CN113931892A - Load-sensitive multi-way valve with independently controlled load port and hydraulic system - Google Patents
Load-sensitive multi-way valve with independently controlled load port and hydraulic system Download PDFInfo
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- CN113931892A CN113931892A CN202111142768.9A CN202111142768A CN113931892A CN 113931892 A CN113931892 A CN 113931892A CN 202111142768 A CN202111142768 A CN 202111142768A CN 113931892 A CN113931892 A CN 113931892A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/026—Pressure compensating valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
- F16K11/20—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members
- F16K11/22—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by separate actuating members with an actuating member for each valve, e.g. interconnected to form multiple-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/04—Construction of housing; Use of materials therefor of sliding valves
- F16K27/041—Construction of housing; Use of materials therefor of sliding valves cylindrical slide valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
- F16K31/0613—Sliding valves with cylindrical slides
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
Abstract
The invention discloses a load sensitive multi-way valve with independently controlled load ports and a hydraulic system, which comprises a valve body with a first oil port and a second oil port, an oil inlet valve core, the pressure compensation valve cavity is connected with the oil inlet valve cavity through an oil inlet oil duct, the pressure compensation valve cavity is connected with an inlet oil duct through an oil inlet oil duct, the pressure compensation valve cavity is connected with the oil inlet valve cavity through an LS signal transmission oil duct, the oil return valve cavity is connected with an oil return oil duct, and at least one end of the oil return valve core is provided with an oil return proportional control valve. The design is simple, the structure is compact, and the precision requirement is lower.
Description
Technical Field
The invention relates to a hydraulic multi-way valve, in particular to a load-sensitive multi-way valve with independently controlled load ports. In addition, the hydraulic system is provided with the load-sensitive multi-way valve with the load ports controlled independently.
Background
The traditional load sensitive multi-way valve adopts a main valve core to control the flow direction of pressure oil, acts on an actuating mechanism connected to a load port of the main valve core, and realizes the change of the direction of the actuating mechanism by reversing control of the valve core. Because the main valve core is adopted for control, the oil inlet channel and the oil return channel are controlled by the same valve core, the opening displacement of the throttling groove is in linkage in the same direction, and the flow area is increased or reduced simultaneously. In order to achieve matching of oil inlet and oil return, different oil inlet and oil return throttling grooves are designed according to different working conditions and different flow rates to meet requirements, even auxiliary elements such as a balance valve, a one-way throttling valve and a back pressure valve are required to be added in a system to increase oil return backpressure, otherwise, a main engine is easy to operate unstably and even stalled, but numerous additional valves are added in the system, so that energy consumption and cost of the main engine are greatly increased.
Therefore, an oil inlet and oil return separate control technology is provided, and the problems encountered by the traditional multi-way valve can be well solved. The existing load port independent control double-spool multi-way valve mainly comprises a main valve body, two main valve spool components, a pilot reversing valve assembly, a signal acquisition part and the like, wherein a pressure sensor and a temperature sensor are embedded in the main valve body and used for acquiring pressure signals and temperature change signals, a displacement sensor is integrated on the main valve spool and the like and used for acquiring spool displacement signals, and the displacement of the main valve spool can be respectively controlled by controlling the strength and the mode of input signals of the pilot reversing valve assembly, so that the pressure and the flow required by the system are controlled, and the problems of the traditional multi-way valve are solved.
However, the flow and pressure requirements of the load port independently controlled multi-way valve are compared and analyzed through data collected by the pressure sensor, the flow sensor and the displacement sensor, and the flow and pressure required by the system are output through program operation, so that the system debugging and control difficulty is greatly increased; due to the integration of a plurality of sensors, the requirements of manufacturing, installing, controlling precision and the like of the valve body and the valve core are greatly increased.
Disclosure of Invention
The invention aims to solve the technical problem of providing a load-sensitive multi-way valve with an independently controlled load port, which has the advantages of simple design, compact structure, convenient control, stable and reliable performance and relatively low requirements on the matching precision and the machining precision of parts.
The invention further aims to solve the technical problem of providing a hydraulic system, wherein the load-sensitive multi-way valve with the load port independently controlled is simple in design, compact in structure, convenient to control, stable and reliable in performance, and relatively low in requirements on part matching precision and machining precision.
In order to solve the technical problems, the invention provides a load-sensitive multi-way valve with independently controlled load ports, which comprises a valve body provided with a first oil port and a second oil port, an oil inlet valve core, an oil return valve core and a pressure compensation valve core, wherein the valve body is internally provided with an oil inlet valve cavity for mounting the oil inlet valve core, an oil return valve cavity for mounting the oil return valve core and a pressure compensation valve cavity for mounting the pressure compensation valve core, the first oil port is connected with the oil inlet valve cavity through a first working oil duct, the second oil port is connected with the oil inlet valve cavity through a second working oil duct, the pressure compensation valve cavity is connected with an inlet oil duct, the pressure compensation valve cavity is connected with the oil inlet valve cavity through an oil inlet oil duct, at least one end of the oil inlet valve core is provided with an oil inlet proportional control valve so as to enable the oil inlet oil duct to be selectively communicated with the first oil port or the second oil port of the valve body, one end of the pressure compensation valve cavity is connected with the oil inlet oil duct, the other end of the pressure compensation valve cavity is connected with the oil inlet valve cavity through an LS signal transmission oil duct, so that the pressure difference between an inlet and an outlet of the oil inlet valve core is constant, the oil return valve cavity is connected with an oil return oil duct, and an oil return proportional control valve is installed at least one end of the oil return valve core, so that the oil return oil duct can be selectively communicated with the first oil port or the second oil port of the valve body.
