CN112855647B - Large-flow shaft flow distribution servo valve - Google Patents
Large-flow shaft flow distribution servo valve Download PDFInfo
- Publication number
- CN112855647B CN112855647B CN202110307359.3A CN202110307359A CN112855647B CN 112855647 B CN112855647 B CN 112855647B CN 202110307359 A CN202110307359 A CN 202110307359A CN 112855647 B CN112855647 B CN 112855647B
- Authority
- CN
- China
- Prior art keywords
- rotor
- groove
- flow distribution
- stator
- communicated
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
- F15B13/022—Flow-dividers; Priority valves
-
- 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
Abstract
The invention relates to a high-flow shaft flow distribution servo valve, which comprises a shaft flow distribution valve body stator, a shaft flow distribution valve sleeve and a shaft flow distribution valve core rotor, the axial flow distribution valve body stator is divided into four stator sealing areas which are not communicated with each other from top to bottom respectively, the shaft distribution valve core rotor is divided into four rotor sealing areas which are not communicated from top to bottom respectively, four sealing areas corresponding to the shaft flow distribution valve body stator from top to bottom are respectively provided with a working oil port A, a working oil port B, an oil supply port and an oil return port, the rotating shaft distribution valve core rotor respectively realizes the continuous proportion communication control between the oil supply channel and the oil return channel and the working oil port A and the working oil port B respectively, and further realizes the continuous different proportion speed control of an external actuating mechanism. Compared with the prior art, the invention has the advantages of large through-flow capacity, reduced rotary wear 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 servo valve.
Background
In the period from the end of the 18 th century to the beginning of the 19 th century, european people invented a single-stage jet pipe valve principle, a single-stage single-nozzle flapper valve and a single-stage double-spraying-group flapper valve, and in the second world war period, with the appearance of new materials, people invented a solenoid and a torque motor, then a two-stage electro-hydraulic servo valve and a two-stage electro-hydraulic servo valve with feedback were developed successively, most of electro-hydraulic servo valves in the 60 th century were two-stage servo valves with feedback and torque motors, and high-reliability multi-redundancy electro-hydraulic servo valves appeared in the aerospace and military fields.
There are many kinds of electro-hydraulic servo valves, and at present, there are mainly dual-nozzle flapper-type electro-hydraulic servo valves, jet servo valves, direct-acting electro-hydraulic servo valves, electro-feedback electro-hydraulic servo valves, and moving-coil/moving-iron/single-nozzle electro-hydraulic servo valves. The nozzle baffle type electro-hydraulic servo valve is mainly characterized in that: the structure is simple, the manufacture is precise, the characteristics can be predicted, no dead zone and friction pair exist, the sensitivity is high, the inertia of the baffle is small, and the dynamic response is high; the jet servo valve has the disadvantages of small distance between the baffle and the nozzle and poor pollution resistance, and is mainly characterized in that: the nozzle has large size, good pollution resistance, high volume efficiency, failure centering, high sensitivity and high resolution; the disadvantages are high processing difficulty and complex process.
The electro-hydraulic servo valve and the electro-hydraulic proportional valve are core elements of a hydraulic control system, the requirement on precision is high, detection and maintenance cost is improved, assembly of the electro-hydraulic servo valve and the electro-hydraulic proportional valve relates to matching of a plurality of precision coupling parts, and inevitable errors exist in machining processes of all parts, so that the electro-hydraulic servo valve and the electro-hydraulic proportional valve after assembly have certain uncertainty in performance, and the problems of abrasion, leakage and small flow rate can also occur.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a high-flow axial flow distribution servo valve.
