CN210461782U - Large-flow electro-hydraulic proportional reversing and exciting dual-purpose valve - Google Patents
Large-flow electro-hydraulic proportional reversing and exciting dual-purpose valve Download PDFInfo
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- CN210461782U CN210461782U CN201921259961.9U CN201921259961U CN210461782U CN 210461782 U CN210461782 U CN 210461782U CN 201921259961 U CN201921259961 U CN 201921259961U CN 210461782 U CN210461782 U CN 210461782U
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Abstract
The utility model discloses a large-traffic electric liquid proportion switching-over excitation dual-purpose valve, including case rotation type proportion reversing valve subassembly, reversing valve subassembly and microprocessor that surges, case rotation type proportion reversing valve subassembly includes secondary valve body, secondary valve barrel, secondary case, rotating electrical machines and linear electric motor, the utility model relates to a hydrovalve technical field. The high-flow electro-hydraulic proportional reversing and exciting dual-purpose valve is relatively simple in structure, the matching relation between a first arc-shaped notch and a second arc-shaped notch on the shoulder at the rightmost end of the secondary valve core and an arc-shaped protruding block fixedly connected to the inner wall of the limiting sleeve is changed, the secondary valve core can be positioned at a zero position, two-stage axial displacement is achieved, a proportional reversing mode can be achieved through first-stage displacement, an exciting reversing mode can be achieved through second-stage displacement, the secondary valve core can be well applied to a high-flow exciting hydraulic system, and meanwhile, the rotating speed of a rotating motor and the propelling displacement of a linear motor can be proportionally controlled to perform high-precision proportional.
Description
Technical Field
The utility model relates to a hydrovalve technical field specifically is a large-traffic electric liquid proportion switching-over excitation dual-purpose valve.
Background
The existing electro-hydraulic proportional valve adopts a proportional control technology, is a hydraulic element between a switch type hydraulic valve and an electro-hydraulic servo valve, can be combined with an electronic control device, can very conveniently calculate and process various input and output signals, and realizes a complex control function, but the electro-hydraulic proportional reversing valve can not realize excitation while controlling the displacement of a valve core to realize proportional reversing by changing the current of an input proportional electromagnet, and can not meet the use requirements of certain large-flow excitation hydraulic systems.
The existing electro-hydraulic servo valve is better than an electro-hydraulic proportional valve in certain performance and can be used as an excitation valve, but the existing electro-hydraulic servo valve has the defects that the adjustment of the vibration amplitude is very difficult, the existing electro-hydraulic servo valve has certain limitation, the structure is complex, the manufacturing precision requirement and the price are obviously higher than those of the electro-hydraulic proportional valve, and the pollution resistance is poor, so that the existing electro-hydraulic 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 vibration frequency and the vibration amplitude of the existing rotary valve type reversing valve are easy to adjust, the valve core is driven by a motor to continuously rotate so as to enable the liquid flow of the valve core to be reversed at a high speed to realize excitation, so that one problem exists that zero position, namely reversing neutral position, cannot be fixed, and proportional reversing control cannot be realized.
Although the existing electromagnetic directional valve has simple structure and low manufacturing cost and can realize excitation by controlling the power on and the power off of an electromagnet, the existing electromagnetic directional valve has very difficult adjustment of the vibration frequency and the vibration amplitude, low control precision, and can not realize proportional direction change and meet the use requirement of a large-flow complex hydraulic system with certain control precision and dynamic characteristic requirements.
Therefore, the existing single reversing valve cannot meet the use requirements of certain large-flow complex hydraulic systems which need proportional reversing and excitation and have certain control precision and dynamic characteristic requirements, and therefore the application range of the existing single reversing valve has certain limitation.
Disclosure of Invention
Technical problem to be solved
The utility model provides a not enough to prior art, the utility model provides a large-traffic electric liquid proportion switching-over excitation dual-purpose valve has solved current single switching-over valve and can not satisfy some not only need proportion switching-over but also need the excitation, have the problem that the large-traffic complicated hydraulic system that certain control accuracy and dynamic characteristic required uses the requirement.
