 9-5和三通流量阀 8共同实现了负载敏感功能。 与第一种具体实施方式不 同的是,此时,单向阀 9-1 - 9-5的进油口 F-1 - F-5不是与所述电液比例节流 阀 2-1 - 2-5的出油口 B-1 - B-5连通, 即不是连接在比例节 ¾ϊ阀与换向阀之 间, 而是连接在换向阀与执行元件之间。 jt匕时, 由于在换向阀的两个工作油 口与执行元件之间设置了两条管路, 因此, 在每一条管路上均连接了一个单 向阀, 即单向的进油口侧。 单向阀的出口均连接至三通流量阀 8的控制油口 Ec。 图 5为本发明所述多路阀第三种具体实施方式的原理图, 其中未使用单 向阀 9-1 - 9-5 , 而是使用梭阀和三通流量阀 8共同实现了负载敏感功能。 jt匕
时,梭阀 10-1 - 10-5的第一进油口侧与所述电液比例节流阀 2-1 - 2-5的出油 口 B-1 - B-5连通, 第一梭阀 10-1 的出油口与三通流量阀 8的控制油口 Ec 连通。 第一梭阀 10-1的第二进油口与第二梭阀 10-2的出油口连通。 第二梭 阀 10-2的第二进油口与第三梭阀 10-3的出油口连通。 第三梭阀 10-3的第二 进油口与第四梭阀 10-4的出油口连通, 第四梭阀 10-4的第二进油口与第五 梭阀 10-5的出油口连通, 第五梭阀 10-5的第二进油口连接至一回油口, 该 回油口可以是总回油口或者任一可以通至回油箱的其他的回油口。 上述说明中, 以五组组合阀为例给出了本发明的多路阀的具体实施例, 本领域技术人员可以理解, 本发明的多路阀也可以由三组、 四组或六组等组 合阀来构成本发明的多路阀。 图 6为本发明的液压装置的第一具体实施方式的原理图。 该液压装置与 前述具有负载敏感功能的多路阀不同的是, 其中未在多路阀中设置三通流量 阀 8作为控制元件, 而是使用包含在液压装置中的带有负载敏感控制机构 11 的变量泵 6配合实现了负载敏感功能。 单向型控制阀 9-1 - 9-5与多路阀的具 体实施方式中类似,即可以选取单向阀或者梭阀,单向阀 9-1 - 9-5或梭阀 10-1 - 10-5既可以安装在比例节流阀 2-1 - 2-5和所述换向阀 3-1 - 3-5之间,也可 以安装在换向阀 3-1 - 3-5与执行元件 4-1 - 4-5之间。 相应地, 在图 6的具体实施方式中, 将负载敏感控制机构 11连接至单向 阀 9-1 - 9-5的出油口 4则。 根据液压装置的另一具体实施方式,与根据图 4的多路阀的实施例对应, 可以将连接在换向阀 3-1 - 3-5与执行元件 4-1 - 4-5之间的两根管路的两个单 向阀的出油口侧均连接到负载敏感控制机构 11。 根据液压装置的另一具体实施方式, 与根据图 5的多路阀的具体实施方 式对应, 此时, 梭阀 10-1 - 10-5的第一进油口侧与所述电液比例节流阀 2-1 - 2-5的出油口 B- 1 - B-5连通,第一梭阀 10-1的出油口与负载敏感控制机构 11连通。 第一梭阀 10-1的第二进油口与第二梭阀 10-2的出油口连通。 第二 梭阀 10-2的第二进油口与第三梭阀 10-3的出油口连通。 第三梭阀 10-3的第 二进油口与第四梭阀 10-4的出油口连通, 第四梭阀 10-4的第二进油口与第 五梭阀 10-5的出油口连通, 第五梭阀 10-5的第二进油口连接至一回油口, 该回油口可以是总回油口或者任一可以通至回油箱的其他的回油口。
同时釆用单向阀 9 (或梭阀) 获取执行元件 4的负载压力传递给三通流 量阀 8 (或变量泵的负载敏感控制机构), 三通流量阀 8 (或变量泵)根据执 行元件 4的实际需求提供所需流量, 油泵 6在执行元件 4的负载压力加上三 通流量阀 8 (或变量泵的负载敏感控制机构) 的控制压差下工作, 从而使得 具有该液压装置的液压***能有效地减少能量损失和***发热。 以上所述仅为本发明的优选实施例而已, 并不用于限制本发明, 对于本 领域的技术人员来说, 本发明可以有各种更改和变化。 凡在本发明的 ^"神和 原则之内, 所作的任何修改、 等同替换、 改进等, 均应包含在本发明的保护 范围之内。 参考标识
1 集成油路块
2- 1 - 2-5 第一、 第二、 第三、 第四、 第五电液比例节流阀
3- 1 - 3-5 第一、 第二、 第三、 第四、 第五电磁换向阀
4- 1 液压马达
4-2 - 4-5 第一、 第二、 第三、 第四液压紅
5 溢流阀
6 变量泵
7 油箱
8 三通流量阀
9-1 - 9-5 第一、 第二、 第三、 第四、 第五单向阀
10-1 - 10-5 第一、 第二、 第三、 第四、 第五梭阀 负载敏感控制机构
Claims
1. 一种多路阀, 包括多个并联的组合阀, 用于控制相应的执行元件(4-1 - 4-5 ), 所述每一个组合阀包括比例节流阀( 2-1 - 2-5 )和换向阀( 3-1 - 3-5 ), 所述比例节流阀的进油口与总进油口 ( P )连接, 并且出油口 与所述换向阀的进油口连接, 所述换向阀的出油口与总回油口 ( T )连 接, 其特征在于: 所述每一个组合阀还包括用于获取所述相应的执行 元件的负载压力的单向型控制阀 (9-1 - 9-5, 10-1 - 10-5 ), 所述单向 型控制阀的一侧接入比例节流阀与执行元件之间的管路上, 所述多路 阀还包括控制元件 ( 8 ), 所述控制元件接收每一个单向型控制阀反馈 的负载压力, 并响应所述负载压力来控制对所述执行元件的液压油供 给。
