High-voltage bidirectional driving servo variable device

Abstract

The invention discloses a high-voltage bidirectional driving servo variable device. Relates to a servo variable device capable of realizing bidirectional driving. Response is rapid, reliability is high, and a reset element is not needed. The servo variable-displacement hydraulic control system comprises a motor, an outer barrel and a controller, the outer barrel comprises a barrel body and a barrel base, the servo variable-displacement hydraulic control system further comprises a servo variable-displacement cylinder, the servo variable-displacement cylinder comprises a valve sleeve and a valve element, the cost is optimized, and the reliability is improved; the forward stroke and the reverse stroke are directly driven by high-pressure oil, no passive reset link exists, the bidirectional response speed reaches the microsecond level, and the requirement of a high-end hydraulic system for bidirectional rapid control is met; the integral matching structure of the rotary valve element and the linear valve sleeve is adopted, complex redundancy design is avoided, the matching process of the valve sleeve and the valve element can be achieved through conventional high-precision grinding, the machining difficulty is low, and batch production is facilitated. The invention is suitable for a hydraulic servo system which needs quick response and bidirectional high-pressure driving.

Description

A high-voltage bidirectional drive servo variable device Technical Field

[0001] This invention relates to the field of hydraulic servo control technology, and more specifically to a servo variable device capable of bidirectional drive. Background Technology

[0002] As the core actuator of a hydraulic control system, the response speed, drive stability, and structural rationality of a hydraulic servo variable cylinder directly determine the control accuracy and working efficiency of the entire hydraulic system. Among them, the helical valve-driven servo variable cylinder, with its advantages of compact structure and sensitive control, has become a new technological direction in the hydraulic field in recent years and is widely used in high-end equipment such as engineering machinery, precision machine tools, and aerospace.

[0003] In practical applications, most hydraulic servo systems do not require unidirectional drive for variable displacement cylinders. Instead, they need to use high pressure in both directions to move the valve sleeve, achieving rapid relative displacement between the valve core and the valve sleeve, thereby meeting the system's rapid response requirements. However, currently available servo valves and their associated variable displacement cylinders suffer from the following technical problems: they can only achieve single hydraulic drive in the valve sleeve extension direction, and their return stroke relies on an additional counteracting piston or high-pressure spring to provide passive reset pressure.

[0004] This structural design, which relies on auxiliary components for reset, increases the number of parts, raising manufacturing costs, assembly difficulties, and subsequent maintenance costs. It also reduces the overall reliability of the structure, as wear and fatigue of auxiliary components can easily lead to reset failures. Furthermore, the passive reset method is affected by factors such as the elastic coefficient and frictional resistance of auxiliary components, resulting in a return stroke response speed that is much lower than the forward drive stroke. This makes it impossible to achieve bidirectional microsecond-level response and fails to meet the requirements of high-end equipment for bidirectional rapid control of hydraulic systems.

[0005] Therefore, developing a variable displacement device that can achieve bidirectional drive using high-pressure hydraulic oil has become a pressing technical problem to be solved in this field. Summary of the Invention

[0006] To address the above-mentioned technical problems, this invention provides a high-pressure bidirectional drive servo variable device that offers rapid response, high reliability, requires no reset element, and whose forward and reverse movements are both driven by hydraulic oil.