Optionally, a first oil inlet throttling groove used for communicating the oil inlet oil duct with the first oil port and a second oil inlet throttling groove used for communicating the oil inlet oil duct with the second oil port are formed in the oil inlet valve core.
Optionally, a first LS signal cavity for feeding back the load pressure signal of the first oil port and a second LS signal cavity for feeding back the load pressure signal of the second oil port are arranged between the oil inlet valve cavity and the LS signal transmission oil passage.
Optionally, the LS signal transmission oil passage is connected with a shuttle valve connected with a variable displacement pump.
Optionally, the shuttle valve is further connected with a three-way pressure compensating spool.
Optionally, the LS signal transmitting oil passage includes a first LS signal transmitting oil passage and a second LS signal transmitting oil passage, the first LS signal cavity and the second LS signal cavity are both connected to the first LS signal transmitting oil passage, and the second LS signal transmitting oil passage is respectively connected to the second LS signal cavity and the shuttle valve.
Optionally, a signal oil duct and a signal hole for communicating the non-spring cavity at the end of the pressure compensation valve core with the oil inlet oil duct are arranged on the pressure compensation valve core.
Optionally, the oil return passage includes a first oil return passage and a second oil return passage, and the oil return valve core is provided with a first oil return throttling groove for communicating the first oil return passage with the first oil port and a second oil return throttling groove for communicating the second oil return passage with the second oil port.
Optionally, a first LS overflow oil passage connected to the first overflow port and a second LS overflow oil passage connected to the second overflow port are further provided in the valve body, and a first overflow passage for communicating the first LS overflow oil passage with the oil inlet oil passage and a second overflow passage for communicating the second LS overflow oil passage with the oil inlet oil passage are provided on the oil inlet valve core.
Optionally, sealing end covers are respectively installed at two ends of the valve body, the sealing end covers and the oil inlet valve cavity enclose a spring control cavity of the oil inlet valve core, and the sealing end covers and the oil return valve cavity enclose a spring control cavity of the oil return valve core.
Optionally, the oil inlet proportional control valve and the oil return proportional control valve are both reversing proportional pressure reducing valves, the spring control cavities at two ends of the oil inlet valve core are respectively connected with the reversing proportional pressure reducing valves, and the spring control cavities at two ends of the oil return valve core are respectively connected with the reversing proportional pressure reducing valves.
The invention also provides a hydraulic system which is provided with the load sensitive multi-way valve with the load port independently controlled according to any one of the technical schemes.
Through the technical scheme, the invention has the following beneficial effects:
the oil inlet proportional control valve and the oil return proportional control valve are independently arranged, so that oil inlet and oil return of a working mechanism can be independently adjusted, the movement sequence and the pressure of the oil inlet proportional control valve and the oil return proportional control valve are controlled, the movement logics of the oil inlet valve core and the oil return valve core can be controlled, and various combinations are obtained to meet different working condition requirements. Compared with the existing technology of independently controlling the double-valve-core multi-way valve by the load port, the independently controlled load sensitive multi-way valve by the load port has the advantages of simple design, compact structure, convenience in control, stable and reliable performance, energy conservation, high efficiency, relatively low requirements on the matching precision and the processing precision of parts, stronger pollution resistance, better maintainability, lower manufacturing cost and easiness in realizing batch production.
Additional features and advantages of the invention will be set forth in the detailed description which follows.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic structural diagram of a load-sensitive multi-way valve with independently controlled load ports according to an embodiment of the present invention;
FIG. 2 is a diagram of the oil passage layout of a load sensitive multi-way valve with independently controlled load ports according to an embodiment of the present invention;
FIG. 3 is a schematic structural view of an oil inlet spool according to an embodiment of the present invention;
FIG. 4 is a schematic structural view of an oil return spool according to an embodiment of the present invention;
fig. 5 is a schematic diagram of a pressure compensating valve cartridge according to an embodiment of the present invention.
Description of the reference numerals
1 valve body and 2 oil inlet valve cores
201 first oil intake throttling groove 202 second oil intake throttling groove
203 first load signal aperture 204 second load signal aperture
205 first load signal oil gallery 206 second load signal oil gallery
3 first oil return throttling groove of oil return valve core 301
302 second return oil throttle groove 4 pressure compensating valve core
401 signal oil channel 402 signal hole
403 pressure compensating throttle groove 11 first working oil passage
12 second working oil gallery 101 inlet oil gallery
102 oil inlet channel 103 first LS signal cavity
104 second LS signal cavity 105 first LS signal transmission oil channel
106 second LS signal transmission oil channel 107 first oil return oil channel
108 second return oil passage 109 first LS spill oil passage
110 second LS spill oil passage 111 first pilot control oil passage
112 second pilot control oil passage 113 shuttle valve oil passage
Oil return proportional control valve 31 of 21 oil inlet proportional control valve
5 shuttle valve 6 sealing end cover
71 first port LS overflow valve 72 first port secondary overflow valve
73 second port secondary relief valve 74 second port LS relief valve
A first oil port and B second oil port
K1 first control gallery K2 second control gallery
X1 first oil return control oil passage X2 first oil inlet control oil passage
X3 second oil return control gallery X4 second oil inlet control gallery
Y1 first overflow outlet Y2 second overflow outlet
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present invention, are given by way of illustration and explanation only, not limitation.
Furthermore, the terms "first", "second" are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated, and therefore the features defined "first", "second" may explicitly or implicitly include one or more of the features described.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "disposed," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; either directly or indirectly through intervening media, either internally or in any combination thereof. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
It should be noted that the load-sensitive multi-way valve with independently controlled load ports of the present invention belongs to the hydraulic field, and for those skilled in the art, the substantial technical idea thereof lies in the hydraulic connection relationship. The related hydraulic components, such as the directional control valve, the pressure compensating valve, the shuttle valve, the spill valve, the hydraulic pump, etc., are well known to those skilled in the art and are common components in existing hydraulic systems, and therefore, they will be described only briefly below. After knowing the technical concept of the present invention, those skilled in the art can also simply replace the oil path or the valve, etc. to implement the function of the load-sensitive multi-way valve with independently controlled load ports of the present invention, which also belongs to the protection scope of the present invention.
