CN110319238B - High-flow electrohydraulic proportional reversing excitation dual-purpose valve - Google Patents
High-flow electrohydraulic proportional reversing excitation dual-purpose valve Download PDFInfo
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- CN110319238B CN110319238B CN201910715778.3A CN201910715778A CN110319238B CN 110319238 B CN110319238 B CN 110319238B CN 201910715778 A CN201910715778 A CN 201910715778A CN 110319238 B CN110319238 B CN 110319238B
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- 230000005284 excitation Effects 0.000 title claims abstract description 33
- 238000006073 displacement reaction Methods 0.000 claims abstract description 39
- 230000000670 limiting effect Effects 0.000 claims description 12
- 229910000831 Steel Inorganic materials 0.000 claims description 6
- 239000010959 steel Substances 0.000 claims description 6
- 230000008878 coupling Effects 0.000 claims description 3
- 238000010168 coupling process Methods 0.000 claims description 3
- 238000005859 coupling reaction Methods 0.000 claims description 3
- 238000001514 detection method Methods 0.000 claims description 3
- 239000011324 bead Substances 0.000 claims description 2
- 230000008859 change Effects 0.000 claims description 2
- 239000012530 fluid Substances 0.000 claims 11
- 239000003921 oil Substances 0.000 description 74
- 239000010720 hydraulic oil Substances 0.000 description 8
- 238000000034 method Methods 0.000 description 6
- 230000009471 action Effects 0.000 description 5
- 230000008569 process Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
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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
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members 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
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
- F16K11/085—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug
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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
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
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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
- F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given
- F16K37/0025—Electrical or magnetic means
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Servomotors (AREA)
Abstract
The invention discloses a high-flow electrohydraulic proportional reversing excitation dual-purpose valve, which comprises a valve core rotary proportional reversing valve assembly, a hydraulic reversing valve assembly and a microprocessor, wherein the valve core rotary proportional reversing valve assembly comprises a secondary valve body, a secondary valve sleeve, a secondary valve core, a rotary motor and a linear motor. The high-flow electrohydraulic proportional reversing excitation dual-purpose valve is relatively simple in structure, the matching relation between a first arc notch and a second arc notch on the right-most end shoulder of the secondary valve core and an arc protruding block fixedly connected to the inner wall of the limit sleeve is changed, the valve can be fixed to a zero position, two-stage axial displacement is achieved, a proportional reversing mode can be achieved through first-stage displacement, an excitation reversing mode can be achieved through second-stage displacement, the valve can be well applied to a high-flow excitation hydraulic system, and meanwhile the vibration frequency and the vibration amplitude of the valve can be adjusted in a high-precision mode through the rotation speed of a proportional control rotating motor and the propelling displacement of a linear motor.
Description
Technical Field
The invention relates to the technical field of hydraulic valves, in particular to a high-flow electro-hydraulic proportional reversing excitation dual-purpose valve.
Background
The existing electro-hydraulic proportional valve adopts a proportional control technology, a hydraulic element is arranged between a switch type hydraulic valve and an electro-hydraulic servo valve, the electro-hydraulic proportional valve can be combined with an electronic control device, various input and output signals can be quite conveniently calculated and processed, a complex control function is realized, but the electro-hydraulic proportional reversing valve can not realize excitation while controlling valve core displacement to realize proportional reversing by changing current of an input proportional electromagnet, and cannot meet the use requirements of certain large-flow excitation hydraulic systems.
The existing electrohydraulic servo valve is better than the electrohydraulic proportional valve in certain performance aspect and can be used as an excitation valve, but has the defects of difficult adjustment of vibration amplitude, certain limitation, complex structure, obviously higher manufacturing precision requirement and price than the electrohydraulic proportional valve and poor pollution resistance, so the electrohydraulic servo valve cannot be widely applied to a large-flow excitation hydraulic system.
When the existing rotary valve type reversing valve is used as an excitation valve, although the adjustment of the vibration frequency and the vibration amplitude is relatively easy, the valve core is driven by a motor to continuously rotate so as to realize high-speed liquid flow reversing, and therefore, one problem is that the zero position can not be positioned, namely the reversing median position can not be realized, and the proportional reversing control can not be realized.
The existing electromagnetic reversing valve has the advantages that the structure is simple, the manufacturing cost is low, excitation can be realized through power-on and power-off control of an electromagnet, but the adjustment of the vibration frequency and the vibration amplitude is very difficult, the control precision is not high, the proportional reversing cannot be realized, and the use requirement of a large-flow complex hydraulic system with certain control precision and dynamic characteristic requirements cannot be met.
