阅读说明：本技术 一种新型大流量电液伺服阀 (Novel large-flow electro-hydraulic servo valve ) 是由 刘勇 姚巍林 毛利亚 路超 李通 王红利 陈志鹏 朱登魁 陈浩 于 2020-11-26 设计创作，主要内容包括：本发明公开了一种新型大流量电液伺服阀,解决了现有双喷嘴挡板式两级电液伺服阀的滑阀刚性冲击大、工作稳定性差、调零麻烦和易零偏的技术问题。本发明包括相连的双喷嘴挡板调节器和阀套组件,所述阀套组件包括相互配合的滑阀、阀套和阀体,双喷嘴挡板调节器的反馈杆穿过阀体和阀套与滑阀相连,滑阀为中空结构,阀套内壁设置有导控通道,阀套、阀体、滑阀和双喷嘴挡板调节器之间设置有导控油路和配流油路。本发明阀套的A配流口和B配流口的具有较大的结构特征,适用于大流量的场合,回油油液需要通过滑阀流至回油口,实现大流量的同时保证了稳、准、快的要求。(The invention discloses a novel high-flow electro-hydraulic servo valve, which solves the technical problems of large rigid impact of a slide valve, poor working stability, trouble zero setting and easy zero offset of the traditional double-nozzle baffle type two-stage electro-hydraulic servo valve. The double-nozzle baffle regulator comprises a double-nozzle baffle regulator and a valve sleeve assembly which are connected, wherein the valve sleeve assembly comprises a slide valve, a valve sleeve and a valve body which are matched with each other, a feedback rod of the double-nozzle baffle regulator penetrates through the valve body and the valve sleeve to be connected with the slide valve, the slide valve is of a hollow structure, a guide and control channel is arranged on the inner wall of the valve sleeve, and a guide and control oil path and a flow distribution oil path are arranged among the valve sleeve, the valve body, the slide valve and the. The flow distribution port A and the flow distribution port B of the valve sleeve have larger structural characteristics, and are suitable for occasions with large flow, return oil needs to flow to the return port through the slide valve, and the requirements of stability, accuracy and quickness are met while the large flow is realized.)

1. The utility model provides a novel large-traffic electro-hydraulic servo valve, includes continuous two nozzle baffle regulator and valve barrel subassembly, the valve barrel subassembly sets up slide valve (17), its characterized in that including valve body (9) of seting up P mouth (29), A mouth (30), B mouth (31) and O mouth (32) in valve body (9): a valve sleeve (15) is arranged between the valve body (9) and the slide valve (17), a feedback rod (19) of the double-nozzle baffle regulator penetrates through the valve body (9) and the valve sleeve (15) to be connected with the slide valve (17), an oil inlet (43) communicated with the P port (29) respectively, an A flow distribution port (26) matched with the A port (30), a B flow distribution port (27) matched with the B port (31) and an oil return port (28) communicated with the O port (32) are arranged on the valve sleeve (15), annular protrusions (33) matched with the A flow distribution port (26) and the B flow distribution port (27) respectively are arranged on the periphery of the slide valve (17) at intervals, an oil return channel (34) communicated with the B flow distribution port (27) and the oil return port (28) when the slide valve (17) moves is arranged in the slide valve (17), oil return holes (41) communicated with the oil return channel (34) are arranged at two end parts of the slide valve (17), and a ring communicated with the A flow distribution port (26) and the oil return port (28) when the slide valve (17 The two-nozzle baffle regulator comprises a shape groove (40), guide and control oil cavities are arranged between two end parts of a slide valve (17) and a valve sleeve (15), guide and control channels for communicating a P port (29) with the guide and control oil cavities are arranged in the valve sleeve (15), the guide and control oil cavities are communicated with a nozzle pipe (22) of the double-nozzle baffle regulator through a valve body (9), and the nozzle pipe (22) is communicated with an oil return hole (41).

2. The new high flow electro-hydraulic servo valve of claim 1, characterized by: the double-nozzle baffle regulator comprises a guide valve body (21) connected with a valve body (9), a threaded hole is formed in the guide valve body (21), a nozzle pipe (22) is in threaded connection with the guide valve body (21) through the threaded hole, and a channel communicated with a guide control oil cavity and the nozzle pipe (22) is formed in the guide valve body (21).