The operation of the walking machine needs a plurality of executing mechanisms to complete the compound movement together, so a plurality of hydraulic reversing valves are needed for controlling. The multi-way valve is a combination of reversing valves capable of controlling a plurality of hydraulic actuating mechanisms, takes more than two reversing valves as main bodies, integrates the reversing valves, the one-way valve, the safety valve, the oil supplementing valve and the flow dividing valve into a whole, is a multifunctional integrated valve, and can realize the centralized control of a plurality of actuating mechanisms. The multiway valve can be divided into a split type multiway valve and an integral multiway valve according to the structural form of a valve body, wherein the split type multiway valve generally comprises a head connection, a working connection and a tail connection. In the load-sensitive multi-way valve with independently controlled load ports, the work units are mainly designed, and the functions of the work units are basically the same, so that the following description mainly takes one work unit as an example. Of course, in the specific embodiment, the structures of the work units may be the same or different, and the specific number of the work units may be set as required, all of which belong to the protection scope of the present invention.
Referring to fig. 1 to 5, the load-sensitive multi-way valve with independently controlled load ports according to the basic technical scheme of the present invention includes a valve body 1 having a first oil port a and a second oil port B, an oil inlet valve core 2, an oil return valve core 3, and a pressure compensation valve core 4, wherein the valve body 1 is provided therein with an oil inlet valve cavity for mounting the oil inlet valve core 2, an oil return valve cavity for mounting the oil return valve core 3, and a pressure compensation valve cavity for mounting the pressure compensation valve core 4, the first oil port a is connected to the oil inlet valve cavity through a first working oil duct 11, the second oil port B is connected to the oil inlet valve cavity through a second working oil duct 12, the pressure compensation valve cavity is connected to an inlet oil duct 101, the pressure compensation valve cavity is connected to the oil inlet valve cavity through an oil duct 102, at least one end of the oil inlet valve core 2 is provided with an oil inlet proportional control valve 21 so as to enable the oil inlet oil duct 102 to be selectively communicated with the first oil port a or the second oil port B of the valve body 1, one end of the pressure compensation valve cavity is connected with the oil inlet duct 102, the other end of the pressure compensation valve cavity is connected with the oil inlet valve cavity through the LS signal transmission oil duct so as to control the pressure difference between the inlet and the outlet of the oil inlet valve core 2 to be constant, the oil return valve cavity is connected with an oil return duct, and at least one end of the oil return valve core 3 is provided with an oil return proportion control valve 31 so as to enable the oil return duct to be selectively communicated with the first oil port A or the second oil port B of the valve body 1.
The hydraulic control system is applied to a specific hydraulic system, the oil inlet proportional control valve 21 is adopted to control the oil inlet valve core 2, the oil inlet oil duct 102 can be communicated with the first oil port A or the second oil port B of the valve body 1, meanwhile, the oil return proportional control valve 31 is adopted to control the oil return valve core 3, so that the oil return oil duct can be communicated with the second oil port B or the first oil port A of the valve body 1, the oil inlet valve core 2 and the oil return valve core 3 are respectively and independently arranged, and the motion logics of the oil inlet valve core 2 and the oil return valve core 3 can be controlled by controlling the action sequence and the pressure of the oil inlet proportional control valve 21 and the oil return proportional control valve 31 to obtain various combinations so as to meet different working condition requirements, and the hydraulic control system has a load port independent control function. And, still arrange pressure compensation case 4 in valve body 1, pressure compensation case 4 can be used for compensating system pressure, and under concrete operating mode, make the pressure differential around the choke of oil feed case 2 invariable. In addition, the LS signal transmission oil passage is connected with the oil inlet valve cavity, so that the load pressure can be fed back to the variable displacement pump, and the load sensing function is achieved. Therefore, the load-sensitive multi-way valve with the independently controlled load port integrates the traditional load-sensitive technology and the load port independent control technology; compared with the prior art that a sensor is arranged on a main valve body of the load port independent control double-valve-core multi-way valve to collect pressure signals, temperature change signals and valve core displacement signals, the load port independent control load sensitive multi-way valve has the advantages of simple design, compact structure, convenient control, stable and reliable performance, energy conservation and high efficiency, relatively low requirements on part matching precision and machining precision, stronger pollution resistance, better maintainability, low manufacturing cost and easy realization of batch production.
For convenience of description, the terms "left and right" are defined below in accordance with the orientation of the structure in fig. 1 to 5, for example, the first oil return control oil passage X1 is located on the left side of the end cover 6, and the second oil return control oil passage X3 is located on the right side of the end cover 6, oppositely.
In the specific embodiment, two ends of the valve body 1 are respectively provided with a sealing end cover 6, in the oil inlet valve cavity, the left end and the right end of the oil inlet valve core 2 are respectively provided with a return spring, a gasket is arranged between the return spring and the valve body 1, and a sealing ring is arranged between the sealing end cover 6 and the valve body 1, so that the sealing end cover 6 and the oil inlet valve cavity are enclosed into a spring control cavity of the oil inlet valve core 2; similarly, in the oil return valve cavity, return springs are respectively installed at the left end and the right end of the oil return valve core 3, a gasket is installed between each return spring and the valve body 1, and a sealing ring is installed between the sealing end cover 6 and the valve body 1, so that the sealing end cover 6 and the oil return valve cavity enclose a spring control cavity of the oil return valve core 3.
