CN112922917B - Axial flow distribution proportional servo valve - Google Patents
Axial flow distribution proportional servo valve Download PDFInfo
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- CN112922917B CN112922917B CN202110291337.2A CN202110291337A CN112922917B CN 112922917 B CN112922917 B CN 112922917B CN 202110291337 A CN202110291337 A CN 202110291337A CN 112922917 B CN112922917 B CN 112922917B
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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)
- Servomotors (AREA)
Abstract
The invention relates to a shaft flow distribution proportional servo valve, which comprises a shaft flow distribution valve body stator and a shaft flow distribution valve core rotor which is rotatably arranged in the inner cavity of the shaft flow distribution valve body stator, the axial flow distribution valve body stator and the axial flow distribution valve core rotor are respectively provided with three sealing areas from top to bottom, the side wall of the axial flow distribution valve body stator is sequentially provided with a working oil port, an oil supply port and an oil return port which respectively correspond to the three sealing areas from top to bottom, the working oil port is respectively communicated with an external actuating mechanism, the oil supply port and the oil return port are respectively communicated with an external oil source, the axial flow distribution valve core rotor is provided with an oil supply channel, an oil return channel and a through hole along the axial direction, the continuous proportional conduction state control between the oil supply channel and the working oil port and between the oil return channel and the working oil port are respectively realized through the rotating shaft distributing valve core rotor, and further the continuous different proportional speed control of an external actuating mechanism is realized. Compared with the prior art, the invention has the advantages of large through-flow capacity, convenient adjustment, reduced rotation abrasion and the like.
Description
Technical Field
The invention relates to the technical field of fluid control, in particular to a shaft flow distribution proportional servo valve.
Background
For a conventional proportional servo valve, the structure of a double-coil proportional reversing valve mainly adopts the structural form of a locking nut, a proportional coil, a core pipe, a spring, a gasket, a proportional valve element, a valve body, a gasket, a spring, a core pipe, a proportional coil and a locking nut; the structure of the proportional reversing valve of the single coil mainly adopts the structural form of a locking nut, a proportional coil, a core pipe, a spring, a gasket, a proportional valve core, a valve body, a gasket, a spring and an end cover;
the power supply of the valve is mainly driven by PWM signals, the valve core moves in the valve body and is mainly supported by a hydraulic oil film, the smoothness of the movement of the valve core is influenced after oil pollution particles flow into a gap between the valve core and the valve body, if a proportional coil is in an electrified state for a long time, the valve core is easy to be clamped and blocked, so that an actuating mechanism is in failure, the size specification of the proportional coil limits the maximum holding force due to the limitation of the installation space, the output power characteristic of the proportional coil is influenced, fluid flows through a cavity formed by the valve core and the valve body, and the generated hydrodynamic force also limits the through-flow capacity; in addition, the size of the proportional coil is limited, the heat dissipation characteristic is also influenced, the coil is easy to burn in a high-temperature or high-humidity environment, and the waterproof grade is also influenced by the plastic packaging process of the coil and the mode of electrical connection.
Disclosure of Invention
The object of the present invention is to provide a shaft-distribution proportional servo valve which overcomes the above-mentioned drawbacks of the prior art.
The purpose of the invention can be realized by the following technical scheme:
a shaft flow distribution proportion servo valve comprises a shaft flow distribution valve body stator and a shaft flow distribution valve core rotor which is rotatably arranged in the inner cavity of the shaft flow distribution valve body stator, and is characterized in that the shaft flow distribution valve body stator and the shaft flow distribution valve core rotor are respectively divided into three sealing areas which are not communicated with each other from top to bottom through 4 sealing rings which are sequentially arranged, a working oil port, an oil supply port and an oil return port which are respectively corresponding to the three sealing areas are sequentially arranged on the side wall of the shaft flow distribution valve body stator from top to bottom, the working oil ports are respectively communicated with an external execution mechanism, the oil supply port and the oil return port are respectively communicated with an external oil source, an oil supply channel, an oil return channel and a plurality of through holes which are used for reducing mass and increasing torque are axially arranged on the shaft flow distribution valve core rotor, and the continuous proportion communication state control between the oil supply channel and the oil return channel and the working oil port is respectively realized through the rotating shaft flow distribution valve core rotor, thereby realizing the continuous different proportional speed control of the external actuating mechanism.
The two working oil ports are arranged, the working oil ports and the working oil ports are respectively arranged on the shaft flow distribution valve body stator in a manner of being opposite to 180 degrees, and the vertical positions of the working oil ports, the oil supply ports and the oil return ports, which are formed in the side wall of the shaft flow distribution valve body stator, are the same.