The purpose of the invention can be realized by the following technical scheme:
a high-flow shaft flow distribution servo valve comprises a shaft flow distribution valve body stator, a shaft flow distribution valve sleeve and a shaft flow distribution valve core rotor, wherein the shaft flow distribution valve body sleeve is cold-assembled in the shaft flow distribution valve body stator, the shaft flow distribution valve core rotor is rotatably installed in the shaft flow distribution valve sleeve, the shaft flow distribution valve body stator is divided into four stator sealing areas which are not communicated with each other from top to bottom through 5 stator sealing rings which are sequentially arranged, the shaft flow distribution valve core rotor is divided into four rotor sealing areas which are not communicated with each other and are in one-to-one correspondence with the four stator sealing areas from top to bottom through 5 rotor 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 are respectively formed in the four sealing areas which correspond to the shaft flow distribution valve body stator from top to bottom, the working oil port A and the working oil port B are respectively communicated with an external execution mechanism, and 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 a plurality of oil supply channels, a plurality of oil return channels and through holes for reducing mass and increasing torque along the axial direction, and the oil supply channels and the oil return channels are respectively communicated and controlled with the continuous proportion between the working oil port A and the working oil port B through the rotating shaft flow distribution valve core rotor, so that the continuous different proportion speed control of an external actuating mechanism is realized, and the state of the actuating mechanism in a set rotating angle range is kept unchanged.
The connecting direction of the axis of the stator of the axial flow distribution valve body and the center of the working oil port A is 0 degree, the clockwise direction is the positive direction, the opening angle between the working oil port A and the working oil port B is 180 degrees, two oil supply ports and two oil return ports are respectively arranged, and the opening angles are +90 degrees and-90 degrees respectively.
The number of the through holes is one, the through holes are formed in the center of the shaft distribution valve core rotor, the number of the oil supply channels is 6 in the range of 0-180 degrees in the circumferential direction, the number of the oil return channels is 6 in the range of 180-360 degrees in the circumferential direction, and the oil return channels and the oil supply channels are arranged in bilateral symmetry by taking a 0-degree straight line as a symmetry axis.
The first rotor sealing area is specifically an area between a first rotor sealing ring and a second rotor sealing ring, a first groove, a second groove, a first throttling groove, a second throttling groove, a third throttling groove, a fourth throttling groove, a fifth throttling groove and a sixth throttling groove which are separated by a non-slotted section are respectively and sequentially arranged on the outer surface of the rotor of the shaft distributing valve core at a first horizontal set position in the first rotor sealing area along the circumferential direction, the first groove and the second groove are identical in structure and are symmetrically arranged and are respectively arranged in the range of +3 degrees to +17 degrees and-3 degrees to-17 degrees, the first groove is gradually deepened and gradually widened along the clockwise direction, the second groove is gradually deepened and gradually widened along the counterclockwise direction so as to realize continuous proportional flow control, and the first throttling groove, the second throttling groove and the third throttling groove are respectively communicated with 3 corresponding oil return channels, the fourth throttling groove, the fifth throttling groove and the sixth throttling groove are respectively communicated with 3 corresponding oil supply channels, the range of a central angle corresponding to each throttling groove is smaller than 12 degrees, and the arc length and the axial size of each section of the section which is not slotted in the circumferential direction are both larger than the bottom diameter of the working oil port A, so that the working oil port is blocked in the rotating process.
The first stator sealing area is specifically an area between the first stator sealing ring and the second stator sealing ring, two long grooves which are not communicated with each other are symmetrically formed in the first horizontal setting position of the first stator sealing area on the inner surface of a stator of the shaft flow distribution valve body along the circumferential direction, a first hole communicated with the first groove and a second hole communicated with the second groove are formed in the first horizontal setting position of the shaft flow distribution valve body, three third holes and three fourth holes formed in the positions of-45 degrees, -90 degrees and-135 degrees are formed in the positions of +45 degrees, +90 degrees and +135 degrees respectively, the first hole and the three third holes are communicated with the first long groove respectively, and the second hole and the three fourth holes are communicated with the second long groove respectively.
When the high-flow shaft flow distribution servo valve is positioned at a 0 signal, the central angles between the first throttling groove, the second throttling groove and the third throttling groove and the corresponding third hole are respectively 5 degrees, the central angles between the fourth throttling groove, the fifth throttling groove and the sixth throttling groove and the corresponding fourth hole are respectively 5 degrees, and the shape of each throttling groove in the conduction direction is gradually deepened and gradually enlarged so as to realize continuous proportional flow control.