A first oil return control oil passage X1 and a first oil inlet control oil passage X2 are arranged in the left sealing end cover 6, the left oil return proportional control valve 31 is connected with a left spring control cavity of the X1 oil return valve core 3 through the first oil return control oil passage, and the left oil inlet proportional control valve 21 is connected with a left spring control cavity of the oil inlet valve core 2 through the first oil inlet control oil passage X2; correspondingly, a first pilot oil passage 111 is provided in the valve body 1, the first pilot oil passage 111 is communicated with the first oil return control oil passage X1 and the first oil inlet control oil passage X2 through a first control oil passage K1, and pilot oil is supplied from the first pilot oil passage 111; similarly, a second oil return control oil passage X3 and a second oil inlet control oil passage X4 are arranged in the sealing end cover 6 on the right side, the oil return proportional control valve 31 on the right side is connected with the right spring control cavity of the oil return valve core 3 through the second oil return control oil passage X3, and the oil inlet proportional control valve 21 on the right side is connected with the right spring control cavity of the oil inlet valve core 2 through the second oil inlet control oil passage X4; accordingly, a second pilot oil passage 112 is provided in the valve body 1, the second pilot oil passage 112 communicates with the second return oil control oil passage X3 and the second oil-taking control oil passage X4 through the second control oil passage K2, respectively, and pilot oil is supplied from the second pilot oil passage 112. Wherein the first pilot oil passage 111 and the second pilot oil passage 112 may be connected by an internal oil passage.
Preferably, the control cavities at two ends of the oil inlet valve core 2 are respectively provided with an oil inlet proportional control valve 21, and the control cavities at two ends of the oil return valve core 3 are respectively provided with an oil return proportional control valve 31. In a preferred case, the oil-feeding proportional control valve 21 and the oil-returning proportional control valve 31 may be a reversing proportional pressure reducing valve, preferably a reversing proportional pressure reducing solenoid valve.
Referring to fig. 2, various channels for flowing hydraulic oil are arranged in the valve body 1, wherein the first working oil duct 11 and the second working oil duct 12 are arranged left and right and are connected with an oil inlet valve cavity, the oil inlet valve cavity is connected with a pressure compensation valve cavity through an oil inlet oil duct 102, the pressure compensation valve cavity is communicated with an inlet oil duct 101, the hydraulic oil flows into the valve body 1 from the inlet oil duct 101, the oil inlet valve cavity is used for installing an oil inlet valve core, the pressure compensation valve cavity is used for installing a pressure compensation valve core 4 to form a pressure compensation valve for controlling the pressure difference between an inlet and an outlet of the oil inlet valve core 2 to be constant, and the pressure compensation valve can be provided with sensors for detecting pressure, flow and the like. Specifically, a first LS signal cavity 103 and a second LS signal cavity 104 are further arranged in the valve body 1, the first LS signal cavity 103 and the second LS signal cavity 104 are arranged in the left-right direction and are arranged between the oil inlet valve cavity and the LS signal transmission oil channel, the LS signal transmission oil channel is composed of a first LS signal transmission oil channel 105 and a second LS signal transmission oil channel 106, the first LS signal cavity 103 is connected with the first LS signal transmission oil channel 105, the first LS signal transmission oil channel 105 is connected with the second LS signal cavity 104, the second LS signal cavity 104 is connected with the second LS signal transmission oil channel 106, the second LS signal transmission oil channel 106 is connected with the shuttle valve 5, the first LS signal cavity 103 is used for feeding back a load pressure signal of the first oil port a, and the second LS signal cavity 104 is used for feeding back a load pressure signal of the second oil port B.
In a specific embodiment, the oil inlet valve core 2 is provided with a first oil inlet throttling groove 201, a first load signal hole 203, a first load signal oil passage 205, a second oil inlet throttling groove 202, a second load signal hole 204 and a second load signal oil passage 206, the first oil inlet throttling groove 201 and the second oil inlet throttling groove 202 are arranged left and right, the first load signal hole 203 and the second load signal hole 204 are arranged left and right, and the first load signal oil passage 205 and the second load signal oil passage 206 are arranged left and right. When the oil inlet proportional control valve 21 on the control right inputs pilot oil into the spring control cavity at the right end of the oil inlet valve core 2, the oil inlet valve core 2 moves leftwards, hydraulic oil input from the inlet oil duct 101 flows to the oil inlet oil duct 102, most of the hydraulic oil in the oil inlet oil duct 102 flows into the first working oil duct 11 through the first oil inlet throttling groove 201, the hydraulic oil acts on the actuator through the first oil port a, and a part of the hydraulic oil flows into the first LS signal cavity 103 through the first load signal hole 203 and the first load signal oil duct 205 in sequence and then flows into the first LS signal transmission oil duct 105 and the second LS signal transmission oil duct 106, so that the load pressure of the first oil port a is fed back to the variable displacement pump. Similarly, when the left oil inlet proportional control valve 21 is controlled to input pilot oil into the spring control cavity at the left end of the oil inlet valve core 2, the oil inlet valve core 2 moves rightwards, the hydraulic oil input by the inlet oil duct 101 flows to the oil inlet oil duct 102, most of the hydraulic oil in the oil inlet oil duct 102 flows into the second working oil duct 12 through the second oil inlet throttling groove 202, the hydraulic oil acts on the actuating mechanism through the second oil port B, one part of the hydraulic oil flows into the second LS signal cavity 104 through the second load signal hole 204 and the second load signal oil duct 206 in sequence, and then flows to the second LS signal transmission oil duct 106, the load pressure of the first oil port a is fed back to the variable displacement pump, and the independent control of the oil inlet valve core 2 and the load port is realized.