Therefore, the existing single reversing valve cannot meet the use requirements of a large-flow complex hydraulic system which needs proportional reversing and vibration excitation and has certain control precision and dynamic characteristic requirements, so that the application range of the valve has certain limitation.
Disclosure of Invention
(one) solving the technical problems
Aiming at the defects of the prior art, the invention provides a high-flow electrohydraulic proportional reversing excitation dual-purpose valve, which solves the problem that the existing single reversing valve can not meet the use requirements of a high-flow complex hydraulic system which needs proportional reversing and excitation and has certain control precision and dynamic characteristic requirements.
(II) technical scheme
In order to achieve the above purpose, the invention is realized by the following technical scheme: the utility model provides a high-flow electrohydraulic proportion switching-over excitation dual-purpose valve, includes case rotary type proportional reversing valve subassembly, hydraulic drive reversing valve subassembly and microprocessor, case rotary type proportional reversing valve subassembly includes secondary valve body, secondary valve barrel, secondary case, rotating electrical machines, linear electric motor and angle sensor, the secondary valve barrel is installed in the inside of secondary valve body, and the secondary valve barrel is installed in the inside of secondary valve barrel, the one end of secondary valve barrel is fixed connection with the output shaft of rotating electrical machines through pivot and shaft coupling respectively, one side of secondary valve body and one side fixed connection of linear electric motor, and one side fixed connection of linear electric motor has the motor cover, the one end that the motor cover kept away from linear electric motor runs through the secondary valve body and extends to the inside of secondary valve body, and the one end that the motor cover extends to the inside of secondary valve body contacts with the one end of secondary valve barrel;
the hydraulic reversing valve assembly comprises a main-stage valve body, a main-stage valve sleeve, a main-stage valve core and a displacement sensor, wherein the main-stage valve sleeve is arranged in the main-stage valve body, the main-stage valve core is arranged in the main-stage valve sleeve, a left pressure cavity and a right pressure cavity are respectively formed in two sides of the inside of the hydraulic reversing valve assembly, a main valve spring is arranged in the right pressure cavity, and one end of the main-stage valve core is fixedly connected with a guide limiting part matched with the main valve spring.
Preferably, the bottom of the main-stage valve body is respectively provided with an oil port P, an oil port T, an oil port A and an oil port B, wherein the oil port P is an oil inlet of the hydraulic reversing valve assembly, the oil port T is an oil outlet of the hydraulic reversing valve assembly, and the oil port A and the oil port B are working oil ports of the hydraulic reversing valve assembly.
Preferably, the bottom of the secondary valve body is provided with an oil inlet P0, a working oil port A0 and a working oil port B0 respectively, the outside oil ports of the oil ports A0 and B0 are oil outlets T0, the oil outlets T0 are communicated with the oil outlets T of the hydraulic reversing valve assembly through an inner cavity and a passage of the valve core rotary type proportional reversing valve assembly, the oil port P0 of the valve core rotary type proportional reversing valve assembly is communicated with the oil inlet P of the hydraulic reversing valve assembly, and the oil ports A0 and B0 are communicated with a left pressure cavity and a right pressure cavity of the hydraulic reversing valve assembly respectively.
Preferably, the output shaft of the rotating motor is fixedly connected with an angle sensor, the detection end of the displacement sensor is fixedly connected with one end of the main-stage valve core, and the wiring end of the microprocessor is electrically connected with the angle sensor and the wiring end of the displacement sensor through conductive wires respectively.
Preferably, one end of the rotating shaft is fixedly connected with one end of the secondary valve core through a sleeve coupler, one side of the inner wall of the secondary valve body is fixedly connected with a bearing matched with the rotating shaft, the front section of the motor sleeve is movably provided with a steel ball, a secondary valve spring is fixedly arranged between the rotating shaft and the secondary valve core, a limit sleeve is arranged between one end of the secondary valve core and the motor sleeve, and the limit sleeve is fixedly connected with the secondary valve sleeve without relative rotation and displacement.
Preferably, the secondary valve core has two degrees of freedom, one is driven by a rotating motor to circumferentially rotate, and the other is driven by a linear motor to axially move.
Preferably, the outer surface of the secondary valve core is fixedly connected with shoulders I, II, III and IV in sequence from left to right, a group of radial openings are formed in the left sides of the shoulders I, II, III and IV, each group of radial openings are four along the circumferential direction, two adjacent groups of radial openings are staggered in the axial direction, and the staggered angle is 45 degrees.
Preferably, a first arc-shaped notch and a second arc-shaped notch are respectively formed in the shoulder at the rightmost end of the secondary valve core, and an arc-shaped protruding block matched with the first arc-shaped notch and the second arc-shaped notch is fixedly connected to the inner wall of the limit sleeve.
