Ultrahigh pressure vessel sealing structure for deep ground and deep sea environment simulation and opening and closing mode

Abstract

The invention relates to an ultrahigh-pressure container sealing structure for deep ground and deep sea environment simulation and an opening and closing mode, the ultrahigh-pressure container sealing structure comprises a first ultrahigh-pressure container and a second ultrahigh-pressure container, the first ultrahigh-pressure container is provided with a first cylindrical section, and the end part of the first cylindrical section is provided with a first end part flange; the second ultrahigh-pressure container is provided with a second cylindrical section, and a second end flange is arranged at the end of the second cylindrical section; a concave sealing groove is formed in the center of the inner side of the second end flange, a bracket is installed in the sealing groove in a matched mode, one end of the bracket is sealed with the first ultrahigh pressure container through an end face O-shaped ring, and the other end of the bracket is sealed with the second ultrahigh pressure container through a radial O-shaped ring. And meanwhile, by matching with unique technical characteristics of the ultrahigh-pressure containers, the hoops and the like and matching hoop driving mechanisms, repeated automatic opening and closing of the ultrahigh-pressure containers are effectively realized.

Description

Technical Field

[0001] This invention relates to the field of ultra-high pressure vessel technology, and in particular to a sealing structure and opening / closing method for an ultra-high pressure vessel used for deep-earth and deep-sea environment simulation. Background Technology

[0002] According to deep earth science, for every 100 meters of descent from the Earth's surface into the deep rock layers, the pressure increases by an average of 2.5 MPa and the temperature rises by an average of 3°C. Therefore, the deep rock layers of the Earth are in a state of high temperature and high pressure.

[0003] Although the ocean is only 10,000 meters deep, relevant ocean research still requires the ability to construct seawater pressure at hundreds of megapascals in the laboratory in order to expand the breadth and depth of scientific research.

[0004] Publication number CN118130193A discloses a device and method for preparing high-fidelity rock core specimens. Specifically, it proposes a method for preparing standard rock core specimens under ultra-high pressure and ultra-high temperature conditions, which is used to test the mechanical properties of rocks in an in-situ environment deep within the Earth constructed in the laboratory. The published document involves operations such as "sealing and connecting the preparation chamber and the first gate valve, sealing and connecting the other end face of the preparation chamber to the second gate valve", "sealing and connecting the specimen chamber and the first side of the second gate valve", and "removing the preparation chamber" to connect and disconnect the flanges of the internal pressure vessel under pressure.

[0005] The publication number CN109777731B discloses a deep-sea hydrothermal vent extreme environment simulation device, which proposes a deep-sea hydrothermal vent extreme environment simulation system, whose reactor also needs to operate at a working pressure of 250MPa.

[0006] The aforementioned test chambers, preparation chambers, reaction vessels, and other internal pressure vessels involve repeated sealing and unsealing between containers due to functional requirements. Even during the connection and unsealing, other containers and pipelines on site are still under high temperature and high pressure, which is extremely dangerous for test operators. Therefore, an automated clamping and loosening mechanism is needed to achieve the sealing connection and unsealing between the ends of the two containers.

[0007] The automated opening and closing mechanism for ultra-high pressure vessels required for deep-earth and deep-sea experiments needs to solve two problems:

[0008] 1. Repeatability. Taking the key R&D program—coordinated testing technology of in-situ testing and shipborne environmental simulation device (2023YFC2812800) as an example, its pressure vessel has a working pressure of 250MPa and a test pressure of over 300MPa. The deep-sea microbial culture cycle is counted in months. In the deep earth field, taking the national major scientific research instrument—deep rock in-situ core sampling and fidelity testing and analysis system as an example, its equipment operation process is shown in the patent with publication number CN118130193A, which also involves the repeated tightening and loosening of multiple pressurized and heated containers.

[0009] If an automated gate opening and closing mechanism requires manual calibration of its accuracy after several or dozens of openings and closings, while other high-temperature and high-pressure equipment on site is continuously operating, this is too dangerous for the maintenance personnel of the gate opening and closing mechanism.

