CN113266613A - Large-flow shaft flow distribution proportion servo valve - Google Patents
Large-flow shaft flow distribution proportion servo valve Download PDFInfo
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- CN113266613A CN113266613A CN202110308041.7A CN202110308041A CN113266613A CN 113266613 A CN113266613 A CN 113266613A CN 202110308041 A CN202110308041 A CN 202110308041A CN 113266613 A CN113266613 A CN 113266613A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0406—Valve members; Fluid interconnections therefor for rotary valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
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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
- F16K11/0856—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 having all the connecting conduits situated in more than one plane perpendicular to the axis of the 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
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
- F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
- F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
- F16K3/262—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member with a transverse bore in the valve member
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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
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/314—Forms or constructions of slides; Attachment of the slide to the spindle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B2013/0413—Valve members; Fluid interconnections therefor with four or more positions
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Sliding Valves (AREA)
- Multiple-Way Valves (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention relates to a high-flow shaft flow distribution proportional servo valve which comprises a shaft flow distribution valve body stator and a shaft flow distribution valve core rotor rotatably arranged in an inner cavity of the shaft flow distribution valve body stator, wherein the shaft flow distribution valve body stator and the shaft flow distribution valve core rotor are sequentially provided with four sealing areas which are not communicated with each other from top to bottom, a working oil port A, a working oil port B, an oil supply port and an oil return port which are respectively corresponding to the four sealing areas are sequentially arranged on the side wall of the shaft flow distribution valve body stator from top to bottom, the opening directions of the working oil port A, the oil supply port A and the oil return port are the same, the opening direction of the working oil port B is opposite to the opening direction of the working oil port A, and the shaft flow distribution valve core rotor is axially provided with an oil supply channel, an oil return channel and a plurality of through holes for reducing mass and increasing torque. Compared with the prior art, the invention has the advantages of proportional linear shaft flow distribution, non-contact abrasion reduction, high expansibility, large flow capacity, simple and convenient maintenance and the like.
Description
Technical Field
The invention relates to the technical field of fluid control, in particular to a high-flow shaft flow distribution proportional servo valve.
Background
The structure of a double-coil electromagnetic valve of the existing switching electromagnetic directional valve mainly adopts the structure of a locking nut, an electromagnetic coil, a core pipe, a spring, a gasket, a valve core, a gasket, a spring, a core pipe, an electromagnetic coil and a locking nut; the electromagnetic valve structure of the single coil mainly adopts the structure of a locking nut, an electromagnetic coil, a core pipe, a spring, a gasket, a valve core, a valve body, a gasket, a spring and an end cover.
The electromagnetic valve can be divided into direct current and alternating current according to the type of power supply voltage, the power supply voltage value can be selected in a wide range, the valve core moves in the valve body and is mainly supported by a hydraulic oil film, oil pollution particles influence the smoothness of the valve core movement through the valve core and valve body gaps of the valve core, and if the electromagnetic coil is in a power-on state for a long time, the valve core is easy to be blocked to cause the fault of an actuating mechanism; due to the limitation of the installation space, the size specification of the coil limits the maximum holding force of the coil, the output power characteristic of the coil is influenced, fluid flows through a cavity formed by the valve core/the valve body, and the generated hydrodynamic force also limits the through-current capacity of the conventional switch electromagnetic directional valve; the size of the coil also affects the heat dissipation characteristic, the coil is easy to be burnt in a high-temperature or high-humidity environment, and the waterproof grade is affected by the plastic packaging process and the electrical connection mode of the coil.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a high-flow shaft flow distribution proportional servo valve.
The purpose of the invention can be realized by the following technical scheme:
a high-flow axial flow distribution proportional servo valve comprises an axial flow distribution valve body stator and an axial flow distribution valve core rotor rotatably arranged in an inner cavity of the axial flow distribution valve body stator, wherein the axial flow distribution valve body stator and the axial flow distribution valve core rotor are respectively divided into four sealing areas which are not communicated with each other from top to bottom through 5 sealing rings which are sequentially arranged, a working oil port A, a working oil port B, an oil supply port and an oil return port which respectively correspond to the four sealing areas are sequentially arranged on the side wall of the axial flow distribution valve body stator from top to bottom, the working oil port A and the working oil port B are connected with an external execution mechanism, the oil supply port and the oil return port are connected with an external oil source, the opening directions of the working oil port A and the oil return port are the same, the opening direction of the working oil port B is opposite to the opening direction of the working oil port A, and an oil supply channel is axially arranged on the axial, And the oil return channel and the through holes are used for reducing the mass and increasing the torque, and the proportional conduction states between the oil supply channel and the oil return channel and between the working oil port A and the working oil port B are respectively realized through the rotating shaft distributing valve core rotor, so that the proportional reversing control of the external actuating mechanism is realized.