3. The new high flow electro-hydraulic servo valve of claim 2, characterized by: and a nozzle nut (23) is arranged at the outer end part of the nozzle pipe (22).

4. A new high flow electro-hydraulic servo valve according to any of claims 1-3, characterized by: the two ends of the valve sleeve (15) are provided with guide control assemblies, each guide control assembly comprises a guide control piston sleeve (11), a guide control piston (14) is arranged in each guide control piston sleeve (11), the inner end of each guide control piston (14) penetrates through each guide control piston sleeve (11) to be pressed against the end of the corresponding slide valve (17), the outer end of each guide control piston (14) is provided with a guide control spring (12), the outer end of each guide control spring (12) is provided with a guide control end cover (13), each guide control end cover (13) and the outer end of each guide control piston (14) form a guide control oil cavity, and each guide control piston sleeve (11) is provided with a guide oil port (35) communicated with each guide control channel.

5. The new high flow electro-hydraulic servo valve of claim 4, characterized by: the pilot control channel comprises a first axial channel (36) arranged in a valve sleeve (15), an inner port of the first axial channel (36) is communicated with a P port (29), an outer port of the first axial channel is connected with a first radial channel (37), a second radial channel (38) communicated with the first radial channel (37) is arranged on the inner wall of the valve body (9), an inner port of the first radial channel (37) is communicated with a pilot oil port (35), an outer port of the first radial channel is communicated with the second radial channel (38), and a second axial channel (39) communicated with the second radial channel (38) and a nozzle pipe (22) is arranged in the valve body (9).

6. The new high flow electro-hydraulic servo valve of claim 5, characterized by: the guide control piston sleeve (11) is T-shaped, the axial section of the guide control piston sleeve (11) is in trapezoidal fit with the inner wall of the valve sleeve (15), the radial section of the guide control piston sleeve (11) is buckled and pressed at the end part of the valve sleeve (15), the outer part of the radial section is buckled and pressed with an end cover (10), and the end cover (10) is in sealing connection with the valve body (9).

7. The new high flow electro-hydraulic servo valve according to claim 5 or 6, characterized by: the outer ports of the first axial channel (36) and the second axial channel (39) respectively extend to the outer end faces of the valve sleeve (15) and the valve body (9), the outer port of the first axial channel (36) and the radial section of the guide control piston sleeve (11) form end face seal, and the outer port of the second axial channel (39) forms end face seal through a plug (20) or with an end cover (10).

8. The new high flow electro-hydraulic servo valve of claim 7, characterized by: the first axial channel (36) is provided with two symmetrical left and right channels arranged in the valve sleeve (15), a corresponding through hole is formed between the valve body (9) and the valve sleeve (15), a lining (18) is arranged in the through hole, and the feedback rod (19) is inserted in the lining (18).

9. A new high flow electro-hydraulic servo valve according to any of claims 1-3, 5-6, 8, characterized by: the oil return hole (41) is arranged in the annular groove (40), an annular groove is formed in the annular groove (40), and the end part of the feedback rod (19) is inserted into the annular groove.

10. The new high flow electro-hydraulic servo valve of claim 9, characterized by: the guide control piston (14) and the guide control piston sleeve (11) are arranged at the insertion matching position and provided with a pressure equalizing groove, the sliding valve (17) comprises a hollow cylindrical body, a sealing plate (16) is arranged at the end part of the cylindrical body, and a horizontal hole (42) which is communicated with the inside and the outside is formed in the sealing plate (16).

Technical Field

The invention relates to the technical field of electro-hydraulic servo valves, in particular to a novel high-flow electro-hydraulic servo valve.

