Two-dimensional electro-hydraulic servo valve with simplified hydraulic half-bridge structure

Abstract

The application provides a two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure, comprising a spool valve assembly connected with an electro-mechanical converter through a transmission mechanism, the spool valve assembly comprises a valve body, a valve core and a valve sleeve, the valve sleeve is sequentially provided with a T port, an A port, a P port, a B port and a T port from left to right, characterized in that the valve core is provided with four shoulders from left to right, the second shoulder and the third shoulder are respectively located at the A port and the B port, the middle part of the valve core is provided with a high-pressure flow channel communicated with the P port, the first shoulder is provided with a low-pressure flow channel communicated with the T port in the axial direction of the valve core, the first shoulder is provided with a high-pressure through groove and a low-pressure through groove perpendicular to the axial direction of the valve core, the high-pressure through groove and the low-pressure through groove are staggered, the high-pressure through groove is located at the right side of the low-pressure through groove, the high-pressure through groove is communicated with the high-pressure flow channel, and the low-pressure through groove is communicated with the low-pressure flow channel. The application significantly reduces the use cost and maintenance workload, is suitable for civil fields, and promotes the development of industrialization.

Description

Technical Field

[0001] This invention relates to the field of electro-hydraulic servo valve technology, and more specifically to a two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure. Background Technology

[0002] Electro-hydraulic servo valves are key components in electro-hydraulic servo control. They are hydraulic control valves that receive analog electrical signals and output modulated flow and pressure accordingly. Electro-hydraulic servo valves have advantages such as fast dynamic response, high control accuracy, and long service life, and are widely used in electro-hydraulic servo control systems in aviation, aerospace, shipbuilding, metallurgy, chemical and other fields.

[0003] Existing two-dimensional electro-hydraulic servo valves generally consist of a spool valve assembly, an electro-mechanical converter module, a displacement sensor module, and a transmission mechanism module. The spool valve assembly includes the valve body, valve core, and valve sleeve. Traditionally, the high-pressure and low-pressure orifices on the valve core are machined using electrical discharge machining (EDM). Generally, EDM equipment is relatively expensive. This is mainly because the structure and working principle of EDM equipment are relatively complex, requiring higher levels of equipment and technical expertise, thus increasing costs. Furthermore, EDM processing speed is relatively slow, especially when handling workpieces with complex shapes.

[0004] Existing two-dimensional electro-hydraulic servo valves generally use magnets to achieve valve core reset. For example, Chinese invention patent application CN114718933A discloses a zero-position adjustable two-dimensional motor direct-drive electro-hydraulic servo valve. This electro-hydraulic servo valve achieves contactless rotational and axial reset of the two-dimensional valve through a magnet reset zero-adjustment mechanism. However, this method has disadvantages such as being difficult to disassemble, insufficient reset force, easy to be damaged and replaced under high pressure, and easy to demagnetize under high temperature.

[0005] For example, Chinese invention patent application number 2023115345545 discloses a two-dimensional electro-hydraulic servo valve based on a dry-wet separation transmission mechanism. This two-dimensional electro-hydraulic servo valve also achieves the rotational reset of the valve core through the mutual attraction of two magnets of opposite polarities. It has the following drawbacks: 1. The magnetism of the magnets gradually weakens with increasing usage time, leading to a slower response speed of the servo valve and affecting control accuracy. 2. The magnet reset is easily affected by external magnetic fields; if a strong magnetic field exists nearby, it may affect the performance of the servo valve. 3. The maintenance and upkeep of the magnet reset are relatively complex, requiring regular inspection and replacement of magnets and other components, increasing usage costs and maintenance workload. Summary of the Invention

[0006] To address the shortcomings of existing technologies, the present invention aims to provide a two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure.