The structures of the second rotor sealing area of the shaft flow distribution valve core rotor and the second stator sealing area of the shaft flow distribution valve body stator are respectively corresponding to the structures of the first rotor sealing area and the second stator sealing area and are separated by 180 degrees.
The third rotor sealing area is specifically an area between a third rotor sealing ring and a fourth rotor sealing ring, the outer surface of the rotor of the shaft distribution valve core is provided with a groove in the third rotor sealing area in the full circumferential direction, and the two oil supply ports are respectively communicated with the oil supply channel through the hole in the valve sleeve of the shaft distribution valve and the full circumferential groove.
The fourth rotor sealing area is specifically an area between a fourth rotor sealing ring and a fifth rotor sealing ring, the outer surface of the shaft distribution valve core rotor is provided with a groove in the fourth rotor sealing area in the full circumferential direction, and the two oil return ports are respectively communicated with the oil return channel through the hole in the shaft distribution valve sleeve and the groove in the full circumferential direction.
When the high-flow shaft flow distribution servo valve is positioned at a 0 signal, a non-grooved section between the first groove and the second groove seals the working oil port A, when the clockwise rotation shaft flow distribution valve core rotor reaches a right end position, the working oil port A is respectively communicated with the first oil supply channel and the second long groove through the second groove, the rest oil supply channels are respectively communicated with the second long groove through the corresponding throttling grooves, further the communication with the working oil port A is realized, in the process that the clockwise rotation shaft flow distribution valve core rotor reaches the right end position, the second groove is communicated with the second long groove before the throttling grooves, the leakage amount is reduced, meanwhile, the working oil port B is communicated with the oil return channel, and similarly, when the counterclockwise rotation shaft flow distribution valve core rotor reaches the left end position, the working oil port A is communicated with the oil return channel, and the working oil port B is communicated with the oil supply 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, realizes shaft flow distribution by adopting a form of slotting on a rotor shaft and a pair of oil supply channels P and oil return channels T, and effectively avoids the influence on the control performance caused by processing errors and assembly errors by arranging the valve sleeve of the shaft flow distribution valve in a cold assembly installation mode in the stator of the shaft flow distribution valve body.
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, the gap sealing length between the working oil port and the oil supply/return passage is realized, and the position matching of the throttling groove, the groove and the hole in the valve sleeve is matched, so that the leakage amount is further reduced, and the circulation capacity is further increased.
And sixthly, the through hole is formed in the shaft distribution valve core rotor, so that the mass of the rotating shaft can be effectively reduced, the driving torque of the servo motor is reduced, and the rotation control is facilitated.
And seventhly, the invention effectively enlarges the circulation area and the circulation volume by arranging a plurality of grooves and throttling grooves which are matched and communicated with the long grooves.
Drawings
FIG. 1 is a front cross-sectional view of the structure of the present invention at each opening.
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.
Fig. 5 is a cross-sectional view of section IV-IV of fig. 1.
The notation in the figure is:
1. the high-flow shaft flow distribution servo valve comprises a high-flow shaft flow distribution servo valve body, 2, a shaft flow distribution valve core rotor, 3, a rotor sealing ring, 4, a shaft flow distribution valve sleeve, 5, a shaft flow distribution valve body stator, 6, a stator sealing ring, 31, a first rotor sealing ring, 32, a second rotor sealing ring, 33, a third rotor sealing ring, 34, a fourth rotor sealing ring, 35, a fifth rotor sealing ring, 61, a first stator sealing ring, 62, a second stator sealing ring, 63, a third stator sealing ring, 64, a fourth stator sealing ring, 65, a fifth stator sealing ring, P, an oil supply channel, T, an oil return channel, A/B, a stator working oil port, P0, an oil supply port, T0, an oil return port, P1, a first oil supply port, T1, a first oil return port, P2, a second oil return port, T2 and a second 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 servo valve, which comprises an internal axial flow distribution valve core rotor 2, an axial flow distribution valve sleeve 4, an external axial flow distribution valve stator 5, and a corresponding rotor seal ring 3 and a corresponding stator seal ring 6, wherein the axial flow distribution valve sleeve 4 and the axial flow distribution valve stator 5 are cold-assembled, and a through hole is formed in the axial center of the axial flow distribution valve rotor 2 to reduce the mass of the axial flow distribution valve rotor.
