CN109630504B - Oil inlet and outlet independent control system with pressure compensation function - Google Patents
Oil inlet and outlet independent control system with pressure compensation function Download PDFInfo
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- CN109630504B CN109630504B CN201811601434.1A CN201811601434A CN109630504B CN 109630504 B CN109630504 B CN 109630504B CN 201811601434 A CN201811601434 A CN 201811601434A CN 109630504 B CN109630504 B CN 109630504B
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
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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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
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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
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
- F15B2013/0448—Actuation by solenoid and permanent magnet
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- Fluid Mechanics (AREA)
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides an oil inlet and outlet independent control system with pressure compensation, which comprises: the hydraulic control system comprises a hydraulic power source (1), an overflow valve (2), an inlet and outlet independent control valve group (3) and a hydraulic actuator (5); the method is characterized in that: a load selection valve (4), a novel electronic pressure compensation valve (6) or an electro-hydraulic pressure compensation valve (7) are further added, the controllability of a multi-actuator oil inlet and outlet independent system is improved, the control complexity of the system for balancing the load difference of multiple actuators is simplified, the system cost can be reduced, and real-time continuous regulation and control of compensation pressure difference and real-time position feedback monitoring of a compensation valve core are realized. The oil inlet and outlet independent control system with the pressure compensation function has the advantages of being simple in control, high in intelligent degree, strong in working condition applicability, low in energy consumption, fast in response and the like.
Description
Technical Field
The invention belongs to a hydraulic system of engineering machinery, and particularly relates to an independent inlet and outlet control system with a pressure compensation valve.
Background
The traditional multi-way valve is adopted in the existing engineering machinery to control the running speed of an actuator, four sides of a hydraulic valve are linked, an inlet and an outlet are throttled simultaneously, only the pressure or flow of a single cavity of the actuator can be controlled at the same time, the controllability is poor, the problems of large throttling loss, serious heating and the like exist, and the problem is more serious especially under the condition of exceeding the load.
Aiming at the problems of four-side linkage throttling control of the traditional multi-way valve, the traditional solution is to adopt a method of independent inlet and outlet control, and adopt two three-position three-way valves or four two-position two-way valves to respectively control the pressure and the flow of two cavities of a hydraulic actuator, thereby increasing the control freedom and reducing the pressure loss and the energy consumption of a system. However, for an excavator, which is a kind of engineering machinery with multiple actuators driven by a single power source in parallel, when the multiple actuators perform combined actions, in order to maintain good controllability and reduce the influence of load pressure of each actuator, the flow of each actuator is distributed as required, multiple sensors are needed to be used, multiple actuator pressure/flow parameters are collected to control multiple reversing valves, the control strategy is extremely complex, and the system cost is high.
Disclosure of Invention
In order to solve the problems, the invention aims to provide an oil inlet and outlet independent control system with pressure compensation, which simplifies the independent control strategy of the composite action inlet and outlet of multiple actuators, reduces the system cost, and has high flow distribution precision and wide working condition applicability.
In order to achieve the purpose, the invention adopts the following technical scheme: an oil inlet and outlet independent control system with pressure compensation comprises: the hydraulic control system comprises a hydraulic power source (1), an overflow valve (2), an inlet and outlet independent control valve group (3) and a hydraulic actuator (5); the method is characterized in that: the system also comprises a load selection valve (4), an electronic pressure compensation valve (6) or an electro-hydraulic pressure compensation valve (7), and the specific adopted pressure compensation valve is determined by the load pressure and the flow of the system;
the electronic pressure compensation valve is a pressure compensation valve controlled by a proportional electromagnet or a pressure compensation valve controlled by a linear motor or a pressure compensation valve controlled by a rotating motor driven ball screw, and when the electronic pressure compensation valve is a pressure compensation valve controlled by a proportional electromagnet, the electronic pressure compensation valve comprises a displacement sensor (12), a proportional electromagnet (13), a compensation valve body (14), a compensation valve core (15), a spring (16), an oil inlet (A), an oil outlet (B) and an I-th control cavity (P)F) And the second control chamber (P)E) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface C of the compensating valve core, the other end acts on the compensating valve body, and the compensating valve core forms a first control cavity PFThe proportional electromagnet is connected with the compensation valve body, acts on the right end surface D of the compensation valve core, and forms a second control cavity P with the compensation valve core and the compensation valve bodyEThe displacement sensor and the proportional electromagnet are integrally installed;