[0007] The technical solution of this invention is: a high-pressure bidirectional drive servo variable device, comprising a motor, an outer cylinder, and a controller. The outer cylinder includes a cylinder body and a cylinder seat, and further includes a servo variable cylinder. The servo variable cylinder includes a valve sleeve and a valve core. The valve core includes a left valve core, a connecting rod, a right valve core, and a drive handle connected in sequence. The drive handle is connected to a mounting base via a movable support. The mounting base is disposed within the cylinder seat. The tail end of the drive handle is connected to the motor. A right valve core helix is ​​formed on the right valve core, penetrating the surface of the right valve core. A left valve core helix is ​​formed on the left valve core, with the right end of the left valve core helix penetrating the right end of the left valve core and the left end of the left valve core ending at the left end of the left valve core. The connecting rod connects the right end of the left valve core and the left end of the right valve core, so that when the drive handle is driven to rotate by the motor, the coaxial left valve core, connecting rod, and right valve core rotate synchronously. The inner cavity of the valve sleeve is provided with a partition, and a central hole is formed at the center of the partition, allowing the valve... The inner cavity of the sleeve is divided into an inner left cavity and an inner right cavity. The right valve core is located in the inner right cavity, and the left valve core is located in the inner left cavity. The connecting rod passes through the central hole, allowing the valve sleeve to move axially relative to the valve core. Raised ribs are provided on both sides of the outer surface of the valve sleeve. A raised ring one is located at the middle of the outer surface of the valve sleeve, and a raised ring two is located at the right end of the outer surface of the valve sleeve. Raised ring one and raised ring two are respectively adapted to the inner surface of the cylinder body, allowing the valve sleeve to move axially relative to the inner surface of the cylinder body. The cylinder body reciprocates in a straight line; between the outer surface of the valve sleeve and the inner surface of the cylinder body, the pair of convex ribs and the first and second convex rings form an upper outer cavity located on the upper part of the outer surface of the valve sleeve and a lower outer cavity located on the lower part of the outer surface of the valve sleeve; the upper part of the cylinder body has an oil port A that connects to the upper outer cavity, and the lower part has an oil port B that connects to the lower outer cavity; oil ports P1 and P2 are respectively opened at two opposite corners of the upper outer cavity, and oil ports T1 and T2 are respectively opened at two opposite corners of the lower outer cavity.

[0008] Furthermore, after the left valve core is installed into the inner left cavity of the valve sleeve, a front cavity is left at the outer end of the inner left cavity.

[0009] Furthermore, the valve core rotates, causing the right valve core to helically connect to P1 or P2, and the left valve core to helically connect to T1 or T2, driving the valve sleeve to move to the left; after connection, the valve core still needs to maintain synchronous rotation with the axial linear movement of the valve sleeve, and the motion relationship is as follows: Where: V(L) is the valve sleeve moving speed, Cd is the valve port flow coefficient, V(θ) is the valve core rotation angular velocity, ΔP is the valve port pressure difference, ρ is the medium density, S is the partition area, r is the valve core radius, and m is the valve port width.

[0010] Furthermore, an anti-rotation structure is provided between the outer surface of the valve sleeve and the inner surface of the cylinder.

[0011] Furthermore, an end cap is provided at the left port of the valve sleeve for connecting the driven component.

[0012] Furthermore, an air hole is provided on the end cap so that the front cavity of the valve sleeve opening can achieve air pressure balance.

[0013] Furthermore, the movable support includes a coupling, a shaft glyph, a first bearing, and a second bearing. The top end of the coupling is connected to the output shaft of the motor, and the bottom end of the coupling is connected to the top end of the valve core. The shaft glyph is provided between the mounting base and the upper end of the valve core. The first bearing is provided below the shaft glyph and between the mounting base, and the second bearing is provided between the upper end of the valve core and the valve sleeve.

[0014] Compared with existing technologies, this invention has the following significant advantages: 1. Cost optimization and improved reliability: It eliminates the need for auxiliary reset components such as counter-springs and counter-plungers, reducing the number of parts, manufacturing costs, assembly difficulty, and subsequent maintenance costs. It also avoids failures caused by wear and fatigue of auxiliary components, improving the overall operational reliability. 2. Bidirectional high-speed response: Both forward and reverse strokes are directly driven by high-pressure oil, eliminating passive reset mechanisms. Bidirectional response speeds reach microsecond levels, meeting the requirements of high-end hydraulic systems for bidirectional rapid control. 3. Simple structure and convenient processing: The overall design adopts an integrated structure of rotary valve core and linear valve sleeve, eliminating complex and redundant designs. Furthermore, the mating process between the valve sleeve and valve core can be achieved through conventional high-precision grinding, resulting in low processing difficulty and facilitating mass production.