In addition, in the specific embodiment, a first LS spill oil passage 109 and a second LS spill oil passage 110 are further provided in the valve body 1, the first LS spill oil passage 109 and the second LS spill oil passage 110 are both connected to the oil inlet valve chamber, the first LS spill oil passage 109 is connected to the first spill port Y1, the first spill port Y1 is connected to the first oil port LS spill valve 71, the second LS spill oil passage 110 is connected to the second spill port Y2, and the second spill port Y2 is connected to the second oil port LS spill valve 74. When the oil inlet proportional control valve 21 on the right side is controlled to input pilot oil into the spring control cavity at the right end of the oil inlet valve core 2, the oil inlet valve core 2 moves leftwards, hydraulic oil which flows into the first LS signal cavity 103 through the first load signal hole 203 and the first load signal oil channel 205 in sequence is divided into two parts, one part flows to the first LS signal transmission oil channel 105 and the second LS signal transmission oil channel 106, the load pressure of the first oil port a is fed back to the variable displacement pump, and the other part flows to the first oil port LS overflow valve 71 through the first LS overflow oil channel 109. Similarly, when pilot oil is input to the spring control cavity at the left end of the oil inlet valve core 2 by the oil inlet proportional control valve 21 controlling the left side, the oil inlet valve core 2 moves rightwards, hydraulic oil flowing into the second LS signal cavity 104 through the second load signal hole 204 and the second load signal oil passage 206 in sequence is divided into two parts, one part flows to the second LS signal transmission oil passage 106, the load pressure of the first oil port a is fed back to the variable displacement pump, and the other part flows to the second oil port LS overflow valve 74 through the second LS overflow oil passage 110.
Further, a shuttle valve 5 is integrated in the valve body 1, a shuttle valve oil passage 113 is arranged in the shuttle valve 5, the shuttle valve oil passage 113 is connected with a variable pump and/or a three-way pressure compensation valve, in a specific hydraulic system, the three-way pressure compensation valve is positioned on an oil passage between an oil inlet passage and an oil return passage, and a spring control cavity of the three-way pressure compensation valve is connected with the second LS signal transmission oil passage 106. When the system is in the middle position, namely the oil inlet valve core 2 in the working connection is in the middle position, at the moment, if the three-way pressure compensation valve is not arranged, the oil inlet oil path still continuously provides hydraulic oil for the oil inlet valve core 2, and the system pressure is increased; however, due to the three-way pressure compensation valve, the spring control cavity of the three-way pressure compensation valve senses the oil pressure transmitted by the second LS signal transmission oil passage 106, the opening of the valve core throttle opening of the three-way pressure compensation valve is adjusted, and the hydraulic oil in the oil inlet oil passage is unloaded, so that the constant differential pressure is maintained when the system is in the middle position.
In a specific embodiment, referring to fig. 5, the pressure compensation valve core 4 is provided with a signal oil passage 401, a signal hole 402 and a pressure compensation throttling groove 403, the pressure compensation throttling groove 403 communicates the inlet oil passage 101 and the oil inlet oil passage 102, the signal oil passage 401 communicates with the signal hole 402, the signal oil passage 401 communicates with the left end of the pressure compensation valve cavity, the second LS signal transmission oil passage 106 communicates with the right end of the pressure compensation valve cavity, and the signal hole 402 communicates with the oil inlet oil passage 102. When the hydraulic oil enters the second LS signal transmission oil duct 106 and acts on the shuttle valve 5, the hydraulic oil also enters the right end of the pressure compensation valve cavity, namely the right spring cavity, the hydraulic oil pressure in the oil inlet oil duct 102 acts on the left end of the pressure compensation valve core 4 through the signal hole 402 and the signal oil duct 401, the pressure difference between the inlet and the outlet of the oil inlet valve core 2 is ensured to be constant, the hydraulic oil entering the load port is only related to the opening sizes of the first oil inlet throttling groove 201 and the second oil inlet throttling groove 202 and is unrelated to the load, and therefore the valve has the load sensing function.
In a specific embodiment, referring to fig. 4, the oil return valve core 3 is provided with a first oil return throttling groove 301 and a second oil return throttling groove 302, and correspondingly, an oil return duct is provided in the valve body 1, the oil return duct includes a first oil return duct 107 and a second oil return duct 108, the first oil return duct 107 and the second oil return duct 108 are arranged left and right and are both connected to the oil return valve cavity, the first oil return duct 107 is connected to the first oil port secondary overflow valve 72, and the second oil return duct 108 is connected to the second oil port secondary overflow valve 73. Similarly, when the right oil return proportional control valve 31 drives the oil return valve core 3 to move leftwards, the first oil return throttling groove 301 connects the first oil return oil passage 107 with the first working oil passage 11, so as to perform oil return on the hydraulic oil at the first oil port a, and when the left oil return proportional control valve 31 drives the oil return valve core 3 to move rightwards, the second oil return throttling groove 302 connects the second oil return oil passage 108 with the second working oil passage 12, so as to perform oil return on the hydraulic oil at the second oil port B, thereby realizing independent control of the oil return valve core 3 and the oil return port.
In order to better understand the technical solution of the present invention, preferred embodiments are described below with reference to relatively full technical features.