The rotor 2 of the distributing valve core of the adjusting shaft rotates to different angles, so that the working oil port is communicated with the oil supply port and the oil return port in a continuous proportion, the continuous different-proportion speed control of the action of the executing mechanism is realized, the executing mechanism can be kept unchanged in a specific rotation angle range, and the distributing valve core has the advantages of few parts, convenience in processing, compact and simple structure, convenience in adjustment, high through-flow capacity, simplicity and convenience in maintenance, high repeatability and the like.
The shaft distribution valve core rotor 2 is divided into four rotor sealing areas by 5 rotor sealing rings 3 from top to bottom, and the communication relation between the four rotor sealing areas and the stator working oil port is as follows:
the first rotor sealing area is a range contained between the first rotor sealing ring 31 and the second rotor sealing ring 32, and the first rotor sealing area is communicated with the working oil port A of the stator under the rotation control;
the second rotor sealing area is a range contained between a second rotor sealing ring 32 and a third rotor sealing ring 33, and the second rotor sealing area is communicated with a working oil port B of the stator under the rotation control;
the third rotor sealing area is specifically a range contained between the third rotor sealing ring 33 and the fourth rotor sealing ring 34, and is grooved in the whole circumferential direction;
the fourth rotor sealing area is specifically a range included between the fourth rotor sealing ring 34 and the fifth rotor sealing ring 35, and is grooved all around;
the communicating relation between the four rotor sealing areas and the rotor oil supply passage P and the oil return passage T is as follows:
the first rotor sealing area is communicated with an oil supply channel P and an oil return channel T of the rotor; the second rotor sealing area is communicated with an oil supply channel P and an oil return channel T of the rotor, the third rotor sealing area is communicated with the oil supply channel P of the rotor, and the fourth rotor sealing area is only communicated with the oil return channel T of the rotor;
the shaft flow distribution valve stator 5 is divided into four stator sealing areas by 5 stator sealing rings 6 from top to bottom, and the communication relation between the four stator sealing areas and the stator working oil port is as follows:
the first stator sealing area is specifically a range included between the first stator sealing ring 61 and the second stator sealing ring 62, a working oil port a is arranged in the first stator sealing area, two symmetrical long grooves are formed in the circumferential direction, and the long grooves are used for realizing communication between the working oil port a and the oil supply channel P and the oil return channel T in the rotating process;
the second stator sealing area is specifically a range contained between the second stator sealing ring 62 and the third stator sealing ring 63, a working oil port B is arranged in the second stator sealing area, two symmetrical long grooves are formed in the circumferential direction, and the long grooves are used for realizing the conduction between the working oil port B and the oil supply channel P and the oil return channel T in the rotating process;
the third stator seal region is specifically a range included between the third stator seal ring 63 and the fourth stator seal ring 64;
the fourth stator seal area is specifically the area encompassed between the fourth stator seal 64 and the fifth stator seal 65.