Preferably, through the drive of rotating electrical machines and linear electric motor, can change first arc incision and second arc incision on the right-hand member circular bead of secondary case with fixed connection in the cooperation relation between the arc protruding piece of stop collar inner wall makes it can fix the zero position, possess two-stage axial displacement, and the first stage displacement can realize proportion switching-over mode, and the second stage displacement can realize excitation switching-over mode, can carry out the quick switch over to it according to the different work requirement of hydraulic system.
Preferably, when the linear motor drives the secondary valve core to move leftwards and axially, a through-flow valve opening formed by a radial opening on the shoulder of the secondary valve core and a window on the secondary valve sleeve is continuously reduced.
(III) beneficial effects
The invention provides a high-flow electrohydraulic proportional reversing excitation dual-purpose valve. Compared with the prior art, the method has the following beneficial effects:
(1) The high-flow electrohydraulic proportional reversing excitation dual-purpose valve has the advantages of an electrohydraulic proportional reversing valve, can realize excitation, can realize proportional adjustment of vibration frequency and vibration amplitude, can meet the use requirements of a high-flow complex hydraulic system which needs proportional reversing and excitation and has certain control precision and dynamic characteristic requirements, adopts a two-stage structure design, wherein a pilot secondary valve is a valve core rotary proportional reversing valve, and a main valve is a hydraulic reversing valve component.
(2) Compared with the existing electromagnetic directional valve, the dual-purpose valve can realize proportional directional control, and has obviously better adjusting precision for vibration frequency and vibration amplitude than the electromagnetic directional valve, and compared with the traditional electro-hydraulic proportional directional valve, the dual-purpose valve has valve sleeve structures for both the secondary valve and the main valve, so that the directional control precision is improved to a certain extent.
(3) According to the high-flow electro-hydraulic proportional reversing excitation dual-purpose valve, the angle sensor and the displacement sensor are respectively arranged on the secondary valve and the main valve of the dual-purpose valve, so that a secondary angle-electric feedback and main displacement-electric feedback two-stage electric feedback system is formed, the control precision and stability of the dual-purpose valve are greatly improved, meanwhile, the return middle spring of the valve core of the main valve of the dual-purpose valve is designed by adopting a single-side spring matched valve sleeve, and the same spring is compressed no matter which working position the main valve core is located, therefore, the structure does not need to be exactly matched with two springs, and the dual-purpose valve has higher performance.
(4) According to the high-flow electrohydraulic proportional reversing excitation dual-purpose valve, when the linear motor drives the secondary valve core of the dual-purpose valve to move leftwards and axially, a through-flow valve opening formed by a radial opening on a shoulder of the secondary valve core and a window on the secondary valve sleeve is continuously reduced, namely the through-flow is gradually reduced, the through-flow valve opening of the general reversing valve is gradually increased along with the movement of the valve core, and meanwhile, the vibration frequency and the vibration amplitude of the reversing valve can be proportionally regulated by proportionally controlling the rotating speed of the rotating motor and the propelling displacement of the linear motor.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a cross-sectional view of the construction of the rotary proportional reversing valve assembly of the present invention;
FIG. 3 is a schematic view of the secondary spool of the present invention;
FIG. 4 is a schematic view of the stop collar of the present invention;
FIG. 5 is a perspective cross-sectional view of the rotary proportional reversing valve assembly of the present invention;
FIG. 6 is a schematic view of the structure of the secondary spool and stop collar of the present invention;
FIG. 7 is a cross-sectional view of the side of the secondary spool and stop collar of the present invention.
In the figure, a valve core rotary type proportional reversing valve assembly 1, a hydraulic reversing valve assembly 2, a microprocessor 3, an angle sensor 4, a rotary motor 5, a coupler 6, a rotary shaft 7, a secondary valve body 8, a secondary valve core 9, a secondary valve sleeve 10, a motor sleeve 11, a linear motor 12, a displacement sensor 13, a primary valve body 14, a left pressure cavity 15, a primary valve core 16, a primary valve sleeve 17, a right pressure cavity 18, a main valve spring 19, a guide limiting piece 20, a sleeve coupler 21, a bearing 22, a steel ball 23, a valve spring 24 times, a limiting sleeve 25, a radial opening 26, a first arc-shaped notch 27, a second arc-shaped notch 28 and a arc-shaped protruding block 29.