[0015] This invention is applicable to hydraulic servo systems requiring rapid response and bidirectional high-pressure drive. It addresses a pressing need for hydraulic component manufacturers to overcome technological bottlenecks and meet high-end market demands. Attached Figure Description

[0016] Figure 1 is a perspective view of the present invention; Figure 2 is an exploded perspective view of the present invention; Figure 3 is a structural schematic diagram of the outer cylinder in the present invention; Figure 4 is a sectional view along line I-I in Figure 3; Figure 5 is a perspective schematic diagram of the servo variable cylinder in the present invention (front view); Figure 6 is a perspective view of the linear motion valve sleeve in the servo variable cylinder of the present invention; Figure 7 is a structural schematic diagram of the linear motion valve sleeve; Figure 8 is a left view of Figure 7; Figure 9 is a sectional view along line II-II in Figure 8; Figure 10 is a perspective schematic diagram of the servo variable cylinder in the present invention (back view); Figure 11 is a perspective view of the valve core in the servo variable cylinder of the present invention; Figure 12 is a working principle diagram of the present invention (first view); Figure 13 is a working principle diagram of the present invention (second view); Figure 14 is a working principle diagram of the present invention (third view); Figure 15 is a sectional view along line III-III in Figure 14; Figure 16 is a sectional view along line IV-IV in Figure 14; Figure 17 is a working principle diagram of the mutual movement between the valve core and the valve sleeve in the present invention (first view); Figure 18 is a sectional view along line V-V in Figure 17; Figure 19 is a perspective view of the present invention... The second working principle diagram of the mutual movement between the valve core and valve sleeve in the invention is shown in Figure 20, which is a sectional view of VI-VI in Figure 19. In the figure, 1 is the motor, 2 is the outer cylinder, 21 is the positioning groove, 211 is the steel ball, 3 is the valve sleeve, 31 is the rib, 32 is the first convex ring, 33 is the steel ball placement groove, 34 is the partition plate, 35 is the second convex ring, 341 is the central hole, 301 is the inner left cavity, 302 is the inner right cavity, 303 is the outer upper cavity, 304 is the outer lower cavity, 305 is the front cavity, and 4 is the mounting base. 41 is the coupling, 42 is the shaft Glyd ring, 43 is bearing one, 44 is bearing two, 5 is the valve core, 51 is the right valve core, 511 is the right valve core screw, 52 is the left valve core, 521 is the left valve core screw, 5210 is the blind end, 53 is the connecting rod, 54 is the drive handle, 6 is the end cap, 61 is the air hole. In the figure, A and B are the oil ports opened on the surface of the outer cylinder 2. In the figure, the dashed arrow indicates the working direction of the hydraulic oil, and the straight arrow and hollow arrow indicate the direction of movement. Detailed Implementation

[0017] The technical solution of the present invention will be further described below with reference to Figures 1-20 and specific embodiments.

[0018] The accompanying drawings are for illustrative purposes only and are schematic diagrams, not actual images. They should not be construed as limiting the scope of this patent. To better illustrate the embodiments of the present invention, some parts in the drawings may be omitted, enlarged, or reduced, and do not represent the actual dimensions of the product. It is understandable to those skilled in the art that some well-known structures and their descriptions may be omitted in the drawings.