Background

As shown in fig. 1, the structure of the conventional dual-nozzle flapper type two-stage electro-hydraulic servo valve includes a dual-nozzle flapper valve and a force feedback centering slide valve, and mainly includes an armature 100, a coil assembly 101, a flapper 102, a nozzle 103, a feedback rod 104, an orifice 105, a permanent magnet 106, a spring tube 107, a magnetizer 108, a slide valve 109, a valve body 110, and the like. The double-nozzle baffle valve is connected with the force feedback centering slide valve through an oil way, and the force feedback centering slide valve is respectively connected with high-pressure oil and a load cavity through the oil way. The dual nozzle flapper valve is located in an intermediate position of the valve body, with the armature 100, flapper 102 and feedback rod 104 rigidly fixed together and supported by a spring tube 107. Hydraulic oil flows in from the ports P on both sides, one way through the two fixed orifices 105, through the nozzle 103 and two variable orifices in the form of baffles, and finally into the return chamber O. The armature baffle assembly deflects under the action of an electrical control signal, so that the baffle 102 deflects to drive the slide valve 109 to move left and right, and the port P is communicated with the port A or the port B. When the flapper 102 is deflected, the orifice between the flapper and one nozzle 103 becomes smaller, and the orifice between the flapper and the other nozzle 103 becomes larger. The pressure difference between the oil on both sides of the spool 109 is formed, so that the oil pushes the spool 109 to move, and the moving position of the spool is realized through the feedback rod.

In the conventional two-stage electrohydraulic servo valve of the double-nozzle flapper type, the clearance between the orifice 105 and the end face of the nozzle 103 is small, and the inner diameters of the orifice 105 and the nozzle 103 are small, so that the orifice is easily blocked by contaminants, thereby causing the failure of the slide valve 109. Moreover, the nozzle 103 is troublesome to install, which causes difficulty in zeroing, and the slide valve 109 is prone to cause zero offset and zero drift. In the normal operation mode of the slide valve 109, the two end faces of the slide valve 109 are easy to generate rigid impact with the end cover, and the operation stability is poor. For an electro-hydraulic servo valve control system with large inertia, small external load and large load change, the improvement of the damping of the system is an effective method for enhancing the stability of the system.

However, any electro-hydraulic servo valve control system is required to work stably, accurately and quickly, and enough damping is required for the system to be stable; the system requires a sufficient velocity constant. The system is fast enough to pass the frequency wide enough. In practice, in engineering practice, these three conditions are mutually restrictive for the same system. In order to make the system stably work, the precision is sacrificed, the speed constant is reduced, and particularly in a system with large inertia and low rigidity, the problems of the stability, the control precision and the response capability of the system are quite sharp and prominent due to the small damping brought by the structure and the low speed constant and the low natural frequency.

Therefore, the slide valve of the prior double-nozzle baffle type two-stage electro-hydraulic servo valve has the defects of large rigid impact, poor working stability, troublesome zero setting and easy zero offset.

Disclosure of Invention

Aiming at the defects in the prior art, the invention provides a novel high-flow electro-hydraulic servo valve, which solves the technical problems of large rigid impact of a slide valve, poor working stability, trouble in zero setting and easy zero offset of the existing double-nozzle baffle type two-stage electro-hydraulic servo valve.

The technical scheme of the invention is realized as follows: a novel large-flow electro-hydraulic servo valve comprises a double-nozzle baffle regulator and a valve sleeve component which are connected, wherein the valve sleeve component comprises a valve body provided with a P port, an A port, a B port and an O port, a slide valve is arranged in the valve body, a valve sleeve is arranged between the valve body and the slide valve, a feedback rod of the double-nozzle baffle regulator penetrates through the valve body and the valve sleeve to be connected with the slide valve, an oil inlet communicated with the P port, an A flow distribution port matched with the A port, a B flow distribution port matched with the B port and an oil return port communicated with the O port are arranged on the valve sleeve, annular bulges matched with the A flow distribution port and the B flow distribution port are arranged at intervals on the periphery of the slide valve, an oil return passage communicated with the B flow distribution port and the oil return port when the slide valve moves is arranged in the slide valve, oil return holes communicated with the oil return passage are all arranged on the slide valve on two sides of the annular bulges, and annular, and guide and control oil cavities are respectively arranged between the two end parts of the slide valve and the valve sleeve, guide and control channels for communicating the P port with the guide and control oil cavities are arranged in the valve sleeve, the guide and control oil cavities are communicated with a nozzle pipe of the double-nozzle baffle regulator through the valve body, and the nozzle pipe is communicated with the oil return hole.