As shown in fig. 2, in a first horizontal setting position (I-I cross section), with the center line of the working oil port a as a reference (0 °), the clockwise direction is the forward direction, a gradually-deep and gradually-wide groove is formed between +3 ° - +17 ° and-3 ° -17 ° on the surface of the shaft distribution valve core rotor 2, and the first groove and the second groove are respectively communicated with an oil return channel T and an oil supply channel P corresponding to the shaft distribution valve core rotor 2;
starting from 45 degrees, opening circular holes at intervals of 45 degrees on the valve sleeve 4 of the shaft distribution valve, wherein three circular holes are arranged on each side, the rotating angle of the six circular holes in a plane circle of the rotor 2 of the shaft distribution valve is 17 degrees at most, in the range of 0-180 degrees, throttling grooves with gradually increasing depth are formed after the three circular holes are clockwise 5 degrees, and the central angle of each throttling groove is 12 degrees at most; the bottom end of the throttling groove is respectively provided with an opening which is communicated with an oil return channel T and an oil supply channel P on the shaft distributing valve rotor; eight non-grooved sections are divided among the eight grooves (2 grooves and 6 throttling grooves), and the arc length and the axial size of each non-grooved area in the circumferential direction are larger than the bottom diameter of the working oil port A;
as shown in fig. 3, in the second horizontal setting position (section II-II), with the center line of the working oil port B as a reference (0 °), and the clockwise direction as the forward direction, the gradually-deepened and gradually-widened grooves are formed between +3 ° +17 ° and-3 ° -17 ° on the surface of the shaft distribution valve core rotor 2, and the oil return channels T corresponding to the third and fourth grooves are communicated with each other and the oil supply channel P is communicated with each other;
starting from 45 degrees, opening circular holes at intervals of 45 degrees on the valve sleeve 4 of the shaft distribution valve, wherein three circular holes are arranged on each side, the rotating angle of the six circular holes in a plane circle of the rotor 2 of the shaft distribution valve is 17 degrees at most, in the range of 0-180 degrees, throttling grooves with gradually increasing depth are formed after the three circular holes are clockwise 5 degrees, and the central angle of each throttling groove is 12 degrees at most; the bottom end of the throttling groove is respectively provided with an opening which is communicated with an oil return channel T and an oil supply channel P on the shaft distributing valve rotor; eight non-grooved sections are divided among the eight grooves (2 grooves and 6 throttling grooves), and the arc length and the axial size of each non-grooved area in the circumferential direction are larger than the bottom diameter of the working oil port B;
as shown in fig. 4, in the section of the third sealing area III-III, the shaft distribution valve core rotor 2 is in a full-circumference slotted mode and is communicated with a middle P channel of the shaft distribution valve core rotor 2;
as shown in fig. 5, in the section of the fourth sealing area IV-IV, the shaft distribution valve core rotor 2 is in a full-circumference slotted mode and is communicated with a middle T channel of the shaft distribution valve core rotor 2;
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.
Except that the overlapping amount between the first oil supply channel and the working oil port A/B is about 3%, the overlapping amount between the other oil supply channels and the first oil supply channel is about 5% so as to reduce the leakage flow of the shaft flow distribution servo valve in the 0 signal, and the overlapping amount between the first oil supply channel and the working oil port forms the pressure gain of the servo function flow distribution valve in the 0 signal.
The relative relationship of the related functions is illustrated by taking the following related angles as examples:
the working angle of the shaft flow distribution servo valve is +/-17 degrees;
the working oil port A is communicated with the oil supply channel P in the clockwise rotation direction of the rotor, and the working oil port B is communicated with the oil return channel T in the clockwise rotation direction;
on the contrary, the working oil port a is communicated with the oil return passage T in the counterclockwise rotation direction of the rotor, and the working oil port a is communicated with the oil supply passage P in the counterclockwise rotation direction.