[0019] In the accompanying drawings of the embodiments of the present invention, the same or similar reference numerals correspond to the same or similar components. In the description of the present invention, it should be understood that if terms such as "upper," "lower," "left," "right," "inner," and "outer" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, they are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or part referred to has a specific orientation, or is constructed and operated in a specific orientation. Therefore, the terms used to describe positional relationships in the accompanying drawings are only for illustrative purposes and should not be construed as limiting the present patent. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0020] In the description of this invention, unless otherwise explicitly specified and limited, the term "connection" or similar designation indicating a connection between components should be interpreted broadly. For example, it can refer to a fixed connection, a detachable connection, or an integral part; it can be a direct connection or an indirect connection via an intermediate medium; it can refer to the internal communication between two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0021] The present invention provides a high-voltage bidirectional drive servo variable device, as shown in Figures 1 and 2, which includes a motor 1, an outer cylinder 2 and a controller. The outer cylinder 2 includes a cylinder body and a cylinder base. In Figures 3 and 4, the cylindrical part is the cylinder body and the block part is the cylinder base.

[0022] It also includes a servo variable cylinder, which includes a valve sleeve 3 and a valve core 5, as shown in Figures 11 and 12. The valve core 5 includes a left valve core 52, a connecting rod 53, a right valve core 51, and a drive handle 54 connected in sequence. The drive handle 54 is connected to a mounting base 4 through a movable support. The mounting base 4 is located inside the cylinder seat. The tail end of the drive handle 54 is connected to a motor 1. A right valve core spiral 511 is formed on the right valve core 51, penetrating the surface of the right valve core 51. A left valve core spiral 521 is formed on the left valve core 52. The right end of the left valve core spiral 521 penetrates the right end of the left valve core 52, and the left end of the left valve core spiral 521 terminates at the left end of the left valve core 52. It is a blind spiral to prevent working oil from entering the front chamber 305. In this invention, both the right valve core spiral 511 and the left valve core spiral 521 adopt a double spiral structure.

[0023] A connecting rod 53 connects the right end of the left valve core 52 to the left end of the right valve core 51, so that when the drive handle 54 is driven to rotate by the motor 1, the coaxial left valve core 52, connecting rod 53 and right valve core 51 rotate synchronously. The synchronous rotation of the left valve core 52, connecting rod 53 and right valve core 51 as a whole, although the overall rotation speed of the valve core 5 is relatively large, can achieve the integrated connection of the three according to the current existing technology.

[0024] As shown in Figures 1, 2, and 5-16, the inner cavity of the valve sleeve 3 is provided with a partition 34, and a central hole 341 is opened at the center of the partition 34, which divides the inner cavity of the valve sleeve 3 into an inner left cavity 301 and an inner right cavity 302. The right valve core 51 is located in the inner right cavity 302, and the left valve core 52 is located in the inner left cavity 301. The connecting rod 53 passes through the central hole 341, allowing the valve sleeve 3 to move axially relative to the valve core 5. Raised ribs 31 are provided on both sides of the outer surface of the valve sleeve 3, a raised ring 32 is provided at the middle of the outer surface of the valve sleeve 3, and a raised ring 35 is provided at the right end of the outer surface of the valve sleeve 3. Raised rings 32 and 35 are respectively adapted to the inner surface of the cylinder, allowing the valve sleeve 3 to perform linear reciprocating motion relative to the cylinder. On the outer surface of the valve sleeve 3 and the inner surface of the cylinder, a pair of raised ribs 31 and raised rings 32 and 35 are respectively fitted to the inner surface of the cylinder, allowing the valve sleeve 3 to perform linear reciprocating motion relative to the cylinder. Between the two convex rings 35, an upper outer cavity 303 is formed on the upper part of the outer surface of the valve sleeve 3, and a lower outer cavity 304 is formed on the lower part of the outer surface of the valve sleeve 3. The upper part of the cylinder has an oil port A connecting to the upper outer cavity 303, and the lower part has an oil port B connecting to the lower outer cavity 304. Oil ports P1 and P2 are respectively opened on the surfaces of the two opposite valve sleeves 3 in the upper outer cavity 303, and oil ports T1 and T2 are respectively opened on the surfaces of the two opposite valve sleeves 3 in the lower outer cavity 304. As shown in Figures 6 and 10, the hydraulic oil in the upper outer cavity 303 enters through oil port P1 or P2, enters the inner right cavity 302 or the inner left cavity 301, and then passes through one of the spiral grooves of the connected double spiral grooves, acting on the surface of the partition plate 34 to drive the valve sleeve 3 to move axially. The oil in the other cavity is discharged through the spiral groove via oil port T1 or T2. See Figures 12-16.