The shaft distribution valve core rotor surface is provided with a first slot, a second slot, a third slot and a fourth slot which are mutually communicated and have the same structure through mutual separation of four un-slotted sections at a first horizontal setting position of a first sealing area along the circumferential direction, the first slot and the second slot are communicated with an oil return channel respectively, the third slot and the fourth slot are communicated with an oil supply channel respectively, and the arc length and the axial size of the four un-slotted sections in the circumferential direction are larger than the bottom diameter of a working oil port so as to realize the plugging of the working oil port in the rotating process.
The connecting line of the hole center directions of the oil supply channel and the oil return channel is used as a straight line of 90 degrees, the first open groove and the fourth open groove are symmetrically arranged by the straight line of 0 degree, the first open groove and the second open groove are symmetrically arranged by the straight line of 90 degrees, and the third open groove and the fourth open groove are symmetrically arranged by the straight line of 90 degrees.
The range of the central angle corresponding to the slotted section and the non-slotted section, which are arranged along the circumferential direction at a first horizontal setting position, corresponding to the first sealing area, on the surface of the rotor of the shaft distribution valve core, is specifically as follows according to the size sequence:
a first grooving: beta is a1～β2；
First ungrooved section: beta is a2～(180-β2)；
And (3) second grooving: (180-. beta.) with a high degree of crystallinity2)～(180-β1)；
A second ungrooved section: (180-. beta.) with a high degree of crystallinity1)～(180+β1)；
And (3) third grooving: (180+ beta)1)～(180+β2)；
A third ungrooved section: (180+ beta)2)～(360-β2)；
A fourth slot: (360-. beta.) of2)～(360-β1)；
A fourth ungrooved section: (360-. beta.) of1)～β1；
Wherein, beta1<β2。
Beta is1The value is 3 DEG beta2The value is 45 °.
In the clockwise direction, the first slot is at beta1～β2Within a range of increasing depth and width, at β2The position is communicated with the oil return channel through a flow passage, and the second slot is positioned at (180-beta)2)～(180-β1) Within the range of gradually decreasing depth and width at (180-beta)2) The position is communicated with the oil return channel through a flow channel, and the third slot is positioned at (180+ beta)1)～(180+β2) Within the range of gradually increasing depth and width at (180+ beta)2) At the positionIs communicated with the oil supply channel through a flow channel, and the fourth slot is arranged at (360-beta)2)～(360-β1) Within the range of gradually decreasing depth and width at (360-beta)2) The position is communicated with the oil supply channel through a flow channel so as to realize the through-flow proportion linearization in the reversing process.
The rotor surface of the shaft distributing valve core is provided with a groove in the second 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 second horizontal set position in the second 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 third 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 third horizontal setting position in the third sealing area so as to be communicated with an oil return opening.
The through holes are arranged in three side by side and are arranged between the oil supply channel and the oil return channel.
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, and realizes shaft flow distribution through a pair of oil supply channels P and oil return channels T.
The invention realizes the reversing and orderly oil supply of the working oil port switch by a 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, the rotor of the shaft distribution valve core is provided with a plurality of through holes, so that the mass of the rotating shaft can be effectively reduced, the driving torque of a servo motor is reduced, and the rotation control is facilitated.
Drawings
FIG. 1 is a main sectional view of the structure of the present invention.
Fig. 2 is a cross-sectional view of section I-I in fig. 1.
Fig. 3 is a cross-sectional view of section II-II in fig. 1.
Fig. 4 is a cross-sectional view of section III-III in fig. 1.
The notation in the figure is:
1. the shaft flow distribution proportional servo valve comprises a shaft flow distribution valve core rotor 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, a P oil supply channel, a T oil return channel, an A/B stator working oil port, a P0 oil supply port, a 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. 1-4, the present invention provides a shaft distribution flow proportional servo valve, which comprises an inner shaft distribution valve core rotor 2, an outer shaft distribution valve body stator 4 and a plurality of sets of sealing rings; through adjusting the continuous proportion intercommunication between the axle distribution valve core rotor 2 rotation to different angles, working oil mouth and fuel feeding mouth P0, oil return port T0, realize the continuous different proportion speed control to the actuating mechanism action, can let actuating mechanism maintain the state unchangeable in specific rotation angle within range, have the part few, processing is convenient, compact structure, simple, it is convenient to adjust, the 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 three separate sealing areas which are not communicated with each other through 4 sealing rings 3 from top to bottom along the axial direction, and the communication relation between the three sealing areas and the working oil port of the stator is as follows:
the first sealing area is a range contained between the first sealing ring 31 and the second sealing ring 32, the first sealing area is communicated with a working oil port A and a working oil port B of the stator, and the working oil port A and the working oil port B are arranged oppositely at a distance of 180 degrees on the circumferential surface;
the second sealing area is a range contained between the second sealing ring 32 and the third sealing ring 33, and the shaft distributing valve core rotor 2 is completely and circumferentially grooved in the range of the second sealing area;
the third sealing area is a range contained between the third sealing ring 33 and the fourth sealing ring 34, and the shaft distributing valve core rotor 2 is completely and circumferentially grooved in the range of the third sealing area;
the second sealing area and the third sealing area are not communicated with the working oil ports A and B.