[0007] To solve the above-mentioned technical problems, the present invention is achieved through the following technical solution:

[0008] A simplified two-dimensional electro-hydraulic servo valve with a hydraulic half-bridge structure includes a spool valve assembly connected to an electro-mechanical converter via a transmission mechanism. The spool valve assembly includes a valve body, a valve core installed inside the valve body, and a valve sleeve disposed outside the valve core. The valve sleeve has ports T, A, P, B, and T-ports sequentially from left to right. The valve core has four shoulders from left to right, with the second and third shoulders located at ports A and B respectively. A high-pressure flow channel communicating with port P is located in the middle of the valve core. A low-pressure flow channel communicating with port T is correspondingly provided through the first shoulder in the axial direction of the valve core. A high-pressure channel and a low-pressure channel perpendicular to the axial direction of the valve core are provided on the first shoulder. The high-pressure channel and the low-pressure channel are arranged alternately, with the high-pressure channel located to the right of the low-pressure channel. The high-pressure channel communicates with the high-pressure flow channel, and the low-pressure channel communicates with the low-pressure flow channel.

[0009] Furthermore: the transmission mechanism includes a connecting housing, within which a wet operating chamber and a dry operating chamber are provided. The wet operating chamber and the dry operating chamber are arranged independently of each other through an intermediate connecting sleeve. The wet operating chamber is connected to the slide valve assembly. The dry operating chamber is provided with a first-stage torque amplification mechanism connected to the electro-mechanical converter. The wet operating chamber is provided with a second-stage torque amplification mechanism connected to the valve core. The first-stage torque amplification mechanism and the second-stage torque amplification mechanism are connected to each other.

[0010] Furthermore: the valve core extends into the wet operating chamber, and an axial zero-adjustment reset assembly is sleeved on its extended end; a rotary zero-adjustment reset assembly is provided on the first-stage torque amplification mechanism.

[0011] Furthermore: a right plug ring is connected between the connecting housing and the slide valve assembly. The right plug ring is sleeved on the outside of the valve core. The axial zeroing and reset assembly includes a first bearing and a second bearing sleeved on the valve core extension end. A first spring groove and a second spring groove are respectively opened on the right plug ring and the intermediate connecting sleeve. A first spring is provided between the first bearing and the first spring groove, and a second spring is provided between the second bearing and the second spring groove.

[0012] Furthermore: the rotary zeroing and reset assembly includes spring retainers corresponding to the positions on both sides of the primary torque amplification mechanism on the connecting housing, a spring retaining rod fixed between the two spring retainers, the spring retaining rod passing through the primary torque amplification mechanism, and a third spring and a fourth spring respectively provided between the two sides of the primary torque amplification mechanism and the spring retainers, the third spring and the fourth spring being sleeved on the outside of the spring retaining rod.

[0013] Furthermore: the primary torque amplification mechanism includes a connected Y-shaped shift fork and a connecting lever, the Y-shaped shift fork being connected to the electro-mechanical converter, and the connecting lever being connected to the secondary torque amplification mechanism.

[0014] Furthermore: the top of the connecting lever is connected to a first ball head, which is placed in the main support fork groove of the Y-shaped fork.

[0015] Furthermore: a first groove communicating with the T-port is provided on the right side of the valve sleeve, and a second groove communicating with the first groove is provided on the right plug ring. The first groove and the second groove constitute a liquid communication channel between the slide valve assembly and the wet operation chamber.

[0016] Furthermore, a valve core plug is provided at the right end of the high-pressure flow channel.

[0017] Compared with the prior art, the present invention has the following advantages and beneficial effects:

[0018] 1. The high-pressure through-slot, low-pressure through-slot, and low-pressure flow channel of the present invention can be processed by wire cutting technology. Compared with the high and low pressure hole EDM processing method used in the prior art, the two high-pressure openings and two low-pressure openings on the valve core of the present invention have higher radial symmetry.

[0019] 2. Furthermore, wire EDM technology is used to process high-pressure channels, low-pressure channels, and low-pressure flow channels. Compared to EDM, it offers faster processing speeds, significantly shortening the processing cycle of servo valves. In addition, wire EDM equipment has relatively lower performance requirements and is more affordable, making it more suitable for civilian applications and promoting industrialization.