Description of the embodiments
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Referring to fig. 1-7, the embodiment of the present invention provides a technical solution: the utility model provides a high-flow electrohydraulic proportion switching-over excitation dual-purpose valve, including case rotation type proportional reversing valve subassembly 1, hydraulic drive reversing valve subassembly 2 and microprocessor 3, this hydraulic drive reversing valve subassembly 2 is the main level valve, case rotation type proportional reversing valve subassembly 1 is the secondary valve, can be applicable in high-flow occasion, case rotation type proportional reversing valve subassembly 1 includes secondary valve body 8, secondary valve housing 10, secondary valve core 9, rotating electrical machines 5, linear electric motor 12 and angle sensor 4, secondary valve housing 10 installs in the inside of secondary valve body 8, and secondary valve core 9 installs in the inside of secondary valve housing 10, one end of secondary valve core 9 is fixed connection with the output shaft of rotating electrical machines 5 through pivot 7 and shaft coupling 6 respectively, one side of secondary valve body 8 and one side fixed connection of linear electric motor 12, and one side fixed connection of linear electric motor 12 has motor cover 11, the one end that linear electric motor cover 11 kept away from linear electric motor 12 runs through secondary valve body 8 and extends to the inside of secondary valve body 8, and the one end that the motor cover 11 extends to the inside of secondary valve body 8 contacts with one end of secondary valve core 9, linear electric motor 12 promotes this secondary valve core 9 axial displacement through the motor cover 11 that is connected with it.
The hydraulic reversing valve assembly 2 comprises a main-stage valve body 14, a main-stage valve sleeve 17, a main-stage valve core 16 and a displacement sensor 13, wherein the type of the displacement sensor 13 is ZLDS100, the displacement sensor 13 can accurately detect the axial displacement of the main-stage valve core 16, the main-stage valve sleeve 17 is arranged in the main-stage valve body 14, the main-stage valve core 16 is arranged in the main-stage valve sleeve 17, the main-stage valve core 16 is equivalent to a piston of a hydraulic cylinder, the two pistons have the same dynamic characteristics, the left pressure cavity 15 and the right pressure cavity 18 are respectively arranged on two sides of the inside of the hydraulic reversing valve assembly 2, a main valve spring 19 is arranged in the right pressure cavity 18 and used for recovering the middle position, and due to the adoption of a single spring design, no matter which working position the main-stage valve core 16 is positioned, the same spring is compressed, therefore, the structure does not need to be accurately matched with two springs, the dual-purpose valve has higher performance, one end of the main valve core 16 is fixedly connected with a guiding limiting piece 20 which is matched with the main valve spring 19, the guiding limiting piece 20 can serve as a guide for the main valve spring 19 and perform a good limiting effect, the bottom of the main valve body 14 is respectively provided with an oil port P, an oil port T, an oil port A and an oil port B, the oil port P is an oil inlet of the hydraulic reversing valve assembly 2, the oil port T is an oil outlet of the hydraulic reversing valve assembly 2, the oil port A and the oil port B are working oil ports of the hydraulic reversing valve assembly 2, the two-way valve is a three-position four-way reversing valve, the oil port P, the oil port T, the oil port A and the oil port B of the hydraulic reversing valve assembly 2 are the oil port P, the oil port T, the oil port A and the oil port B of the two-way valve respectively, the oil port P0, the working oil port A0 and the oil port B0 are respectively arranged at the bottom of the secondary valve body 8, the outer side oil ports of the oil port A0 and the oil port B0 are the oil port T0, the oil outlet T0 is communicated with the oil outlet T of the hydraulic reversing valve assembly 2 through an inner cavity and a passage of the valve core rotary type proportional reversing valve assembly 1, an oil port P0 of the valve core rotary type proportional reversing valve assembly 1 is communicated with an oil inlet P of the hydraulic reversing valve assembly 2, an oil port A0 and an oil port B0 are respectively communicated with a left pressure cavity 15 and a right pressure cavity 18 of the hydraulic reversing valve assembly 2 and are used for pushing the valve core of the hydraulic reversing valve assembly 2 to move left and right axially and respectively correspond to a left working position and a right working position of the hydraulic reversing valve assembly 2, namely, a left working position and a right working position of a dual-purpose valve, an output shaft of the rotary motor 5 is fixedly connected with an angle sensor 4, a detection end of a displacement sensor 13 is fixedly connected with one end of a main stage valve core 16, wiring ends of a microprocessor 3 are respectively electrically connected with wiring ends of the angle sensor 4 and the displacement sensor 13 through conductive wires, the model of the angle sensor 4 is SSA00XXH2-V010, the angle sensor 4 can accurately detect the rotation angle of the rotating motor 5, namely the rotation angle of the secondary