CN113153852B - Direction and flow combined type high-frequency response proportional rotary valve - Google Patents
Direction and flow combined type high-frequency response proportional rotary valve Download PDFInfo
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- CN113153852B CN113153852B CN202110333564.7A CN202110333564A CN113153852B CN 113153852 B CN113153852 B CN 113153852B CN 202110333564 A CN202110333564 A CN 202110333564A CN 113153852 B CN113153852 B CN 113153852B
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- 230000004044 response Effects 0.000 title claims abstract description 20
- 230000005540 biological transmission Effects 0.000 claims abstract description 9
- 239000003921 oil Substances 0.000 claims description 48
- 239000010720 hydraulic oil Substances 0.000 claims description 7
- 238000000034 method Methods 0.000 claims description 7
- 230000008569 process Effects 0.000 claims description 6
- 230000004323 axial length Effects 0.000 claims description 3
- 230000002457 bidirectional effect Effects 0.000 claims description 3
- 150000001875 compounds Chemical class 0.000 claims 3
- 230000010349 pulsation Effects 0.000 abstract description 2
- 230000001105 regulatory effect Effects 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 7
- 238000009826 distribution Methods 0.000 description 6
- 230000009471 action Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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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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Abstract
A direction and flow combined type high-frequency response proportional rotary valve comprises a main motor, a secondary motor, two end covers, a transmission cover plate, a valve seat, a valve sleeve, a valve core, a left valve plate, a right valve plate, a left screw shaft, a right screw shaft, a left screw thread, a right screw thread, a left valve plate, a right valve plate, a left valve plate, a right valve sleeve, a left valve plate, a right valve plate, a left valve core and a right valve plate. On one hand, the servo motor is used as a driving element to realize the on-off of the valve port, on the other hand, the high-frequency reversing function and the flow regulation are realized through the matching of the valve sleeve, the valve core and the valve plate, the working frequency of the hydraulic valve is improved, and the rotary inertia of a mechanical part is reduced by adopting a valve sleeve rotating mode; the valve plates at two ends of the valve core ensure that the impact force of axial oil is effectively balanced when the flow is regulated; the oil inlet and the oil outlet are symmetrically distributed to reduce radial hydraulic moment and flow pulsation of the valve body part.
Description
Technical Field
The invention belongs to the field of high-frequency hydraulic valves, and particularly relates to a direction and flow combined high-frequency response proportional rotary valve.
Background
The rotary electro-hydraulic proportional valve is a direct-acting single-stage valve with a power-stage valve core directly pushed by an electromechanical converter, and has the advantages of compact structure, strong pollution resistance, high reliability, convenience in maintenance and the like, and the development prospect is wide. But compared with a multistage valve, the frequency response of the single-stage valve is not high, and the output flow is low. And because the radial force of the rotary valve is unbalanced, the operating force required by the rotary valve core is large, and the sealing performance is poor, the rotary valve is generally used in low-pressure and small-flow occasions or used as a pilot valve. Particularly, on test equipment requiring high-frequency vibration, the actuating cylinder needs high-frequency stable action, and the imported high-frequency valve is adopted at present, so that the manufacturing cost is high and limited. Therefore, research and development of the rotary type proportional valve, particularly the single-stage, high-frequency-response and large-flow rotary type electro-hydraulic proportional valve, is an important direction for development of the electro-hydraulic proportional valve, and can solve the great requirements of the fields of forging and pressing industry, fatigue detection and the like in China on high-frequency-response proportion and servo valves.
Disclosure of Invention
In order to overcome the disadvantages of the prior art, the present invention provides a direction and flow combined high frequency response ratio rotary valve, which uses two ac servo motors as the driving elements of the valve, wherein the main motor is used for driving the rotation of the valve sleeve, and the secondary motor is used for adjusting the position of the valve plate. The rotary valve is composed of a mechanical body and a motor control part, wherein the mechanical body part takes an alternating current servo motor as an electric-mechanical converter, and a valve core, a valve plate, a valve sleeve and the like form an action executing assembly of the valve; the output flow of the valve is adjusted by adopting a spiral mechanism and realizing that the symmetrically arranged valve plates do linear motion through the rotation of the secondary motor.