[0020] 3. Unlike existing magnetic reset and zeroing mechanisms, this invention employs a spring-driven mechanical feedback method. This method offers greater reset force, stronger compressive strength, and higher temperature resistance. Importantly, the spring's reset force remains stable and does not gradually weaken over time, thus ensuring the servo valve's response speed and control accuracy. Furthermore, the zeroing and reset assembly used in this invention eliminates the need for periodic inspection and component replacement, significantly reducing operating costs and maintenance workload. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the overall structure of the present invention;

[0022] Figure 2 This is a typical cross-sectional structural diagram of the present invention;

[0023] Figure 3 yes Figure 2 Enlarged view of point C in the middle;

[0024] Figure 4 yes Figure 2 Cross-sectional view along the DD direction;

[0025] Figure 5 This is a schematic diagram of the connection between the transmission mechanism and the valve core of the present invention;

[0026] Figure 6 This is a schematic diagram of the structure of the two-stage torque amplification mechanism of the present invention;

[0027] Figure 7 This is a schematic diagram of the structure of the first-stage torque amplification mechanism of the present invention;

[0028] Figure 8 This is a schematic diagram of the valve core structure of the present invention;

[0029] Figure 9 This is a cross-sectional view of the valve sleeve of the present invention;

[0030] Figure 10 This is a bottom view of the valve sleeve of the present invention;

[0031] Figure 11 This is an assembly diagram of the valve core and valve sleeve of the present invention;

[0032] Figure 12 This is a schematic diagram of the valve sleeve of the present invention;

[0033] Figure 13 This is a schematic diagram of a typical cross-sectional structure of the right plug ring of the present invention.

[0034] Reference numerals: 1-Slide valve assembly; 2-Transmission mechanism; 3-Electro-mechanical converter; 4-Valve body; 5-Valve core; 6-Valve sleeve; 7-First shoulder; 8-Second shoulder; 9-Third shoulder; 10-Fourth shoulder; 11-High-pressure flow channel; 12-Low-pressure flow channel; 13-High-pressure through groove; 14-Low-pressure through groove; 15-Connecting housing; 16-Wet operating chamber; 17-Dry operating chamber; 18-Intermediate connecting sleeve; 19-First-stage torque amplification mechanism; 20-Second-stage torque amplification mechanism; 21-Right plug ring; 22-First bearing; 23-Second bearing; 24-First spring groove; 25-Second spring groove; 26-First spring; 27-Second spring. 28-Spring retainer; 29-Spring retainer rod; 30-Y-type shift fork; 31-Connecting lever; 32-First ball head; 33-Main support; 34-Shift fork groove; 35-Valve core lever; 36-π shaft; 37-Second ball head; 38-First groove; 39-Second groove; 40-Valve core plug; 41-High pressure opening; 42-Low pressure opening; 43-Angled through groove; 44-Sensitive chamber; 45-High pressure chamber; 46-L-type support; 47-Plug ring; 48-Third bearing; 49-Left end cap; 50-Fan-shaped swing part; 51-Connecting part; 52-Concentric ring; 53-Third spring; 54-Fourth spring; 55-Ball head through groove. Detailed Implementation

[0035] To enable those skilled in the art to better understand the technical solutions of the present invention, preferred embodiments of the present invention are described below in conjunction with specific examples. However, it should be understood that the accompanying drawings are for illustrative purposes only and should not be construed as limiting the present invention. For better illustration of this embodiment, some components in the drawings may be omitted, enlarged, or reduced, and do not represent the actual dimensions of the product. It is understandable that some well-known structures and their descriptions may be omitted in the drawings for those skilled in the art. The positional relationships described in the drawings are for illustrative purposes only and should not be construed as limiting the present invention.

[0036] The present invention will be further described below with reference to the accompanying drawings and embodiments, but this should not be construed as limiting the present invention.