Claims (10)
1. A high-flow axial flow distribution servo valve is characterized by comprising an axial flow distribution valve body stator (5), an axial flow distribution valve sleeve (4) which is cold-assembled in the axial flow distribution valve body stator (5) and an axial flow distribution valve core rotor (2) which is rotatably arranged in the axial flow distribution valve sleeve (4), wherein the axial flow distribution valve body stator (5) is divided into four stator sealing areas which are not communicated with each other from top to bottom through 5 stator sealing rings which are sequentially arranged, the axial flow distribution valve core rotor (2) is divided into four rotor sealing areas which are not communicated with each other and are in one-to-one correspondence with the four stator sealing areas from top to bottom through 5 rotor sealing rings which are sequentially arranged, the four sealing areas which correspond to the axial flow distribution valve body stator (5) from top to bottom are respectively provided with a working oil port A, a working oil port B, an oil supply port (P0) and an oil return port (T0), the hydraulic control system is characterized in that the working oil port A and the working oil port B are respectively communicated with an external actuating mechanism, the oil supply port (P0) and the oil return port (T0) are respectively communicated with an external oil source, a plurality of oil supply channels (P), a plurality of oil return channels (T) and a through hole for reducing mass and increasing torque are formed in the shaft distribution valve core rotor (2) along the axial direction, and continuous proportion communication control between the oil supply channels (P) and the oil return channels (T) and the working oil port A and the working oil port B is respectively realized through the rotating shaft distribution valve core rotor (2), so that continuous different proportion speed control of the external actuating mechanism is realized, and the actuating mechanism in a set rotating angle range is kept unchanged.
2. The high-flow axial flow distribution servo valve according to claim 1, wherein the direction of a connecting line between the axis of the stator of the axial flow distribution valve body and the center of the working oil port a is 0 °, the clockwise direction is the positive direction, the opening angle between the working oil port a and the working oil port B is 180 °, two oil supply ports (P0) and two oil return ports (T0) are provided, and the opening angles are +90 ° and-90 ° respectively.
3. The high-flow axial flow distribution servo valve according to claim 2, wherein one through hole is formed in the center of the axial flow distribution valve core rotor (2), 6 oil supply channels (P) are formed in the range of 0-180 degrees in the circumferential direction, 6 oil return channels (T) are formed in the range of 180-360 degrees in the circumferential direction, and the oil return channels (T) and the oil supply channels (P) are arranged in a left-right symmetrical mode by taking a 0-degree straight line as a symmetrical axis.
4. The high-flow axial flow distribution servo valve according to claim 3, wherein the first rotor sealing area is a region between a first rotor sealing ring (31) and a second rotor sealing ring (32), the outer surface of the axial flow distribution valve core rotor (2) is provided with a first groove, a second groove, a first throttling groove, a second throttling groove, a third throttling groove, a fourth throttling groove, a fifth throttling groove and a sixth throttling groove which are separated by a non-slotted section at a first horizontal setting position in the first rotor sealing area along the circumferential direction, the first groove and the second groove are same in structure and are symmetrically arranged and are respectively arranged in the range of +3 degrees to +17 degrees and-3 degrees to-17 degrees, the shape of the first groove along the clockwise direction is gradually deeper and wider, the shape of the second groove along the counterclockwise direction is gradually deeper and wider, the first throttling groove, the second throttling groove and the third throttling groove are respectively communicated with 3 corresponding oil return channels, the fourth throttling groove, the fifth throttling groove and the sixth throttling groove are respectively communicated with 3 corresponding oil supply channels, the range of a central angle corresponding to each throttling groove is smaller than 12 degrees, and the arc length and the axial size of each section of the section which is not slotted in the circumferential direction are larger than the bottom diameter of the working oil port A, so that the working oil port is blocked in the rotating process.
5. The high-flow axial flow distribution servo valve according to claim 4, wherein the first stator sealing area is specifically an area between the first stator sealing ring (61) and the second stator sealing ring (62), two long slots which are not communicated with each other are symmetrically arranged on the inner surface of the stator (5) of the axial flow distribution valve body at a first horizontal setting position of the first stator sealing area along the circumferential direction, the shaft valve sleeve (4) is provided with a first hole communicated with the first groove, a second hole communicated with the second groove, three third holes at the positions of +45 degrees, +90 degrees and +135 degrees and three fourth holes at the positions of-45 degrees, -90 degrees and-135 degrees along the circumferential direction at a first horizontal setting position, the first hole and the three third holes are respectively communicated with the first long slot, and the second hole and the three fourth holes are respectively communicated with the second long slot.