In order to achieve the purpose, the technical scheme provided by the invention is as follows:
a direction and flow combined type high-frequency response proportional rotary valve comprises a main motor, a secondary motor, a left end cover, a right end cover, a transmission cover plate, a valve seat, a valve sleeve, a valve core, a trapezoidal left and right threaded shaft, a left valve plate, a right valve plate, a deep groove ball bearing and a fixed support; the valve sleeve is arranged in the valve seat, two through holes which are symmetrically distributed at 180 degrees are arranged in the circumferential radial direction at intervals of fixed axial length, and 8 through holes are formed in total, namely four groups of symmetrical oil ports; the inner cylindrical surface of the valve sleeve is matched with the outer cylindrical surface of the valve core, the outer cylindrical surface is matched with the inner cylindrical surface of the valve seat, the valve core is arranged in the valve sleeve and is fixedly positioned with the deep groove ball bearing through the valve seat, the opening position of the valve seat is the same as that of the valve sleeve, and four groups of 8 blind holes in the radial direction are formed in the cylindrical surface of the valve core; the axial positions of the four groups of holes are the same as those of the valve seat and the valve sleeve, and the tail ends of the eight holes which are symmetrically distributed in the radial direction are communicated with the other three groups of holes in the axial direction through eight internal flow passages; two pairs of deep groove ball bearings are connected between the valve core and the valve sleeve; the left-handed trapezoidal thread is matched with the left valve plate, and the right-handed trapezoidal thread is matched with the right valve plate; the left end mounting part of the trapezoidal left and right threaded shafts is connected with a motor output shaft of the secondary motor through a flat key; the secondary motor is fixed with the left end cover through a first bolt and a second bolt, and a pair of angular contact ball bearings which are arranged face to face are connected between the left end cover and the trapezoidal left and right threaded shafts and are respectively a first angular contact ball bearing and a second angular contact ball bearing; the left end cover, the valve seat and the valve core are connected and fastened with the fixed support through bolts.
Furthermore, four groups of two through holes which are equidistantly arranged in the axial direction and symmetrically distributed at intervals of 45 degrees in the radial direction are formed in the valve sleeve; the position of the opening of the valve seat is the same as that of the valve sleeve, namely, two holes in the radial direction are symmetrically distributed at 180 degrees, every two holes in each row of axial symmetrical holes are spaced at 45 degrees at the same distance, and each pair of symmetrical holes are respectively an external oil port P, an external oil port T, an external oil port A and an external oil port B.
Furthermore, the outer side of the radial hole is provided with an annular groove with a certain depth on the outer cylindrical surface of the valve sleeve, so that each annular groove is communicated with the oil port of the valve seat, when the valve sleeve rotates, the outer oil port is communicated with the valve core without rotating to the position of the oil port on the valve seat, and the response process is accelerated.
Furthermore, four groups of 8 blind holes in the radial direction are formed in the cylindrical surface of the valve core, and the axial positions of the four groups of blind holes are the same as those of the valve seat and the valve sleeve; and the tail ends of the eight holes symmetrically distributed in the radial direction are communicated with the other three groups in the axial direction through eight internal flow passages.
Furthermore, the two ends of the valve core, the left valve plate and the right valve plate form four independent sector cavities through the cross special-shaped grooves, when oil enters and the valve sleeve rotates for a certain angle, the oil port communicated with the valve cavity is changed, and the direction change of the hydraulic oil way is realized.
Furthermore, the deep groove ball bearing is arranged between the valve seat and the valve sleeve to bear the radial load and a certain bidirectional axial load of the rotary valve body; the first angular contact ball bearing and the second angular contact ball bearing are arranged between the left and right trapezoidal threaded shafts and the left end cover and bear axial and radial loads on the threaded shafts at the same time; the rotary valve body is fixed by bolts, and the transmission cover plate is connected with the valve sleeve by hexagon socket head cap screws.
Compared with the prior art, the invention has the beneficial effects that:
the rotary valve of the invention uses the servo motor as a driving element to realize the on-off of the valve port on one hand, and realizes the high-frequency reversing function and the flow regulation through the matching of the valve sleeve, the valve core and the valve plate on the other hand. The valve sleeve rotating mode is skillfully adopted under the condition of improving the working frequency of the hydraulic valve, so that the rotational inertia of a mechanical part is effectively reduced; the valve plates are symmetrically arranged at two ends of the valve core and used for balancing the impact force of axial oil liquid when the flow is regulated; the radial hydraulic moment and the flow pulsation phenomenon of the valve body part are reduced by the way that the oil inlet and the oil outlet are symmetrically distributed.
Compared with the prior art, the rotary valve structure provided by the invention has the advantages that the main servo motor drives the valve sleeve to rotate at a constant speed, the flow area formed by the cooperation of the valve sleeve and the valve core is periodically changed, and the flow rate and the direction of oil entering and exiting the reversing valve are periodically changed. The 8 oil ports which are symmetrically designed are matched with the flow passages to be switched on and off, so that the reversing frequency of the rotary valve can be greatly improved, and the rotary valve actually executes four reversing periods when the servo motor drives the valve sleeve to rotate for one circle. The annular grooves with certain depth are formed in the outer side of the outer cylindrical surface hole of the valve sleeve, so that each annular groove is communicated with the oil port of the valve seat, when the valve sleeve rotates, the outer oil port is communicated with the valve core without rotating to the position of the oil port on the valve seat, and the response process is accelerated.
When the secondary motor rotates, the left valve plate and the right valve plate move linearly in opposite directions or in reverse directions on the threaded shaft through threaded connection with the threaded shaft. Through the schematic structural diagram of the rotary valve shown in fig. 1, it can be known that the valve sleeve is a main rotating part, and the valve sleeve and the valve body and the valve core simultaneously keep the contact of the cylindrical surfaces in the rotating process, so that pressure equalizing grooves are processed on the outer cylindrical surface of the valve core and the outer cylindrical surface of the valve sleeve to improve the mechanical sealing performance, and balance the radial hydrodynamic force better.
Drawings
FIG. 1 is a schematic structural diagram of a direction and flow compounded high frequency response ratio rotary valve of the present invention.
FIG. 2 is a schematic representation of the hydraulic graphic symbol of the present invention.
Fig. 3 is a schematic structural view of the valve sleeve of the present invention, wherein (a) is a front view and (b) is a sectional view a-a of (a).
FIG. 4 is a schematic view of the flow channel structure of the present invention.
Fig. 5 is a schematic diagram of the operation of the rotary valve of the present invention, wherein (a) is the initial position of the flow passage and (b) is the position of the flow passage after the valve housing is rotated through a fixed angle.
FIG. 6 is a view showing the adjustment of the height of the port chambers at both ends of the pair of left and right valve plates and the trapezoidal left and right screw shafts, wherein (a) is the initial position of the port chamber and (b) is the adjusted position of the port chamber.
Detailed Description
The present invention is described in more detail below by way of examples, but it should not be construed that the scope of the subject matter described above is limited to the examples described below, and that techniques implemented based on the subject matter described above are within the scope of the present invention.
The terms "upper, lower, inner and outer" and the like refer to orientations and positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the present invention. Terms such as "mounted, connected" are to be understood in a broad sense, for example: can be fixedly connected, detachably connected or integrally connected; they may be mechanically, electrically, or directly connected, or indirectly connected through intervening media, or may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those of ordinary skill in the art.
In the embodiment, as shown in fig. 1, a direction and flow combined type high-frequency response proportional rotary valve comprises a main motor 11, a secondary motor 1, a left end cover 20, a right end cover 8, a transmission cover plate 9, a valve seat 5, a valve sleeve 6, a valve core 2, a trapezoidal left and right threaded shaft 27, a left valve plate 3, a right valve plate 7, a deep groove ball bearing 4, a fixing support 10 and the like, wherein a motor output shaft of the main motor 11 is connected with the transmission cover plate 9 through a key groove 12, the transmission cover plate 9 is connected with the valve sleeve 6 through a bolt so as to transmit the rotary motion output by the main motor, the valve sleeve 6 is arranged in the valve seat 5, two through holes symmetrically distributed at 180 degrees are arranged at intervals of fixed axial length in the circumferential radial direction, the total number of 8 through holes is four groups of symmetrical oil ports, the inner cylindrical surface of the valve sleeve 6 is matched with the outer cylindrical surface of the valve core 2, the cylindrical surface is matched with the inner cylindrical surface of the valve seat 5, the valve core 2 is arranged in the valve sleeve 6 and is fixedly positioned with the deep groove ball bearing 4 through the valve seat 5, the opening position of the valve seat 5 is the same as that of the valve sleeve, the cylindrical surface of the valve core 2 is provided with 8 blind holes in four groups, the number of the blind holes is 32, the number of the blind holes is in the radial direction, the axial positions of the four groups of blind holes are the same as that of the valve seat 5 and the valve sleeve 6, and the tail ends of eight holes symmetrically distributed in the radial direction are communicated with the other three groups of blind holes through eight internal flow channels in the axial direction. Two pairs of deep groove ball bearings 4 are connected between the valve core 2 and the valve sleeve 6. The inner part of the valve core 2 is a hollow structure for placing a trapezoidal left and right threaded shaft 27, trapezoidal threads with left and right turns are respectively processed at two ends of the shaft of the trapezoidal left and right threaded shaft 27, threaded parts are respectively matched and installed with the left valve plate 3 and the right valve plate 7, the left end installation part of the trapezoidal left and right threaded shaft 27 is connected with the motor output shaft of the secondary motor 1 through a flat key 26, the secondary motor 1 is fixed with the left end cover 20 through a first bolt 21 and a second bolt 22, and a pair of angular contact ball bearings which are a first angular contact ball bearing 23 and a second angular contact ball bearing 24 are connected between the left end cover 20 and the trapezoidal left and right threaded shaft 27 in a face-to-face installation manner. The left end cover 20, the valve seat 5 and the valve core 2 are connected and fastened with the fixed support 10 through bolts.
In the embodiment, four groups of two through holes are symmetrically distributed at intervals of 45 degrees in the radial direction and are equidistant in the axial direction on the valve sleeve 6. The position of the opening of the valve seat 5 is the same as that of the valve sleeve 6, namely, two holes in the radial direction are symmetrically distributed at 180 degrees, the symmetrical holes in each row in the axial direction are spaced at 45 degrees at intervals at the same distance, and each pair of the symmetrical holes is respectively an external oil port P, an external oil port T, an external oil port A and an external oil port B.
In the embodiment, the annular grooves with a certain depth are formed in the outer side of the radial hole on the outer cylindrical surface of the valve sleeve 6, so that each annular groove is communicated with the oil port of the valve seat, when the valve sleeve 6 rotates, the outer oil port is communicated with the valve core 2 without rotating to the position of the oil port on the valve seat 5, and the response process is accelerated.
In the embodiment, the cylindrical surface of the valve core 2 is provided with four groups of 8 blind holes with 32 blind holes in the radial direction, wherein the axial positions of the four groups of blind holes are the same as those of the valve seat 5 and the valve sleeve 6. And the tail ends of the eight holes symmetrically distributed in the radial direction are communicated with the other three groups in the axial direction through eight internal flow passages.
As the preferred scheme, two ends of the valve core 2, the left valve plate 3 and the right valve plate 7 form four independent sector cavities through a cross-shaped irregular groove, and when oil enters and the valve sleeve 6 rotates for a certain angle, an oil port communicated with the valve cavity is changed, so that the reversing of a hydraulic oil circuit is realized.
In the embodiment, a deep groove ball bearing 4 is arranged between a valve seat 5 and a valve sleeve 6 to bear the radial load of the valve body and a certain bidirectional axial load. The first angular contact ball bearing 23 and the second angular contact ball bearing 24 are installed between the trapezoidal left and right threaded shafts 27 and the left end cover 20, and bear axial and radial loads on the threaded shafts. The valve body is fixed by bolts, and the transmission cover plate 9 is connected with the valve sleeve 6 by inner hexagon screws.
In the rotary valve structure provided by the invention, the main servo motor drives the valve sleeve to rotate at a constant speed, the size of an overflowing area formed by matching the valve sleeve and the valve core is periodically changed, and the flow size and the direction of oil liquid entering and exiting the reversing valve are also periodically changed. The 8 oil ports of symmetrical design and the cooperation break-make of runner can greatly improve the switching-over frequency of rotary valve, and when servo motor drove the valve barrel and rotated a week, the rotary valve actually executed four switching-over periods.
The working principle of the invention is as follows:
when the main motor rotates, taking the connection between the port P and the port a and the connection between the port B and the port T for oil return as an example, the flow diagrams of the valve body on the four sections of the port P, the port T, the port a and the port B are shown in fig. 4 (a), (B), (c) and (d), respectively, the left side of each diagram is an axial sectional view, the right side of each diagram is a radial sectional view, and black arrows in the diagram are the trend of hydraulic oil in a flow channel.
The two ends of the valve core 2, the left valve plate 3 and the right valve plate 7 form four independent fan-shaped cavities through the cross special-shaped grooves, when oil enters the valve, as shown in the left side of the figure 5, and when the valve sleeve rotates by a certain angle, an oil port communicated with the valve cavity is changed, namely, as shown in the right side of the figure 3, so that the reversing of a hydraulic oil way is realized.
The valve sleeve 6 has the same opening position as the valve seat, namely, two holes in the radial direction are symmetrically distributed at 180 degrees, and every axial symmetrical hole in each row is at the same distance and is at 45 degrees as shown in fig. 3. On the outer cylindrical surface of the valve sleeve, an annular groove with a certain depth is formed in the outer side of the radial hole, as shown in (a) of fig. 4, so that each annular groove is communicated with the oil port of the valve seat, when the valve sleeve rotates, the outer oil port is communicated with the valve core without rotating to the position of the oil port on the valve seat, and the response process is accelerated.
The main motor M1 controls the reversing of the valve body and the valve port flow characteristics, and the secondary motor M2 realizes the valve port flow change by adjusting the position of the valve plate.
Through the graph of fig. 4, it can be known that the hydraulic oil enters the valve seat, the valve sleeve and the valve core from the radial direction, and then enters the flow distribution cavity formed by the valve core and the valve plate from the interior of the valve core along the axial circular flow channel. Two ends of the valve core and the valve plate form four independent sector cavities through the cross special-shaped grooves, when oil enters the valve, as shown in the left side of the figure 5, and when the valve sleeve rotates for a certain angle, an oil port communicated with the valve cavity is changed, namely as shown in the right side of the figure 5, so that the reversing of a hydraulic oil way is realized.
The height of the left and right valve plates and the flow distribution chambers at the two ends of the trapezoidal left and right threaded shaft pair is adjusted as shown in fig. 6, when the left and right valve plates move oppositely on the threaded shaft, the height of the flow distribution chambers is reduced, and when the left and right valve plates move reversely, the height of the flow distribution chambers is increased as shown at the right side of fig. 6. The height of the flow distribution cavity is changed through the secondary motor, so that the flow of the valve port is adjusted.
In order to reduce the processing, manufacturing and maintenance costs under the condition of high pressure and large flow rate, the rotary valve provided by the invention selects the permanent magnet synchronous alternating current proportional motor as a primary driving element and a secondary driving element, and adopts symmetrical valve ports and multi-channel distribution on the valve body structure, so that the working frequency of the rotary valve is improved to be four times of the rotating speed of the motor. In the main work, only the valve sleeve rotates at a high speed, so that the rotational inertia and the energy consumption of the system are reduced. Therefore, the rotary valve mainly comprises two parts, namely a valve body mechanical structure part and a main and secondary driving motor part.
The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention in any way, and any simple modifications, equivalents and improvements made by those skilled in the art without departing from the technical scope of the present invention are all within the scope of the present invention.
Claims (4)
1. The utility model provides a direction and flow combined type high frequency response proportion rotary valve which characterized in that: the valve comprises a main motor (11), a secondary motor (1), a left end cover (20), a right end cover (8), a transmission cover plate (9), a valve seat (5), a valve sleeve (6), a valve core (2), a trapezoidal left and right threaded shaft (27), a left valve plate (3), a right valve plate (7), a deep groove ball bearing (4) and a fixing support (10); the valve sleeve (6) is arranged in the valve seat (5), two through holes which are symmetrically distributed at 180 degrees are formed in the circumferential radial direction at intervals of fixed axial length, and 8 through holes are formed in total, namely four groups of symmetrical oil ports; the inner cylindrical surface of the valve sleeve (6) is matched with the outer cylindrical surface of the valve core (2), the outer cylindrical surface of the valve sleeve (6) is matched with the inner cylindrical surface of the valve seat (5), the valve core (2) is installed inside the valve sleeve (6) and is fixedly positioned and fastened with the deep groove ball bearing (4) through the valve seat (5), the opening position of the valve seat (5) is the same as that of the valve sleeve, the cylindrical surface of the valve core (2) is provided with 8 blind holes in four groups, and the number of the blind holes is 32 in the radial direction; the axial positions of the four groups of holes are the same as that of the valve seat (5) and the valve sleeve (6), and the tail ends of eight holes which are symmetrically distributed in the radial direction are communicated with the other three groups of holes in the axial direction through eight internal flow passages; two pairs of deep groove ball bearings (4) are connected between the valve core (2) and the valve sleeve (6); the left-handed trapezoidal thread is matched with the left valve plate (3), and the right-handed trapezoidal thread is matched with the right valve plate (7); the left end mounting part of the trapezoidal left and right threaded shaft (27) is connected with the motor output shaft of the secondary motor (1) through a flat key (26); the secondary motor (1) is fixed with the left end cover (20) through a first bolt (21) and a second bolt (22), and a pair of angular contact ball bearings which are installed face to face are connected between the left end cover (20) and the trapezoidal left and right threaded shaft (27), wherein the angular contact ball bearings are respectively a first angular contact ball bearing (23) and a second angular contact ball bearing (24); the left end cover (20), the valve seat (5) and the valve core (2) are connected and fastened with the fixed support (10) through bolts; the valve sleeve (6) is provided with four groups of two through holes which are equidistantly distributed in the axial direction and symmetrically distributed at intervals of 45 degrees in the radial direction; the position of the opening of the valve seat (5) is the same as that of the valve sleeve (6), namely, two holes in the radial direction are symmetrically distributed at 180 degrees, every other distance and every other distance are 45 degrees on each row of axial symmetrical holes, and each pair of symmetrical holes are respectively an external oil port P, an external oil port T, an external oil port A and an external oil port B; and annular grooves with certain depth are formed in the outer side of the radial hole on the outer cylindrical surface of the valve sleeve (6), so that each annular groove is communicated with the oil port of the valve seat, when the valve sleeve (6) rotates, the outer oil port is communicated with the valve core (2) without rotating to the position of the oil port on the valve seat (5), and the response process is accelerated.
2. The direction and flow compound high frequency response ratio rotary valve of claim 1, wherein: four groups of 8 blind holes in the radial direction are formed in the cylindrical surface of the valve core (2), and the axial positions of the four groups of blind holes are the same as those of the valve seat (5) and the valve sleeve (6); and the tail ends of the eight holes symmetrically distributed in the radial direction are communicated with the other three groups in the axial direction through eight internal flow passages.
3. The direction and flow compound high frequency response ratio rotary valve of claim 1, wherein: two ends of the valve core (2) and the left valve plate (3) and the right valve plate form four independent fan-shaped cavities through the cross special-shaped grooves, and when oil enters and the valve sleeve rotates for a certain angle, an oil port communicated with the valve cavity is changed, so that the reversing of a hydraulic oil way is realized.
4. The direction and flow compound high frequency response ratio rotary valve of claim 1, wherein: the deep groove ball bearing (4) is arranged between the valve seat (5) and the valve sleeve (6) to bear the radial load and a certain bidirectional axial load of the rotary valve body; the first angular contact ball bearing (23) and the second angular contact ball bearing (24) are arranged between the left and right trapezoidal threaded shafts (27) and the left end cover (20) and bear axial and radial loads on the threaded shafts at the same time; the rotary valve body is fixed by bolts, and the transmission cover plate (9) is connected with the valve sleeve (6) by hexagon socket head cap screws.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110333564.7A CN113153852B (en) | 2021-03-29 | 2021-03-29 | Direction and flow combined type high-frequency response proportional rotary valve |
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| CN202110333564.7A CN113153852B (en) | 2021-03-29 | 2021-03-29 | Direction and flow combined type high-frequency response proportional rotary valve |
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| CN113153852B true CN113153852B (en) | 2022-08-30 |
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| CN115234695B (en) * | 2022-09-09 | 2024-09-24 | 南京工程学院 | Piezoelectric impact type pneumatic digital flow valve |
| CN115853851B (en) * | 2022-12-05 | 2024-01-02 | 上海羿弓氢能科技有限公司 | Novel central distributing rotary reversing valve for hydrogen diaphragm compressor |
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| CN201145632Y (en) * | 2007-12-14 | 2008-11-05 | 浙江工业大学 | Electrohydraulic excitation control valve |
| CN102889254A (en) * | 2011-07-22 | 2013-01-23 | 杨世祥 | Dual-drive servo valve and control method thereof |
| CN204419740U (en) * | 2014-12-30 | 2015-06-24 | 浙江大学台州研究院 | Spool transfer composite hydraulic excitation controlling valve |
| CN105972255B (en) * | 2016-05-20 | 2018-04-06 | 太原理工大学 | A kind of revolving high-speed switch 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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Application publication date: 20210723 Assignee: Suzhou Tieshu Machinery Technology Co.,Ltd. Assignor: NANJING INSTITUTE OF TECHNOLOGY Contract record no.: X2024980001828 Denomination of invention: A direction and flow compound high-frequency response proportional rotary valve Granted publication date: 20220830 License type: Common License Record date: 20240202 |
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