[0037] like Figures 1 to 2 As shown, a simplified hydraulic half-bridge structure two-dimensional electro-hydraulic servo valve includes a spool valve assembly 1. The spool valve assembly 1 is connected to an electro-mechanical converter 3 via a transmission mechanism 2. The spool valve assembly 1 includes a valve body 4, a valve core 5 installed inside the valve body 4, and a valve sleeve 6 disposed outside the valve core 5. The valve core 5 and the valve sleeve 6 can slide and rotate relative to each other. Figure 9 , 10 As shown, the valve sleeve 6 has T-port, A-port, P-port, B-port and T-port in sequence from left to right, where P-port is the liquid inlet and has system pressure. The valve core 5 has four shoulders from left to right, with the second shoulder 8 and the third shoulder 9 located at A-port and B-port respectively. The valve core 5 has a high-pressure flow channel 11 in the middle that communicates with P-port. A valve core plug 40 is provided at the right end of the high-pressure flow channel 11. The first shoulder 7 has a low-pressure flow channel 12 that communicates with T-port through it in the axial direction of the valve core 5. The first shoulder 7 has a high-pressure channel 13 and a low-pressure channel 14 that are perpendicular to the axial direction of the valve core 5. The high-pressure channel 13 and the low-pressure channel 14 are arranged alternately, and the high-pressure channel 13 is located to the right of the low-pressure channel 14. The high-pressure channel 13 communicates with the high-pressure flow channel 11, and the low-pressure channel 14 communicates with the low-pressure flow channel 12.

[0038] like Figure 8 As shown, the high-pressure channel 13 forms a pair of axisymmetric high-pressure openings 41 on the surface of the first shoulder 7, and the low-pressure channel 14 forms a pair of axisymmetric low-pressure openings 42 on the surface of the first shoulder 7. In this embodiment, both the high-pressure channel 13 and the low-pressure channel 14 are configured as square channels with chamfered edges on all four sides, so that the high-pressure openings 41 and the low-pressure openings 42 both present a square structure with chamfered edges.

[0039] like Figure 11As shown, a concentric ring 52 is provided on the right side of the fourth shoulder 10 on the valve core 5. The valve core 5, valve sleeve 6, and concentric ring 52 form a high-pressure chamber 45. A left end cap 49 is provided on the left side of the slide valve assembly 1. The valve core 5, valve sleeve 6, and left end cap 49 form a sensitive chamber 44. The valve sleeve 6 is provided with a pair of axisymmetric oblique through grooves 43. The high-pressure through groove 13 and the low-pressure through groove 14 are connected to the sensitive chamber 44 through the oblique through grooves 43. The oblique through grooves 43 cover the area between the bowstrings of the adjacent high-pressure opening 41 and the bowstrings of the low-pressure opening 42 (the "bow" part of the present invention is arranged in a right-angled shape). The oblique through grooves 43, the high-pressure opening 41, and the low-pressure opening 42 form a hydraulic resistance half-bridge. The hydraulic resistance half-bridge controls the pressure in the sensitive chamber 44 through the oblique through grooves 43.

[0040] like Figure 3 As shown, the transmission mechanism 2 includes a connecting housing 15, within which a wet operating chamber 16 and a dry operating chamber 17 are provided. The wet operating chamber 16 and the dry operating chamber 17 are arranged independently of each other through an intermediate connecting sleeve 18. The wet operating chamber 16 is connected to the slide valve assembly 1. The dry operating chamber 17 is provided with a first-stage torque amplification mechanism 19 connected to the electro-mechanical converter 3. The wet operating chamber 16 is provided with a second-stage torque amplification mechanism 20 connected to the valve core 5. The first-stage torque amplification mechanism 19 and the second-stage torque amplification mechanism 20 are connected to each other.

[0041] The valve core 5 extends into the wet operating chamber 16, and an axial zero-adjustment reset assembly is sleeved on its extended end; a rotary zero-adjustment reset assembly is provided on the first-stage torque amplification mechanism 19.

[0042] like Figure 3 As shown, a right plug ring 21 connects the connecting housing 15 and the slide valve assembly 1. The right plug ring 21 is sleeved on the outside of the valve core 5. The axial zeroing and reset assembly includes a first bearing 22 and a second bearing 23 sleeved on the extended end of the valve core 5. The first bearing 22 and the second bearing 23 are respectively located on both sides of the valve core lever 35. A first spring groove 24 and a second spring groove 25 are respectively formed on the right plug ring 21 and the intermediate connecting sleeve 18. A first spring 26 is provided between the first bearing 22 and the first spring groove 24, and a second spring 27 is provided between the second bearing 23 and the second spring groove 25. The outer diameters of the first bearing 22 and the second bearing 23 are smaller than the outer diameters of the first spring groove 24 and the second spring groove 25, respectively.