2. 根据权利要求 1所述的多路阀, 其特征在于, 每一个组合阀中的单向 型控制阀 (9-1 -9-5, 10-1 - 10-5 ) 一侧接入比例节¾¾阀 (2-1 -2-5 ) 和所述换向阀 ( 3-1 - 3-5 ) 之间或所述换向阀和相应的执行元件 ( 4-1 -4-5 )之间的管路上。
3. 根据权利要求 2所述的多路阀, 其特征在于, 所述单向型控制阀为单 向阀 (9-1 - 9-5 ), 所述单向阀的进油口侧 (F-1 - F-5 )为接入的一侧。
4. 根据权利要求 2所述的多路阀, 其特征在于, 所述单向型控制阀为梭 阀 ( 10-1 - 10-5 ), 所述梭阀的第一进油口侧为接入的一侧, 所述多个 组合阀中的第一个组合阀的梭阀( 10-1 )的出油口连接至控制元件( 8 ), 最后一个组合阀的梭阀 ( 10-5 ) 的第二进油口连接至一回油口, 相邻 两两组合阀的梭阀通过前一个组合阀的梭阀的第二进油口连通至后一 个组合阀的梭阀的出油口而彼 jtb连接。
5. 根据权利要求 3或 4所述的多路阀, 其特征在于, 所述控制元件为三 通流量阀 (8 ), 其进油口 (Ep) 连接至所述总进油口 (P ) ,其回油口 连接至所述总回油口 (T) ,其控制油口 (Ec) 连接至所述单向阀的出 油口 ( G-1 - G-5 ) 或第一个组合阀的梭阀 ( 10-1 ) 的出油口。
6. 根据权利要求 5所述的多路阀, 其特征在于, 还包括集成油路块, 所 述集成油路块 ( 1 ) 上具有所述总进油口 (P) 和所述总回油口 (T), 所述组合阀和三通流量阀 (8 ) 安装在所述集成油路块上。
7. —种液压装置, 包括液压泵、 以及设计为液压马达或液压紅的执行元 件, 以及设置在所述液压泵和所述执行元件之间的根据权利要求 1-6 中任一项所述的多路阀。
8. —种液压装置, 包括液压泵 (6 )、 多个执行元件、 以及设置在所述液 压泵和所述执行元件之间的多路阀, 所述多路阀包括多个并联的组合 阀, 每一个组合阀设置用于控制相应的执行元件 ( 4-1 - 4-5 ), 所述每 一个组合阀包括串联的比例节流阀 ( 2-1 - 2-5 )和换向阀 ( 3-1 - 3-5 ), 所述比例节流阀的进油口与总进油口 ( P )连接并且出油口与所述换向 阀的进油口连接, 所述换向阀的出油口与总回油口 ( T )连接, 其特征 在于: 所述每一个组合阀还包括用于获取所述相应的执行元件的负载 压力的单向型控制阀 (9-1 - 9-5 , 10-1 - 10-5 ), 所述单向型控制阀的 一侧连接到比例节流阀与执行元件之间的管路上, 所述液压泵为带有 负载敏感控制机构 ( 11 ) 的变量泵( 6 ), 所述负载敏感控制机构 ( 11 ) 接收每一个单向型控制阀反馈的负载压力, 所述变量泵(6 )响应所述 负载压力来控制对所述执行元件的液压油供给。
9. 才艮据权利要求 8所述的液压装置, 其特征在于, 每一个组合阀中的单 向型控制阀 ( 9-1 - 9-5 , 10-1 - 10-5 )一侧接入比例节¾¾阀 ( 2-1 - 2-5 ) 和所述换向阀 ( 3-1 - 3-5 ) 之间或所述换向阀和相应的执行元件 ( 4-1 - 4-5 )之间的管路上。
10. 根据权利要求 9所述的液压装置, 其特征在于, 所述单向型控制阀为 单向阀 (9-1 - 9-5 ), 所述单向阀的进油口侧 (F-1 - F-5 ) 为接入的一 侧, 出油口侧 ( G-1 - G-5 ) 连接至所述负载敏感控制机构 ( 11 )。
11. 根据权利要求 9所述的液压装置, 其特征在于, 所述单向型控制阀为 梭阀 ( 10-1 - 10-5 ), 所述梭阀的第一进油口侧为接入侧, 所述多个组 合阀中的第一个组合阀的梭阀 ( 10-1 ) 的出油口连接至所述负载敏感 控制机构 ( 11 ), 最后一个组合阀的梭阀 ( 10-5 ) 的第二进油口连接至 一回油口, 相邻两两组合阀的梭阀通过前一个组合阀的梭阀的第二进 油口与后一个组合阀的梭阀的出油口彼此连接。 一种混凝土泵车, 其特征在于: 所述混凝土泵车具有 居权利要求 1-6 中任一项所述的多路阀或根据权利要求 7-11 中任一项所述的液压装 置。
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EP10829506.4A EP2500584A4 (en) | 2009-11-10 | 2010-11-04 | Multi-way valve, hydraulic device and concrete pump |
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CN200920278542XU CN201574992U (zh) | 2009-11-10 | 2009-11-10 | 多路阀、液压装置及混凝土泵车 |
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