[0025] Furthermore, after the left valve core 52 is inserted into the inner left cavity 301 of the valve sleeve 3, a front cavity 305 is left at the outer end of the inner left cavity 301. Even when the left valve core 52 is at its leftmost extreme position, the front cavity 305 will still be retained. Its function is to ensure pressure balance and avoid negative pressure adsorption, which would lead to poor movement.

[0026] Furthermore, the valve core 5 rotates, causing the right valve core screw 511 to connect to P1 or P2, and the left valve core screw 521 to connect to T1 or T2, driving the valve sleeve 3 to move to the left; this is a sudden movement, and the sudden movement amount can be set according to the required motion index.

[0027] After connection, the valve core 5 must still maintain a rotational relationship adapted to the axial linear motion of the valve sleeve 3. The motion relationship is as follows: Where: V(L) is the valve sleeve moving speed, Cd is the valve port flow coefficient, V(θ) is the valve core rotation angular velocity, ΔP is the valve port pressure difference, ρ is the medium density, S is the partition area, r is the valve core radius, and m is the oil port width.

[0028] In this invention, the valve core 5 is made of 40Cr material, and after heat treatment, it is precision machined. The helix angle of the outer peripheral spiral groove (i.e., the right valve core spiral 511 and the left valve core spiral 521) is set to 15°, the groove width is 5mm, and the groove depth is 3mm to ensure that the high-pressure oil flow is matched with the driving thrust. The linear motion valve sleeve 3 is made of 2Cr13 stainless steel, and the inner wall is ground with high precision, and the roughness is controlled below Ra0.8μm. The width of the connecting groove on the transverse partition is 8mm to ensure smooth oil flow. As a preferred embodiment, P1, P2, T1, and T2 of this invention are parallelograms, as shown in Figures 17-20, where m is the oil port width and n is the oil port height.

[0029] In addition, the above four oil ports can also be in the form of oblique squares, circles or ellipses, but the opening area of ​​the oil ports must be controlled to increase / decrease linearly with the rotation angle of the valve core 5, and the transient hydraulic pressure fluctuation must be controlled within 5%.

[0030] Furthermore, an anti-rotation structure is provided between the outer surface of the valve sleeve 3 and the inner surface of the cylinder. As shown in Figures 1-4, such as steel balls, an elastic pad is required to restrict the rotational freedom of the valve sleeve around its axis, retaining only its linear reciprocating motion freedom along the axial direction.

[0031] Furthermore, an end cap 6 is provided at the left port of the valve sleeve 3 for connecting the driven component (the driven component is a double-dotted square in Figures 12 and 13).

[0032] Furthermore, an air hole 61 is provided on the end cap 6, so that the front cavity 305 at the opening of the valve sleeve 3 can achieve air pressure balance. This ensures the accuracy and sensitivity of the valve sleeve 3's operation.

[0033] Furthermore, the movable support includes a coupling 41, a shaft glyph 42, a first bearing 43, and a second bearing 44. The top end of the coupling 41 is connected to the output shaft of the motor 1, and the bottom end of the coupling 41 is connected to the top end of the valve core 5. A shaft glyph 42 is provided between the mounting base 4 and the upper end of the valve core 5. A first bearing 43 is provided between the lower end of the shaft glyph 42 and the mounting base 4. A second bearing 44 is provided between the upper end of the valve core 5 and the valve sleeve 3.