[0043] like Figure 4As shown, the rotary zeroing and reset assembly includes spring retainers 28 on the connecting housing 15, corresponding to the positions on both sides of the primary torque amplification mechanism 19. A spring retaining rod 29 is fixed between the two spring retainers 28. The spring retaining rod 29 passes through the primary torque amplification mechanism 19. A third spring 53 and a fourth spring 54 are respectively provided between the two sides of the primary torque amplification mechanism 19 and the spring retainers 28. The third spring 53 and the fourth spring 54 are sleeved on the outside of the spring retaining rod 29. The spring retaining rod 29 supports the third spring 53 and the fourth spring 54.

[0044] like Figure 5 , 7 As shown, the primary torque amplification mechanism 19 includes a Y-shaped shift fork 30 and a connecting lever 31 connected together. The Y-shaped shift fork 30 is connected to the electro-mechanical converter 3, and the connecting lever 31 is connected to the secondary torque amplification mechanism 20. The top of the connecting lever 31 is connected to a first ball head 32, which is placed in the shift fork groove 34 of the main support column 33 of the Y-shaped shift fork 30. The Y-shaped shift fork 30 has a main support column 33 with a shift fork groove 34 in the middle and an L-shaped support column 46 located on the right side of the main support column 33. The L-shaped support column 46 is integrally formed with the main support column 33. The spring retaining rod 29 is placed between the L-shaped support column 46 and the main support column 33, and its two ends are fixedly connected to the corresponding spring retainers 28.

[0045] like Figure 5 , 6 As shown, the secondary torque amplification mechanism 20 includes a valve core lever 35 and a π-axis 36. The upper end of the valve core lever 35 is fixedly connected to the valve core 5, and the lower end is movably connected to the π-axis 36. The π-axis 36 passes through the intermediate connecting sleeve 18 and is connected to the primary torque amplification mechanism 19. The π-axis 36 is integrally formed. The π-axis 36 includes a fan-shaped swing part 50 and connecting parts 51 on both sides of the fan-shaped swing part 50. The bottom of the fan-shaped swing part 50 is provided with a ball head through groove 55. The lower end of the valve core lever 35 is connected to a second ball head 37, which cooperates with the ball head through groove 55 of the fan-shaped swing part 50.

[0046] The length of the ball head groove 55 is matched with the design stroke distance L of the axial movement of the valve core 5.

[0047] The secondary torque amplification mechanism 20 of the present invention is located in the lower part of the wet operation chamber 16, that is, the whole is arranged downward, which makes it more stable and reliable when there is no external force and no oil flow and no operation.

[0048] like Figure 3As shown, sealing and positioning structures are respectively fitted on the connecting portions 51 on both sides of the fan-shaped swing portion 50. The π shaft 36 is rotatably connected to the sealing and positioning structure, and the sealing and positioning structure is fixedly connected to the connecting housing 15. The sealing and positioning structure includes a plug ring 47 and a third bearing 48. Both the plug ring 47 and the third bearing 48 are fitted on the connecting portion 51. The plug ring 47 is located outside the third bearing 48, and a sealing ring is provided on the plug ring 47.

[0049] like Figure 12 , 13 As shown, the valve sleeve 6 has a first groove 38 on its right side that communicates with the T port, and a second groove 39 on the right plug ring 21 that communicates with the first groove 38. The first groove 38 and the second groove 39 constitute a liquid communication channel between the slide valve assembly 1 and the wet operation chamber 16.

[0050] Both the primary torque amplification mechanism 19 and the secondary torque amplification mechanism 20 amplify the output torque of the electro-mechanical converter 3 by a factor, and the final torque output to the valve core 5 is the product of the amplification factors of the primary torque amplification mechanism 19 and the secondary torque amplification mechanism 20. This invention can amplify the output torque of the electro-mechanical converter 3 through multiple stages, reducing the motor output torque required for the valve core 5 to rotate. This allows for the use of a smaller electro-mechanical converter, reducing the overall weight and size of the two-dimensional electro-hydraulic servo valve, and saving costs.