Furthermore, the double-nozzle baffle regulator comprises a pilot valve body connected with the valve body, a threaded hole is formed in the pilot valve body, the nozzle pipe is in threaded connection with the pilot valve body through the threaded hole, and a channel for communicating the pilot oil cavity with the nozzle pipe is formed in the pilot valve body.

Further, the outer end of the nozzle pipe is provided with a nozzle nut.

Furthermore, the two ends of the valve sleeve are provided with guide control assemblies, each guide control assembly comprises a guide control piston sleeve, a guide control piston is arranged in each guide control piston sleeve, the inner end part of each guide control piston penetrates through the guide control piston sleeve and is pressed against the end part of the corresponding slide valve, the outer end part of each guide control piston is provided with a guide control spring, the outer end part of each guide control spring is provided with a guide control end cover, each guide control end cover and the outer end part of each guide control piston form a guide control oil cavity, and each guide control piston sleeve is provided with a guide oil port communicated with the guide control channel.

Furthermore, the guide and control channel comprises a first axial channel arranged in the valve sleeve, an inner port of the first axial channel is communicated with the P port, an outer port of the first axial channel is connected with a first radial channel, the inner wall of the valve body is provided with a second radial channel communicated with the first radial channel, the inner port of the first radial channel is communicated with the guide oil port, the outer port of the first radial channel is communicated with the second radial channel, and a second axial channel communicated with the second radial channel and the nozzle pipe is arranged in the valve body.

Furthermore, the guide control piston sleeve is T-shaped, the axial section of the guide control piston sleeve is in trapezoidal fit with the inner wall of the valve sleeve, the radial section of the guide control piston sleeve is buckled and pressed at the end part of the valve sleeve, the outer part of the radial section is buckled and pressed with an end cover, and the end cover is connected with the valve body in a sealing mode.

Further, the outer ports of the first axial channel and the second axial channel respectively extend to the outer end faces of the valve sleeve and the valve body, the outer port of the first axial channel and the radial section of the guide control piston sleeve form end face seal, and the outer port of the second axial channel forms end face seal through a plug or an end cover.

Furthermore, the first axial channel is provided with two and is arranged in the valve sleeve in a bilateral symmetry manner, a corresponding through hole is formed between the valve body and the valve sleeve, a bushing is arranged in the through hole, and the feedback rod is inserted in the bushing.

Furthermore, the oil return hole is arranged in the annular groove, an annular groove is arranged in the annular groove, and the end part of the feedback rod is inserted into the annular groove.

Furthermore, the interpenetration matching part of the guide control piston and the guide control piston sleeve is provided with a pressure equalizing groove, the slide valve comprises a hollow cylindrical body, the end part of the cylindrical body is provided with a sealing plate, and the sealing plate is provided with a horizontal hole which is through inside and outside.

The flow distribution port A and the flow distribution port B of the valve sleeve have larger structural characteristics, and are suitable for occasions with large flow, return oil needs to flow to the return port through the slide valve, and the requirements of stability, accuracy and quickness are met while the large flow is realized. The slide valve adopts the joint movement of the end surface of the pilot control piston of the pilot control assembly, and compared with the movement of the traditional hydraulic control slide valve, the rigid impact of the action of the slide valve is reduced, the working stability is improved, and the working zero offset and zero drift of the slide valve are reduced under the action of the springs at the two sides of the pilot control piston. The gap between the nozzle and the baffle is adjusted by adjusting the position of the nozzle pipe through the nozzle nut, and the nut adjusts and fixes the position of the nozzle pipe, so that the zero setting is convenient. When the external oil supply fails, the slide valve is centered under the action of the spring, namely, the slide valve fails and returns to zero, so that the control oil circuit is protected.

Drawings

In order to illustrate the embodiments of the invention more clearly, the drawings that are needed in the description of the embodiments will be briefly described below, it being apparent that the drawings in the following description are only some embodiments of the invention, and that other drawings may be derived from those drawings by a person skilled in the art without inventive effort.

