A rotary servo valve for high-flow and high-pressure oil cylinders

Abstract

The present invention relates to the technical field of fluid pressure actuators, and in particular to a rotary servo valve for a large-flow, high-pressure oil cylinder, comprising an outer shell, a valve sleeve and a valve core which are sequentially mounted from the outside to the inside, a conical block is arranged at the end of the valve core, a first gap is formed between the conical block and the conical hole on the outer shell, an epitaxial flow channel is arranged in the conical block, the epitaxial flow channel is connected between the central flow channel and the first gap, and a pressure valve is arranged in the epitaxial flow channel. In the rotary servo valve of the present invention, when the valve core rotates, causing the oil circuit to be disconnected and the oil pressure in the central flow channel to increase, the pressure valve opens, and the oil flows into the first gap through the epitaxial flow channel, forming a leak-proof mechanical sealing structure, which can also play a lubricating role and can regulate the oil pressure. As a fluid pressure actuator, the rotary servo valve of the present invention has broad application prospects in fields such as high-end equipment manufacturing.

Description

Technical Field

[0001] The invention relates to the technical field of fluid pressure actuators, in particular to a rotary servo valve for a large-flow, high-pressure oil cylinder. Background Art

[0002] The electro-hydraulic servo valve is a key component in electro-hydraulic servo control. After receiving the analog electrical signal, it will adjust the flow and pressure of the hydraulic control valve accordingly. Due to its advantages such as fast dynamic response, high control accuracy and long service life, it has been widely used in electro-hydraulic servo control systems in the fields of aviation, aerospace, ships, metallurgy, chemical industry, etc.

[0003] The rotary servo valve changes the flow and pressure of the valve body by using a motor to drive the valve core to rotate a certain angle. In order to connect the external motor to the valve core, the valve core needs to extend through the side cover of the valve body, which will cause the high-pressure oil in the valve body to leak easily. Usually, an elastic sealing ring is used to ensure that the valve core can rotate smoothly relative to the outer shell while ensuring the sealing between the valve body and the valve core extension rod. However, the service life of this elastic seal is limited, it is easy to be damaged and fail, and needs to be replaced frequently. At the same time, when the rotary servo valve switches the oil channel, the high-pressure oil will have a momentary pause, so it will form a large hydraulic shock, which will affect the service life of the servo valve.

[0004] The information disclosed in the background technology section of the present invention is only intended to deepen the understanding of the general background technology of the present invention, and should not be regarded as acknowledging or suggesting in any form that the information constitutes the prior art already known to those skilled in the art. Summary of the invention

[0005] Based on this, it is necessary to provide a rotary servo valve for a large-flow high-pressure oil cylinder to address the problem of frequent replacement of seals in the current rotary servo valve.

[0006] The above purpose is achieved through the following technical solutions:

[0007] A rotary servo valve for a large-flow, high-pressure oil cylinder, comprising:

[0008] A housing, the housing comprising a valve body and a side cover connected to an end of the valve body, a valve cavity is arranged in the housing, the side cover comprises a tapered hole and an overflow cavity, the tapered hole is connected between the valve cavity and the overflow cavity, and the size of the tapered hole near one end of the valve cavity is larger than the size of the tapered hole near one end of the overflow cavity;

[0009] A valve sleeve, the valve sleeve is sleeved in the outer shell and fixedly connected to the outer shell;

[0010] A valve core, wherein the valve core is sleeved in the valve sleeve, and the valve core can rotate relative to the valve sleeve. A conical block is provided at the end of the valve core, and the conical block is provided in the conical hole. A first gap is formed between the conical block and the conical hole, and the first gap is connected with the overflow chamber. A central flow channel is provided in the valve core, and an epitaxial flow channel is provided in the conical block. The epitaxial flow channel is connected between the central flow channel and the first gap, and a pressure valve is provided in the epitaxial flow channel.

[0011] Furthermore, a buffer is provided at one end of the central flow channel close to the conical block, and the buffer is used to buffer the hydraulic shock in the central flow channel.

[0012] Furthermore, the buffer member includes a plurality of disc springs stacked along the extension direction of the central flow channel.

[0013] Furthermore, the central flow channel is an axial hole arranged in the center of the valve core, and a connecting hole coaxial with the central flow channel is arranged in the conical block. The aperture of the connecting hole is smaller than the central flow channel, and a step surface is formed at the connection between the central flow channel and the connecting hole, and the buffer member is installed on the step surface.