[0034] Referring to Figures 12-20, the bidirectional drive working principle of the present invention is further explained as follows: Leftward stroke: Oil enters through port A, motor 1 drives valve core 5 to rotate, so that port P1 on valve sleeve 3 is connected to the right valve core screw 511 on right valve core 51; hydraulic oil flows into inner right cavity 302 through channel P1 via right valve core screw 511, and hydraulic oil pushes the partition 34 in the middle of valve sleeve 3, driving valve sleeve 3 to move to the left. Hydraulic oil in inner left cavity 301 of valve sleeve 3 is connected to port T1 via left valve core screw 521 on left valve core 52, and then discharged through port B.

[0035] Rightward stroke: Oil enters through port A, motor 1 drives valve core 5 to rotate, making port P2 on valve sleeve 3 connected to the left valve core screw 521 on the left valve core 52; hydraulic oil flows into the inner left cavity 301 through channel P2 via the left valve core screw 521, and the hydraulic oil pushes the partition 34 in the middle of valve sleeve 3, driving valve sleeve 3 to move to the right. The hydraulic oil in the inner right cavity 302 of valve sleeve 3 is connected to port T2 via the right valve core screw 511 on the right valve core 51, and then discharged through port B.

[0036] The blind end 5210 structure set at the outer end of the left valve core spiral 521 can effectively prevent hydraulic oil from leaking to the left end and entering the front chamber 305.

[0037] It should be noted that: 1. The design of the double helix structure, as well as the position and size relationship of P1, P2, T1 and T2, should meet the above working principle and avoid motion interference.

[0038] II. In the above working process of the present invention, the opening area of ​​the valve port needs to be set according to the actual operating environment when conducting this link. The relationship between the valve port opening area and the valve core rotation angle, valve port size, etc. is: Sa=m×tanθ×r; where: Sa is the valve port opening area, m is the valve port width, θ is the valve core rotation angle, and r is the valve core radius.

[0039] After the valve core 5 rotates to the designed position, it must maintain linear motion in tandem with the valve sleeve 3, as explained earlier. To achieve reverse motion, the valve core 5 must be controlled to rotate in the opposite direction, thus realizing bidirectional reciprocating motion. During operation, the motor 1 drives the valve core 5 to rotate. The high-pressure oil pressure is set to 10-30 MPa, and the low-pressure oil pressure is set to 0.5-1 MPa. During the forward stroke, the valve sleeve 3 moves to the left, with a stroke range of 0-50 mm and a response time ≤50 μs. During the reverse stroke, the valve sleeve 3 moves to the right, with a stroke accuracy controlled within ±0.01 mm and a bidirectional motion repeatability error ≤0.1%.

[0040] It should be stated that the above-described specific embodiments are merely preferred embodiments of the present invention and the technical principles employed. Those skilled in the art should understand that various modifications, equivalent substitutions, and variations can be made to the present invention based on the technical content disclosed in this application. However, such variations, as long as they do not depart from the spirit of the present invention, should be within the protection scope of the present invention. Furthermore, some terminology used in this specification and claims is not limiting but merely for ease of description.