[0010] Solving the repetitiveness of automated opening and closing mechanisms presents the following challenges: Figure 8 For example, when a clamp achieves automated clamping of two containers, it is essential that at least two of the three components—the two containers and the clamp—are in a state of free movement along the axial direction. Otherwise, the clamping of the two containers cannot be achieved. Therefore, in automated opening and closing mechanisms, whether clamping or releasing, the position of the free-moving containers must not be deviated. Otherwise, the coaxiality of the two containers will deteriorate, affecting the realization of the next automatic clamping function. Existing technologies cannot solve the repeatability problem.

[0011] 2. Automated opening and closing mechanisms are not manually operated, making it impossible to guarantee extremely high coaxiality at the connection points of the two containers when they are tightly clamped. The GB / T 34019-2017 standard for "Ultra-High Pressure Vessels" (hereinafter referred to as the standard) stipulates that B-rings or wedges should be used for sealing structures below 300MPa. However, both of these sealing methods involve the fit between the outer circle of the seal and the inner circle of the container, which is too demanding for achieving repetitive and automated opening and closing mechanisms. Commercially available U-shaped slip ring combination seals can achieve sealing up to 300MPa. Their sealing structure is similar to end-face sealing O-rings, which slightly reduces the coaxiality requirement at the connection points of ultra-high pressure vessels. However, their sealing grooves are common rectangular grooves, making it difficult to eliminate the risk of seal detachment during automated opening and closing. In addition, this type of seal is highly dependent on the quality of the sealing element rather than the design of the sealing structure.

[0012] In summary, automated opening and closing mechanisms need to be able to achieve repeatable clamping and loosening between ultra-high pressure vessels to ensure the safety of personnel during long-term deep-earth and deep-sea experiments. They also need to have a matching sealing structure to meet the low coaxiality conditions of the connection parts when the automated opening and closing mechanism clamps the ultra-high pressure vessel. Finally, they need to ensure that the seals will not fall off during automatic opening and closing and can provide a reliable seal for a long time. Summary of the Invention

[0013] To address the shortcomings of existing production technologies, the applicant provides a sealing structure and opening / closing method for ultra-high pressure vessels used in deep-earth and deep-sea environment simulation. The sealing structure has not only undergone pressure testing up to 320 MPa, but also, in conjunction with the unique technical features of ultra-high pressure vessels and clamps, as well as the matching clamp drive mechanism, effectively realizes the repeated automated opening and closing of ultra-high pressure vessels.

[0014] The technical solution adopted in this invention is as follows:

[0015] A sealing structure for an ultra-high pressure vessel used for deep-earth and deep-sea environment simulation includes a first ultra-high pressure vessel and a second ultra-high pressure vessel. The first ultra-high pressure vessel is provided with a first cylindrical section, and its end is provided with a first end flange.

[0016] The second ultra-high pressure vessel is equipped with a second cylindrical section, and a second end flange is provided at its end;

[0017] A recessed sealing groove is provided at the center of the inner side of the No. 2 end flange. A bracket is installed in the sealing groove. One end of the bracket is sealed to the first ultra-high pressure vessel through an end face O-ring, and the other end of the bracket is sealed to the second ultra-high pressure vessel through a radial O-ring.

[0018] As a further improvement to the above technical solution:

[0019] The bracket adopts a circular structure.

[0020] The bracket has a transverse convex shape in cross section. An outer circle is formed on the outermost ring of the bracket, and an end face is formed on one side of the outer circle. An end face groove for installing an end face O-ring is provided on the end face. The outer circle and the inner circle of the sealing groove are in clearance fit. A radial groove for installing a radial O-ring is provided on the other side of the outer circle.

[0021] The depth and width of the radial groove are matched with the wire diameter of the radial O-ring.

[0022] The upper annular surface of the end face groove is a circular surface, and the lower annular surface of the end face groove is a conical surface. The conical surface and the bracket share the same center line. The cone angle of the conical surface is 2γ, where γ is 10°-20°. The depth and width of the end face groove match the wire diameter of the end face O-ring.