[0051] pass Figures 1-12 It can be seen that:

[0052] 1. Upon receiving a control signal, the electro-mechanical converter 3 rotates clockwise (viewed from right to left), causing the Y-shaped fork 30 to swing to the right (viewed from right to left). The first ball head 32 on the connecting lever 31 is compressed, causing the connecting lever 31 to rotate clockwise by a corresponding angle under the influence of the Y-shaped fork 30, achieving a first-stage torque amplification. The rotation of the connecting lever 31 causes the π-axis 36 to swing to the left (viewed from right to left). The sidewall of the ball head groove 55 of the π-axis 36 compresses the second ball head 37, causing the valve core lever 35 to rotate clockwise (viewed from right to left) by the π-axis 36, achieving a second-stage torque amplification. The clockwise rotation of the valve core lever 35 ultimately drives the valve core 5 to rotate clockwise (viewed from right to left). After the valve core 5 rotates, the interface area between the high-pressure opening 41 and the low-pressure opening 42 and the oblique groove 43 changes, causing a change in the pressure within the sensitive cavity 44, resulting in axial movement of the valve core 5.

[0053] When the valve core 5 rotates clockwise (viewed from right to left) with the valve core fork 7, the intersection area of ​​the high-pressure opening 41 and the oblique groove 43 on the valve core 5 decreases, the intersection area of ​​the low-pressure opening 42 and the oblique groove 43 increases, the pressure in the left sensitive chamber 44 of the valve core 5 decreases, and the pressure in the right high-pressure chamber 45 of the valve core 5 remains constant. Therefore, the valve core 5 moves axially to the left under the action of the unbalanced hydraulic pressure in the left and right chambers.

[0054] 2. Similarly, when the electro-mechanical converter 3 receives a control signal, the output shaft of the electro-mechanical converter 3 rotates counterclockwise (viewed from right to left), causing the Y-shaped fork 30 to swing to the left (viewed from right to left). The first ball head 32 on the connecting lever 31 is squeezed, causing the connecting lever 31 to rotate counterclockwise by the Y-shaped fork 30, thus achieving first-stage torque amplification. The rotation of the connecting lever 31 causes the π-axis 36 to swing to the right (viewed from right to left). The side wall of the ball head groove 55 of the π-axis 36 squeezes the second ball head 37, causing the valve core lever 35 to be driven by the π-axis 36 to rotate counterclockwise (viewed from right to left) by the corresponding angle, thus achieving second-stage torque amplification. The counterclockwise rotation of the valve core lever 35 ultimately drives the valve core 5 to rotate counterclockwise (viewed from right to left). After the valve core 5 rotates, the interface area between the high pressure opening 41 and the low pressure opening 42 and the oblique through groove 43 changes, which causes the pressure in the sensitive cavity 44 to change, and the valve core 5 moves axially.

[0055] When the valve core 5 rotates counterclockwise (viewed from right to left) with the valve core fork 7, the intersection area of ​​the high-pressure opening 41 and the oblique groove 43 on the step of the valve core 5 increases, the intersection area of ​​the low-pressure opening 42 and the oblique groove 43 decreases, the pressure of the left sensitive chamber 44 of the valve core 5 increases, and the pressure of the right high-pressure chamber 45 of the valve core 5 remains constant. Therefore, the valve core 5 moves axially to the right under the action of the unbalanced hydraulic pressure in the left and right chambers.

[0056] Based on the description and accompanying drawings of this invention, those skilled in the art can readily manufacture or use a two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure as described in this invention, and can achieve the positive effects described in this invention.

[0057] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any way. Any simple modifications or equivalent changes made to the above embodiments based on the technical essence of the present invention shall fall within the protection scope of the present invention.