6. The high-flow axial flow distribution servo valve according to claim 5, wherein when the high-flow axial flow distribution servo valve is at 0 signal, the central angles between the first throttling groove, the second throttling groove and the third throttling groove and the corresponding third hole are respectively 5 °, the central angles between the fourth throttling groove, the fifth throttling groove and the sixth throttling groove and the corresponding fourth hole are respectively 5 °, and the shape of each throttling groove in the conduction direction gradually deepens and gradually enlarges to realize continuous proportional flow control.
7. A high flow rate axial flow distributing servo valve according to claim 6, characterized in that the second rotor sealing area of the axial flow distributing valve core rotor (2) and the second stator sealing area of the axial flow distributing valve body stator (5) have the same structure and are spaced 180 ° apart from the first rotor sealing area and the second stator sealing area, respectively.
8. A high flow rate shaft valve according to claim 3, wherein the third rotor sealing area is a region between the third rotor sealing ring (33) and the fourth rotor sealing ring (34), the outer surface of the shaft valve core rotor (2) is circumferentially grooved in the third rotor sealing area, and the two oil supply ports are respectively communicated with the oil supply channel (P) through the hole of the shaft valve sleeve and the circumferentially grooved.
9. A high flow rate shaft distributing servo valve according to claim 3, wherein the fourth rotor sealing area is specifically the area between the fourth rotor sealing ring (34) and the fifth rotor sealing ring (35), the outer surface of the shaft distributing valve core rotor (2) is circumferentially grooved in the fourth rotor sealing area, and the two oil return ports are respectively communicated with the oil return channel (T) through the holes on the shaft distributing valve sleeve and the circumferential grooves.
10. The high flow rate axial flow distribution servo valve according to claim 7, wherein when the high flow rate axial flow distribution servo valve is at 0 signal, the un-grooved section between the first groove and the second groove seals the working oil port A, when the valve core rotor is rotated clockwise to the right end position, the working oil port A is communicated with the first oil supply channel and the second long groove through the second groove, and the rest oil supply channels are communicated with the second long groove through the corresponding throttling groove, respectively, to further achieve the communication with the working oil port A, and when the valve core rotor is rotated clockwise to the right end position, the second groove is communicated with the second long groove before the throttling groove to reduce the leakage, and at the same time, the working oil port B is communicated with the oil return channel (T), similarly, when the valve core rotor is rotated counterclockwise to the left end position, the working oil port A is communicated with the oil return channel (T), and the working oil port B is communicated with the oil supply channel (P).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110307359.3A CN112855647B (en) | 2021-03-23 | 2021-03-23 | Large-flow shaft flow distribution servo valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110307359.3A CN112855647B (en) | 2021-03-23 | 2021-03-23 | Large-flow shaft flow distribution servo valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112855647A CN112855647A (en) | 2021-05-28 |
| CN112855647B true CN112855647B (en) | 2021-12-31 |
Family
ID=75992310
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110307359.3A Active CN112855647B (en) | 2021-03-23 | 2021-03-23 | Large-flow shaft flow distribution servo valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112855647B (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05333939A (en) * | 1992-06-04 | 1993-12-17 | Toshiba Corp | Valve assembly |
| BRPI0408657A (en) * | 2003-03-28 | 2006-03-28 | Microgen Energy Ltd | separating valve |