FIG. 1 is a schematic cross-sectional view of a prior art dual nozzle flapper servo valve;

FIG. 2 is a cross-sectional view of the present invention;

fig. 3 is a schematic structural view of the valve sleeve of fig. 2;

fig. 4 is a schematic view of an oil port of the valve body of fig. 2.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without inventive effort based on the embodiments of the present invention, are within the scope of the present invention.

A novel large-flow electro-hydraulic servo valve is shown in figures 2-4 and comprises a double-nozzle baffle regulator and a valve sleeve component which are connected, wherein the valve sleeve component comprises a valve body 9 provided with a P port 29, an A port 30, a B port 31 and an O port 32, a slide valve 17 is arranged in the valve body 9, a valve sleeve 15 is arranged between the valve body 9 and the slide valve 17, and a feedback rod 19 of the double-nozzle baffle regulator penetrates through the valve body 9 and the valve sleeve 15 to be connected with the slide valve 17. When the double-nozzle baffle regulator is not electrified, the port P29 is not communicated with the port A30, the port B31 and the port O32, and the system is in a balanced state. When the dual-nozzle baffle regulator is electrified, the feedback rod 19 deflects to drive the slide valve 17 to move to one side, the port P29 is communicated with the port a 30 or the port B31 through the valve sleeve 15, and oil in the port a 30 or the port B31 which is not communicated with the port P29 flows to the port O32 through the valve sleeve 15, the slide valve 17 and the valve sleeve 15 in sequence. After the feedback rod 19 of the double-nozzle baffle regulator deflects, the distance between the two sides of the double-nozzle baffle regulator and the nozzles on each side changes, the pressure on one side, to which the slide valve 17 moves, becomes larger, the pressure on the other side becomes smaller, the slide valve 17 gradually reaches balance under the action of differential pressure, and the opening degree of the communicated oil ports is kept unchanged.

Specifically, the double-nozzle baffle regulator comprises an upper magnetizer 2, a lower magnetizer 8, an armature 5, a permanent magnet 3, a coil assembly 4, a baffle 6, a feedback rod 19, a valve guide body 21, a nozzle pipe 22, a nozzle nut 23 and a spring pipe 7. The guide valve body 21 is fixed on the valve body 9 through a bolt, the guide valve body 21 is provided with a lower magnetizer 8 and an upper magnetizer 2, the upper magnetizer and the lower magnetizer are separated by the permanent magnet 3, the upper pole shoe and the lower pole shoe are fixed with the left coil component 4 and the right coil component 4 through bolts, and the inner side of the lower magnetizer 8 is provided with the spring tube 7. The coil assembly 4 is formed by winding a polyimide enameled round copper wire on a coil assembly 4 framework, and the armature 5 penetrates through the inner ring of the coil assembly 4 framework of the coil assembly 4. One end of the baffle 6 passes through a central hole on the armature 5 and is pressed and connected with the armature 5, and the other end of the baffle 6 passes through the spring tube 7 and the pilot valve body 21 and is connected with the feedback rod 19. The casing 1 covers and fixes the double-nozzle baffle device on the valve body 9 through screws, a corresponding through hole is arranged between the valve body 9 and the valve sleeve 15, a lining 18 is arranged in the through hole, and the feedback rod 19 is inserted in the lining 18.

A threaded hole is formed in the valve guide body 21, the nozzle pipe 22 is in threaded connection with the valve guide body 21 through the threaded hole, an inclined channel which is communicated with the guide control oil cavity and the inner cavity of the nozzle pipe 22 is formed in the valve guide body (21), and a nozzle nut 23 is arranged at the outer end of the nozzle pipe 22. The position of the nozzle pipe 22 is adjusted through the nozzle nut 23, so that the gap between the nozzle of the nozzle pipe 22 and the baffle 6 is adjusted, the position of the nozzle pipe 22 is adjusted and fixed through the nozzle nut 23, and zero adjustment is convenient.

The valve sleeve 15 is provided with an oil inlet 43 respectively communicated with the P port 29, a pilot control port 25 communicated with the P port 29, an A flow distribution port 26 matched with the A port 30, a B flow distribution port 27 matched with the B port 31 and an oil return port 28 communicated with the O port 32, a plurality of annular grooves are arranged on the outer wall of the valve sleeve 15 at intervals, the oil return port 28, the A flow distribution port 26, the pilot control port 25 and the B flow distribution port 27 are sequentially arranged in the annular grooves of the valve sleeve 15 and are isolated from each other, wherein the A flow distribution port 26, the B flow distribution port 27 and the oil return port 28 penetrate through the inner wall and the outer wall of the valve sleeve 15 and are communicated to the outer wall of the slide valve 17.