Referring to fig. 1 to 5, the invention provides a load-sensitive multi-way valve with independently controlled load ports, which comprises a valve body 1 provided with a first oil port a and a second oil port B, an oil inlet valve core 2, an oil return valve core 3 and a pressure compensation valve core 4, wherein an oil inlet valve cavity for mounting the oil inlet valve core 2, an oil return valve cavity for mounting the oil return valve core 3 and a pressure compensation valve cavity for mounting the pressure compensation valve core 4 are arranged in the valve body 1, the first oil port a is connected with the oil inlet valve cavity through a first working oil duct 11, the second oil port B is connected with the oil inlet valve cavity through a second working oil duct 12, the pressure compensation valve cavity is connected with an inlet oil duct 101, and the pressure compensation valve cavity is connected with the oil inlet valve cavity through an oil inlet oil duct 102. Sealing end covers 6 are respectively installed on two sides of the valve body 1, the sealing end covers 6 and the oil inlet valve cavity are defined into a spring control cavity of the oil inlet valve core 2, the spring control cavities at two ends of the oil inlet valve core 2 are respectively provided with an oil inlet proportional control valve 21, the sealing end covers 6 and the oil return valve cavity are defined into a spring control cavity of the oil return valve core 3, and the spring control cavities at two ends of the oil return valve core 3 are respectively provided with an oil return proportional control valve 31. The valve body 1 is also internally provided with a first LS signal cavity 103 and a second LS signal cavity 104, the first LS signal cavity 103 and the second LS signal cavity 104 are arranged in a left-right manner, the first LS signal cavity 103 is connected with a first LS signal transmission oil duct 105, the first LS signal transmission oil duct 105 is connected with a second LS signal cavity 104, the second LS signal cavity 104 is connected with a second LS signal transmission oil duct 106, the second LS signal transmission oil duct 106 is connected with the shuttle valve 5, the first LS signal cavity 103 is used for feeding back a load pressure signal of a first oil port A, the second LS signal cavity 104 is used for feeding back a load pressure signal of a second oil port B, the oil inlet valve core 2 is provided with a first oil inlet groove 201, a first load signal hole 203, a first load signal oil duct 205, a second oil inlet throttling groove 202, a second load signal hole 204 and a second load signal oil duct 206, the first oil inlet groove is used for communicating the oil inlet duct 102 and the first working oil duct 11, the second oil-inlet throttling groove 202 is used for communicating the oil-inlet oil passage 102 with the second working oil passage 12, the first load signal hole 203 and the first load signal oil passage 205 are used for communicating the oil-inlet oil passage 102 with the first LS signal cavity 103, and the second load signal hole 204 and the second load signal oil passage 206 are used for communicating the oil-inlet oil passage 102 with the second LS signal cavity 104. The valve body 1 is also internally provided with a first LS overflow oil channel 109 and a second LS overflow oil channel 110, the first LS overflow oil channel 109 and the second LS overflow oil channel 110 are both connected with the oil inlet valve cavity, the first LS overflow oil channel 109 is connected with a first overflow port Y1, the first overflow port Y1 is connected with a first oil port LS overflow valve 71, the second LS overflow oil channel 110 is connected with a second overflow port Y2, and the second overflow port Y2 is connected with a second oil port LS overflow valve 74. A first oil return oil passage 107 and a second oil return oil passage 108 are arranged in the valve body 1, a first oil return throttling groove 301 and a second oil return throttling groove 302 are arranged on the oil return valve core 3, the first oil return throttling groove 301 is used for communicating the first oil return passage 107 with the first working oil passage 11, and the second oil return throttling groove 302 is used for communicating the second oil return oil passage 108 with the second working oil passage 12. The pressure compensation valve core 4 is provided with a signal oil passage 401, a signal hole 402 and a pressure compensation throttling groove 403, the pressure compensation throttling groove 403 is used for communicating the inlet oil passage 101 with the oil inlet oil passage 102, and the signal oil passage 401 and the signal hole 402 are used for enabling hydraulic oil pressure in the oil inlet oil passage 102 to act on the left end of the pressure compensation valve core 4 through the signal hole 402 and the signal oil passage 401.
When the right oil inlet proportional control valve 21 is powered on, pilot control oil of the second pilot control oil passage 112 enters a right spring control cavity of the oil inlet valve core 2 through the second control oil passage K2 and the second oil inlet control oil passage X4 to push the oil inlet valve core 2 to move to the left; hydraulic oil enters the oil inlet duct 102 through the inlet oil duct 101, enters the first oil port a through the first oil inlet throttling groove 201 of the oil inlet valve core 2 and the first working oil duct 11 on the valve body 1, and drives a load; the load pressure signal enters the first port LS spill valve 71 via the first load signal orifice 203, the first load signal oil passage 205, the first LS signal chamber 103, the first LS spill oil passage 109, meanwhile, a load pressure signal enters the second LS signal transmission oil channel 106 through the first LS signal transmission oil channel 105 and acts on the shuttle valve 5, then acts on the three-way pressure compensation valve core and the variable pump through the shuttle valve oil channel 113, meanwhile, the hydraulic oil enters a right spring cavity of the pressure compensation valve 4 and acts on the right side of the pressure compensation valve 4, the pressure of the hydraulic oil in the oil inlet oil duct 102 acts on the left end of the pressure compensation valve core 4 through the signal hole 402 and the signal oil duct 401, the pressure difference between an inlet and an outlet of the oil inlet valve core 2 is ensured to be constant, the hydraulic oil entering the first oil port A is only related to the opening size of the first oil inlet throttling groove 201, the valve has a load sensitive function regardless of the load, and simultaneously realizes independent control of the oil inlet valve core 2 and the load port;