valve core 9 of the dual-purpose valve, the model of the microprocessor 3 is ARM9, the microprocessor 3 is used for analyzing and processing the angle signal collected by the angle sensor 4 and the displacement signal collected by the displacement sensor 13, thus the working parameters of the dual-purpose valve can be adjusted as necessary according to the working requirement and the required relevant characteristics of the dual-purpose valve, thus the closed-loop dual-feedback proportional control of the dual-purpose valve is formed, the dual-purpose valve has higher dynamic performance obviously, one end of the rotating shaft 7 is fixedly connected with one end of the secondary valve core 9 through the sleeve coupler 21, the rotation precision can be ensured, one side of the inner wall of the secondary valve body 8 is fixedly connected with the bearing 22 matched with the rotating shaft 7, the front section of the motor sleeve 11 is movably provided with a steel ball 23, the main purpose of the steel ball 23 is to reduce the friction resistance between the motor sleeve 11 and the secondary valve core 9 when the rotary motor 5 drives the secondary valve core 9 to rotate through the rotary shaft 7, so that the secondary valve core 9 has better rotation performance, a secondary valve spring 24 is fixedly arranged between the rotary shaft 7 and the secondary valve core 9, the main purpose of the secondary valve spring 24 is to relieve the impact force caused by the fact that the linear motor 12 pushes the secondary valve core 9 to move leftwards axially through the motor sleeve 11, meanwhile, when the linear motor 12 retreats, the secondary valve spring 24 can provide certain restoring elastic force to push the secondary valve core 9 to move rightwards axially to return to a zero position, a limit sleeve 25 is arranged between one end of the secondary valve core 9 and the motor sleeve 11, the limit sleeve 25 is fixedly connected with the secondary valve sleeve 10, no relative rotation and displacement are caused, the limit sleeve 25 is used for limiting the rotation angle of the secondary valve core 9, the secondary valve core 9 can only rotate positively and negatively within a certain angle range, and corresponds to the left working position and the right working position of the valve core rotary type proportional reversing valve assembly 1 respectively, the secondary valve core 9 has two degrees of freedom, one is driven by the rotary motor 5 to rotate circumferentially, the other is driven by the linear motor 12 to drive the secondary valve core 9 to move axially, the outer surface of the secondary valve core 9 is fixedly connected with shoulders I, II, III and IV from left to right, a group of radial openings 26 are respectively formed on the left sides of the shoulders I, II, III and IV, each group of radial openings 26 is provided with four radial openings along the circumferential direction, two adjacent groups of radial openings 26 are staggered with each other in the axial direction, the staggered angle is 45 degrees, a first arc-shaped notch 27 and a second arc-shaped notch 28 are respectively formed on the rightmost shoulder of the secondary valve core 9, and the inner wall fixedly connected with of stop collar 25 with first arc incision 27 and second arc incision 28 looks adaptation arc protruding piece 29, wherein different cooperation correspond different work positions, it is to be noted that the axis at the bottom center of second arc incision 28 is at the same time stagger completely with the axis at all radial openings 26 on shoulder I, II, III, IV, this secondary case 9's right-most end has a recess, its effect is in placing the steel ball 23 on the motor cover 11, thereby make things convenient for linear motor 12 to promote secondary case 9 and move about, can not influence rotating electrical machines 5 drive secondary case 9 and rotate, thereby guaranteed the normal switching work of case structure.
The specific working principle of the invention is explained as follows:
in the invention, the limit sleeve 25 is arranged in the secondary valve sleeve 10 without relative movement, the plane of the arc-shaped protruding block 29 of the limit sleeve 25 and the plane of the window of the secondary valve sleeve 10 belong to the same plane, and the different working positions of the valve core rotary type proportional reversing valve 1 corresponding to the three working positions of zero position, extension and retraction of the linear motor 12 are described in detail below:
1) The linear motor is in zero position
When the linear motor 12 is at zero position, the arc-shaped protruding block 29 inside the limit sleeve 25 is just clamped at the bottom center of the second arc-shaped notch 28 on the right-most shoulder of the secondary valve core 9, and because the axis of the bottom center of the second arc-shaped notch 28 is completely staggered with the axes of all radial openings 26 on the shoulders I, II, III and IV, no through-flow valve opening can be formed between all radial openings 26 on the shoulders I, II, III and IV on the secondary valve core 9 and the window opened on the secondary valve sleeve 10, that is, all valve openings of the valve core rotary type proportional reversing valve assembly 1 are in a closed state and cannot be filled with oil, and the corresponding valve core rotary type proportional reversing valve assembly 1 is the middle position and the middle position can be O.