when the electronic pressure compensation valve is a pressure compensation valve controlled by a linear motor, the electronic pressure compensation valve comprises a displacement sensor, a compensation valve body, a compensation valve core, a spring, the linear motor (17), an oil inlet (A), an oil outlet (B) and an I-th control cavity (P)F) And the second control chamber (P)E) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface C of the compensating valve core, the other end acts on the compensating valve body and forms a first control cavity P with the compensating valve coreFThe linear motor is connected with the compensation valve body, arranged on the right end surface D of the compensation valve core and forms a II-th control cavity P together with the compensation valve body and the compensation valve coreE；
When the electronic pressure compensation valve is controlled by a ball screw driven by a rotating motor, the electronic pressure compensation valve comprises a displacement sensor, a compensation valve body, a compensation valve core, a spring, a rotating motor (18), a ball screw (19), a connecting rod (20), an oil inlet (A), an oil outlet (B) and a first control cavity (P)F) And the second control chamber (P)E) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface C of the compensating valve core, the other end acts on the compensating valve body and forms a first control cavity P with the compensating valve coreFThe displacement sensor is arranged on the compensating valve core through the compensating valve body, directly detects the position X and the speed XV of the valve core, and the rotating motor is connected with the compensating valve body and forms a second control cavity P with the compensating valve body and the compensating valve coreEAn extension shaft of the rotating motor is connected with a screw rod of the ball screw, a nut of the ball screw is connected with the connecting rod, the rotating motor drives the ball screw to rotate, and the rotating motion of the motor is converted into linear motion through the ball screw, so that the connecting rod is driven to output different forces and displacements;
the electro-hydraulic pressure compensation valve comprises a displacement sensor, a compensation valve body, a compensation valve core, a spring, an oil inlet (A), an oil outlet (B) and a first control cavity (P)F) II control chamber (P)E) And III control chamber (P)G) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface C of the compensating valve core, and the other end of the spring acts on the left end surface C of the compensating valve coreActing on the compensating valve body and forming a control chamber I with the compensating valve coreFThe displacement sensor is arranged on the compensating valve core through the compensating valve body to directly detect the position X and the speed XV of the valve core, and the other end of the compensating valve core forms a second control cavity P with the compensating valve body respectivelyEAnd III control chamber PG；
When the electro-hydraulic pressure compensation valve is adopted, the system also comprises a pilot oil way (21) and a pilot proportional pressure reducing valve (22), wherein an output oil port of the pilot proportional pressure reducing valve and a III control cavity P of the electro-hydraulic pressure compensation valveGThe oil inlet and the oil outlet of the pilot proportional pressure reducing valve are respectively communicated with the pilot oil way and the oil tank;
the inlet and outlet independent control valve group consists of a first two-position two-way proportional reversing valve (8), a second two-position two-way proportional reversing valve (9), a third two-position two-way proportional reversing valve (10) and a fourth two-position two-way proportional reversing valve (11);
an oil inlet A of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is communicated with an oil outlet of the hydraulic power source, an oil outlet B of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is communicated with a second control cavity P of the pressure compensation valveEOil port C of second two-position two-way proportional reversing valveⅡAnd oil port C of a III two-position two-way proportional reversing valveⅢOil port C of a second I two-position two-way proportional reversing valveⅠAnd oil port C of the IV two-position two-way proportional reversing valveⅣOil ports D of a first two-position two-way proportional reversing valve and a second two-position two-way proportional reversing valve which are respectively communicated with an oil tankⅠ、DⅡThrough an oil passage L1 and a hydraulic actuator control cavity pAOil port D of communicated III, IV two-position two-way proportional reversing valveⅢ、DⅣThrough an oil passage L2 and a hydraulic actuator control cavity pAThe load selection valve oil port E, F is respectively communicated with the oil passages L1 and L2, and the load selection valve oil port G is communicated with the I-th control cavity P of the pressure compensation valveFCommunication, the actuator p being selectively actuated by controlling the operating position of the load-selecting valveAOr pBThe oil is introduced into the control cavity P of the pressure compensating valve IFControlling the same;
or the inlet and outlet independent control valve group is reversed by the third three-position three-way valveThe valve (23) and a third three-position three-way reversing valve (24); an oil inlet A of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is communicated with an oil outlet of the hydraulic power source, and an oil outlet B of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is respectively communicated with an oil inlet P of the third three-position three-way reversing valve IⅠAnd an oil inlet P of a third three-position three-way reversing valveⅡCommunicated oil outlet T of a third three-position three-way reversing valveⅠAnd oil outlet T of a third three-position three-way reversing valveⅡWorking oil port H of the third three-position three-way reversing valve respectively communicated with an oil tankⅠAnd II working oil port H of three-position three-way reversing valveⅡTwo cavities p of the hydraulic actuator are respectively communicated with the pipelines L1 and L2A、pBThe load selection valve oil port E, F is respectively communicated with the oil passages L1 and L2, and the load selection valve oil port G is communicated with the I-th control cavity P of the pressure compensation valveFAnd (4) communicating.