The communication relation between the three 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 areas are 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 of the rotor, the third sealing area is communicated with the oil return channel T of the rotor, namely the depth of the oil supply channel P reaches the second sealing area, and the depth of the oil return channel T reaches the third 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 second 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 third sealing area range corresponding to the shaft distribution valve core rotor 2;
in a first horizontal setting position (I-I section) in a first sealing area, a gradually-deepened and gradually-widened groove, namely a first groove, is formed in the periphery of the outer surface of the rotor 2 of the shaft distribution valve core in the clockwise direction between +3 degrees and +45 degrees and +135 degrees and +177 degrees, and a gradually-deepened and gradually-widened groove, namely a second groove, is formed in the counterclockwise direction between-3 degrees and-45 degrees and-135 degrees and-177 degrees, and the third groove and the fourth groove are linearly and symmetrically formed with the first groove and the second groove at 0 degree.
The four slots are separated by four un-slotted sections and are not communicated with each other, the first slot and the second slot are respectively communicated with the oil supply channel P through a direct current channel, the third slot and the fourth slot are respectively communicated with the oil return channel T through a direct current channel, and the arc length and the axial size of the four un-slotted sections in the circumferential direction are both larger than the bottom diameter of the working oil port A, B so as to realize the plugging of the working oil port in the rotating process;
in a second horizontal setting position (section II-II) of the second sealing region, the oil supply port P0 communicates with the oil supply passage P of the shaft distribution valve core rotor 2 through a circumferential full-open groove;
in a third horizontal setting position (III-III section) of the third sealing area, an oil return port T0 is communicated with an oil return channel T of the shaft distributing 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 distribution valve core rotor 2 realizes the continuous switching of the left, middle and right three-position performances of the switching electromagnetic valve by adjusting the rotation of a servo motor/a stepping motor within +/-45 degrees, and specifically comprises the following steps:
a corresponding median coverage in the range of +/-3 °;
the left end position P-A/B-T of the flow distributing valve of the reversing shaft with the corresponding proportion of +3 degrees to +45 degrees;
the right end position P-B/A-T of the distributing valve of the reversing shaft with the corresponding proportion of-3 degrees to-45 degrees;
the corresponding sealing section is +/-3 degrees, and the covering amount can be used as a proportional servo valve.
The practical related angle and axial distribution valve neutral position machine can design and adjust the mutual corresponding angle relation according to the requirement, the specific corresponding angle is communicated or disconnected with the oil supply port P/oil return port T through the grooving of the distribution shaft on the working oil port, the switching of the A/B oil supply pressure of the working oil port is realized, and the switch reversing control of the action of the actuating mechanism is realized.
Claims (8)
1. A shaft flow distribution proportion servo valve comprises a shaft flow distribution valve body stator (4) and a shaft flow distribution valve core rotor (2) rotatably arranged in an inner cavity of the shaft flow distribution valve body stator (4), and is characterized in that the shaft flow distribution valve body stator (4) and the shaft flow distribution valve core rotor (2) are respectively divided into three sealing areas which are not communicated with each other from top to bottom through 4 sealing rings which are sequentially arranged, a working oil port, an oil supply port (P0) and an oil return port (T0) which respectively correspond to the three sealing areas are sequentially arranged on the side wall of the shaft flow distribution valve body stator (4) from top to bottom, the working oil port is respectively communicated with an external execution mechanism, the oil supply port (P0) and the oil return port (T0) are respectively communicated with an external oil source, an oil supply channel (P), an oil return channel (T) and a plurality of through holes which are used for reducing mass and increasing torque are arranged on the shaft flow distribution valve core rotor (2) along the axial direction, continuous proportion conduction state control between an oil supply channel (P), an oil return channel (T) and working oil ports is respectively realized through a rotating shaft distributing valve core rotor (2), and further continuous different proportion speed control of an external actuating mechanism is realized, two working oil ports are arranged, the working oil ports (A) and the working oil ports (B) are respectively arranged on a shaft distributing valve body stator (4) in a way of facing 180 degrees, the vertical positions of the working oil ports (A), the oil supply port (P0) and the oil return port (T0) arranged on the side wall of the shaft distributing valve body stator (4) are the same, a first open groove, a second open groove, a third open groove and a fourth open groove which are mutually separated through four non-open groove sections and are not mutually communicated and have the same structure are respectively arranged on the surface of the shaft distributing valve core rotor (2) in a first horizontal setting position of a first sealing area along the circumferential direction, the first open groove and the second open groove are respectively communicated with the oil return channel (T), the third slot and the fourth slot are respectively communicated with the oil supply channel (P), and the arc length and the axial size of the four non-slotted sections in the circumferential direction are both larger than the bottom diameter of the working oil port, so that the working oil port is blocked in the rotating process.