2) The linear motor is in the extended position
Along with the extension of the linear motor 12, the motor sleeve 11 connected with the linear motor 12 is driven to push the secondary valve core 9 to move leftwards and axially, and at the moment, two stages of displacement respectively correspond to different working modes, and the following details are described:
(1) First-stage displacement-proportional reversing mode
Along with the extension of the linear motor 12, the secondary valve core 9 is pushed to move axially leftwards, when the linear motor 12 is in a zero position, the arc-shaped protruding block 29 in the limit sleeve 25 is just clamped at the bottom center of the second arc-shaped notch 28 on the rightmost shoulder of the secondary valve core 9, but along with the leftward axial movement of the secondary valve core 9, the bottom center of the second arc-shaped notch 28 on the rightmost shoulder of the secondary valve core 9 is gradually separated from the arc-shaped protruding block 29 in the limit sleeve 25 until the limit sleeve is completely separated from the constraint of the whole second arc-shaped notch 28, namely the first-stage displacement.
At this time, the arc-shaped protruding block 29 inside the limiting sleeve 25 is completely separated from the constraint of the whole second arc-shaped notch 28, but is simultaneously constrained by the first arc-shaped notch 27, so that the secondary valve core 9 can rotate positively and negatively within a certain angle range under the driving of the rotating motor 5, the set angle range is 45 degrees, and the different working positions of the valve core rotary proportional reversing valve assembly 1 corresponding to the two working states of forward rotation and reverse rotation of the rotating motor 5 are explained as follows:
i rotating Electrical machine forward rotation (counterclockwise) -left working position
After the first-stage displacement is completed, the rotating motor 5 rotates forward by a certain angle until the arc-shaped protruding block 29 in the limit sleeve 25 contacts the contact surface a between the first arc-shaped notch 27 and the second arc-shaped notch 28 on the secondary valve core 9, at this moment, the secondary valve core 9 is limited and cannot rotate any more, at this moment, the radial openings 26 on the land II and the land IV of the secondary valve core 9 and the window on the secondary valve sleeve 10 form a through-flow valve opening, so that hydraulic oil which cannot pass through originally can smoothly flow through the valve opening, the specific flow direction of hydraulic oil is that hydraulic oil flows in from the oil port P0 of the valve core rotating type proportional reversing valve assembly 1, the oil port P0 is connected with the oil port P of the main valve hydraulic reversing valve assembly 2, namely the oil port P of the whole dual-purpose valve, then flows into the oil port A0 through the through-flow valve opening on the land II of the secondary valve core 9, the oil return port A0 is pushed to move axially to the right of the main valve core 16, the hydraulic oil return port 18 passes through the oil port B0 and then flows into the dual-purpose valve chamber T of the dual-purpose valve through the land T, and finally flows into the oil tank through the inner side chamber T of the dual-purpose valve: p0 and A0 are communicated, and B0 and T0 are communicated, and the left working position of the valve core rotary type proportional reversing valve assembly 1 corresponds to the left working position.
Ii rotating electric machine reverse rotation (clockwise) -right working position
After the first displacement is completed, the rotating electrical machine 5 reverses a certain angle until the arc-shaped protruding block 29 inside the limit sleeve 25 contacts the contact surface B between the first arc-shaped notch 28 and the second arc-shaped notch 28 on the secondary valve core 9, at this time, the secondary valve core 9 is limited and cannot rotate any more, at this time, the radial openings 25 on the land i and the land iii of the secondary valve core 9 and the window on the secondary valve sleeve 10 form a through-flow valve opening, so that hydraulic oil which cannot pass through originally can smoothly flow through the valve opening, the specific flow direction of hydraulic oil thereof is that hydraulic oil flows in from the oil port P0 of the valve core rotary proportional reversing valve assembly 1, the oil port P0 is connected with the oil port P of the main valve hydraulic reversing valve assembly 2, namely the oil port P of the whole dual-purpose valve, then flows into the oil port B0 through the through-flow valve opening on the land iii of the secondary valve core 9, the oil return port B0 is connected with the right pressure cavity 15 of the main valve hydraulic reversing valve assembly 2, the main valve 16 is pushed to move axially left, the left pressure cavity 15 is that the hydraulic oil passes through the oil port A0, and then flows into the oil tank through the land i of the dual-purpose valve through the land T, and finally flows into the oil tank through the inner cavity of the valve: p0 and B0 are communicated, A0 and T0 are communicated, and the right working position of the valve core rotary type proportional reversing valve assembly 1 corresponds to the left working position.