(II) technical scheme
In order to achieve the above purpose, the utility model discloses a following technical scheme realizes: a high-flow electro-hydraulic proportional reversing and exciting dual-purpose valve comprises a valve core rotary proportional reversing valve component, a hydraulic reversing valve component and a microprocessor, the valve core rotary type proportional reversing valve component comprises a secondary valve body, a secondary valve sleeve, a secondary valve core, a rotary motor, a linear motor and an angle sensor, wherein the secondary valve sleeve is arranged in the secondary valve body, and a secondary valve core is arranged in the secondary valve sleeve, one end of the secondary valve core is respectively and fixedly connected with an output shaft of the rotating motor through a rotating shaft and a coupling, one side of the secondary valve body is fixedly connected with one side of the linear motor, one side of the linear motor is fixedly connected with a motor sleeve, one end of the motor sleeve, which is far away from the linear motor, penetrates through the secondary valve body and extends into the secondary valve body, and one end of the motor sleeve, which extends into the secondary valve body, is contacted with one end of the secondary valve core;
the reversing valve subassembly surges includes main valve body, main valve barrel, main case and displacement sensor, the inside at the main valve body is installed to the main valve barrel, and the main case is installed in the inside of main valve barrel, left pressure chamber and right pressure chamber have been seted up respectively to the inside both sides of reversing valve subassembly surges, and the internally mounted of right pressure chamber has the main valve spring, the one end fixedly connected with of main case has the direction locating part with main valve spring looks adaptation.
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, 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 respectively provided with an oil inlet P0, a working oil port a0 and a working oil port B0, the outer oil ports of the oil port a0 and the oil port B0 are oil outlets T0, the oil outlet T0 is communicated with the oil outlet T of the hydraulic reversing valve assembly through an inner chamber 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 port a0 and the oil port B0 are respectively communicated with a left pressure cavity and a right pressure cavity of the hydraulic reversing valve assembly.
Preferably, an output shaft of the rotating motor is fixedly connected with an angle sensor, a detection end of the displacement sensor is fixedly connected with one end of the main-stage valve core, and a wiring end of the microprocessor is electrically connected with wiring ends of the angle sensor and the displacement sensor through conducting 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, a steel ball is movably mounted at the front section of the motor sleeve, a secondary valve spring is fixedly mounted between the rotating shaft and the secondary valve core, a limiting sleeve is mounted between one end of the secondary valve core and the motor sleeve, and the limiting sleeve is fixedly connected with the secondary valve sleeve without relative rotation and displacement.
Preferably, the secondary valve core has two degrees of freedom in two directions, one is driven by a rotating motor to rotate circumferentially, and the other is driven by a linear motor to move axially.
Preferably, the outer surface of the secondary valve element is fixedly connected with shoulders I, II, III and IV from left to right in sequence, a group of radial openings are formed in the left sides of the shoulders I, II, III and IV, four radial openings are arranged in each group 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 a shoulder at the rightmost end of the secondary valve core, and an arc-shaped protrusion block matched with the first arc-shaped notch and the second arc-shaped notch is fixedly connected to the inner wall of the limiting sleeve.
Preferably, the matching relationship between the first arc-shaped notch and the second arc-shaped notch on the shoulder at the rightmost end of the secondary valve core and the arc-shaped protruding block fixedly connected to the inner wall of the limiting sleeve can be changed through the driving of the rotating motor and the linear motor, so that the secondary valve core can be positioned at a zero position and has two-stage axial displacement, the first-stage displacement can realize a proportional reversing mode, the second-stage displacement can realize an excitation reversing mode, and the secondary valve core can be quickly switched according to different working requirements of a hydraulic system.