Claims

1. A high-voltage bidirectional drive servo variable device, comprising a motor (1), an outer cylinder (2), and a controller, wherein the outer cylinder (2) comprises a cylinder body and a cylinder base, characterized in that, It also includes a servo variable cylinder, which includes a valve sleeve (3) and a valve core (5). The valve core (5) includes a left valve core (52), a connecting rod (53), a right valve core (51), and a drive handle (54) connected in sequence. The drive handle (54) is connected to a mounting base (4) through a movable support. The mounting base (4) is located inside the cylinder seat. The tail end of the drive handle (54) is connected to the motor (1). A right valve core helix (511) penetrating the surface of the right valve core (51) is provided on the right valve core (51). A left valve core helix (521) is provided on the left valve core (52). The right end of the left valve core (52) passes through the right end of the left valve core (52), and the left end of the left valve core spiral (521) ends at the left end of the left valve core (52); the right end of the left valve core (52) and the left end of the right valve core (51) are connected by the connecting rod (53), so that when the drive handle (54) is driven to rotate by the motor (1), the coaxial left valve core (52), connecting rod (53) and right valve core (51) rotate synchronously; the inner cavity of the valve sleeve (3) is provided with a partition (34), and a central hole (341) is opened at the center of the partition (34), so that the inner cavity of the valve sleeve (3) is divided into an inner left cavity (301) and an inner right cavity (301). 302), the right valve core (51) is located in the inner right cavity (302), the left valve core (52) is located in the inner left cavity (301), the connecting rod (53) passes through the central hole (341), so that the valve sleeve (3) can move axially relative to the valve core (5); ribs (31) are provided on both sides of the outer surface of the valve sleeve (3), a first rib (32) is provided at the middle position of the outer surface of the valve sleeve (3), and a second rib (35) is provided at the right end of the outer surface of the valve sleeve (3); the first rib (32) and the second rib (35) are respectively adapted to the inner surface of the cylinder, so that the valve sleeve (3) can move axially relative to the valve core (5). The cylinder body performs a linear reciprocating motion; between the outer surface of the valve sleeve (3) and the inner surface of the cylinder body, a pair of convex ribs (31) and convex ring one (32) and convex ring two (35) form an upper outer cavity (303) located on the upper part of the outer surface of the valve sleeve (3) and an lower outer cavity (304) located on the lower part of the outer surface of the valve sleeve (3); the upper part of the cylinder body is provided with an oil port A that connects to the upper outer cavity (303), and the lower part is provided with an oil port B that connects to the lower outer cavity (304); oil ports P1 and P2 are respectively provided at two opposite corners of the upper outer cavity (303), and oil ports T1 and T2 are respectively provided at two opposite corners of the lower outer cavity (304).

2. The high-voltage bidirectional drive servo variable device according to claim 1, characterized in that, After the left valve core (52) is installed into the inner left cavity (301) of the valve sleeve (3), a front cavity (305) is left at the outer end of the inner left cavity (301).

3. The high-voltage bidirectional drive servo variable device according to claim 1, characterized in that, The valve core (5) rotates, causing the right valve core screw (511) to connect to P1 or P2, and the left valve core screw (521) to connect to T1 or T2, driving the valve sleeve (3) to move to the left; after connection, the valve core (5) still needs to maintain synchronous rotation with the axial linear motion of the valve sleeve (3), and the motion relationship is as follows: ； Where: V(L) is the valve sleeve moving speed, Cd is the valve port flow coefficient, V(θ) is the valve core rotation angular velocity, ΔP is the valve port pressure difference, ρ is the medium density, S is the partition area, r is the valve core radius, and m is the valve port width.

4. The high-voltage bidirectional drive servo variable device according to claim 1, characterized in that, An anti-rotation structure is provided between the outer surface of the valve sleeve (3) and the inner surface of the cylinder.

5. A high-voltage bidirectional drive servo variable device according to claim 1, characterized in that, An end cap (6) is also provided at the left port of the valve sleeve (3) for connecting the driven component.

6. A high-voltage bidirectional drive servo variable device according to claim 5, characterized in that, An air hole (61) is provided on the end cap (6) so that the front cavity (305) of the valve sleeve (3) can achieve air pressure balance.

7. The high-voltage bidirectional drive servo variable device according to claim 1, characterized in that, The movable support includes a coupling (41), a shaft glyph (42), a bearing one (43), and a bearing two (44). The top end of the coupling (41) is connected to the output shaft of the motor (1), and the bottom end of the coupling (41) is connected to the top end of the valve core (5). The shaft glyph (42) is provided between the mounting base (4) and the upper end of the valve core (5). The bearing one (43) is provided between the lower end of the shaft glyph (42) and the mounting base (4). The bearing two (44) is provided between the upper end of the valve core (5) and the valve sleeve (2).

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