The electronic pressure compensation valve and the electro-hydraulic pressure compensation valve are one of a normally open type and a normally closed type.
The electronic pressure compensation valve and the electro-hydraulic pressure compensation valve can also be arranged behind the inlet and outlet independent control valve group.
The displacement sensor is integrated on the proportional electromagnet, and detects the position X and the speed XV of the valve core by detecting the proportional electromagnet, or is arranged on the compensation valve core to directly detect the position X and the speed XV of the valve core.
The proportional electromagnet is one of a unidirectional proportional electromagnet and a bidirectional proportional electromagnet.
The rotating motor is one of a direct current motor, a synchronous motor and an asynchronous motor.
The hydraulic pump of the hydraulic power source can be one of a mechanical load sensitive pump, an electronic proportional pressure pump and an electronic proportional variable displacement pump, and the power source for driving the hydraulic pump can be a three-phase asynchronous motor with constant rotating speed, an alternating current servo motor, a switched reluctance motor or an internal combustion engine.
The hydraulic actuator can be one of a single-rod hydraulic cylinder, a double-rod hydraulic cylinder and a hydraulic motor.
Furthermore, the system can also be provided with a plurality of hydraulic actuators, a plurality of oil inlet and outlet independent control valve groups, a plurality of electronic pressure compensation valves or electro-hydraulic pressure compensation valves or a combination of two pressure compensation valves, and the system only has one hydraulic power source.
Compared with the prior art, the invention has the following beneficial effects:
according to the invention, the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is additionally arranged in the traditional oil inlet and outlet independent control system, so that the controllability of the multi-actuator oil inlet and outlet independent system is improved, the control complexity of the system for balancing the load difference of multiple actuators is simplified, meanwhile, the use of a pressure sensor can be reduced, and the system cost is reduced.
The invention designs a novel electronic pressure compensation valve and an electro-hydraulic pressure compensation valve, adopts an electronic or electro-hydraulic control unit to change the control differential pressure of the compensation valve, realizes the real-time continuous regulation and control of the compensation differential pressure of the compensation valve, adopts a displacement sensor to monitor the position of a compensation valve core in real time, overcomes the problem that the compensation valve core of the traditional pressure compensation valve is uncontrollable and unmeasured, realizes the intelligent control of the pressure compensation valve, and lays a foundation for further implementing an advanced control technology.
The invention has stronger advanced technology, can be suitable for different machine types and working conditions, matches the compensation pressure difference based on the working condition requirement, reduces the compensation pressure difference, reduces the valve port flow gain and improves the control stability during fine operation; when the valve acts rapidly, the compensation pressure difference of the compensation valve is improved, the flow gain of the valve port is increased, and the rapid response and the efficient work of the actuator are realized.
Drawings
FIG. 1 is a schematic diagram of a system according to embodiment 1 of the present invention;
FIG. 2 is a schematic diagram of a first construction of the electronic pressure compensating valve of the present invention;
FIG. 3 is a schematic diagram of a second construction of the electronic pressure compensating valve of the present invention;
FIG. 4 is a schematic diagram of a third construction of the electronic pressure compensating valve of the present invention;
FIG. 5 is a schematic diagram of a system according to embodiment 2 of the present invention;
FIG. 6 is a schematic diagram of the electro-hydraulic pressure compensating valve of the present invention;
fig. 7 is a system schematic diagram of embodiment 3 of the present invention.