Preferably, when the linear motor drives the secondary valve core to move axially leftward, a through-flow valve port 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) advantageous effects
The utility model provides a large-traffic electric-hydraulic proportion switching-over excitation dual-purpose valve. Compared with the prior art, the method has the following beneficial effects:
(1) the high-flow electro-hydraulic proportional reversing and exciting dual-purpose valve not only has the advantages of an electro-hydraulic proportional reversing valve, but also can realize excitation, the vibration frequency and the vibration amplitude can be proportionally adjusted, the use requirements of a high-flow complex hydraulic system which needs both proportional reversing and excitation and has certain control precision and dynamic characteristic requirements can be met, the dual-purpose valve adopts the design of a two-stage structure, a pilot secondary valve of the dual-purpose valve is a valve core rotating type proportional reversing valve, a primary valve is a hydraulic reversing valve component, the valve contains two-stage hydraulic power amplification and can sufficiently overcome the hydraulic interference on a main valve, the dual-purpose valve has higher stability when the load changes, the defects of a direct-acting type electro-hydraulic proportional reversing valve for controlling the high-flow hydraulic system are overcome, the dual-purpose valve can be widely applied to the high-flow excitation hydraulic system, and compared with the existing electro, the manufacturing precision requirement and the price are obviously lower than those of an electro-hydraulic servo valve, the anti-pollution performance is better, and the adjustment of the vibration amplitude is obviously better than that of the electro-hydraulic servo valve.
(2) This dual-purpose valve of large-traffic electric-hydraulic proportion switching-over excitation compares with current commentaries on classics valve formula switching-over valve, the special structural design that this dual-purpose valve adopted, but make it zero-setting bit, possess two-stage axial displacement, the proportion switching-over can be realized to first order displacement, the excitation can be realized to the second displacement, can carry out fast switch-over to it according to the different job requirements of hydraulic system, compare with current electromagnetic reversing valve, proportional reversing can be realized to this dual-purpose valve, and is obviously superior to the electromagnetic reversing valve to the regulation precision of vibration frequency and vibration amplitude, different with traditional electric-hydraulic proportion switching-over valve, the utility model discloses a secondary valve and the primary valve of dual-purpose valve all have the valve sleeve structure, and this makes its switching-over control precision have certain.
(3) This dual-purpose valve of large-traffic electric liquid proportion switching-over excitation, through installed angle sensor and displacement sensor on secondary valve and the primary valve of this dual-purpose valve additional respectively, constitute secondary angle-electric feedback + primary displacement-electric feedback's doublestage electric feedback system, greatly improved the control accuracy and the stability of this dual-purpose valve, the return meso position spring of the primary valve case of this dual-purpose valve is owing to adopt unilateral spring cooperation valve barrel design simultaneously, no matter which work position this primary valve case is in, all compress same spring, consequently, this kind of structure need not accurately match two springs, so make this dual-purpose valve have higher performance.
(4) When the linear motor drives the secondary valve core of the dual-purpose valve to move axially leftwards, the through-flow valve port formed by the radial opening on the shoulder of the secondary valve core and the window on the secondary valve sleeve is continuously reduced, namely the through-flow rate is gradually reduced, the through-flow valve port of the general reversing valve is gradually increased along with the movement of the valve core, and meanwhile, the high-precision proportional adjustment can be performed on the vibration frequency and the vibration amplitude of the general reversing valve through the rotating speed of the proportional control rotating motor and the propulsion displacement of the linear motor.
Drawings
Fig. 1 is a schematic structural view of the present invention;
FIG. 2 is a sectional view of the valve core rotary type proportional reversing valve assembly structure of the present invention;
fig. 3 is a schematic structural diagram of the secondary valve element of the present invention;
FIG. 4 is a schematic structural view of the stop collar of the present invention;
FIG. 5 is a perspective sectional view of the valve element rotary type proportional directional valve assembly structure of the present invention;
FIG. 6 is a schematic structural view of the secondary valve element and the stop collar of the present invention;
fig. 7 is a cross-sectional view of the secondary valve element and the side of the 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 part 20, a sleeve coupler 21, a bearing 22, a steel ball 23, a secondary valve spring 24, a limiting sleeve 25, a radial opening 26, a first arc-shaped notch 27, a second arc-shaped notch 28 and an arc-shaped protrusion block 29.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
Referring to fig. 1-7, an embodiment of the present invention provides a technical solution: a high-flow electro-hydraulic proportional reversing and shock excitation dual-purpose valve comprises a valve core rotary proportional reversing valve component 1, a hydraulic reversing valve component 2 and a microprocessor 3, wherein the hydraulic reversing valve component 2 is a primary valve, the valve core rotary proportional reversing valve component 1 is a secondary valve and is suitable for high-flow occasions, the valve core rotary proportional reversing valve component 1 comprises a secondary valve body 8, a secondary valve sleeve 10, a secondary valve core 9, a rotating motor 5, a linear motor 12 and an angle sensor 4, the secondary valve sleeve 10 is installed inside the secondary valve body 8, the secondary valve core 9 is installed inside the secondary valve sleeve 10, one end of the secondary valve core 9 is fixedly connected with an output shaft of the rotating motor 5 through a rotating shaft 7 and a coupling 6, one side of the secondary valve body 8 is fixedly connected with one side of the linear motor 12, a motor sleeve 11 is fixedly connected with one side of the linear motor 12, one end of the motor sleeve 11 far away from the linear motor 12 penetrates through, and one end of the motor sleeve 11 extending to the interior of the secondary valve body 8 is contacted with one end of the secondary valve core 9, and the linear motor 12 pushes the secondary valve core 9 to move axially through the motor sleeve 11 connected with the linear motor.