The two pilot control ports 25 are arranged at intervals, the two pilot control ports 25 are respectively communicated with first axial channels 36 symmetrically arranged in the valve sleeve 15, one end of each first axial channel 36 is communicated with the pilot control port 25, the other end of each first axial channel extends to the end part of the valve sleeve 15, and the first axial channels 36 extending to the end part of the valve sleeve 15 are connected with first radial channels 37. The inner wall of the valve body 9 is provided with a second radial passage 38 communicating with the first radial passage 37, the valve body 9 is provided with a second axial passage 39 communicating the second radial passage 38 with the nozzle pipe 22, and the second axial passage 39 communicates with the inner cavity of the nozzle pipe 22 through an inclined passage provided in the pilot valve body 21.

The periphery of the slide valve 17 is provided with annular bulges 33 which are matched with the A flow distribution port 26 and the B flow distribution port 27 respectively at intervals, when the slide valve 17 is positioned at a middle position, the annular bulges 33 are opposite to the A flow distribution port 26 and the B flow distribution port 27 to seal the A flow distribution port 26 and the B flow distribution port 27, and when the slide valve 17 moves, the A flow distribution port 26 and the B flow distribution port 27 are gradually opened. The slide valve 17 comprises a cylindrical body with a hollow interior, the annular protrusions 33 are arranged on the outer wall of the cylindrical body, the annular groove between the two annular protrusions 33 forms a flow guide cavity for communicating the A flow distribution port 26 and the B flow distribution port 27 with the oil inlet 43, and the flow guide cavity can communicate the A flow distribution port 26 or the B flow distribution port 27 with the oil inlet 43 along with the movement of the slide valve 17.

The outer wall of the cylindrical body at the left and right ends of the slide valve 17 is provided with an annular groove 40, the annular groove 40 is internally provided with an oil return hole 41 communicated with the inner cavity of the cylindrical body, and the two annular grooves 40 can be communicated through the inner cavity of the cylindrical body through the oil return hole 41. When the slide valve 17 moves leftwards, the oil inlet 43 is directly communicated with the A flow distribution port 26 through the flow guide cavity, and the B flow distribution port 27 is communicated with the oil return port 28 through the oil return hole 41 in the right annular groove 40, the tubular inner cavity, and the frontal oil return hole 41 in the left annular groove 40 in sequence. When the slide valve 17 moves rightwards, the oil inlet 43 is directly communicated with the B flow distribution port 27 through the flow guide cavity, and the A flow distribution port 26 is directly communicated with the oil return port 28 through the annular groove 40 on the right side. The annular groove 40 at the left end of the slide valve 17 corresponds to the bushing 18, that is, the oil sprayed from the nozzle pipe 22 of the dual nozzle flapper adjuster can flow to the inner cavity of the cylindrical body and the oil return opening 28 through the annular groove 40.

And guide control assemblies are arranged at two ends of the valve sleeve 15, and the reset control of the slide valve 17 is realized through the guide control assemblies. The guide control assembly comprises a guide control piston sleeve 11, the guide control piston sleeve 11 is T-shaped, the axial section of the guide control piston sleeve 11 is in trapezoidal fit with the inner wall of the valve sleeve 15, the radial section of the guide control piston sleeve 11 is buckled and pressed at the end part of the valve sleeve 15, an end cover 10 is buckled and pressed outside the radial section, and the end cover 10 is in sealing connection with the valve body 9. A pilot control piston 14 is arranged in the axial section of the pilot control piston sleeve 11, the inner end part of the pilot control piston 14 penetrates through the pilot control piston sleeve 11 and is pressed against the end part of the slide valve 17, a pilot control spring 12 is arranged at the outer end part of the pilot control piston 14, a pilot control end cover 13 is arranged at the outer end part of the pilot control spring 12, and a pilot control oil cavity is formed by the pilot control end cover 13 and the outer end part of the pilot control piston 14.