(2) Second-stage displacement-excitation reversing mode
Then, as the linear motor 12 stretches out further, the contact surface between the first arc notch 27 and the second arc notch 28 on the secondary valve core 9 gradually breaks away from the arc-shaped protruding block 29 inside the limiting sleeve 25, finally, the arc-shaped protruding block 29 inside the limiting sleeve 25 is completely separated from the constraint of the first arc-shaped notch 27, at the moment, the secondary valve core 9 is not completely constrained by the limiting sleeve 25, the rotary motor 5 can drive the secondary valve core 9 to rotate continuously at a specific speed, the radial openings 25 on the lands I, II, III and IV of the secondary valve core 9 and the through-flow valve opening formed by the windows on the secondary valve sleeve 10 are continuously opened and closed, the land I and the land IV are a group, the on-off condition of the valve openings of the same group is consistent, and the through-flow valve opening of the rotary motor 5 drives the secondary valve core 9 to rotate continuously and alternately, so that the main valve 16 of the rotary proportional reversing valve assembly 2 continuously moves left and right, the hydraulic valve assembly 2 is driven by the rotary motor, and the amplitude of the hydraulic reversing valve can be controlled by the vibration valve through the vibration of the vibration motor, and the vibration of the vibration type reversing valve is controlled by the vibration type of the reversing valve.
3) The linear motor is in the retreating position
The process of withdrawing the linear motor 12 in the case of the second stage displacement is discussed herein, and the situation of withdrawing from the first stage displacement is also included, so that the situation of withdrawing from the first stage displacement is not separately discussed, and as the linear motor 12 withdraws, the secondary valve element 9 is pushed to move axially to the right under the action of the resilience force of the secondary valve spring 24, and as the secondary valve element 9 is subjected to uninterrupted rotation in the excitation mode, the rotation stop position is arbitrary, and two situations exist at this time, which are explained as follows:
first case
The arc-shaped protruding block 29 inside the limit sleeve 25 just slides into the first arc-shaped notch 27 on the secondary valve core 9, and due to the arc-shaped structure at the front end of the arc-shaped protruding block 29, the secondary valve core 9 can easily slide into the bottom center along the arc surface of the first arc-shaped notch 27 under the resilience force of the secondary valve spring 24, and the corresponding valve core rotary type proportional conversion assembly 1 can move towards the middle position of the valve, and the middle position can be O-shaped and oil can not be passed according to the detailed description of the working state of the linear motor 12 when the linear motor 12 is at the zero position.
Second case
The arc-shaped protruding block 29 inside the limit sleeve 25 firstly touches the second arc-shaped notch 28 on the secondary valve core 9, at this time, the secondary valve core 9 can easily slide into the first arc-shaped notch 27 along the arc surface of the second arc-shaped notch 28 under the resilience force of the secondary valve spring 24, at this time, the second valve core 9 becomes the first condition, and can easily slide into the bottom center along the arc surface of the first arc-shaped notch 27 under the resilience force of the secondary valve spring 24, and the same can be known according to the above detailed description of the working state of the linear motor 12 when in the zero position, at this time, the corresponding valve core rotary proportional reversing valve assembly 1 is the middle position, and the middle position function is of an 'O' -type and can not be filled with oil.
Therefore, according to the above description, the two cases are in fact quite the same way, and finally, the secondary valve core 9 is returned to the zero position under the action of the resilience force of the secondary valve spring 24, that is, the middle position of the valve core rotary proportional reversing valve assembly 1.
It is noted that relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made therein without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (6)
1. The utility model provides a high-flow electrohydraulic proportion switching-over excitation dual-purpose valve, includes case rotation type proportion switching-over valve subassembly (1), hydraulic drive switching-over valve subassembly (2) and microprocessor (3), its characterized in that: the valve core rotary type proportional reversing valve assembly (1) comprises a secondary valve body (8), a secondary valve sleeve (10), a secondary valve core (9), a rotary motor (5), a linear motor (12) and an angle sensor (4), wherein the secondary valve sleeve (10) is arranged in the secondary valve body (8), the secondary valve core (9) is arranged in the secondary valve sleeve (10), one end of the secondary valve core (9) is fixedly connected with an output shaft of the rotary motor (5) through a rotating shaft (7) and a coupling (6) respectively, one side of the secondary valve body (8) is fixedly connected with one side of the linear motor (12), one side of the linear motor (12) is fixedly connected with a motor sleeve (11), one end of the motor sleeve (11) away from the linear motor (12) penetrates through the secondary valve body (8) and extends to the interior of the secondary valve body (8), and one end of the motor sleeve (11) extends to the interior of the secondary valve body (8) to be in contact with one end of the secondary valve core (9);