The hydraulic reversing valve component 2 comprises a main valve body 14, a main valve sleeve 17, a main valve core 16 and a displacement sensor 13, wherein the model of the displacement sensor 13 is ZLDS100, the displacement sensor 13 can accurately detect the axial displacement of the main valve core 16, the main valve sleeve 17 is arranged inside the main valve body 14, the main valve core 16 is arranged inside the main valve sleeve 17, the main valve core 16 is equivalent to a piston of a hydraulic cylinder and has the same dynamic characteristics, a left pressure cavity 15 and a right pressure cavity 18 are respectively arranged on two sides inside the hydraulic reversing valve component 2, a main valve spring 19 is arranged inside the right pressure cavity 18, the main valve spring 19 is used for returning to a middle position, and the single spring design is adopted, so that the same spring is compressed no matter which working position the main valve core 16 is positioned, therefore, the structure does not need to be accurately matched with the two springs, and the dual-purpose valve has higher performance, one end of the main valve element 16 is fixedly connected with a guide limiting piece 20 matched with the main valve spring 19, the guide limiting piece 20 can guide the main valve spring 19 and has 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 respectively the oil port P, the oil port T, the oil port a and the oil port B of the two-way valve, the bottom of the secondary valve body 8 is respectively provided with an oil inlet P0, a working oil port a0 and a working oil port B0, the oil outlet T0 is communicated with the oil outlet T of the hydraulic reversing valve assembly 2 through an internal cavity and a passage of the valve core rotary type proportional reversing valve assembly 1, the oil port P0 of the valve core rotary type proportional reversing valve assembly 1 is communicated with the oil inlet P of the hydraulic reversing valve assembly 2, the oil port A0 and the oil port B0 are respectively communicated with the left pressure cavity 15 and the 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 axially left and right and respectively correspond to the left working position and the right working position of the hydraulic reversing valve assembly 2, namely the left working position and the right working position of the dual-purpose valve, 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, the terminal of the microprocessor 3 is, 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, thereby the necessary adjustment can be made to the working parameters of the dual-purpose valve according to the working requirement and the required relevant characteristics of the dual-purpose valve, so as to form the closed-loop dual-feedback proportional control of the dual-purpose valve, obviously, the dual-purpose valve has higher dynamic performance, 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 the, the main purpose of the steel ball 23 is to reduce the friction resistance between the motor housing 11 and the secondary valve element 9 when the rotary motor 5 drives the secondary valve element 9 to rotate through the rotating shaft 7, so that the secondary valve element 9 has better rotation performance, and a secondary valve spring 24 is fixedly installed between the rotating shaft 7 and the secondary valve element 9, the primary function of the secondary valve spring 24 is to relieve the impact force caused by the linear motor 12 pushing the secondary valve element 9 to move axially leftward through the motor housing 11, and at the same time, the secondary valve spring 24 can provide a certain return elastic force when the linear motor 12 retracts, so as to push the secondary valve element 9 to move axially rightward to return to a zero position, a limit sleeve 25 is installed between one end of the secondary valve element 9 and the motor housing 11, and the limit sleeve 25 is fixedly connected with the secondary valve housing 10, and has no relative rotation or displacement, the limit sleeve 25 is used for limiting the rotation angle of the secondary valve element 9, so that the secondary valve element 9 can only rotate forward, the secondary valve core 9 has two degrees of freedom in two directions corresponding to the left working position and the right working position of the valve core rotary type proportional reversing valve component 1 respectively, one is that the secondary valve core 9 is driven to rotate circumferentially by the rotary motor 5, the other is that the secondary valve core 9 is driven to move axially by the linear motor 12, 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, the left sides of the shoulders I, II, III and IV are respectively provided with a group of radial openings 26, each group of radial openings 26 is four in the circumferential direction, two adjacent groups of radial openings 26 are staggered mutually in the axial direction, the staggered angle is 45 degrees, the right-end shoulder of the secondary valve core 9 is respectively provided with a first arc-shaped notch 27 and a second arc-shaped notch 28, and the inner wall of the limit sleeve 25 is fixedly connected with an arc-shaped protrusion block 29 matched with the first arc-shaped notch 27 and the second arc-, wherein different cooperation corresponds different work positions, it is to be noted that the axis at the bottom center of second arc incision 28 staggers completely with the axis at all radial openings 26 on circular bead I, II, III, IV again, there is a recess at the rightmost end of this secondary case 9, its effect lies in placing steel ball 23 on the motor cover 11, thereby make things convenient for linear electric motor 12 to promote secondary case 9 and remove when moving, can not influence rotating electrical machines 5 and drive secondary case 9 and rotate, thereby guaranteed the normal switching work of case structure.
The specific working principle of the utility model is explained as follows:
the utility model discloses well stop collar 25 is installed in the inside of secondary valve barrel 10, and does not have relative motion, and the plane at the protruding piece 29 place of arc of this stop collar 25 and the plane at secondary valve barrel 10 window place belong to the coplanar, and following will be to linear electric motor 12 zero-bit, stretch out and return the different work positions of case rotation type proportional reversing valve 1 that these three kinds of work positions correspond and elaborate:
1) linear motor at zero position
When the linear motor 12 is in a zero position, the arc-shaped protruding block 29 inside the limiting sleeve 25 is just clamped at the bottom center of the second arc-shaped notch 28 on the shoulder at the rightmost end 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 axis of all the radial openings 26 on the shoulders i, ii, iii and iv, at this time, a through-flow valve port cannot be formed between all the 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, at this time, all the valve ports of the valve core rotary type proportional reversing valve assembly 1 are in a closed state, and cannot be filled with oil, at this time, the corresponding valve core rotary type proportional reversing valve assembly 1 is in a middle position, and the middle position can be in an 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 is driven to push the secondary valve core 9 to move axially leftwards, and at the moment, the two-stage displacement can be divided into two stages which respectively correspond to different working modes, and the detailed explanation is as follows:
(1) first stage displacement-proportional reversing mode
The secondary valve core 9 is pushed to move axially leftwards along with the extension of the linear motor 12, when the linear motor 12 is in a zero position, the arc-shaped protruding block 29 in the limiting sleeve 25 is just clamped at the bottom center of the second arc-shaped notch 28 on the shoulder at the rightmost end of the secondary valve core 9, but when the secondary valve core 9 moves axially leftwards, the bottom center of the second arc-shaped notch 28 on the shoulder at the rightmost end of the secondary valve core 9 is gradually separated from the arc-shaped protruding block 29 in the limiting sleeve 25 until the secondary valve core is completely separated from the constraint of the whole second arc-shaped notch 28, namely, the primary displacement.