similarly, when the left oil inlet proportional control valve 21 is powered on, the pilot control oil in the first pilot control oil passage 111 enters the left spring control cavity of the oil inlet valve core 2 through the first control oil passage K1 and the first oil inlet control oil passage X2 to push the oil inlet valve core 2 to move to the right; hydraulic oil enters the oil inlet duct 102 through the inlet oil duct 101, enters the first oil port B through the first oil inlet throttling groove 202 of the oil inlet valve core 2 and the first working oil duct 11 on the valve body, and drives a load; a load pressure signal enters the second oil port LS overflow valve 74 through the second load signal hole 204, the second load signal oil channel 206, the second LS signal cavity 104 and the second LS overflow oil channel 110, and simultaneously enters the second LS signal transmission oil channel 106, acts on the shuttle valve 5, then acts on the three-way pressure compensation valve core and the variable pump through the shuttle valve oil channel 113, and simultaneously enters the spring cavity at the right side of the pressure compensation valve 4, acts on the right side of the pressure compensation valve 4, the hydraulic oil pressure of the oil inlet oil channel 102 acts on the left end of the pressure compensation valve core 4 through the signal hole 402 and the signal oil channel 401, so that the pressure difference between the inlet and the outlet of the oil inlet valve core 2 is ensured to be constant, the hydraulic oil entering the second oil port B is only related to the size of the opening of the second oil inlet throttling groove 202 and is unrelated to the load, the valve has a load sensing function, and simultaneously realizes the independent control of the oil inlet valve core 2 and the load port;
when the oil return proportional control valve 31 on the left side is powered on, pilot control oil enters a spring cavity at the left end of the oil return valve core 3 through the first oil return control oil channel X1 to push the oil return valve core 3 to move towards the right side, and hydraulic oil of the second oil port B returns to the first oil return channel 107 in the valve body 1 through the first oil return throttling groove 301; when the right oil return proportional control valve 31 is powered on, pilot control oil enters a spring cavity at the right end of the oil return valve core 3 through the second oil return control oil passage X3 to push the oil return valve core 3 to move to the left, and hydraulic oil at the first oil port a returns to the second oil return oil passage 108 in the valve body 1 through the second oil return throttling groove 302, so that the independent control of the oil return valve core 3 and the oil return port is realized;
when the right oil inlet proportional control valve 21 is electrified to work, control oil enters a right spring control cavity of the oil inlet valve core 2 to push the oil inlet valve core 2 to move to the left side; hydraulic oil enters the oil inlet oil duct 102 through the oil inlet oil duct 101, enters the first oil port A through the first oil inlet throttling groove 201 of the oil inlet valve core 2 and the first working oil duct 11 on the valve body 1, and can drive the single-action hydraulic oil cylinder, when the oil inlet proportional control valve 2 on the right side is out of power and does not work, the oil inlet valve core 2 returns to the middle position, the load is in a locking state, when the oil return proportional control valve 31 on the right side is powered and works, control oil enters the spring cavity at the right end of the oil return valve core 3, the oil return valve core 3 is pushed to move towards the left side, and the hydraulic oil of the first oil port A returns to the second oil return oil duct 108 of the valve body 1, so that the single-action independent control of the first oil port A is realized;
similarly, when the left oil inlet proportional control valve 21 is powered on to work, control oil enters a left spring control cavity of the oil inlet valve core 2 to push the oil inlet valve core 2 to move to the right; hydraulic oil enters the oil inlet oil duct 102 through the oil inlet oil duct 101, enters the first oil port B through the first oil inlet throttling groove 202 of the oil inlet valve core 2 and the first working oil duct 11 on the valve body, and can drive the single-action hydraulic oil cylinder, when the left oil inlet proportional control valve 21 is not powered and does not work, the oil inlet valve core 2 returns to the middle position, the load is in a locking state, after the left oil return proportional control valve 31 is powered and works, control oil enters the spring cavity at the left end of the oil return valve core 3, the oil return valve core 3 is pushed to move towards the right side, and hydraulic oil at the second oil port B returns to the first oil return duct 107 of the valve body 1, so that the single-action independent control of the second oil port B is realized.
The invention adopts the upper layer, the middle layer and the lower layer arranged in the same valve body to be respectively provided with the oil return valve core 3, the oil inlet valve core 2 and the pressure compensation valve core 4, the electric control pilot reversing valve is directly inserted into the sealing end cover 6, the traditional load sensing technology, the load port independent control technology and the electric proportional control technology are integrated, the oil inlet valve core 2 and the oil return valve core 3 are independently arranged, the oil inlet and the oil return of a working mechanism can be independently regulated, and the motion logic of the oil inlet valve core 2 and the oil return valve core 3 can be controlled by controlling the action sequence and the pressure of the pilot proportional reversing valve to obtain various combinations; compared with the existing technology of independently controlling the double-valve-core multi-way valve through the load port, the double-valve-core multi-way valve is simple in design, compact in structure, convenient to control, stable and reliable in performance, more energy-saving and efficient, relatively low in requirements on the matching precision and the machining precision of parts, stronger in pollution resistance, better in maintainability, low in manufacturing cost and easier to realize batch production.
The hydraulic system of the invention comprises the load-sensitive multi-way valve with the independently controlled load port according to any one of the above technical schemes, so that the hydraulic system at least has all the advantages brought by the technical scheme of the embodiment of the load-sensitive multi-way valve with the independently controlled load port.
The load sensitive multi-way valve with the independently controlled load port can be applied to various engineering machines needing the multi-way valve, such as cranes, shoveling machines and the like.
The preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, however, the present invention is not limited to the specific details of the above embodiments, and various simple modifications can be made to the technical solution of the present invention within the technical idea of the present invention, and these simple modifications are within the protective scope of the present invention.
It should be noted that the various features described in the above embodiments may be combined in any suitable manner without departing from the scope of the invention. The invention is not described in detail in order to avoid unnecessary repetition.
In addition, any combination of the various embodiments of the present invention is also possible, and the same should be considered as the disclosure of the present invention as long as it does not depart from the spirit of the present invention.