[0014] Furthermore, the side cover includes an oil recovery port, which is connected to the bottom of the overflow chamber and communicates with the overflow chamber.

[0015] Furthermore, the conical block is coaxially arranged with the valve core, the cross section of the conical block along the axial direction is trapezoidal, the epitaxial flow channel extends radially along the conical block, the conical block is evenly provided with a plurality of the epitaxial flow channels along the circumferential direction, and a pressure valve is installed in each of the epitaxial flow channels.

[0016] Furthermore, the first gap is an annular gap surrounding the outer circumference of the conical block.

[0017] Furthermore, two central flow channels are arranged in the axial direction at intervals in the valve core.

[0018] Furthermore, the side sealing covers are arranged at both ends of the valve body, the conical blocks are symmetrically arranged at both ends of the valve core, and the side sealing covers are provided with the conical holes matched with the conical blocks.

[0019] Furthermore, the rotary servo valve also includes a driving member for driving the valve core to rotate, and an extension rod is provided at one end of the valve core, and the extension rod passes through the corresponding side cover and is connected to the driving member.

[0020] The beneficial effects of the present invention are:

[0021] The present invention arranges a conical block at the end of the valve core to form a first gap between the conical block and the conical hole on the outer shell. When the valve core rotates to cause the oil circuit to change, the hydraulic shock generated in the central flow channel opens the pressure valve, and the oil fills the first gap to form a mechanical sealing structure using oil sealing. Compared with existing elastic seals, the sealing structure of the present invention has a longer service life and does not need to be replaced frequently.

[0022] The present invention arranges a buffer inside the central flow channel for pressure reduction and buffering, and arranges an outer flow channel and a pressure valve. When the oil circuit changes, the high-pressure oil that generates hydraulic shock can be released, thereby avoiding damage to the device caused by the hydraulic shock and extending the service life.

[0023] In addition, the oil entering the first gap can lubricate the rotation of the valve core, so that the oil in the epitaxial flow channel flows out and enters the first gap, which can prepare for the next pressure reduction lubrication. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a schematic structural diagram of a rotary servo valve for a large flow and high pressure oil cylinder according to an embodiment of the present invention;

[0025] Figure 2 A top view of a rotary servo valve for a large flow and high pressure oil cylinder according to an embodiment of the present invention;

[0026] Figure 3 for Figure 2 Sectional view at AA;

[0027] Figure 4 for Figure 3 A partial enlarged view of point B in the middle;

[0028] Figure 5 A schematic diagram of the structure of a valve core according to an embodiment of the present invention;

[0029] Figure 6 A schematic structural diagram of a valve sleeve according to an embodiment of the present invention;

[0030] Figure 7 A schematic diagram of the structure of a side cover according to an embodiment of the present invention;

[0031] Figure 8 Schematic diagram of the structure of a buffer according to an embodiment of the present invention.

[0032] in:

[0033] 100. Valve core; 101. Central flow channel; 102. Extended flow channel; 103. Pressure valve; 104. Tapered block; 105. Buffer; 106. Connecting hole; 107. Extension rod; 108. Central hole; 200. Valve sleeve; 300. Housing; 301. Overflow chamber; 302. Oil recovery port; 303. Valve chamber; 310. Valve body; 311. First working oil port; 312. High-pressure oil inlet; 313. Low-pressure oil outlet; 314. Second working oil port; 320. Side cover; 321. Tapered hole; 322. First gap; 400. Drive member. DETAILED DESCRIPTION

[0034] In order to make the purpose, technical solution and advantages of the present invention more clearly understood, the present invention is further described in detail below through embodiments and in conjunction with the accompanying drawings. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0035] The serial numbers assigned to the components herein, such as "first", "second", etc., are only used to distinguish the objects described and do not have any order or technical meaning. The "connection" and "coupling" mentioned in the present invention, unless otherwise specified, include direct and indirect connections (couplings). In the description of the present invention, it should be understood that the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", etc., indicating the orientation or position relationship are based on the orientation or position relationship shown in the accompanying drawings, which is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0036] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being "above", "above" or "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below", "below" or "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0037] like Figures 1 to 8 As shown, an embodiment of the present invention provides a rotary servo valve for a large flow and high pressure oil cylinder, which includes a housing 300, a valve sleeve 200 and a valve core 100. The housing 300, the valve sleeve 200 and the valve core 100 are nested and assembled in sequence from the outside to the inside.