2. The axial flow proportioning servo valve of claim 1 wherein a line connecting the hole centers of the oil supply passage (P) and the oil return passage (T) is taken as a line of 90 °, the first slot and the fourth slot are symmetrically disposed with respect to the line of 0 °, the first slot and the second slot are symmetrically disposed with respect to the line of 90 °, and the third slot and the fourth slot are symmetrically disposed with respect to the line of 90 °.
3. The axial flow proportioning servo valve of claim 2 wherein the ranges of the central angles corresponding to the slotted and non-slotted sections, which are circumferentially opened at a first horizontal setting position of the surface of the axial flow proportioning valve core rotor (2) corresponding to the first sealing area, are in the order of magnitude:
a first grooving: beta is a1～β2；
First ungrooved section: beta is a2～(180-β2)；
And (3) second grooving: (180-. beta.) with a high degree of crystallinity2)～(180-β1)；
A second ungrooved section: (180-. beta.) with a high degree of crystallinity1)～(180+β1)；
And (3) third grooving: (180+ beta)1)～(180+β2)；
A third ungrooved section: (180+ beta)2)～(360-β2)；
A fourth slot: (360-. beta.) of2)～(360-β1)；
A fourth ungrooved section: (360-. beta.) of1)～β1；
Wherein, beta1<β2。
4. The axial flow proportional servo valve of claim 3, wherein β is1The value is 3 DEG beta2The value is 45 °.
5. The axial flow proportional servo valve of claim 3, wherein the first slot is defined at β in a clockwise direction1～β2Within a range of increasing depth and width, at β2The position is communicated with an oil return channel (T) through a flow passage, and the second slot is positioned at (180-beta)2)～(180-β1) Within the range of gradually decreasing depth and width at (180-beta)2) The position is communicated with an oil return channel (T) through a flow channel, and the third openingThe groove is (180+ beta)1)～(180+β2) Within the range of gradually increasing depth and width at (180+ beta)2) The position is communicated with the oil supply channel (P) through a flow passage, and the fourth slot is positioned at (360-beta)2)～(360-β1) Within the range of gradually decreasing depth and width at (360-beta)2) The position is communicated with the oil supply channel (P) through a flow channel to realize the through-flow proportion linearization in the reversing process.
6. The axial flow proportioning servo valve of claim 1 wherein the surface of said axial flow proportioning valve core rotor (2) is circumferentially slotted in a second sealing area and said oil supply passageway (P) communicates with said circumferential slot through three flow passages and further communicates with an oil supply port (P0) at a second horizontal setting position in said second sealing area.
7. The axial flow proportioning servo valve of claim 1 wherein the surface of said axial flow proportioning valve core rotor (2) is circumferentially slotted in a third sealing area and said oil return passage (T) communicates with said circumferential slot through three flow passages and further communicates with an oil return port (T0) at a third horizontal setting position in said third sealing area.
8. The axial flow proportioning servo valve of claim 1 wherein said through holes are arranged in three side by side positions between the oil supply passage (P) and the oil return passage (T).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110291337.2A CN112922917B (en) | 2021-03-18 | 2021-03-18 | Axial flow distribution proportional servo valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110291337.2A CN112922917B (en) | 2021-03-18 | 2021-03-18 | Axial flow distribution proportional servo valve |
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| Publication Number | Publication Date |
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| CN112922917A CN112922917A (en) | 2021-06-08 |
| CN112922917B true CN112922917B (en) | 2022-02-18 |
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| CN202110291337.2A Active CN112922917B (en) | 2021-03-18 | 2021-03-18 | Axial flow distribution proportional servo valve |
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Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN201763711U (en) * | 2010-02-01 | 2011-03-16 | 长沙溇澧机电科技有限公司 | Hydraulic proportional control valve |
| CN102720669B (en) * | 2012-06-29 | 2015-03-04 | 泸州天府液压件有限公司 | Follower rotary valve for plane oil distribution |
| CN203115181U (en) * | 2013-03-19 | 2013-08-07 | 宋久林 | Rotating type multichannel reversing valve |
| CN104315200B (en) * | 2014-11-07 | 2017-02-01 | 合肥长源液压股份有限公司 | Single valve element type multichannel reversing valve |
| CN105757025B (en) * | 2016-04-13 | 2017-11-07 | 浙江大学舟山海洋研究中心 | The big flow three-way switch valve of valve element hollow structure |
| CN111207128A (en) * | 2020-03-11 | 2020-05-29 | 江苏东顺新能源科技有限公司 | Rotary valve type hydraulic reversing valve, hydraulic system and grid punching equipment |
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2021
- 2021-03-18 CN CN202110291337.2A patent/CN112922917B/en active Active
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