In the figure: the hydraulic control system comprises a hydraulic power source 1, an overflow valve 2, an oil inlet and outlet independent control valve group 3, a load selection valve 4, a hydraulic actuator 5, an electronic pressure compensation valve 6, an electro-hydraulic pressure compensation valve 7, a second two-position two-way proportional reversing valve 8, a second two-position two-way proportional reversing valve 9, a second two-position two-way proportional reversing valve 10, a second three-position two-way proportional reversing valve 11, a fourth two-position two-way proportional reversing valve 11, a displacement sensor 12, a proportional electromagnet 13, a compensating valve body 14, a compensating valve core 15, a spring 16, a linear motor 17, a rotary motor 18, a ball screw 19, a connecting rod 20, a pilot oil circuit 21, a pilot proportional pressure reducing valve 22, a three-position three-way reversing valve 23, a first three-way reversing valve 23 and a third three-position three.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings 1 to 7.
Example 1
An oil inlet and outlet independent control system with pressure compensation comprises: the hydraulic actuator comprises a hydraulic power source 1, an overflow valve 2, an inlet and outlet independent control valve group 3 and a hydraulic actuator 5; the method is characterized in that: the system also comprises a load selection valve 4, an electronic pressure compensation valve 6;
as shown in fig. 1, the inlet and outlet independent control valve group 3 is composed of a first two-position two-way proportional directional valve 8, a second two-position two-way proportional directional valve 9, a third two-position two-way proportional directional valve 10 and a fourth two-position two-way proportional directional valve 11;
an oil inlet A of the electronic pressure compensation valve 6 is communicated with an oil outlet of the hydraulic power source 1, an oil outlet B of the electronic pressure compensation valve 6 is communicated with a II-th control cavity P of the electronic pressure compensation valve 6EOil port C of second two-position two-way proportional reversing valve 9ⅡAnd oil port C of the III two-position two-way proportional reversing valve 10ⅢOil port C of the second I two-position two-way proportional reversing valve 8ⅠAnd oil port C of IV two-position two-way proportional reversing valve 11ⅣOil ports D of a first two-position two-way proportional reversing valve 8 and a second two-position two-way proportional reversing valve 9 which are respectively communicated with an oil tankⅠ、DⅡThrough an oil passage L1 and a control cavity p of the hydraulic actuator 5AThe oil ports D of the third two-position two-way proportional reversing valve 10 and the fourth two-position two-way proportional reversing valve 11 are communicatedⅢ、DⅣThrough an oil passage L2 and a control cavity p of the hydraulic actuator 5AThe oil port E, F of the load selection valve 4 is respectively communicated with the oil passages L1 and L2, the oil port G of the load selection valve 4 is communicated with the I-th control cavity P of the electronic pressure compensation valve 6FCommunication, the actuator p being selectively actuated by controlling the operating position of the load selector valve 4AOr pBThe oil is introduced into the I control cavity P of the electronic pressure compensating valve 6FControlling the same;
the electronic pressure compensation valve 6 is a pressure compensation valve controlled by a proportional electromagnet, a pressure compensation valve controlled by a linear motor or a pressure compensation valve controlled by a rotating motor driven ball screw, as shown in fig. 2, when the electronic pressure compensation valve 6 is a pressure compensation valve controlled by a proportional electromagnet 13, the electronic pressure compensation valve comprises a displacement sensor 12, a proportional electromagnet 13, a compensation valve body 14, a compensation valve core 15, a spring 16, an oil inlet A, an oil outlet B and a first control cavity PFAnd the second control chamber PE(ii) a The compensation valve core 15 is arranged in the compensation valve body 14, one end of the spring 16 acts on the left end face C of the compensation valve core 15, the other end acts on the compensation valve body 14, and the compensation valve core 15 forms a first control chamber PFThe proportional electromagnet 13 is connected with the compensation valve body 14, acts on the right end surface D of the compensation valve core 15, and forms a second control cavity P with the compensation valve core 15 and the compensation valve body 14EThe displacement sensor 12 and the proportional electromagnet 13 are integrally installed;