the hydraulic reversing valve assembly (2) comprises a main-stage valve body (14), a main-stage valve sleeve (17), a main-stage valve core (16) and a displacement sensor (13), wherein the main-stage valve sleeve (17) is arranged in the main-stage valve body (14), the main-stage valve core (16) is arranged in the main-stage valve sleeve (17), a left pressure cavity (15) and a right pressure cavity (18) are respectively formed in two sides of the inside of the hydraulic reversing valve assembly (2), a main valve spring (19) is arranged in the right pressure cavity (18), and one end of the main-stage valve core (16) is fixedly connected with a guide limiting part (20) which is matched with the main valve spring (19);
the secondary valve core (9) has two degrees of freedom, one is driven by the rotary motor (5) to circumferentially rotate, and the other is driven by the linear motor (12) to axially move;
one end of the rotating shaft (7) is fixedly connected with one end of the secondary valve core (9) through a sleeve coupler (21), one side of the inner wall of the secondary valve body (8) is fixedly connected with a bearing (22) matched with the rotating shaft (7), the front end of the motor sleeve (11) is movably provided with a steel ball (23), a secondary valve spring (24) is fixedly arranged between the rotating shaft (7) and the secondary valve core (9), a limit sleeve (25) is arranged between one end of the secondary valve core (9) and the motor sleeve (11), and the limit sleeve (25) is fixedly connected with the secondary valve sleeve (10) without relative rotation and displacement;
a first arc-shaped notch (27) and a second arc-shaped notch (28) are respectively formed in the shoulder at the rightmost end of the secondary valve core (9), and an arc-shaped protruding block (29) matched with the first arc-shaped notch (27) and the second arc-shaped notch (28) is fixedly connected with the inner wall of the limit sleeve (25);
through the drive of rotating electrical machines (5) and linear electric motor (12), can change first arc incision (27) and second arc incision (28) on the right-most end circular bead of secondary case (9) with fixed connection in the cooperation relation between arc protruding piece (29) of stop collar (25) inner wall makes it can fix the zero position, possess two-stage axial displacement, and first stage displacement can realize proportion switching-over mode, and second stage displacement can realize excitation switching-over mode, can carry out quick switch over to it according to the different work requirements of hydraulic system.
2. The high-flow electro-hydraulic proportional reversing excitation dual-purpose valve according to claim 1, wherein: the bottom of the main-stage valve body (14) is respectively provided with an oil port P, an oil port T, an oil port A and an oil port B, wherein the oil port P is an oil inlet of the hydraulic reversing valve assembly (2), the oil port T is an oil outlet of the hydraulic reversing valve assembly (2), and the oil port A and the oil port B are working oil ports of the hydraulic reversing valve assembly (2).
3. The high-flow electro-hydraulic proportional reversing excitation dual-purpose valve according to claim 1, wherein: the bottom of secondary valve body (8) has seted up oil inlet P0, work hydraulic fluid port A0 and work hydraulic fluid port B0 respectively, and the outside hydraulic fluid port of hydraulic fluid port A0 and hydraulic fluid port B0 is oil-out T0 promptly, oil-out T0 is linked together with the oil-out T of hydraulic fluid switching-over valve subassembly (2) through the inside cavity and the passageway of case rotation type proportional switching-over valve subassembly (1), and the hydraulic fluid port P0 of case rotation type proportional switching-over valve subassembly (1) is linked together with the oil inlet P of hydraulic fluid switching-over valve subassembly (2), hydraulic fluid port A0 and hydraulic fluid port B0 are linked together with left pressure chamber (15) and right pressure chamber (18) of hydraulic fluid switching-over valve subassembly (2) respectively.
4. The high-flow electro-hydraulic proportional reversing excitation dual-purpose valve according to claim 1, wherein: the output shaft of the rotating motor (5) is fixedly connected with an angle sensor (4), the detection end of the displacement sensor (13) is fixedly connected with one end of the main-stage valve core (16), and the wiring end of the microprocessor (3) is electrically connected with the angle sensor (4) and the wiring end of the displacement sensor (13) through conductive wires respectively.
5. The high-flow electro-hydraulic proportional reversing excitation dual-purpose valve according to claim 1, wherein: the outer surface of the secondary valve core (9) is fixedly connected with shoulders I, II, III and IV from left to right in sequence, a group of radial openings (26) are formed in the left sides of the shoulders I, II, III and IV, each group of radial openings (26) are four along the circumferential direction, two adjacent groups of radial openings (26) are staggered in the axial direction, and the staggered angle is 45 degrees.
6. The high-flow electro-hydraulic proportional reversing excitation dual-purpose valve according to claim 1 or 5, wherein: when the linear motor (12) drives the secondary valve core (9) to move leftwards and axially, a through-flow valve opening formed by a radial opening (26) on a shoulder of the secondary valve core (9) and a window on the secondary valve sleeve (10) is continuously reduced.
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