[0023] An opening and closing method for an ultra-high pressure vessel used for deep-earth and deep-sea environment simulation includes an opening and closing device. The structure of the opening and closing device is as follows: it includes a base plate, and a slide rail is fixed on the upper surface of the base plate. A pair of opposing first clamps and second clamps are installed on the slide rail, and the first clamps and second clamps hold the first ultra-high pressure vessel and the second ultra-high pressure vessel.

[0024] A first vertical plate is vertically installed at one end of the base plate, and a second vertical plate is vertically installed at the other end of the base plate. Upper limit plates and lower limit plates are installed at the upper and lower ends of the first and second vertical plates. The two ends of the upper screw are inserted into the limit holes of the upper limit plate, and the two ends of the lower screw are inserted into the limit holes of the lower limit plate. An upper motor and an upper reducer are installed above the outer side of the second vertical plate to drive the upper screw to rotate. A lower motor and a lower reducer are installed below the outer side of the second vertical plate to drive the lower screw to rotate. The upper and lower ends of the first clamp and the second clamp pass through the upper screw and the lower screw, respectively.

[0025] During operation, the upper and lower motors rotate, driving the upper and lower reducers respectively, which in turn drive the upper and lower lead screws to rotate, enabling the first and second clamps to move along the slide rail. When the motor rotates forward, the first and second clamps move relative to each other, and the two clamps gradually engage with the end flanges of the two ultra-high pressure vessels, pushing the floating vessel towards the fixed vessel, thus achieving a tight contact between the end flanges of the two ultra-high pressure vessels, thereby achieving the clamping of the first and second ultra-high pressure vessels. When the motor rotates in reverse, the first and second clamps move in opposite directions, and the two clamps gradually disengage from the end flanges of the two ultra-high pressure vessels, allowing the end flanges of the two ultra-high pressure vessels to return to a free contact state, thereby achieving the separation of the first and second ultra-high pressure vessels.

[0026] As a further improvement to the above technical solution:

[0027] The first clamp and the second clamp have the same structure. The first clamp has a pair of top double ears at the top, and a top pin hole is opened on the top double ears. The upper threaded block is installed by the upper pin and the upper threaded block matches the upper threaded rod. The middle part of the first clamp is a semi-circular ring-shaped body. The bottom double ears extend from the bottom of the semi-circular ring-shaped body. The bottom double ears have a bottom pin hole. The lower threaded block is installed by the lower pin and the lower threaded block matches the lower threaded rod. A sliding base plate is provided at the bottom of the bottom double ears.

[0028] The semi-circular body has a first cylindrical hole, a first transition elliptical groove, a second cylindrical hole, a second transition elliptical groove, and a third cylindrical hole arranged sequentially from one end to the other. A clamping first conical surface is provided between the first cylindrical hole and the first transition elliptical groove. The clamping first conical surface and the first cylindrical hole share the same center line. The angle α between the generatrix and the bottom surface of the conical surface is 3±1°. A clamping second conical surface is provided between the third cylindrical hole and the second transition elliptical groove. The two conical surfaces have the same characteristics.

[0029] The outer end faces of the No. 1 end flange and the No. 2 end flange form a mating surface. The connection surface between the No. 1 end flange and the No. 1 cylindrical section adopts a conical surface. The included angle β between the connection surface and the mating surface is 3±1°. When the first clamp tightens or loosens the two ultra-high pressure vessels, the first conical surface of the clamp and the connection surface, the second conical surface of the clamp and the corresponding connection surface of the second ultra-high pressure vessel gradually fit together or separate. The tightening or loosening process of the second clamp is the same and synchronous.

[0030] The upper wire block adopts a rectangular wire block body with a shaft hole at the axial center and a screw hole at the radial center.

[0031] The beneficial effects of this invention are as follows:

[0032] This invention features a unique and rational sealing structure. By designing a specially structured bracket, the fit clearance between the bracket and the container wall decreases as the internal pressure of the container increases, thus ensuring that the O-rings placed between the bracket and the container will not be squeezed out under high pressure. In addition, the O-ring groove on the bracket is designed as a non-traditional inclined groove, and the design relationship between the inclined groove size and the O-ring size is given. This not only effectively prevents the O-rings from falling off during automated assembly and disassembly, but also achieves a 320MPa seal together with the aforementioned bracket. At the same time, the sealing structure described in this invention significantly reduces the coaxiality requirement when the container ends are sealed, providing a foundation for the automated connection and disconnection between the container ends.