as shown in fig. 3, when the electronic pressure compensation valve 6 is a pressure compensation valve controlled by a linear motor 17, the electronic pressure compensation valve includes a displacement sensor 12, a compensation valve body 14, a compensation valve core 15, a spring 16, a linear motor 17, an oil inlet a, an oil outlet B, and a first control chamber PFAnd the second control chamber PE(ii) a The compensation valve core 15 is arranged in the compensation valve body 14, one end of the spring 16 acts on the left end face C of the compensation valve core 15, the other end acts on the compensation valve body 14 and forms an I-th control cavity P with the compensation valve core 15FThe displacement sensor 12 is arranged on the compensating valve core 15 through the compensating valve body 14, and directly detects the position of the valve core 15X and speed XV, the linear motor 17 is connected with the compensation valve body 14, installed on the right end surface D of the compensation valve core 15, and forms a second control cavity P with the compensation valve body 14 and the compensation valve core 15E；
As shown in fig. 4, when the electronic pressure compensating valve 6 is a pressure compensating valve controlled by a ball screw 19 driven by a rotating motor 18, the electronic pressure compensating valve comprises a displacement sensor 12, a compensating valve body 14, a compensating valve core 15, a spring 16, the rotating motor 18, the ball screw 19, a connecting rod 20, an oil inlet a, an oil outlet B, and an i-th control chamber PFAnd the second control chamber PE(ii) a The compensation valve core 14 is arranged in the compensation valve body 15, one end of the spring 16 acts on the left end face C of the compensation valve core 15, the other end acts on the compensation valve body 14 and forms a first control cavity P with the compensation valve core 15FThe displacement sensor 12 is arranged on the compensating valve core 15 through the compensating valve body 14, directly detects the position X and the speed XV of the valve core 15, the rotating electrical machine 18 is connected with the compensating valve body 14, and forms a second control cavity P with the compensating valve body 14 and the compensating valve core 15EAn extending shaft of the rotating motor 18 is connected with a screw rod of the ball screw 19, a nut of the ball screw 19 is connected with a connecting rod, the rotating motor 18 drives the ball screw 19 to rotate, and the rotating motion of the motor is converted into linear motion through the ball screw 19, so that the connecting rod 20 is driven to output different forces and displacements;
the electronic pressure compensating valve 6 is one of a normally open type and a normally closed type.
The electronic pressure compensating valve 6 can also be arranged behind the inlet and outlet independent control valve group 3.
The displacement sensor 12 is integrated on the proportional electromagnet 13, and detects the position X and the speed XV of the spool by detecting the proportional electromagnet 13, or is installed on the compensation spool 15 to directly detect the position X and the speed XV of the spool.
The proportional electromagnet 13 is one of a unidirectional proportional electromagnet and a bidirectional proportional electromagnet.
The rotating electric machine 18 is one of a direct current motor, a synchronous motor, and an asynchronous motor.
The hydraulic pump of the hydraulic power source 1 can be one of a mechanical load sensitive pump, an electronic proportional pressure pump and an electronic proportional variable displacement pump, and the power source for driving the hydraulic pump can be a three-phase asynchronous motor with constant rotating speed, an alternating current servo motor, a switched reluctance motor or an internal combustion engine.
The hydraulic actuator 5 may be one of a single-rod hydraulic cylinder, a double-rod hydraulic cylinder and a hydraulic motor.
Furthermore, the system can also be provided with a plurality of hydraulic actuators 5, a plurality of oil inlet and outlet independent control valve groups 3 and a plurality of electronic pressure compensation valves 6, and the system is only provided with one hydraulic power source 1.