At this moment, the arc-shaped protrusion block 29 inside the stop collar 25 has completely separated from the constraint of the whole second arc-shaped notch 28, but at the same time, the constraint of the first arc-shaped notch 27 is received, so the secondary spool 9 can rotate forward and backward within a certain angle range under the driving of the rotating electrical machine 5, the utility model discloses the set angle range is 45 °, and the following explains the different working positions of the spool rotary type proportional reversing valve assembly 1 corresponding to the two working states of forward rotation and reverse rotation of the rotating electrical machine 5:
i rotating electric machine positive rotation (anticlockwise) -left working position
After the first-stage displacement is completed, the rotating motor 5 rotates forward by a certain angle until the arc-shaped protrusion block 29 inside the limiting 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 spool 9, at this time, the secondary valve spool 9 is limited and cannot rotate any more, at this time, the radial openings 26 on the shoulder ii and the shoulder iv of the secondary valve spool 9 and the window on the secondary valve sleeve 10 form a through-flow valve port, so that the hydraulic oil which cannot pass originally can smoothly flow through the valve port, the hydraulic oil has a specific flow direction, the hydraulic oil flows in from the oil port P0 of the valve spool rotary type proportional reversing valve assembly 1, the oil port P0 is connected with the oil port P of the primary valve which is hydraulically switched to the valve assembly 2, namely the oil inlet P of the whole dual-purpose valve, and then flows into the oil port a0 through the through-flow valve port on the shoulder, the oil port a0 is connected to the left pressure chamber 15 of the main stage valve hydraulic directional valve assembly 2, which pushes the main stage valve core 16 to move axially to the right, and the return oil of the right pressure chamber 18 flows through the oil port B0, through the through-flow valve port on the shoulder iv of the secondary valve core 9, flows into the oil port T0, then flows through the internal chamber and the passage of the dual-purpose valve, and finally flows into the oil tank, and the oil path communication direction is: p0 and A0 are communicated, B0 and T0 are communicated, and the left working position of the valve core rotary type proportional reversing valve component 1 corresponds to.
Ii rotating electric machine reverse rotation (clockwise) -right working position
After the first-stage displacement is completed, the rotating motor 5 rotates reversely by a certain angle until the arc-shaped protrusion block 29 inside the limiting 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 spool 9, at this time, the secondary valve spool 9 is limited and cannot rotate any more, at this time, the radial openings 25 on the shoulder i and the shoulder iii of the secondary valve spool 9 and the window on the secondary valve sleeve 10 form a through-flow valve port, so that the hydraulic oil which cannot pass originally can smoothly flow through the valve port, the hydraulic oil has a specific flow direction, the hydraulic oil flows in from the oil port P0 of the valve spool rotary type proportional reversing valve assembly 1, the oil port P0 is connected with the oil port P of the primary valve hydraulic switching valve assembly 2, namely the oil inlet P of the whole dual-purpose valve, and then flows into the oil port B0 through the through-flow valve port on the shoulder iii of the secondary, the oil port B0 is connected to the right pressure chamber 15 of the main valve hydraulic directional valve assembly 2, which pushes the main valve core 16 to move axially leftward, and the return oil from the left pressure chamber 15 flows through the oil port a0, through the through-flow valve port on the shoulder i of the secondary valve core 9, into the oil port T0, then through the internal chamber and the passage of the dual-purpose valve, and finally into the oil tank, and the oil path communication direction is: p0 and B0 are communicated, A0 and T0 are communicated, and the right working position of the valve core rotary type proportional reversing valve component 1 corresponds to.
(2) Second stage displacement-excitation reversing mode
Then, with the further extension of the linear motor 12, the contact surface between the first arc-shaped notch 27 and the second arc-shaped notch 28 on the secondary valve core 9 will gradually separate from the arc-shaped protrusion block 29 inside the position-limiting sleeve 25, and finally the arc-shaped protrusion block 29 inside the position-limiting sleeve 25 will completely separate from the constraint of the first arc-shaped notch 27, and at this time, the secondary valve core 9 will not be bound by the position-limiting sleeve 25 at all, so that the rotary motor 5 can drive the secondary valve core 9 to rotate uninterruptedly at a specific speed, and the through-flow valve ports formed by the radial openings 25 on the lands i, ii, iii, iv of the secondary valve core 9 and the window on the secondary valve sleeve 10 will be continuously opened and closed, wherein the lands i and iii are in one group, the lands ii and iv are in one group, and the opening and closing conditions of the same group are consistent, and because the rotary motor 5 drives the secondary valve core, the liquid flow of the valve core rotary type proportional reversing valve component 1 is continuously reversed, the main valve core 16 of the main valve hydraulic reversing valve component 2 is continuously moved in the left-right axial direction, the liquid flow of the hydraulic reversing valve component 2 is continuously reversed, namely the liquid flow of the dual-purpose valve is continuously reversed, and finally the hydraulic cylinder connected with the dual-purpose valve is continuously reversed in the left-right axial direction, at the moment, vibration is generated due to high-frequency reversing, the vibration frequency of the valve can be proportionally controlled by proportionally controlling the rotating speed of the rotating motor 5, the vibration amplitude of the valve can be proportionally controlled by proportionally controlling the axial displacement of the linear motor 12, and at the moment, the corresponding mode is the vibration exciting mode of the valve core rotary type proportional reversing valve component 1.