[0038] The housing 300 includes a valve body 310 and a side cover 320 connected to the end of the valve body 310. The valve body 310 and the side covers 320 at both ends are connected to form a closed structure. A valve cavity 303 is arranged in the housing 300. The side cover 320 includes a tapered hole 321 and an overflow cavity 301. The tapered hole 321 and the overflow cavity 301 are arranged at intervals along the axial direction of the valve body 310. The tapered hole 321 is arranged at one end of the side cover 320 close to the valve cavity 303. The tapered hole 321 is connected between the valve cavity 303 and the overflow cavity 301. The size of the tapered hole 321 close to the valve cavity 303 is larger than the size of the tapered hole 321 close to the overflow cavity 301. The valve sleeve 200 is sleeved in the housing 300 and fixedly connected to the housing 300.

[0039] The valve core 100 is sleeved in the valve sleeve 200, and the valve core 100 can rotate relative to the valve sleeve 200. A conical block 104 is provided at the end of the valve core 100, and the conical block 104 is provided in the conical hole 321. The conical block 104 matches the shape of the conical hole 321, and a first gap 322 is formed between the conical block 104 and the conical hole 321. The first gap 322 is connected to the overflow chamber 301 and the valve chamber 303. A central flow channel 101 is provided in the valve core 100, and an epitaxial flow channel 102 is provided in the conical block 104. The epitaxial flow channel 102 is connected between the central flow channel 101 and the first gap 322, and a pressure valve 103 is provided in the epitaxial flow channel 102.

[0040] Specifically, when the valve core 100 is in the first working state, the oil path where the central flow channel 101 is located is unblocked, the pressure valve 103 is closed, and the outer flow channel 102 is blocked. When the valve core 100 rotates to the second working state, the oil path where the central flow channel 101 is located is disconnected, the pressure valve 103 is opened, and the outer flow channel 102 is connected.

[0041] Specifically, the first gap 322 is relatively narrow and can be used as a sealing gap. When the valve core 100 rotates, the oil circuit where the central flow channel 101 is located is disconnected, and the oil pressure in the central flow channel 101 increases. The impact force generated can open the pressure valve 103 in the epitaxial flow channel 102, and the oil enters the first gap 322, so that the outside air cannot enter the valve cavity 303, and sealing can be achieved. At the same time, when the valve core 100 rotates, the oil in the first gap 322 can play a lubricating role, which can reduce the wear between the tapered block 104 and the tapered hole 321 and extend the service life. In addition, it should be noted that when the oil circuit is unblocked, the oil pressure in the valve cavity 303 is not enough to make the oil flow out of the first gap 322, and the oil pressure in the connecting part of the epitaxial flow channel 102 and the central flow channel 101 is not enough to open the pressure valve 103 in the epitaxial flow channel 102.

[0042] The rotary servo valve provided in the embodiment of the present invention is provided with a conical block 104 at the end of the valve core 100, and the conical block 104 extends into the conical hole 321 on the side cover 320 from the large end of the conical hole 321, so that a narrow first gap 322 is formed between the conical block 104 and the conical hole 321. When the valve core 100 rotates and causes the oil circuit to change, the pressure valve 103 is opened by the hydraulic impact of the high-pressure oil, and the oil fills the first gap 322, thereby forming an oil-sealed mechanical sealing structure between the end of the valve core 100 and the side cover 320. Compared with the elastic sealing member used in the related art, the sealing structure of the present invention is more reliable and has a longer service life, and does not require frequent replacement.

[0043] At the same time, when the oil circuit changes, the impact force generated by the high-pressure oil can open the pressure valve 103, and the oil pressure can be released outward, avoiding damage to the equipment due to excessive oil pressure, and extending the service life of the rotary servo valve. In addition, the oil in the epitaxial flow channel 102 flows out to prepare for the next pressure reduction lubrication.

[0044] In some embodiments, a buffer 105 is provided at one end of the central flow channel 101 close to the conical block 104. The buffer 105 is used to buffer the hydraulic shock in the central flow channel 101. A center hole 108 is provided on the buffer 105 to allow the oil in the central flow channel 101 to enter the epitaxial flow channel 102 through the center hole 108.

[0045] Among them, in the valve core 100, the central flow channel 101 is connected with the outer flow channel 102 at the end, and the buffer 105 is arranged in the central flow channel 101 near the end position of the outer flow channel 102. When the oil circuit where the central flow channel 101 is located is disconnected, the high-pressure oil in the central flow channel 101 generates a large hydraulic shock. The buffer 105 can relieve part of the oil pressure to avoid excessive hydraulic shock and damage to the hydraulic structure, such as the pressure valve 103.

[0046] It should be noted that when the oil circuit is disconnected, the high-pressure oil in the central channel 101 can still open the pressure valve 103 after being decompressed and buffered by the buffer 105 in the central channel 101, and then the oil flows along the epitaxial channel 102 and fills the first gap 322.

[0047] In some embodiments, the buffer member 105 includes a plurality of disc springs stacked along the extension direction of the central flow channel 101 .

[0048] Among them, multiple disc springs are stacked in sequence along the axial direction of the central flow channel 101. When the oil circuit is disconnected and the oil pressure in the central flow channel 101 suddenly increases, the high-pressure oil acts on the disc spring, forcing the disc spring to produce compression deformation. In this process, the disc spring converts part of the energy of the hydraulic impact into its own elastic potential energy and stores it, avoiding the entire impact force directly acting on the pressure valve 103 and causing damage.

[0049] Of course, in other embodiments, when the oil circuit is disconnected and the hydraulic shock generated in the central flow channel 101 does not need to be buffered, the buffer 105 can also be omitted.

[0050] In some embodiments, the central flow channel 101 is an axial hole disposed at the center of the valve core 100, and a connecting hole 106 coaxial with the central flow channel 101 is disposed in the conical block 104. The hole diameter of the connecting hole 106 is smaller than that of the central flow channel 101. A step surface is formed at the connection between the central flow channel 101 and the connecting hole 106, and the buffer 105 is installed on the step surface. In this way, when the oil circuit in the central flow channel 101 is disconnected and the oil pressure suddenly increases, the buffer 105 can play a buffering role in a timely and effective manner.

[0051] In some embodiments, the side cover 320 includes an oil recovery port 302, which is connected to the bottom of the overflow chamber 301 and communicates with the overflow chamber 301. The oil recovery port 302 can collect the oil collected by the overflow chamber 301 to avoid waste, and the oil can be recycled. For example, the collected oil can be further processed and then transported back to the oil circuit system of the rotary servo valve to participate in the hydraulic transmission and other related working processes again, thereby improving the utilization rate of the oil.

[0052] In some embodiments, the conical block 104 is coaxially arranged with the valve core 100, the cross-section of the conical block 104 along the axial direction is trapezoidal, the epitaxial flow channel 102 extends radially along the conical block 104, and the conical block 104 is evenly provided with multiple epitaxial flow channels 102 along the circumferential direction, and a pressure valve 103 is installed in each epitaxial flow channel 102.

[0053] Among them, the coaxial setting ensures the movement stability of the conical block 104 during the rotation of the valve core 100, making its cooperation with related components more precise, which helps to maintain the stability of the entire rotary servo valve during operation. The multiple epitaxial flow channels 102 evenly distributed in the circumference can effectively avoid the situation where the local oil pressure is too high or too low, ensuring the balance of the oil circuit. The pressure valve 103 installed in each epitaxial flow channel 102 can regulate the oil pressure in each epitaxial flow channel 102.

[0054] In some embodiments, the first gap 322 is an annular gap surrounding the outer periphery of the conical block 104. When the valve core 100 rotates and causes the oil circuit to change, the central flow channel 101 oil circuit is disconnected and the oil pressure increases, the first gap 322 can be opened with the help of the pressure valve 103 to allow oil to fill, forming a reliable oil-sealed mechanical seal structure, effectively preventing high-pressure oil leakage in the valve body, replacing traditional elastic seals, and improving sealing reliability. During the rotation of the valve core 100, the oil in the first gap 322 can play a lubricating role. The annular structure makes the oil distribution relatively uniform, and can buffer and regulate the oil flow and pressure changes when the oil circuit changes, maintain the pressure balance inside the system, and avoid excessive impact on the rotating servo valve caused by sudden changes in oil pressure.

[0055] In some embodiments, two central flow channels 101 arranged at intervals along the axial direction are disposed in the valve core 100. Specifically, the two central flow channels 101 in the valve core 100 are coaxially arranged at intervals to ensure independent control of the oil circuits in which they are located.

[0056] In some embodiments, side covers 320 are disposed at both ends of the valve body 310 , tapered blocks 104 are symmetrically disposed at both ends of the valve core 100 , and tapered holes 321 matching with the tapered blocks 104 are disposed on the side covers 320 .

[0057] In some embodiments, the rotary servo valve further includes a driving member 400 for driving the valve core 100 to rotate. An extension rod 107 is provided at one end of the valve core 100, and the extension rod 107 passes through the corresponding side cover 320 and is connected to the driving member 400. The driving member 400 is an external motor, which drives the valve core in the servo valve to rotate by rotating its output shaft. For example, the driving member 400 can use a servo motor as a power source for the rotation of the valve core. After receiving the command issued by the control system, the servo motor will accurately rotate a certain angle according to the command requirements.

[0058] The working principle of the rotary servo valve for a large flow and high pressure oil cylinder in the above embodiment is as follows: when the direction of the oil circuit remains unchanged, the hydraulic oil flows according to the existing established path, so the oil pressure in the central flow channel 101 is not enough to open the pressure valve 103. That is, under normal circumstances, the pressure valve 103 is closed and the extension flow channel 102 is blocked. When the oil circuit changes, that is, the driving member 400 drives the valve core 100 to rotate through the extension rod 107, changing the position relationship of the valve core 100 relative to the valve sleeve 200 and the housing 300, thereby causing the oil circuit to change. Specifically, the rotation of the valve core 100 causes the oil circuit to be disconnected, and the oil pressure in the central flow channel 101 will increase rapidly, thereby generating a hydraulic shock. After the pressure reduction buffering of the buffer 105, when the impact pressure can still reach the opening pressure threshold of the pressure valve 103, the pressure valve 103 opens, and the oil flows into the first gap 322 between the conical block 104 and the conical hole 321 through the epitaxial flow channel 102. The first gap 322 is an annular gap surrounding the outer periphery of the conical block 104. After being filled with oil, it can prevent the outside air from entering, forming a reliable mechanical sealing structure, and can prevent the oil in the valve cavity from flowing out in large quantities when the oil circuit is disconnected. Through the cooperation of the central flow channel 101, the epitaxial flow channel 102, the pressure valve 103 and the first gap 322, the sudden change of oil pressure caused by the change of the oil circuit can also be adjusted, the pressure balance inside the system is maintained, and the stable operation of the rotary servo valve is guaranteed. In addition, the side covers 320 at both ends of the valve body 310 and the conical blocks 104 and conical holes 321 symmetrically arranged at both ends of the valve core 100 ensure bidirectional oil circuit control and overall force balance, and the independent control of different oil circuits can be achieved through the central flow channel 101 arranged axially at intervals in the valve core 100. During the oil circuit conversion process, part of the oil will flow into the overflow chamber 301 from the first gap 322, and the collected oil can be collected through the oil recovery port 302 for further recycling.

[0059] For example, Figure 3 As shown, the valve body 310 is provided with a first working oil port 311, a high-pressure oil inlet 312, a low-pressure oil outlet 313 and a second working oil port 314. When the valve core 100 is in the first working state, the high-pressure oil inlet 312 and the first working oil port 311 are connected through the oil circuit where one of the central flow channels 101 is located, and the second working oil port 314 and the low-pressure oil outlet 313 are connected through the oil circuit where the other central flow channel 101 is located. When the valve core 100 is in the second working state, the oil circuit between the high-pressure oil inlet 312 and the first working oil port 311 is disconnected, and the oil circuit between the second working oil port 314 and the low-pressure oil outlet 313 is also disconnected. That is, when the oil circuit is unblocked, the oil flows into or out of the valve cavity 303 from each oil port on the valve body 310.

[0060] The specific structure and working principle of the oil circuit part of the rotary servo valve of the present invention are prior art, and reference may be made to the relevant contents in the patent document with publication number CN103216639B.

[0061] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0062] The above-described embodiments only express several implementation methods of the present invention, and the description thereof is relatively specific and detailed, but it cannot be understood as limiting the scope of the present invention. It should be pointed out that, for a person of ordinary skill in the art, several modifications and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the attached claims.

Claims

1. A rotary servo valve for a large flow and high pressure oil cylinder, characterized in that: include: A housing (300), the housing (300) comprising a valve body (310) and a side cover (320) connected to an end of the valve body (310), a valve cavity (303) being provided in the housing (300), the side cover (320) comprising a tapered hole (321) and an overflow cavity (301), the tapered hole (321) being connected between the valve cavity (303) and the overflow cavity (301), the dimension of the tapered hole (321) at one end close to the valve cavity (303) being larger than the dimension of the tapered hole (321) at one end close to the overflow cavity (301); A valve sleeve (200), the valve sleeve (200) being sleeved inside the outer shell (300) and fixedly connected to the outer shell (300); A valve core (100), wherein the valve core (100) is sleeved in the valve sleeve (200), and the valve core (100) can rotate relative to the valve sleeve (200). A conical block (104) is provided at the end of the valve core (100), and the conical block (104) is provided in the conical hole (321). A first gap (322) is formed between the conical block (104) and the conical hole (321), and the first gap (322) is communicated with the overflow chamber (301). A central flow channel (101) is provided in the valve core (100), and an epitaxial flow channel (102) is provided in the conical block (104). The epitaxial flow channel (102) is communicated between the central flow channel (101) and the first gap (322), and a pressure valve (103) is provided in the epitaxial flow channel (102).

2. A rotary servo valve for a large flow and high pressure oil cylinder according to claim 1, characterized in that: A buffer (105) is provided at one end of the central flow channel (101) close to the conical block (104), and the buffer (105) is used to buffer hydraulic shock in the central flow channel (101).

3. A rotary servo valve for a large flow and high pressure oil cylinder according to claim 2, characterized in that: The buffer component (105) comprises a plurality of disc springs stacked along the extension direction of the central flow channel (101).

4. A rotary servo valve for a large flow and high pressure oil cylinder according to claim 2, characterized in that: The central flow channel (101) is an axial hole arranged at the center of the valve core (100), and a connecting hole (106) coaxial with the central flow channel (101) is arranged in the conical block (104). The hole diameter of the connecting hole (106) is smaller than that of the central flow channel (101). A step surface is formed at the connection between the central flow channel (101) and the connecting hole (106), and the buffer member (105) is installed on the step surface.

5. The rotary servo valve for a large flow and high pressure oil cylinder according to claim 1, characterized in that: The side cover (320) comprises an oil recovery port (302), wherein the oil recovery port (302) is connected to the bottom of the overflow chamber (301) and communicates with the overflow chamber (301).

6. A rotary servo valve for a large flow and high pressure oil cylinder according to claim 1, characterized in that: The conical block (104) is coaxially arranged with the valve core (100); the cross section of the conical block (104) along the axial direction is a trapezoid; the epitaxial flow channel (102) extends radially along the conical block (104); the conical block (104) is evenly provided with a plurality of the epitaxial flow channels (102) along the circumferential direction; and a pressure valve (103) is installed in each of the epitaxial flow channels (102).

7. A rotary servo valve for a large flow and high pressure oil cylinder according to claim 1, characterized in that: The first gap (322) is an annular gap surrounding the outer circumference of the conical block (104).

8. The rotary servo valve for a large flow and high pressure oil cylinder according to claim 1, characterized in that: Two central flow channels (101) are arranged in the valve core (100) at intervals along the axial direction.

9. A rotary servo valve for a large flow and high pressure oil cylinder according to claim 8, characterized in that: The side sealing covers (320) are arranged at both ends of the valve body (310), the conical blocks (104) are symmetrically arranged at both ends of the valve core (100), and the side sealing covers (320) are provided with the conical holes (321) that cooperate with the conical blocks (104).

10. A rotary servo valve for a large flow and high pressure oil cylinder according to claim 1, characterized in that: The rotary servo valve further comprises a driving member (400) for driving the valve core (100) to rotate, an extension rod (107) being provided at one end of the valve core (100), the extension rod (107) passing through the corresponding side cover (320) and connected to the driving member (400).

Images