Example 2
As shown in fig. 5, the second embodiment of the independent control system for oil inlet and outlet with pressure compensation of the present invention is different from example 1 in that: the hydraulic pump of the hydraulic power source 1 is a mechanical load-sensitive pump;
LS oil circuit of mechanical load-sensitive pump and I control cavity P of electro-hydraulic pressure compensation valve 7 at the same timeFAnd the oil port G of the load selection valve 4. An oil inlet A of the electro-hydraulic pressure compensation valve 7 is communicated with an oil outlet of the hydraulic power source 1, and an oil outlet B of the electro-hydraulic pressure compensation valve 7 is communicated with a second control cavity P of the electro-hydraulic pressure compensation valve 7EOil port C of second two-position two-way proportional reversing valve 9ⅡAnd oil port C of the III two-position two-way proportional reversing valve 10ⅢOil port C of the second I two-position two-way proportional reversing valve 8ⅠAnd oil port C of IV two-position two-way proportional reversing valve 11ⅣOil ports D of a first two-position two-way proportional reversing valve 8 and a second two-position two-way proportional reversing valve 9 which are respectively communicated with an oil tankⅠ、DⅡThrough an oil passage L1 and a control cavity p of the hydraulic actuator 5AThe oil ports D of the third two-position two-way proportional reversing valve 10 and the fourth two-position two-way proportional reversing valve 11 are communicatedⅢ、DⅣThrough an oil passage L2 and a control cavity p of the hydraulic actuator 5AThe oil port E, F of the load selection valve 4 is respectively communicated with the oil passages L1 and L2, the oil port G of the load selection valve 4 is communicated with the I-th control cavity P of the electronic pressure compensation valve 6FCommunication, the actuator p being selectively actuated by controlling the operating position of the load selector valve 4AOr pBThe oil is introduced into the I control cavity P of the electronic pressure compensating valve 6FControlling the same;
when the electro-hydraulic pressure compensation valve 7 is adopted, the system further comprises a pilot oil way 21 and a pilot proportional pressure reducing valve 22, wherein an output oil port of the pilot proportional pressure reducing valve 22 and a III control cavity P of the electro-hydraulic pressure compensation valve 7GThe oil inlet and the oil outlet of the pilot proportional reducing valve 22 are respectively communicated with the pilot oil path 21 and the oil tank;
as shown in fig. 6, the electrohydraulic pressure compensating valve 7 includes a displacement sensor 12, a compensating valve body 14, a compensating valve core 15, a spring 16, an oil inlet a, an oil outlet B, and a first control chamber PFII control chamber PEAnd III control chamber PG(ii) a The compensation valve core 15 is arranged in the compensation valve body 14, one end of the spring 16 acts on the left end face C of the compensation valve core 15, the other end acts on the compensation valve body 14 and forms an I-th control cavity P with the compensation valve core 15FThe displacement sensor 12 is arranged on the compensating valve core 15 through the compensating valve body 14, directly detects the position X and the speed XV of the valve core, and the other end of the compensating valve core 15 forms a second control cavity P with the compensating valve body 14 respectivelyEAnd III control chamber PG；
The electro-hydraulic pressure compensating valve 7 is one of a normally open type and a normally closed type.
The electro-hydraulic pressure compensation valve 7 can also be arranged behind an inlet and outlet independent control valve group.
Furthermore, the system can also be provided with a plurality of hydraulic actuators 5, a plurality of oil inlet and outlet independent control valve groups 3 and a plurality of electro-hydraulic pressure compensation valves 7, and the system is only provided with one hydraulic power source 1.
Example 3
As shown in fig. 7, the third embodiment of the independent control system for oil inlet and outlet with pressure compensation of the present invention is different from that of example 1 in that: the inlet and outlet independent control valve group 3 consists of a first three-position three-way reversing valve 23 and a second three-position three-way reversing valve 24;
an oil inlet A of the electronic pressure compensation valve 6 is communicated with an oil outlet of the hydraulic power source 1, and an oil outlet B of the electronic pressure compensation valve 6 is respectively communicated with a third three-position three-way reversing valve23 oil inlet PⅠAnd an oil inlet P of a third three-position three-way reversing valve 24ⅡCommunicated oil outlet T of a third three-position three-way reversing valve 23ⅠAnd oil outlet T of a third three-position three-way reversing valve 24ⅡRespectively communicated with an oil tank, a working oil port H of a third three-position three-way reversing valve 23ⅠAnd a working oil port H of a third three-position three-way reversing valve 24ⅡTwo cavities p of the hydraulic actuator 5 are respectively connected with the pipelines L1 and L2A、pBThe oil port E, F of the load selection valve 4 is respectively communicated with the oil passages L1 and L2, the oil port G of the load selection valve 4 is communicated with the I-th control cavity P of the electronic pressure compensation valve 23FAnd (4) communicating.