Claims

1. A simplified two-dimensional electro-hydraulic servo valve with a hydraulic half-bridge structure, comprising a spool valve assembly (1), the spool valve assembly (1) being connected to an electro-mechanical converter (3) via a transmission mechanism (2), the spool valve assembly (1) comprising a valve body (4), a valve core (5) installed inside the valve body (4), and a valve sleeve (6) disposed outside the valve core (5), the valve sleeve (6) having a T-port, an A-port, a P-port, a B-port, and a T-port in sequence from left to right, the valve core (5) having four shoulders from left to right, the second shoulder (8) and the third shoulder (9) being located at the A-port and the B-port respectively, and the valve core (5) having a central part... It has a high-pressure flow channel (11) connected to the P port, and a low-pressure flow channel (12) connected to the T port is correspondingly provided through the first shoulder (7) in the axial direction of the valve core (5). The first shoulder (7) is provided with a high-pressure channel (13) and a low-pressure channel (14) perpendicular to the axial direction of the valve core (5). The high-pressure channel (13) and the low-pressure channel (14) are arranged alternately, and the high-pressure channel (13) is located to the right of the low-pressure channel (14). The high-pressure channel (13) is connected to the high-pressure flow channel (11), and the low-pressure channel (14) is connected to the low-pressure flow channel (12). The feature is that: The transmission mechanism (2) includes a connecting housing (15), in which a wet operating chamber (16) and a dry operating chamber (17) are provided. The wet operating chamber (16) and the dry operating chamber (17) are arranged independently through an intermediate connecting sleeve (18). The wet operating chamber (16) is connected to the slide valve assembly (1). The dry operating chamber (17) is provided with a first-stage torque amplification mechanism (19) connected to the electro-mechanical converter (3). The wet operating chamber (16) is provided with a second-stage torque amplification mechanism (20) connected to the valve core (5). The first-stage torque amplification mechanism (19) and the second-stage torque amplification mechanism (20) are connected to each other.

2. The two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure according to claim 1, characterized in that: The valve core (5) extends into the wet operation chamber (16), and an axial zero-adjustment reset assembly is sleeved on its extension end; a rotary zero-adjustment reset assembly is provided on the first-stage torque amplification mechanism (19).

3. A two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure according to claim 2, characterized in that: The connecting housing (15) is connected to the slide valve assembly (1) by a right plug ring (21), which is sleeved on the outside of the valve core (5). The axial zeroing reset assembly includes a first bearing (22) and a second bearing (23) sleeved on the end of the valve core (5). A first spring groove (24) and a second spring groove (25) are respectively opened on the right plug ring (21) and the intermediate connecting sleeve (18). A first spring (26) is provided between the first bearing (22) and the first spring groove (24), and a second spring (27) is provided between the second bearing (23) and the second spring groove (25).

4. A two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure according to claim 3, characterized in that: The rotary zeroing and reset assembly includes spring retainers (28) on the connecting housing (15) corresponding to the positions on both sides of the primary torque amplification mechanism (19). A spring retaining rod (29) is fixed between the two spring retainers (28). The spring retaining rod (29) passes through the primary torque amplification mechanism (19). A third spring (53) and a fourth spring (54) are respectively provided between the two sides of the primary torque amplification mechanism (19) and the spring retainers (28). The third spring (53) and the fourth spring (54) are sleeved on the outside of the spring retaining rod (29).

5. A two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure according to claim 2, characterized in that: The first-stage torque amplification mechanism (19) includes a Y-shaped fork (30) and a connecting lever (31) connected to each other. The Y-shaped fork (30) is connected to the electro-mechanical converter (3), and the connecting lever (31) is connected to the second-stage torque amplification mechanism (20).

6. A two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure according to claim 5, characterized in that: The top of the connecting lever (31) is connected to the first ball head (32), which is placed in the main support fork groove (34) of the Y-shaped fork (30).

7. A two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure according to claim 4, characterized in that: The valve sleeve (6) has a first groove (38) on its right side that communicates with the T port, and a second groove (39) on the right plug ring (21) that communicates with the first groove (38). The first groove (38) and the second groove (39) form a liquid communication channel between the slide valve assembly (1) and the wet operating chamber (16).

8. A two-dimensional electro-hydraulic servo valve with a simplified hydraulic half-bridge structure according to claim 1, characterized in that: A valve core plug (40) is provided at the right end of the high-pressure flow channel (11).

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