The oil guide piston sleeve 11 is provided with an oil guide port 35 communicating the oil guide control chamber with a first radial passage 37, one path of oil entering from the P port 29 sequentially passes through the oil guide control port 25, a first axial passage 36, a first radial passage 37 and the oil guide port 35 to flow into the oil guide control chamber, the other path of oil sequentially passes through the oil guide control port 25, the first axial passage 36, the first radial passage 37, a second radial passage 38, a second axial passage 39, an inclined passage in the valve guide body 21 and an inner cavity of the nozzle pipe 22 to flow to the baffle 6, when the baffle 6 deflects, pressure difference is generated on two sides of the baffle, the oil guide control chambers on two sides of the slide valve 17 generate pressure difference, the oil guide control piston 14 on one side extends out under the action of the pressure difference, the oil guide control piston 14 on the other side retracts, reverse pushing of the slide valve 17 is realized, and finally the feedback moment is balanced with the.

Furthermore, a pressure equalizing groove is formed at the insertion matching position of the guide control piston 14 and the guide control piston sleeve 11, so that the hydraulic clamping force of the guide control piston 14 during working is prevented. The end of the cylindrical body is provided with a sealing plate 16, the sealing plate 16 is provided with a horizontal hole 42 which is through inside and outside, so that the oil in the pilot oil cavity can flow into the cylindrical body from the horizontal hole 42 and finally flow to the O port 32 through the oil return port 28.

Further, the outer ports of the first axial channel 36 and the second axial channel 39 extend to the outer end faces of the valve sleeve 15 and the valve body 9, respectively, so that the processing and manufacturing are convenient. The outer port of the first axial channel 36 forms an end-face seal with the radial section of the pilot piston sleeve 11, and the outer port of the second axial channel 39 forms an end-face seal with the end cap 10 or with the end cap 20.

The specific working process of the invention is as follows. The upper and lower magnetizers 2 and 8 of the double nozzle flapper adjuster are magnetized by the permanent magnet 3 sandwiched therebetween to form a fixed magnetic flux therearound. The power supply voltage of the control loop is 24VDC, the power supply adopts a stabilized voltage power supply and is connected with a fuse in series, and the control signal adopts a range of +/-10 VDC. When the left coil block 4 is energized, the coil block 4 generates a control magnetic flux under the influence of the current. The control magnetic flux formed by electrifying the coil assembly 4 interacts with the fixed magnetic flux formed by magnetizing the magnetizer, so that the magnetic flux between the armature 5 and the left coil assembly 4 is increased, the magnetic flux between the armature 5 and the right coil assembly 4 is reduced, and the armature 5 drives the baffle 6 to rotate clockwise to drive the slide valve 17 to move leftwards. The clockwise rotation amount of the baffle 6 is different according to different input control signal voltages. At this time, the port a 26 and the port B27 between the spool valve 17 and the valve housing 15 are opened and gradually increased, the oil flows from the port P into the port a through the pilot chamber, the oil flows from the port B31 into the port O32 from the inside of the spool valve 17, and the oil is controlled to be ejected from the two nozzles 22 and to flow back into the port O32 through the spool valve 17. The offset of the flapper 6 causes the variable restriction between the left nozzle tube 22 and the flapper 6 to decrease, causing the pressure in the left control channel to increase, the pressure between the left pilot piston 14 and the pilot cap 13 to increase, pushing the spool 17 to the right, and the feedback rod 19 to move synchronously with the spool 17. The movement of the feedback rod 19 drives the baffle 6 to deflect in the opposite direction, so that the variable orifice between the left baffle nozzles is enlarged and the right is reduced. When the feedback torque becomes gradually equal to the electromagnetic torque, the spool valve 17 remains in position.

The position of the spool valve 17 is proportional to the magnitude of the input control voltage, i.e., the greater the control voltage across the coil assembly 4, the greater the torque deflecting the armature 5, the deflection of the flapper 6, the pressure differential across the spool valve 17, and the displacement of the spool valve 17, the greater the flow output from the servo valve.

Nothing in this specification is intended to be exhaustive of all conventional and well known techniques.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.