The foregoing is directed to only some embodiments of the present application and not all embodiments of the present application. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
Claims (9)
1. An oil inlet and outlet independent control system with pressure compensation comprises: the hydraulic control system comprises a hydraulic power source (1), an overflow valve (2), an inlet and outlet independent control valve group (3) and a hydraulic actuator (5); the method is characterized in that: the system also comprises a load selection valve (4), an electronic pressure compensation valve (6) or an electro-hydraulic pressure compensation valve (7), and the specific adopted pressure compensation valve is determined by the load pressure and the flow of the system;
when the electronic pressure compensation valve is a pressure compensation valve controlled by a proportional electromagnet, the electronic pressure compensation valve comprises a displacement sensor (12), a proportional electromagnet (13), a compensation valve body (14), a compensation valve core (15), a spring (16), an oil inlet (A), an oil outlet (B) and a first control cavity (P)F) And the second control chamber (P)E) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface (C) of the compensating valve core, the other end acts on the compensating valve body and forms a first control cavity (P) with the compensating valve coreF) The proportional electromagnet is connected with the compensating valve body, acts on the right end surface (D) of the compensating valve core, and forms a second control cavity (P) with the compensating valve core and the compensating valve bodyE) The displacement sensor and the proportional electromagnet are integrally installed;
saidWhen the electronic pressure compensation valve is a pressure compensation valve controlled by a linear motor, the electronic pressure compensation valve comprises a displacement sensor, a compensation valve body, a compensation valve core, a spring, the linear motor (17), an oil inlet (A), an oil outlet (B) and a first control cavity (P)F) And the second control chamber (P)E) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface (C) of the compensating valve core, the other end acts on the compensating valve body and forms a first control cavity (P) with the compensating valve coreF) The linear motor is connected with the compensation valve body, is arranged on the right end surface (D) of the compensation valve core, and forms a second control cavity (P) with the compensation valve body and the compensation valve coreE)；
When the electronic pressure compensation valve is controlled by a ball screw driven by a rotating motor, the electronic pressure compensation valve comprises a displacement sensor, a compensation valve body, a compensation valve core, a spring, a rotating motor (18), a ball screw (19), a connecting rod (20), an oil inlet (A), an oil outlet (B) and a first control cavity (P)F) And the second control chamber (P)E) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface (C) of the compensating valve core, the other end acts on the compensating valve body and forms a first control cavity (P) with the compensating valve coreF) The displacement sensor is installed on the compensating valve core through the compensating valve body, directly detects the position X and the speed XV of the valve core, the rotating electrical machine is connected with the compensating valve body, and forms a second control cavity (P) with the compensating valve body and the compensating valve coreE) An extension shaft of the rotating motor is connected with a screw rod of the ball screw, a nut of the ball screw is connected with the connecting rod, the rotating motor drives the ball screw to rotate, and the rotating motion of the motor is converted into linear motion through the ball screw, so that the connecting rod is driven to output different forces and displacements;
the electro-hydraulic pressure compensation valve comprises a displacement sensor, a compensation valve body, a compensation valve core, a spring, an oil inlet (A), an oil outlet (B) and a first control cavity (P)F) II control chamber (P)E) And III control chamber (P)G) (ii) a The compensating valve core is arranged in the compensating valve body, one end of the spring acts on the left end surface (C) of the compensating valve core, and the other end acts on the compensating valve body and is connected with the compensating valve coreThe compensating valve core forms the first control cavity (P)F) The displacement sensor is arranged on the compensating valve core through the compensating valve body to directly detect the position X and the speed XV of the valve core, and the other end of the compensating valve core forms a second control cavity (P) with the compensating valve body respectivelyE) And III control chamber (P)G)；
When the electro-hydraulic pressure compensation valve is adopted, the system also comprises a pilot oil way (21) and a pilot proportional pressure reducing valve (22), wherein an output oil port of the pilot proportional pressure reducing valve and a III control cavity (P) of the electro-hydraulic pressure compensation valveG) The oil inlet and the oil outlet of the pilot proportional pressure reducing valve are respectively communicated with the pilot oil way and the oil tank;
the inlet and outlet independent control valve group consists of a first two-position two-way proportional reversing valve (8), a second two-position two-way proportional reversing valve (9), a third two-position two-way proportional reversing valve (10) and a fourth two-position two-way proportional reversing valve (11);