The shaft distribution valve core rotor surface is provided with a first notch and a second notch along the circumferential direction at a first horizontal setting position of a first sealing area, the opening direction of a working oil port A is a 0-degree straight line, the clockwise direction is the forward direction, the first notch and the second notch are symmetrically arranged by taking the 0-degree straight line as a symmetry axis, the first notch is communicated with an oil return channel, the second notch is communicated with an oil supply channel, the first notch and the second notch are respectively divided in the circumferential direction through two non-notched sections and are not communicated with each other, the arc length of the two non-notched sections between the first notch and the second notch in the circumferential direction and the axial size are larger than the bottom diameter of the working oil port A, and the blocking of the working oil port A is realized in the rotating process.
The central angle range corresponding to the first open slot is-beta1～-β2The central angle range corresponding to the second slot is + beta1～+β2。
The shaft distributing valve core rotor surface is provided with a third slot and a fourth slot along the circumferential direction at a second horizontal setting position of a second sealing area, the opening direction of a working oil port B is a 180-degree straight line, the clockwise direction is the forward direction, the third slot and the fourth slot are symmetrically arranged by taking the 180-degree straight line as a symmetry axis, the third slot is communicated with an oil return channel, the fourth slot is communicated with an oil supply channel, the third slot and the fourth slot are respectively divided in the circumferential direction through two unslotted sections and are not communicated with each other, the arc length and the axial size of the two unslotted sections between the third slot and the fourth slot in the circumferential direction are larger than the bottom diameter of the working oil port B, and the shaft distributing valve core rotor surface is used for plugging the working oil port B in the rotating process.
The central angle range corresponding to the third groove is plus (180 plus beta)1)°～+(180+β2) The central angle range corresponding to the fourth groove is plus (180-beta)1)°～+(180-β2)°。
Beta is1Is 3 DEG, beta2Is 135 degrees, and the angle adjusting range of the shaft flow distribution proportional servo valve is-beta2～+β2。
The rotor surface of the shaft distributing valve core is provided with a groove in the third sealing area in the whole circumferential direction, and the oil supply channel is communicated with the groove in the whole circumferential direction through three flow passages at a third horizontal setting position in the third sealing area so as to be communicated with the oil supply port.
The surface of the rotor of the shaft distributing valve core is provided with a groove in the fourth sealing area in the whole circumferential direction, and the oil return channel is communicated with the groove in the whole circumferential direction through three flow passages at a fourth horizontal setting position in the fourth sealing area so as to be communicated with an oil return opening.
First fluting and second fluting shape the same, first fluting is along the width and the degree of depth crescent of clockwise for realize the through-flow proportion linearization of switching-over in-process, and the passageway scope part coincidence of first fluting and oil return passage, make first fluting and oil return passage directly communicate, be used for realizing large-traffic circulation, similarly, the width and the degree of depth crescent of second fluting along counter-clockwise, and the passageway scope part coincidence of second fluting and oil supply passage, make first fluting and oil supply passage directly communicate.
Third fluting and fourth fluting shape the same, the width and the degree of depth crescent along clockwise in the third fluting for realize the through-flow proportion linearization of switching-over in-process, and the coincidence of the passageway scope part of third fluting and oil return channel, make third fluting and oil return channel directly communicate, be used for realizing large-traffic circulation, and is same, the width and the degree of depth crescent along counter-clockwise in the fourth fluting, and the coincidence of the passageway scope part of fourth fluting and oil feed channel, make third fluting and oil feed channel directly communicate.
Compared with the prior art, the invention has the following advantages:
the invention breaks through the design concept of the conventional switch valve at present, adopts a form of slotting on a rotor shaft, realizes shaft flow distribution through a pair of oil supply channels P and oil return channels T, and can also realize the form of expanding into a plurality of pairs of oil supply channels P and oil return channels T.
The invention realizes the proportional reversing and ordered oil supply of the working oil port through the non-full-circumference slotting structure of the rotor in the circumferential direction, thereby realizing the logic flow distribution control of the actuating mechanism.
And thirdly, as the rotor and the stator of the axial flow distribution electromagnetic valve are in clearance fit, and a thrust bearing is adopted outside to reduce the rotation resistance moment of the rotor and the radial acting force generated when a large flow passes through.
And no matter the axial distribution valve is in a working or non-working state, the rotor and the stator of the axial distribution valve are not in mechanical contact, so that the mechanical contact abrasion and eccentric wear hidden danger between the rotor and the stator are reduced, and the long-term effective work of the axial distribution valve is ensured.
And fifthly, an axial flow distribution structure is adopted, so that the gap sealing length between the working oil port and the oil supply/return passage is realized, the leakage amount is reduced, and the circulation capacity is further increased.
And sixthly, a plurality of through holes are formed in the rotor of the shaft distribution valve core, so that the weight of the valve body is reduced, and the rotating torque is increased.
Seventh, when the first groove and the fourth groove are formed, the depth and the width of the grooves are directly communicated with the oil supply channel P and the oil return channel T, so that large-flow circulation can be achieved, and proportional servo control can be better achieved by matching with small middle position covering amount.
Drawings
FIG. 1 is a main sectional view of the structure of the present invention.
Fig. 2 is a sectional view of a port a of the shaft distributing valve core rotor, namely a sectional view from I to I in fig. 1.
Fig. 3 is a sectional view of a port B of the rotor of the shaft distributing valve core, namely a sectional view II-II in fig. 1.
Fig. 4 is a cross-sectional view of the port P of the shaft distributing valve core rotor, i.e., a cross-sectional view III-III in fig. 1.
Fig. 5 is a cross-sectional view of a T-port of the shaft distributing valve core rotor, i.e., a cross-sectional view IV-IV in fig. 1.
Description of the reference numerals
1. The shaft flow distribution valve comprises a shaft flow distribution valve body, 2, a shaft flow distribution valve core rotor, 3, a sealing ring, 4, a shaft flow distribution valve body stator, 31, a first sealing ring, 32, a second sealing ring, 33, a third sealing ring, 34, a fourth sealing ring, 35, a fifth sealing ring, P, an oil supply channel, T, an oil return channel, A/B, a working oil port, P0, an oil supply port, T0 and an oil return port.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments.
Examples
As shown in fig. 1-5, the present invention provides a high flow rate axial flow distribution proportional servo valve, which comprises an inner axial flow distribution valve core rotor 2 and an outer axial flow distribution valve body stator 4; through adjusting shaft flow distribution valve core rotor 2 and rotating to different angle ranges, adjust the continuous proportion intercommunication between work hydraulic fluid port and fuel feed inlet and the oil return opening, realize the continuous different proportion speed control to actuating mechanism action, can let actuating mechanism maintain the state unchangeable in setting for rotation angle within range, have the part few, processing is convenient, compact structure, simple, it is convenient to adjust, the through-flow capacity is big, maintain portably, advantages such as repeatability height.
The shaft flow distribution valve core rotor 2 and the shaft flow distribution valve body stator 4 form four separate sealing areas which are not communicated with each other through 5 sealing rings 3 from top to bottom along the axial direction, and the communication relation between the four sealing areas and the working oil port of the stator is as follows:
the first sealing area is specifically a range contained between the first sealing ring 31 and the second sealing ring 32, and the first sealing area is communicated with a working oil port A of the stator;
the second sealing area is specifically a range contained between the second sealing ring 32 and the third sealing ring 33, and the second sealing area is communicated with a working oil port B of the stator;
the third sealing area is specifically a range included between the third sealing ring 33 and the fourth sealing ring 34, and is grooved all around;
the fourth sealing area is specifically a range included between the fourth sealing ring 34 and the fifth sealing ring 35, and is grooved all around;
the third sealing area and the fourth sealing area are not communicated with the working oil ports A and B.
The communication relation between the four sealing areas and the oil supply passage P and the oil return passage T on the shaft distributing valve core rotor 2 is as follows:
the first sealing area is communicated with the oil supply channel P and the oil return channel T, the second sealing area is communicated with the oil supply channel P and the oil return channel T, the third sealing area is communicated with the oil supply channel P of the rotor only, the fourth sealing area is communicated with the oil return channel T of the rotor only, the depth of the oil supply channel P reaches the third sealing area, and the depth of the oil return channel T reaches the fourth sealing area.
The external oil supply port P0 is arranged on the shaft distribution valve stator and is communicated with an oil supply channel P on the shaft distribution valve core rotor 2 through a full circumferential slot in a third sealing area range corresponding to the shaft distribution valve core rotor 2; the external oil return port T0 is communicated with an oil return channel T on the shaft distribution valve core rotor 2 through a full circumferential groove in a fourth sealing area range corresponding to the shaft distribution valve core rotor 2;
as shown in fig. 2, in a first horizontal setting position (I-I cross section) in the first sealing area, with the opening direction of the working oil port a as a 0 ° straight line and the clockwise direction as a forward direction, a gradually-deep and gradually-wide groove, i.e., a second groove, is formed in the shaft distribution valve core rotor 2 between +3 ° and +135 °, and is communicated with the oil supply passage P, and a gradually-deep and gradually-wide groove, i.e., a first groove, is formed between-3 ° and +135 °, and is communicated with the oil return passage T, and the first groove and the second groove are separated by two non-grooved sections (0 ° direction and 180 ° direction), respectively, and the arc length and the axial dimension of the two non-grooved sections in the circumferential direction are greater than the bottom diameter of the working oil port a, so as to plug the working oil port a during the rotation;
as shown in fig. 3, in a second horizontal setting position (section II-II) in the second sealing area, the structure is the same as that of the first horizontal setting position, but the difference is 180 °, the opening direction of the working oil port B is a 180 ° straight line, the clockwise direction is the forward direction, a gradually-deep and gradually-wide groove, i.e., a third groove, which is communicated with the oil return channel T, is formed on the shaft distribution valve core rotor 2 between +183 ° and +315 °, and a gradually-deep and gradually-wide groove, i.e., a first groove, is formed between-45 ° and +177 °, is communicated with the oil supply channel P, is separated between the third groove and the fourth groove (between 0 ° and 180 °) by two unslotted sections, and the arc length and the axial dimension of the two unslotted sections in the circumferential direction are both greater than the bottom diameter of the working oil port B, so as to plug the working oil port B during the rotation;
as shown in fig. 4, in the third horizontal setting position (section III-III) of the third seal region, the oil supply port P0 communicates with the oil supply passage P of the shaft distribution valve core rotor 2 through the circumferential fully-open groove;
as shown in fig. 5, in a fourth horizontal setting position (section IV-IV) of the fourth sealing area, the oil return port T0 is communicated with the oil return passage T of the shaft distribution valve core rotor 2 through a circumferential full-open groove;
the number of the middle openings of the shaft distribution valve core rotor 2 can be designed into one group to multiple groups of P, T channels according to the passing flow size, the switching frequency and the shaft size of the shaft distribution valve core rotor 2.
The following correlation angles are taken as examples to illustrate the correlation function relative relationship:
the shaft flow distribution valve core rotor of the shaft flow distribution proportional reversing valve is driven and adjusted to rotate between-135 degrees and +135 degrees through a servo motor/a stepping motor, so that the continuous switching between the left, middle and right three-position functions of the shaft flow distribution proportional reversing valve is realized, and the method specifically comprises the following steps:
a corresponding median coverage in the range of +/-3 °;
the left end position P-A/B-T of the distributing valve of the reversing shaft with the corresponding proportion of-3 degrees to-135 degrees;
the right end position P-B/A-T of the valve of the reversing shaft with the corresponding proportion of +3 degrees to +135 degrees;
the corresponding seal segments are between +/-3 deg..
The actual relevant angles and the middle-position machine can be designed and adjusted according to the requirements, and the corresponding angles are communicated or disconnected with the oil supply port P0 and the oil return port T0 through the cutting groove of the flow distribution shaft in the working oil port area, so that the continuous switching of the A/B oil supply flow of the working oil port is realized, and the control of the action of the actuating mechanism is realized.
Claims (10)
1. The high-flow axial flow distribution proportion servo valve is characterized by comprising an axial flow distribution valve body stator (4) and an axial flow distribution valve core rotor (2) rotatably arranged in an inner cavity of the axial flow distribution valve body stator (4), wherein the axial flow distribution valve body stator (4) and the axial flow distribution valve core rotor (2) are respectively divided into four non-communicated sealing areas from top to bottom through 5 sealing rings which are sequentially arranged, a working oil port A, a working oil port B, an oil supply port (P0) and an oil return port (T0) which respectively correspond to the four sealing areas are sequentially arranged on the side wall of the axial flow distribution valve body stator (4) from top to bottom, the working oil port A and the working oil port B are connected with an external execution mechanism, the oil supply port (P0) and the oil return port (T0) are connected with an external oil source, the opening directions of the working oil port A, the oil supply port (P0) and the oil return port (T0) are the same, the opening direction of the working oil port B is opposite to that of the working oil port A, the shaft distribution valve core rotor (2) is provided with an oil supply channel (P), an oil return channel (T) and a plurality of through holes for reducing mass and increasing torque along the axial direction, and the proportion breakover state between the oil supply channel (P) and the oil return channel (T) and between the working oil port A and the working oil port B and further the proportion reversing control of an external execution mechanism are respectively realized through the rotating shaft distribution valve core rotor (2).
2. A high flow rate shaft-to-shaft proportional servo valve according to claim 1, the surface of the shaft distributing valve core rotor (2) is respectively provided with a first open slot and a second open slot along the circumferential direction at a first horizontal setting position of a first sealing area, the opening direction of the working oil port A is taken as a 0-degree straight line, the clockwise direction is taken as the positive direction, the first open slot and the second open slot are symmetrically arranged by taking the 0-degree straight line as a symmetrical axis, the first open slot is communicated with the oil return channel (T), the second open slot is communicated with the oil supply channel (P), the first slot and the second slot are respectively divided by two unslotted sections in the circumferential direction and are not communicated with each other, and the arc length and the axial size of the two unslotted sections between the first slot and the second slot in the circumferential direction are both larger than the bottom diameter of the working oil port A so as to realize the plugging of the working oil port A in the rotating process.
3. A high flow rate axial flow distribution proportional servo valve as claimed in claim 2, wherein said first slot corresponds to a central angle in the range of- β1～-β2The central angle range corresponding to the second slot is + beta1～+β2。
4. A high flow rate shaft-to-shaft proportional servo valve according to claim 1, the surface of the shaft distributing valve core rotor (2) is respectively provided with a third open slot and a fourth open slot along the circumferential direction at a second horizontal setting position of a second sealing area, the opening direction of the working oil port B is taken as a 180-degree straight line, the clockwise direction is taken as the positive direction, the third open slot and the fourth open slot are symmetrically arranged by taking the 180-degree straight line as a symmetry axis, the third open groove is communicated with the oil return channel (T), the fourth open groove is communicated with the oil supply channel (P), the third slot and the fourth slot are respectively divided by two unslotted sections in the circumferential direction and are not communicated with each other, and the arc length and the axial size of the two unslotted sections between the third slot and the fourth slot in the circumferential direction are both larger than the bottom diameter of the working oil port B so as to plug the working oil port B in the rotating process.
5. A high flow rate shaft-to-shaft flow ratio servo valve as claimed in claim 4 wherein the third opening corresponds to a central angle in the range of + (180+ β)1)°～+(180+β2) The central angle range corresponding to the fourth groove is plus (180-beta)1)°～+(180-β2)°。
6. A high flow rate shaft-to-shaft proportional servo valve as claimed in claim 3 or 5, wherein β is1Is 3 DEG, beta2Is 135 degrees, and the angle adjusting range of the shaft flow distribution proportional servo valve is-beta2～+β2。
7. A high flow rate shaft-to-valve proportional servo valve according to claim 1, wherein the surface of the shaft-to-valve core rotor (2) is circumferentially grooved in a third sealing area, and in a third horizontal setting position in the third sealing area, the oil supply passage (P) communicates with the circumferential groove through three flow passages, and further communicates with the oil supply port (P0).
8. A high flow rate shaft-to-valve proportional servo valve according to claim 1, wherein the surface of the shaft-to-valve core rotor (2) is circumferentially grooved in a fourth sealing area, and at a fourth horizontal setting position in the fourth sealing area, the oil return passage (T) communicates with the circumferential groove through three flow passages, and further communicates with the oil return port (T0).
9. The high-flow-rate shaft flow distribution proportional servo valve as claimed in claim 2, wherein the first slot and the second slot are identical in shape, the width and depth of the first slot gradually increase along the clockwise direction to achieve proportional linearization of through flow during reversing, and the channel range of the first slot and the channel range of the oil return channel (T) partially coincide, so that the first slot is directly communicated with the oil return channel (T) to achieve high-flow circulation, and likewise, the width and depth of the second slot gradually increase along the counterclockwise direction, and the channel range of the second slot and the channel range of the oil supply channel (P) partially coincide, so that the first slot is directly communicated with the oil supply channel (P).
10. The high-flow-rate axial flow distribution proportional servo valve as claimed in claim 4, wherein the third slot and the fourth slot are identical in shape, the width and depth of the third slot gradually increase along the clockwise direction to achieve through-flow proportional linearization during reversing, and the channel range of the third slot and the channel range of the oil return channel (T) partially coincide, so that the third slot is directly communicated with the oil return channel (T) to achieve high-flow circulation, and likewise, the width and depth of the fourth slot gradually increase along the counterclockwise direction, and the channel range of the fourth slot and the channel range of the oil supply channel (P) partially coincide, so that the third slot and the oil supply channel (P) are directly communicated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110308041.7A CN113266613B (en) | 2021-03-23 | 2021-03-23 | Large-flow shaft flow distribution proportion servo valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110308041.7A CN113266613B (en) | 2021-03-23 | 2021-03-23 | Large-flow shaft flow distribution proportion servo valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113266613A true CN113266613A (en) | 2021-08-17 |
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