Claims (12)
1. The load sensitive multi-way valve with the independently controlled load ports is characterized by comprising a valve body (1) provided with a first oil port (A) and a second oil port (B), an oil inlet valve core (2), an oil return valve core (3) and a pressure compensation valve core (4), wherein an oil inlet valve cavity for installing the oil inlet valve core (2), an oil return valve cavity for installing the oil return valve core (3) and a pressure compensation valve cavity for installing the pressure compensation valve core (4) are arranged in the valve body (1), the first oil port (A) is connected with the oil inlet valve cavity through a first working oil duct (11), the second oil port (B) is connected with the oil inlet valve cavity through a second working oil duct (12), the pressure compensation valve cavity is connected with an inlet oil duct (101), and the pressure compensation valve cavity is connected with the oil inlet through an oil duct (102), an oil inlet proportional control valve (21) is installed to at least one end of the oil inlet valve core (2), so that the oil inlet oil duct (102) selectively communicates with a first oil port (A) or a second oil port (B) of the valve body (1), one end of the pressure compensation valve cavity is connected with the oil inlet oil duct (102), and the other end of the pressure compensation valve cavity is connected with the oil inlet valve cavity through an LS signal transmission oil duct to control the inlet and outlet pressure difference of the oil inlet valve core (2) to be constant, the oil return valve cavity is connected with an oil return oil duct, the oil return proportional control valve (31) is installed to at least one end of the oil return valve core (3), so that the oil return oil duct selectively communicates with the first oil port (A) or the second oil port (B) of the valve body (1).
2. The load-port-independently-controlled load-sensitive multi-way valve according to claim 1, wherein a first oil-inlet throttling groove (201) for communicating the oil-inlet duct (102) with the first oil port (a) and a second oil-inlet throttling groove (202) for communicating the oil-inlet duct (102) with the second oil port (B) are formed in the oil-inlet valve core (2).
3. The load-port independently controlled load-sensitive multi-way valve according to claim 1, wherein a first LS signal chamber (103) for feeding back a load pressure signal of the first oil port (a) and a second LS signal chamber (104) for feeding back a load pressure signal of the second oil port (B) are provided between the oil inlet valve chamber and the LS signal transmission oil passage.
4. Load-sensitive multi-way valve with independent control of the load ports according to claim 3, characterized in that the LS signal transfer oil gallery is connected with a shuttle valve (5) for connection with a variable pump.
5. The load-sensitive multiple-way valve with independently controlled load ports according to claim 4, characterized in that the shuttle valve (5) is further connected with a three-way pressure compensation valve.
6. The load port independently controlled load sensitive multiplex valve according to claim 4, wherein said LS signal transfer oil passages comprise a first LS signal transfer oil passage (105) and a second LS signal transfer oil passage (106), said first LS signal chamber (103) and said second LS signal chamber (104) are both connected to said first LS signal transfer oil passage (105), said second LS signal transfer oil passage (106) is connected to said second LS signal chamber (104) and said shuttle valve (5), respectively.
7. The load-sensing multi-way valve with the independently controlled load ports as claimed in claim 1, wherein the pressure compensation valve core (4) is provided with a signal oil passage (401) and a signal hole (402) which are used for communicating a non-spring cavity at the end part of the pressure compensation valve core (4) with the oil inlet oil passage (102).
8. The load-port-independently-controlled load-sensitive multi-way valve according to any one of claims 1 to 7, wherein the oil return gallery comprises a first oil return gallery (107) and a second oil return gallery (108), and the oil return valve core (3) is provided with a first oil return throttling groove (301) for communicating the first oil return gallery (107) with the first oil port (A) and a second oil return throttling groove (302) for communicating the second oil return gallery (108) with the second oil port (B).
9. The load-port-independently-controlled load-sensitive multi-way valve according to any one of claims 1 to 7, characterized in that a first LS spill oil passage (109) connected to a first spill port (Y1) and a second LS spill oil passage (110) connected to a second spill port (Y2) are further provided in the valve body (1), and a first spill passage for communicating the first LS spill oil passage (109) with the oil inlet passage (102) and a second spill passage for communicating the second LS spill oil passage (110) with the oil inlet passage (102) are provided on the oil inlet spool (2).
10. The load-port-independently-controlled load-sensitive multi-way valve according to any one of claims 1 to 7, wherein two ends of the valve body (1) are respectively provided with a sealing end cover (6), the sealing end cover (6) and the oil inlet valve cavity define a spring control cavity of the oil inlet valve core (2), and the sealing end cover (6) and the oil return valve cavity define a spring control cavity of the oil return valve core (3).
11. The load-port-independently-controlled load-sensitive multi-way valve according to claim 10, wherein the oil inlet proportional control valve (21) and the oil return proportional control valve (31) are both reversing proportional pressure reducing valves, the spring control chambers at both ends of the oil inlet valve core (2) are respectively connected with the reversing proportional pressure reducing valves (21), and the spring control chambers at both ends of the oil return valve core (3) are respectively connected with the reversing proportional pressure reducing valves (31).
12. A hydraulic system, characterized in that a load-sensitive multi-way valve with independently controlled load ports according to any one of claims 1 to 11 is provided.
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| CN202111142768.9A CN113931892B (en) | 2021-09-28 | 2021-09-28 | Load-sensitive multi-way valve with independently controlled load port and hydraulic system |
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| CN113931892B (en) | 2022-06-14 |
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Effective date of registration: 20220712 Address after: 415001 No. 321, Deshan Avenue, Deshan economic development zone, Changde City, Hunan Province Patentee after: CHANGDE ZHONGLIAN ZHONGKE HYDRAULIC Co.,Ltd. Address before: 410013 No. 361 South silver basin, Changsha, Hunan, Yuelu District Patentee before: ZOOMLION HEAVY INDUSTRY SCIENCE AND TECHNOLOGY Co.,Ltd. |
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