3) The linear motor is in the retracted position
The retraction process of the linear motor 12 in the case of the second-stage displacement is discussed here, and naturally, the retraction from the first-stage displacement is also included, so that the retraction from the first-stage displacement is not discussed separately, and with the retraction of the linear motor 12, the secondary spool 9 is pushed to move axially to the right by the resilience force of the secondary valve spring 24, and since the secondary spool 9 rotates to any stop position after undergoing the uninterrupted rotation in the excitation mode, there are two cases, which are described below:
first case
The arc-shaped protruding block 29 in the limiting 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 center of the bottom along the arc-shaped surface of the first arc-shaped notch 27 under the action of the resilience force of the secondary valve spring 24.
Second case
The arc-shaped protrusion 29 inside the stop collar 25 first touches the second arc-shaped notch 28 on the secondary spool 9, at this time, the secondary spool 9 will easily slide into the first arc-shaped notch 27 along the arc surface of the second arc-shaped notch 28 under the effect of the resilience force of the secondary valve spring 24, and at this time, the first situation is changed, the secondary spool 9 will easily slide into the bottom center along the arc surface of the first arc-shaped notch 27 finally under the effect of the resilience force of the secondary valve spring 24, and similarly, as can be seen from the above detailed description of the working state when the linear motor 12 is in the zero position, the corresponding position at this time is the middle position of the spool rotary type proportional reversing valve assembly 1, and the middle position function is "O" type, and oil cannot be introduced.
Therefore, as can be seen from the above description, the two situations are quite different in nature, and finally, the secondary spool 9 returns to the zero position, i.e. the neutral position of the spool-type proportional reversing valve assembly 1, under the resilient force of the secondary valve spring 24.
It is noted that, herein, relational terms such as first and second, and the like may be 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. Also, 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 appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (10)
1. The utility model provides a large-traffic electric liquid proportion switching-over excitation dual-purpose valve, includes case rotation type proportion switching-over valve subassembly (1), switching-over valve subassembly (2) and microprocessor (3) that surges, its characterized in that: the valve core rotary type proportional reversing valve component (1) comprises a secondary valve body (8), a secondary valve sleeve (10), a secondary valve core (9), a rotating motor (5), a linear motor (12) and an angle sensor (4), wherein the secondary valve sleeve (10) is installed inside the secondary valve body (8), the secondary valve core (9) is installed inside the secondary valve sleeve (10), one end of the secondary valve core (9) is fixedly connected with an output shaft of the rotating motor (5) through a rotating shaft (7) and a coupler (6), 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, far away from the linear motor (12), of the motor sleeve (11) penetrates through the secondary valve body (8) and extends into the secondary valve body (8), and one end, extending into the secondary valve body (8), of the motor sleeve (11) is contacted with one end of the secondary valve core (9);
the hydraulic reversing valve assembly (2) comprises a main valve body (14), a main valve sleeve (17), a main valve core (16) and a displacement sensor (13), the main valve sleeve (17) is installed in the main valve body (14), the main valve core (16) is installed in the main valve sleeve (17), a left pressure cavity (15) and a right pressure cavity (18) are respectively formed in two sides of the interior of the hydraulic reversing valve assembly (2), a main valve spring (19) is installed in the interior of the right pressure cavity (18), and one end of the main valve core (16) is fixedly connected with a guide limiting part (20) matched with the main valve spring (19).
2. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 1, characterized in that: 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), 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 and excitation dual-purpose valve according to claim 1, characterized in that: an oil inlet P0, a working oil port A0 and a working oil port B0 are respectively formed in the bottom of the secondary valve body (8), the outer oil ports of the oil port A0 and the oil port B0 are oil outlets T0, the oil outlet T0 is communicated with an 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), the 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), and the oil port A0 and the 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).
4. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 1, characterized in that: the output shaft of the rotating motor (5) is fixedly connected with an angle sensor (4), the detection end of a displacement sensor (13) is fixedly connected with one end of a main-stage valve core (16), and the wiring end of the microprocessor (3) is electrically connected with the wiring ends of the angle sensor (4) and the displacement sensor (13) through conducting wires respectively.
5. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 1, characterized in that: the one end of pivot (7) is passed through sleeve coupling (21) and the one end fixed connection of secondary case (9), and one side fixedly connected with of secondary valve body (8) inner wall and bearing (22) of pivot (7) looks adaptation, the front end movable mounting of motor cover (11) has steel ball (23), and fixed mounting has time valve spring (24) between pivot (7) and secondary case (9), install stop collar (25) between the one end of secondary case (9) and motor cover (11), and stop collar (25) and secondary valve barrel (10) fixed connection, no relative rotation and displacement.
6. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 1, characterized in that: the secondary valve core (9) has two-direction freedom degrees, one is that the secondary valve core (9) is driven to rotate circumferentially by the rotating motor (5), and the other is that the secondary valve core (9) is driven to move axially by the linear motor (12).
7. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 1, characterized in that: the outer surface of the secondary valve core (9) is fixedly connected with shoulders I, II, III and IV sequentially from left to right, a group of radial openings (26) are formed in the left sides of the shoulders I, II, III and IV, four radial openings (26) are formed in each group along the circumferential direction, two adjacent groups of radial openings (26) are staggered in the axial direction, and the staggered angle is 45 degrees.
8. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 1 or 5, characterized in that: 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 protrusion block (29) matched with the first arc-shaped notch (27) and the second arc-shaped notch (28) is fixedly connected to the inner wall of the limiting sleeve (25).
9. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 8, characterized in that: through the driving of the rotating motor (5) and the linear motor (12), the matching relation between the first arc-shaped notch (27) and the second arc-shaped notch (28) on the shoulder at the rightmost end of the secondary valve core (9) and the arc-shaped protruding block (29) fixedly connected to the inner wall of the limiting sleeve (25) can be changed, so that the secondary valve core can be set to a zero position and has two-stage axial displacement, the first-stage displacement can realize a proportional reversing mode, the second-stage displacement can realize an excitation reversing mode, and the secondary valve core can be quickly switched according to different working requirements of a hydraulic system.
10. The high-flow electro-hydraulic proportional reversing and excitation dual-purpose valve according to claim 1 or 7, characterized in that: when the linear motor (12) drives the secondary valve core (9) to move axially leftwards, a through-flow valve port formed by a radial opening (26) on the shoulder of the secondary valve core (9) and a window on the secondary valve sleeve (10) is continuously reduced.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201921259961.9U CN210461782U (en) | 2019-08-05 | 2019-08-05 | Large-flow electro-hydraulic proportional reversing and exciting dual-purpose valve |
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| CN201921259961.9U CN210461782U (en) | 2019-08-05 | 2019-08-05 | Large-flow electro-hydraulic proportional reversing and exciting dual-purpose valve |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110319238A (en) * | 2019-08-05 | 2019-10-11 | 安徽理工大学 | A kind of big flow electric-hydraulic proportion commutation exciting dual-purpose valve |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110319238A (en) * | 2019-08-05 | 2019-10-11 | 安徽理工大学 | A kind of big flow electric-hydraulic proportion commutation exciting dual-purpose valve |
| CN110319238B (en) * | 2019-08-05 | 2024-03-22 | 安徽理工大学 | High-flow electrohydraulic proportional reversing excitation dual-purpose valve |
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