an oil inlet (A) of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is communicated with an oil outlet of the hydraulic power source, an oil outlet (B) of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is communicated with a second control cavity (P) of the pressure compensation valveE) Oil port (C) of second two-position two-way proportional reversing valveⅡ) And the oil port (C) of the second two-position two-way proportional reversing valveⅢ) An oil port (C) of a second two-position two-way proportional reversing valveⅠ) And the oil port (C) of the IV two-position two-way proportional reversing valveⅣ) Oil ports D of a first two-position two-way proportional reversing valve and a second two-position two-way proportional reversing valve which are respectively communicated with an oil tankⅠ、DⅡThrough an oil passage L1 and a hydraulic actuator control cavity pAOil port D of communicated III, IV two-position two-way proportional reversing valveⅢ、DⅣThrough an oil passage L2 and a hydraulic actuator control cavity pBThe load selection valve oil port E, F is respectively communicated with the oil passages L1 and L2, the load selection valve oil port G is communicated with the I-th control cavity (P) of the pressure compensation valveF) Communication, by controlling the working position of the load selection valve, the actuator control chamber p can be selectively controlledAOr pBThe oil is introduced into the control chamber (P) of the pressure compensating valveF) Controlling the same;
or the inlet and outlet independent control valve group consists of a third three-position three-way reversing valve (I)23) And a third three-position three-way reversing valve (24); an oil inlet (A) of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is communicated with an oil outlet of the hydraulic power source, and an oil outlet (B) of the electronic pressure compensation valve or the electro-hydraulic pressure compensation valve is respectively communicated with an oil inlet (P) of the third three-position three-way reversing valveⅠ) And an oil inlet (P) of a third three-position three-way reversing valveⅡ) Communicated oil outlet (T) of a third three-position three-way reversing valveⅠ) And oil outlet (T) of the third three-position three-way reversing valveⅡ) Respectively communicated with an oil tank, a working oil port (H) of a third three-position three-way reversing valveⅠ) And the working oil port (H) of the third three-position three-way reversing valveⅡ) Respectively through pipelines L1 and L2 and a hydraulic actuator control cavity pA、pBThe load selection valve oil port E, F is respectively communicated with the oil passages L1 and L2, the load selection valve oil port G is communicated with the I-th control cavity (P) of the pressure compensation valveF) And (4) communicating.
2. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the electronic pressure compensation valve and the electro-hydraulic pressure compensation valve are one of a normally open type and a normally closed type.
3. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the electronic pressure compensation valve and the electro-hydraulic pressure compensation valve can also be arranged behind the inlet and outlet independent control valve group.
4. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the displacement sensor is integrated on the proportional electromagnet, and detects the position X and the speed XV of the valve core by detecting the proportional electromagnet, or is arranged on the compensation valve core to directly detect the position X and the speed XV of the valve core.
5. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the proportional electromagnet is one of a unidirectional proportional electromagnet and a bidirectional proportional electromagnet.
6. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the rotating motor is one of a direct current motor, a synchronous motor and an asynchronous motor.
7. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the hydraulic pump of the hydraulic power source can be one of a mechanical load sensitive pump, an electronic proportional pressure pump and an electronic proportional variable displacement pump, and the power source for driving the hydraulic pump can be a three-phase asynchronous motor with constant rotating speed, an alternating current servo motor, a switched reluctance motor or an internal combustion engine.
8. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the hydraulic actuator can be one of a single-rod hydraulic cylinder, a double-rod hydraulic cylinder and a hydraulic motor.
9. The oil inlet and outlet independent control system with pressure compensation function as claimed in claim 1, wherein: the system can be provided with a plurality of hydraulic actuators, a plurality of oil inlet and outlet independent control valve groups, a plurality of electronic pressure compensation valves or electro-hydraulic pressure compensation valves or a combination of two pressure compensation valves, and the system is only provided with one hydraulic power source.
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| CN110685968B (en) * | 2019-10-17 | 2021-05-25 | 江苏汇智高端工程机械创新中心有限公司 | Control valve group, actuating mechanism and actuating system |
| CN111734698B (en) * | 2020-07-03 | 2022-04-08 | 中国矿业大学 | Shunt motor speed change synchronization system capable of resisting time-varying large unbalance load and working method |
| CN112648244B (en) * | 2021-02-19 | 2022-06-14 | 太原理工大学 | Pump-valve-cooperated multi-actuator electro-hydraulic system and control method thereof |
| CN116164003A (en) * | 2023-03-07 | 2023-05-26 | 浙江大学 | Load port independent control valve for distributed hydraulic system and control method thereof |
| CN117309363B (en) * | 2023-11-30 | 2024-03-19 | 广东智能无人***研究院(南沙) | Full sea depth hydraulic simulation test system and method based on water-based working medium |
| CN117703855A (en) * | 2023-12-15 | 2024-03-15 | 江苏汇智高端工程机械创新中心有限公司 | Bidirectional compensation valve, hydraulic system, engineering machinery and bidirectional compensation control method |
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