| CN201763711U (en) * | 2010-02-01 | 2011-03-16 | 长沙溇澧机电科技有限公司 | Hydraulic proportional control valve |
| CN102297171A (en) * | 2010-07-30 | 2011-12-28 | 三一重工股份有限公司 | Hydraulic valve, hydraulic valve group and hydraulic valve control method |
| CN102434504A (en) * | 2011-12-09 | 2012-05-02 | 哈尔滨工业大学 | Hydraulic transformer with axial flow distribution |
| CN102619798A (en) * | 2011-01-26 | 2012-08-01 | 南京工程学院 | High-frequency hydraulic rotating valve |
| CN203115181U (en) * | 2013-03-19 | 2013-08-07 | 宋久林 | Rotating type multichannel reversing valve |
| CN205534383U (en) * | 2015-10-17 | 2016-08-31 | 丰铁机械(苏州)有限公司 | A rotatory valve tower structure for carrying low pressure fluid |
| CN112049829A (en) * | 2020-08-18 | 2020-12-08 | 温州大学 | Bidirectional variable mechanism and bidirectional variable pump |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106567944B (en) * | 2016-09-19 | 2019-03-26 | 北京精密机电控制设备研究所 | A kind of big flow servo valve multi-step variable cross-section slide valve pair |
-
2021
- 2021-03-23 CN CN202110307359.3A patent/CN112855647B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05333939A (en) * | 1992-06-04 | 1993-12-17 | Toshiba Corp | Valve assembly |
| BRPI0408657A (en) * | 2003-03-28 | 2006-03-28 | Microgen Energy Ltd | separating valve |
| CN201763711U (en) * | 2010-02-01 | 2011-03-16 | 长沙溇澧机电科技有限公司 | Hydraulic proportional control valve |
| CN102297171A (en) * | 2010-07-30 | 2011-12-28 | 三一重工股份有限公司 | Hydraulic valve, hydraulic valve group and hydraulic valve control method |
| CN102619798A (en) * | 2011-01-26 | 2012-08-01 | 南京工程学院 | High-frequency hydraulic rotating valve |
| CN102434504A (en) * | 2011-12-09 | 2012-05-02 | 哈尔滨工业大学 | Hydraulic transformer with axial flow distribution |
| CN203115181U (en) * | 2013-03-19 | 2013-08-07 | 宋久林 | Rotating type multichannel reversing valve |
| CN205534383U (en) * | 2015-10-17 | 2016-08-31 | 丰铁机械(苏州)有限公司 | A rotatory valve tower structure for carrying low pressure fluid |
| CN112049829A (en) * | 2020-08-18 | 2020-12-08 | 温州大学 | Bidirectional variable mechanism and bidirectional variable pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112855647A (en) | 2021-05-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106737827B (en) | Corner self-servo passive flexible hydraulic robot joint | |
| CN112855647B (en) | Large-flow shaft flow distribution servo valve | |
| CN113027846B (en) | Synchronous-acting shaft flow distribution switch reversing multi-way valve | |
| CN112901586B (en) | Shaft flow distribution proportional reversing multi-way valve with sequential action | |
| US3630230A (en) | Fluid valve with controlled axial thrust | |
| CN112855648B (en) | Multi-redundancy shaft flow distribution servo valve | |
| CN111649021A (en) | Two-dimensional force feedback type electro-hydraulic servo valve | |
| US3773081A (en) | Power steering gear assembly | |
| CN113027845B (en) | Synchronous-acting shaft flow distribution proportional reversing multi-way valve | |
| CN113266613B (en) | Large-flow shaft flow distribution proportion servo valve | |
| JP2607754B2 (en) | Planetary roller type flow control valve | |
| US11092249B2 (en) | Binary mode fluid valve | |
| CN112943731B (en) | Reversing valve of shaft flow distribution switch | |
| CN111749939A (en) | Large-traffic two-dimensional piston flow servo valve | |
| US4700747A (en) | Proportional hydraulic distributor | |
| CN112922917B (en) | Axial flow distribution proportional servo valve | |
| US3586051A (en) | Rotary union | |
| CN112963398B (en) | Axial flow distribution proportional reversing valve | |
| CN112983917B (en) | Shaft flow distribution switch reversing multi-way valve with sequential action | |
| CN210371410U (en) | Large-traffic two-dimensional piston flow servo valve | |
| CN113175458B (en) | Multistage damping low-noise reversing valve | |
| CN112879602A (en) | Axial flow distribution pulse switch valve | |
| CN113153850A (en) | Shaft flow distribution high-frequency switch reversing valve | |
| CN117108576A (en) | Flow-adjustable three-position four-way rotary valve | |
| CN218235339U (en) | Low-speed large-torque radial plunger motor with middle through hole |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |