Ultrahigh-pressure self-locking anti-rotation hydraulic jacking oil cylinder

Abstract

The invention relates to the technical field of hydraulic cylinders, and provides an ultrahigh-pressure self-locking anti-rotation type hydraulic jacking oil cylinder which is characterized in that a plunger is arranged in an outer cylinder barrel in a sliding mode, a first oil liquid containing cavity is formed between the inner bottom wall of the outer cylinder barrel and the outer bottom wall of the plunger, an inner cylinder barrel is arranged in the plunger, and a second oil liquid containing cavity is formed between the outer wall of the inner cylinder barrel and the inner wall of the plunger; the bottom of the inner cylinder barrel is connected with the outer cylinder barrel, a seventeenth flow channel and a fifteenth flow channel which are communicated with the sixteenth flow channel are horizontally formed in the top end and the bottom end of the inner cylinder barrel respectively, the seventeenth flow channel and the fifteenth flow channel are communicated with the second oil containing cavity and the thirteenth flow channel respectively, and a first oil opening and a second oil opening are formed in the lower portion of the outer cylinder barrel. The second hydraulic control one-way valve is connected with the first oil port and the first oil containing cavity, and the first hydraulic control one-way valve is connected with the second oil port and the thirteenth flow channel. According to the jacking oil cylinder, the structural rigidity is greatly improved, the sealing performance is guaranteed by optimizing anti-rotation measures, and the strict requirements for efficient, stable and safe operation of a hydraulic jacking device in the ultrahigh pressure environment are comprehensively met.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic cylinders, and in particular to an ultra-high-pressure self-locking anti-rotation hydraulic jacking oil cylinder. Background Art

[0002] As industrial equipment's requirements for ultra-high loads and high stability continue to increase, the demand for hydraulic jacking devices that can operate stably under ultra-high working pressures of 60-100MPa is becoming increasingly urgent.

[0003] During the jacking process, traditional designs often struggle to balance the lifting thrust and recovery phase energy consumption, and inadequate anti-rotation measures can easily subject seals to additional torsional stress due to plunger rotation. For example, the hydraulic jacking cylinder solution proposed in patent CN113090608 A relies on traditional external oil pipe connections and a cylinder earring structure. While this solves the initial deflection problem caused by the deadweight of the piston rod to some extent, the complex external piping connections not only increase the risk of leakage and pipe bursts, but also result in a loose overall structural layout, hindering efficient oil transfer and sealing stability in ultra-high-pressure environments.

[0004] Therefore, in response to the above problems, an ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder is proposed to solve the above problems. Summary of the Invention

[0005] In response to the shortcomings of the existing technology, the present invention develops an ultra-high pressure self-locking and anti-rotation hydraulic jacking cylinder. The present invention not only realizes the self-locking function and integrated design, eliminates the external high-pressure pipeline and greatly improves the structural rigidity, but also ensures the sealing performance by optimizing the anti-rotation measures, and fully meets the strict requirements for efficient, stable and safe operation of the hydraulic jacking device under ultra-high pressure environment.

[0006] The technical solution to the technical problem solved by the present invention is as follows: the present invention provides an ultra-high pressure self-locking anti-rotation hydraulic jacking oil cylinder, comprising an outer cylinder, a plunger, an inner cylinder, a hydraulically controlled one-way valve 1 and a hydraulically controlled one-way valve 2, the plunger is slidably arranged in the outer cylinder, an oil storage chamber 1 is formed between the inner bottom wall of the outer cylinder and the outer bottom wall of the plunger, an inner cylinder is arranged in the plunger, an oil storage chamber 2 is formed between the outer wall of the inner cylinder and the inner wall of the plunger, a sixteenth flow channel is vertically provided in the inner cylinder, the bottom of the inner cylinder is connected to the outer cylinder, a thirteenth flow channel is formed between the bottom of the inner cylinder and the outer cylinder, a seventeenth flow channel and a fifteenth flow channel connected to the sixteenth flow channel are horizontally provided at the top and bottom ends of the inner cylinder respectively, the seventeenth flow channel and the fifteenth flow channel are connected to the oil storage chamber 2 and the thirteenth flow channel respectively, an oil port 1 and an oil port 2 are provided at the lower part of the outer cylinder, the hydraulically controlled one-way valve 2 is connected to the oil port 1 and the oil storage chamber 1 respectively, and the hydraulically controlled one-way valve 1 is connected to the oil port 2 and the thirteenth flow channel respectively.

[0007] As an optimization, an interlayer cavity is provided at the bottom of the outer cylinder, and an installation port communicating with the interlayer cavity is opened below the outer wall of the outer cylinder. A hydraulically controlled one-way valve 1 and a hydraulically controlled one-way valve 2 are provided at the installation port, and an oil pipeline assembly is provided in the interlayer cavity.

[0008] As an optimization, the oil circuit pipeline assembly also includes a first flow channel, a seventh flow channel, a ninth flow channel and a twelfth flow channel. The first flow channel is horizontally arranged and connected to the oil port one. The twelfth flow channel is respectively connected to the first flow channel, the ninth flow channel and the oil chamber one. The ninth flow channel is horizontally arranged and connected to the seventh flow channel at the bottom. A hydraulically controlled one-way valve two is arranged at the ninth flow channel. The hydraulically controlled one-way valve two controls the circulation or closing of the first flow channel, the seventh flow channel and the twelfth flow channel.

[0009] As an optimization, the oil circuit pipeline assembly also includes an eleventh flow channel, a second flow channel, a third flow channel, a fourth flow channel, a fifth flow channel, a sixth flow channel and an eighth flow channel. The eleventh flow channel is horizontally arranged and connected to the oil port two. The eleventh flow channel is connected to the seventh flow channel through the eighth flow channel; the fourth flow channel is respectively connected to the eleventh flow channel, the fifth flow channel and the third flow channel, the third flow channel is connected to the thirteenth flow channel, the fifth flow channel is horizontally arranged and connected to the sixth flow channel, the sixth flow channel is vertically arranged and connected to the first flow channel through the second flow channel, and a hydraulically controlled one-way valve one is arranged at the fifth flow channel. The hydraulically controlled one-way valve one controls the circulation or closing of the fourth flow channel, the sixth flow channel and the eleventh flow channel.

[0010] As an optimization, it also includes a cylinder cover, which has a threaded hole and a bolt connected to the outer cylinder barrel set in the threaded hole.

[0011] As an optimization, a guide groove 1 is symmetrically provided along the radial direction of the cylinder head, a guide block is provided in the guide groove 1, the plunger is provided through the center of the cylinder head, and a guide groove 2 adapted to the guide block is provided on the outer wall of the plunger.

[0012] As an optimization, the bottom of the inner cylinder is connected to the bottom of the outer cylinder via a connecting nut.

[0013] As an optimization, step one is set at the top of the inner cylinder, the radius of step one is larger than the radius of the inner cylinder, and the outer wall of the step is set in contact with the inner cavity of the plunger, and step two is set on the bottom wall of the inner cavity of the plunger to prevent step one from falling out of the plunger.

[0014] The effects provided in the summary of the invention are only the effects of the embodiments, rather than all the effects of the invention. The above technical solution has the following advantages or beneficial effects: 1. The double-tube structure combines the outer cylinder, plunger, and inner cylinder into two independent load-bearing cavities, eliminating the traditional external high-pressure pipeline and directly using the cylinder body as the oil circuit. This not only significantly improves the overall structural rigidity and avoids potential failure problems caused by welding or joints, but also shortens the oil transmission path and reduces pressure loss, ensuring excellent working performance even in ultra-high pressure environments of 60-100 MPa. 2. Oil port 1, oil port 2, oil pipeline components, and hydraulic control check valve 1 and hydraulic control check valve 2 are directly arranged below the outer cylinder. This centralized arrangement integrates the oil circuit, reducing the number of external oil pipes and connectors, and reducing leakage, pipe burst, and the complexity of device installation and maintenance. 3. By optimizing the limiting structure of the cylinder head and plunger, a guide groove 1 is milled on the cylinder head, and a corresponding guide groove 2 is milled on the plunger, and a guide block is installed in conjunction with it. This effectively limits the rotation of the plunger, reduces the additional torsional stress on the seal, and significantly improves the sealing reliability and dynamic response performance of the entire system. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] The accompanying drawings are used to provide further understanding of the present invention and constitute a part of the specification. They are used to explain the present invention together with the embodiments of the present invention and do not constitute a limitation of the present invention.

[0016] Figure 1 It is a schematic diagram of the overall structure of the present invention; Figure 2 A cross-sectional view of the plunger of the present invention in a reset state; Figure 3 It is a cross-sectional view of the plunger in the lifting state of the present invention; Figure 4 is a cross-sectional view of the inner cylinder of the present invention; Figure 5 is a cross-sectional view of the plunger of the present invention; Figure 6 It is a structural diagram of the oil pipeline assembly of the present invention.

[0017] In the figure, 1, outer cylinder; 1-1, first flow channel; 1-2, second flow channel; 1-3, third flow channel; 1-4, fourth flow channel; 1-5, fifth flow channel; 1-6, sixth flow channel; 1-7, seventh flow channel; 1-8, eighth flow channel; 1-9, ninth flow channel; 1-11, eleventh flow channel; 1-12, twelfth flow channel; 1-13, thirteenth flow channel; 1-14, oil chamber 1; 1-15, threaded hole; 2, Plunger; 2-1, oil chamber 2; 2-2, guide groove 2; 2-3, step 2; 3, cylinder head; 4, guide block; 5, bolt; 6, inner cylinder; 6-1, fifteenth flow channel; 6-2, sixteenth flow channel; 6-3, seventeenth flow channel; 6-4, step 1; 7, connecting nut; 8, hydraulically controlled one-way valve 1; 9, hydraulically controlled one-way valve 2; 10, oil port 1; 11, oil port 2; 12, mounting port; 13, interlayer cavity. DETAILED DESCRIPTION

[0018] To clearly illustrate the technical features of this solution, the present invention is described in detail below through specific embodiments and in conjunction with the accompanying drawings. The following disclosure provides numerous different embodiments or examples for implementing various configurations of the present invention. To simplify the disclosure of the present invention, the following description focuses on components and configurations of specific examples. Furthermore, reference numbers and / or letters may be repeated throughout the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself indicate a relationship between the various embodiments and / or configurations discussed. It should be noted that the components illustrated in the drawings are not necessarily drawn to scale. Descriptions of well-known components and processing techniques and processes are omitted to avoid unnecessarily limiting the present invention. Terms such as "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer" indicate positions or locations based on the positions or locations shown in the drawings. These terms are used solely to facilitate the description of the present invention and simplify the description. They are not intended to indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation, and are therefore not to be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0019] like Figures 1 to 6As shown, an ultra-high pressure self-locking anti-rotation hydraulic jacking oil cylinder includes an outer cylinder 1, a plunger 2, an inner cylinder 6, a hydraulically controlled one-way valve 8 and a hydraulically controlled one-way valve 9. The plunger 2 is slidably arranged in the outer cylinder 1, and an oil storage chamber 1-14 is formed between the inner bottom wall of the outer cylinder 1 and the outer bottom wall of the plunger 2. The inner cylinder 6 is arranged in the plunger 2, and an oil storage chamber 2-1 is formed between the outer wall of the inner cylinder 6 and the inner wall of the plunger 2. A sixteenth flow channel 6-2 is vertically opened in the inner cylinder 6. The bottom of the inner cylinder 6 is connected to the outer cylinder 1, and a fluid flow chamber 2-1 is formed between the bottom of the inner cylinder 6 and the outer cylinder 1. The thirteenth flow channel 1-13 is formed, and the top and bottom ends of the inner cylinder 6 are respectively horizontally provided with the seventeenth flow channel 6-3 and the fifteenth flow channel 6-1 connected to the sixteenth flow channel 6-2, the seventeenth flow channel 6-3 and the fifteenth flow channel 6-1 are respectively connected to the oil storage chamber 2 2-1 and the thirteenth flow channel 1-13, and the lower part of the outer cylinder 1 is provided with an oil port 10 and an oil port 2 11, the hydraulically controlled one-way valve 2 9 is respectively connected to the oil port 10 and the oil storage chamber 1 1-14, and the hydraulically controlled one-way valve 1 8 is respectively connected to the oil port 2 11 and the thirteenth flow channel 1-13. The seventeenth flow channel 6-3 and the fifteenth flow channel 6-1 are both opened several times along the radial direction of the inner cylinder 6. The hydraulic jacking cylinder adopts a double-tube structure, combining the outer cylinder 1, the plunger 2 and the inner cylinder 6 into two independent force-bearing cavities, eliminating the traditional external high-pressure pipeline, and directly using the cylinder body as the oil circuit, which not only greatly improves the overall structural rigidity and avoids the failure problems that may be caused by welding or joints, but also shortens the oil transmission path and reduces pressure loss, ensuring that it can still maintain excellent working performance in an ultra-high pressure environment of 60 to 100 MPa. The oil port 1 10 and the oil port 2 11 are concentratedly arranged under the outer cylinder 1, and the oil circuit is directly integrated, which greatly simplifies the external pipeline connection and reduces the risk of leakage and pipe burst.

[0020] In this embodiment, an interlayer cavity 13 is provided at the bottom of the outer cylinder 1. An installation port 12 communicating with the interlayer cavity 13 is provided below the outer wall of the outer cylinder 1. A hydraulically controlled one-way valve 1 8 and a hydraulically controlled one-way valve 2 9 are provided at the installation port 12, and an oil pipeline assembly is provided within the interlayer cavity 13. The installation method and installation structure of the hydraulically controlled one-way valve 1 8 and the hydraulically controlled one-way valve 2 9 are prior art and will not be described in detail here. This hydraulic jacking cylinder adopts a highly integrated design, arranging the oil pipeline assembly and the hydraulically controlled one-way valve 1 8 and the hydraulically controlled one-way valve 2 9 directly below the outer cylinder 1, achieving a purely cylindrical shape for the overall structure. This effectively reduces the number of external oil pipes and connectors, and reduces the risk of leakage, pipe bursts, and the complexity of device installation and maintenance.

[0021] In this embodiment, the contact area between the upper inner wall of the outer cylinder 1 and the upper outer wall of the plunger 2 is greater than the contact area between the lower outer wall of the inner cylinder 6 and the lower inner wall of the plunger 2. When the working cylinder is performing the lifting process, the hydraulic oil acts on the oil chamber 1 1-14 and the oil chamber 2 2-1 respectively. Because the contact area between the upper inner wall of the outer cylinder 1 and the upper outer wall of the plunger 2 is greater than the contact area between the lower outer wall of the inner cylinder 6 and the lower inner wall of the plunger 2, under the same pressure, the upper thrust is much greater than the lower reverse thrust, thereby achieving one-way efficient lifting and ensuring sufficient net thrust in the lifting direction. This area difference design can effectively amplify the lifting force while reducing the pressure demand on the lower chamber, allowing the device to maintain stable force characteristics under ultra-high pressure conditions. Because the plunger 2 only needs to overcome the friction between itself and the seal during the recovery process, and does not need to provide the high thrust required during lifting, the contact area between the lower outer wall of the inner cylinder 6 and the lower inner wall of the plunger 2 can be relatively small. Doing so not only helps save material and reduce structural weight, but also reduces the return pressure demand of the hydraulic system, thereby improving overall efficiency.

[0022] In this embodiment, the oil pipeline assembly includes a first flow channel 1-1, a seventh flow channel 1-7, a ninth flow channel 1-9 and a twelfth flow channel 1-12. The first flow channel 1-1 is horizontally arranged and connected to the oil port 10. The twelfth flow channel 1-12 is respectively connected to the first flow channel 1-1, the ninth flow channel 1-9 and the oil chamber 1-14. The ninth flow channel 1-9 is horizontally arranged and connected to the seventh flow channel 1-7 at the bottom. A hydraulically controlled one-way valve 29 is arranged at the ninth flow channel 1-9. The hydraulically controlled one-way valve 29 controls the circulation or closing of the first flow channel 1-1, the seventh flow channel 1-7 and the twelfth flow channel 1-12.

[0023] The oil pipeline assembly also includes an eleventh flow channel 1-11, a second flow channel 1-2, a third flow channel 1-3, a fourth flow channel 1-4, a fifth flow channel 1-5, a sixth flow channel 1-6 and an eighth flow channel 1-8. The eleventh flow channel 1-11 is horizontally arranged and connected to the oil port 2 11. The eleventh flow channel 1-11 is connected to the seventh flow channel 1-7 through the eighth flow channel 1-8; the fourth flow channel 1-4 is respectively connected to the eleventh flow channel 1-11, the fifth flow channel 1-5 and the third flow channel 1-3, the third flow channel 1-3 is connected to the thirteenth flow channel 1-13, the fifth flow channel 1-5 is horizontally arranged and connected to the sixth flow channel 1-6, the sixth flow channel 1-6 is vertically arranged and connected to the first flow channel 1-1 through the second flow channel 1-2, and a hydraulically controlled one-way valve 8 is arranged at the fifth flow channel 1-5. The hydraulically controlled one-way valve 8 controls the circulation or closing of the fourth flow channel 1-4, the sixth flow channel 1-6 and the eleventh flow channel 1-11.

[0024] In this embodiment, a cylinder head 3 is further provided with threaded holes 1-15, within which bolts 5 are mounted for connection to the outer cylinder 1. Sealing strips are provided between the outer cylinder 1, the plunger 2, the inner cylinder 6, and the cylinder head 3 to prevent oil leakage, which will not be described in detail here.

[0025] Cylinder head 3 has radially symmetrical guide grooves 1 formed in the cylinder head 3, with guide blocks 4 positioned within them. Plunger 2 extends through the center of cylinder head 3, and a second guide groove 2-2 is formed on the outer wall of plunger 2, corresponding to guide blocks 4. By optimizing the retaining structure of cylinder head 3 and plunger 2, guide groove 1 is milled into cylinder head 3, and a corresponding guide groove 2-2 is milled into plunger 2, which, in conjunction with guide blocks 4, effectively restricts the rotation of plunger 2, reducing the additional torsional stress on the seal and significantly improving the sealing reliability and dynamic response performance of the entire system.

[0026] In this embodiment, the bottom of the inner cylinder 6 is connected to the bottom of the outer cylinder 1 through a connecting nut 7.

[0027] A step 6-4 is provided at the top of inner cylinder 6. The radius of step 6-4 is larger than that of inner cylinder 6, and the outer wall of step 6-4 contacts the inner cavity of plunger 2. A step 2-3 is provided on the bottom wall of the inner cavity of plunger 2 to prevent step 6-4 from slipping out of plunger 2. The provision of steps 6-4 and 2-3 achieves an automatic self-locking function during the lifting process, ensuring that the equipment remains securely locked once the oil chamber formed by plunger 2 and inner cylinder 6 reaches the cutoff position, significantly improving safety and stability during ultra-high-pressure operation.

[0028] The working process is: During the lifting process of the plunger 2, high-pressure oil (60-100 MPa) is introduced into the oil port 10 and then divided into two flow channels after passing through the first flow channel 1-1. One part passes through the oil inlet of the hydraulically controlled one-way valve 2 9, and then opens the oil outlet of the hydraulically controlled one-way valve 2 9 to enter the oil chamber 1-14. Since the plunger 2 is at the bottom before the working state, the plunger 2 is lifted up under the action of the oil pressure. Since the inner cylinder 6 is fixed to the outer cylinder 1 by the connecting nut 7, the volume of the oil chamber 2-1 formed by the plunger 2 and the inner cylinder 6 is also reduced, and the oil enters the inner cavity 16th flow channel 6-2 through the seventeenth flow channel 6-3 above the inner cylinder 6. The bottom of the sixteenth flow channel 6-2 is also connected to the fifteenth flow channel 6-1, and the fifteenth flow channel 6-1 is connected to the third flow channel 1-3 through the thirteenth flow channel 1-13. The subsequent oil return function of the oil chamber depends on the second part of the oil in the oil port 10 entering the second flow channel 1-2 and the sixth flow channel 1-6 and then reaching the control oil port of the hydraulic control one-way valve 18. When there is oil pressure in the control oil circuit, the hydraulic control one-way valve 18 can pass oil in both directions, so that the oil in the third flow channel 1-3 can enter the eleventh flow channel 1-11 through the hydraulic control one-way valve 18 to return oil to the oil port 2 11.

[0029] When the volume of the oil chamber 2-1 formed by the plunger 2 and the inner cylinder 6 continues to decrease until the upper shoulder of the inner cylinder 6 abuts the lower end of the plunger 2's inner chamber, that is, step 1 6-4 abuts step 2-3, the plunger 2 reaches the stop position and cannot be lifted further, completing the self-locking function. Furthermore, the cylinder head 3 also cooperates with the shoulder of the plunger 2 through its lower end surface, providing auxiliary self-locking and protection.

[0030] During the plunger 2's recovery process, oil enters oil port 2 11, passes through the eleventh flow channel 1-11, and then splits into two streams. One stream flows through the oil inlet of hydraulically controlled one-way valve 1-8, then opens the oil outlet of hydraulically controlled one-way valve 1-8, enters the third flow channel 1-3, and then enters the thirteenth flow channel 1-13. It then enters the inner cylinder 6 and, under the action of oil pressure, passes through the fifteenth flow channel 6-1 at the bottom of the inner cavity, the sixteenth flow channel 6-2, and the seventeenth flow channel 6-3 that runs through the top. The oil pressure enters the oil chamber 2-1 formed by the plunger 2 and the inner cylinder 6. Because the inner cylinder 6 is stationary and the volume of the oil chamber 2-1 has expanded, the oil pushes against the bottom surface of the plunger 2's inner cavity, causing the plunger 2 to recover.

[0031] After entering the oil port 2 11, another part of the oil passes through the eighth flow channel 1-8 and the seventh flow channel 1-7 in sequence and then enters the control oil port of the hydraulically controlled one-way valve 2 9. When there is oil pressure in the control oil circuit, the hydraulically controlled one-way valve 2 9 can pass oil in both directions, thereby returning oil to the oil chamber 1 1-14, and then passing through the eleventh flow channel 1-11 and the first flow channel 1-1 in sequence and returning oil to the oil port 10, thereby restoring the plunger 2.

[0032] The performance parameters of the present invention and the ordinary hydraulic cylinder (cylinder diameter 700mm, rod diameter 300mm, stroke 500) are compared in Table 1 below. Table 1 Performance parameter comparison For an explanation of performance parameters, see the industry standard JB / T10205-2010 "Hydraulic Cylinder" As can be seen from Table 1, compared with ordinary hydraulic cylinders, the hydraulic jacking cylinder of the present invention has excellent working performance, which is reflected in high pressure resistance, small internal leakage, and low minimum starting pressure; and excellent dynamic performance, which is reflected in low starting pressure and high load efficiency. This shows that the hydraulic jacking cylinder of the present invention has good sealing performance and low dynamic friction.

[0033] Although the above describes the specific implementation methods of the invention in conjunction with the accompanying drawings, it does not limit the scope of protection of the invention. Based on the technical solution of the present invention, various modifications or variations that can be made by those skilled in the art without creative work are still within the scope of protection of the present invention.

Claims

1. An ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder, characterized by: It includes an outer cylinder (1), a plunger (2), an inner cylinder (6), a hydraulically controlled one-way valve (1) (8) and a hydraulically controlled one-way valve (2) (9). A plunger (2) is slidably arranged in the outer cylinder (1), and an oil chamber (1-14) is formed between the inner bottom wall of the outer cylinder (1) and the outer bottom wall of the plunger (2). An inner cylinder (6) is provided in the plunger (2), and an oil storage chamber 2 (2-1) is formed between the outer wall of the inner cylinder (6) and the inner wall of the plunger (2). A sixteenth flow channel (6-2) is vertically provided in the inner cylinder (6), and the bottom of the inner cylinder (6) is connected to the outer cylinder (1). A thirteenth flow channel (1-13) is formed between the bottom of the inner cylinder (6) and the outer cylinder (1). A seventeenth flow channel (6-3) and a fifteenth flow channel (6-1) are horizontally provided at the top and bottom ends of the inner cylinder (6) respectively, and are connected to the sixteenth flow channel (6-2). The seventeenth flow channel (6-3) and the fifteenth flow channel (6-1) are connected to the oil storage chamber 2 (2-1) and the thirteenth flow channel (1-13), respectively. The lower portion of the outer cylinder (1) is provided with an oil port 1 (10) and an oil port 2 (11); the hydraulically controlled one-way valve 2 (9) is respectively connected to the oil port 1 (10) and the oil chamber 1 (1-14); and the hydraulically controlled one-way valve 1 (8) is respectively connected to the oil port 2 (11) and the thirteenth flow channel (1-13).

2. The ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder according to claim 1 is characterized by: An interlayer cavity (13) is provided at the bottom of the outer cylinder (1), and an installation opening (12) communicating with the interlayer cavity (13) is provided below the outer wall of the outer cylinder (1). A hydraulically controlled one-way valve (1) (8) and a hydraulically controlled one-way valve (2) (9) are provided at the installation opening (12), and an oil pipeline assembly is provided in the interlayer cavity (13).

3. The ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder according to claim 2 is characterized by: The oil pipeline assembly also includes a first flow channel (1-1), a seventh flow channel (1-7), a ninth flow channel (1-9) and a twelfth flow channel (1-12). The first flow channel (1-1) is horizontally arranged and connected to the oil port 1 (10). The twelfth flow channel (1-12) is respectively connected to the first flow channel (1-1), the ninth flow channel (1-9) and the oil chamber 1 (1-14). The ninth flow channel (1-9) is horizontally arranged and connected to the seventh flow channel (1-7) at the bottom. A second hydraulically controlled one-way valve (9) is arranged at the ninth flow channel (1-9). The second hydraulically controlled one-way valve (9) controls the flow or closing of the first flow channel (1-1), the seventh flow channel (1-7) and the twelfth flow channel (1-12).

4. The ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder according to claim 3 is characterized by: The oil pipeline assembly also includes an eleventh flow channel (1-11), a second flow channel (1-2), a third flow channel (1-3), a fourth flow channel (1-4), a fifth flow channel (1-5), a sixth flow channel (1-6) and an eighth flow channel (1-8). The eleventh flow channel (1-11) is horizontally arranged and connected to the oil port 2 (11). The eleventh flow channel (1-11) is connected to the seventh flow channel (1-7) through the eighth flow channel (1-8). The fourth flow channel (1-4) is respectively connected to the eleventh flow channel (1-11), the fifth flow channel (1-5), the sixth flow channel (1-6) and the eighth flow channel (1-8). (1-5) and the third flow channel (1-3), the third flow channel (1-3) is connected to the thirteenth flow channel (1-13), the fifth flow channel (1-5) is horizontally arranged and connected to the sixth flow channel (1-6), the sixth flow channel (1-6) is vertically arranged and connected to the first flow channel (1-1) through the second flow channel (1-2), and a hydraulically controlled one-way valve (8) is arranged at the fifth flow channel (1-5), and the hydraulically controlled one-way valve (8) controls the flow or closing of the fourth flow channel (1-4), the sixth flow channel (1-6) and the eleventh flow channel (1-11).

5. The ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder according to claim 1 is characterized by: It also includes a cylinder cover (3), a threaded hole (1-15) is provided on the cylinder cover (3), and a bolt connected to the outer cylinder barrel (1) is arranged in the threaded hole (1-15).

6. The ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder according to claim 5 is characterized by: A guide groove 1 is symmetrically provided along the radial direction of the cylinder cover (3), a guide block (4) is provided in the guide groove 1, the plunger (2) is provided through the center of the cylinder cover (3), and a guide groove 2 (2-2) adapted to the guide block (4) is provided on the outer wall of the plunger (2).

7. The ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder according to claim 1 is characterized by: The bottom of the inner cylinder (6) is connected to the bottom of the outer cylinder (1) via a connecting nut (7).

8. The ultra-high pressure self-locking anti-rotation hydraulic jacking cylinder according to claim 1 is characterized by: A step 1 (6-4) is provided on the top of the inner cylinder (6), the radius of the step (6-4) is larger than the radius of the inner cylinder (6), and the outer wall of the step (6-4) is provided in contact with the inner cavity of the plunger (2), and a step 2 (2-3) is provided on the bottom wall of the inner cavity of the plunger (2) to prevent the step 1 (6-4) from falling out of the plunger (2).

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