[0033] The ultra-high pressure vessel end structure and clamp technology of this invention not only enable the floating container to move and closely contact the stationary container when the two containers are clamped together, but also prevent the floating container from shifting its position when the two containers are released. The clamp drive mechanism of this invention uses the same driver to drive two motors, effectively eliminating the synchronization error between the two motors. By setting a reducer after the motor, the synchronization speed error between the upper and lower lead screws is further reduced, thereby greatly improving the synchronization of the upper and lower lead screws of the clamp during the opening and closing process and avoiding the clamp tilting and jamming phenomenon that is prone to occur when the clamp is repeatedly opened and closed. Combined with the aforementioned low coaxiality requirement, anti-fall-off, and self-tightening sealing structure, the repeated automatic opening and closing between ultra-high pressure vessels is finally realized.

[0034] The sealing structure of this invention has been applied in the National Key Research and Development Program—Collaborative Testing Technology of In-situ Testing and Shipborne Environmental Simulation Device (2023YFC2812800), and the sealing structure and opening and closing method have been applied in the National Major Scientific Instrument—Deep Rock In-situ Fidelity Core Sampling and Fidelity Testing and Analysis System. Attached Figure Description

[0035] Figure 1 This is a cross-sectional view of the sealing structure of the present invention.

[0036] Figure 2 for Figure 1 A magnified view of part A in the middle.

[0037] Figure 3 This is a cross-sectional view of the sealing structure component bracket of the present invention.

[0038] Figure 4 for Figure 3 Enlarged view of part B in the middle.

[0039] Figure 5 This is a partial view of the first clamp body of the present invention.

[0040] Figure 6 for Figure 5 Side view.

[0041] Figure 7 This is a schematic diagram of the O-ring dimensions of the present invention.

[0042] Figure 8 This is a schematic diagram of the overall structure of the present invention.

[0043] Figure 9 This is a schematic diagram of the clamp driving mechanism of the present invention.

[0044] Figure 10 This is a schematic diagram of the structure of the first clamp of the present invention (without the screw block installed).

[0045] Figure 11 This is a schematic diagram of the structure of the first clamp of the present invention (with threaded blocks and pins installed).

[0046] Figure 12 for Figure 11 A structural diagram from another perspective.

[0047] Figure 13 This is a schematic diagram of the structure of the filament block of the present invention.

[0048] Figure 14 This is a schematic diagram of the sliding fit between the slide rail and the bottom of the clamp in this invention.

[0049] The components are: 1. First clamp; 2. First ultra-high pressure vessel; 3. Second ultra-high pressure vessel; 4. Bracket; 5. Radial O-ring; 6. End face O-ring; 7. Second clamp; 8. First vertical plate; 9. Second vertical plate; 10. Base plate; 11. Slide rail; 12. Upper lead screw; 13. Lower lead screw; 14. Upper motor; 15. Upper reducer; 16. Lower motor; 17. Lower reducer.

[0050] 18. Upper thread block; 19. Upper pin; 20. Lower thread block; 21. Lower pin;

[0051] 22. Lower limit plate; 23. Upper limit plate;

[0052] 101. First cylindrical hole; 102. First transition elliptical groove; 103. Second cylindrical hole; 104. Second transition elliptical groove; 105. Third cylindrical hole; 106. Top double ears; 107. Top pin hole; 108. Semi-circular ring-shaped body; 109. Bottom double ears; 110. Bottom pin hole; 111. Sliding base plate; 112. First conical surface of clamp; 113. Second conical surface of clamp.

[0053] 201. End flange No. 1; 202. Cylindrical section No. 1; 203. Abutment surface; 204. Connection surface;

[0054] 301. End flange No. 2; 302. Cylindrical section No. 2;

[0055] 303, sealing groove;

[0056] 401. Radial groove; 402. End face groove; 403. End face; 404. Outer circle;

[0057] 1801. Wire block body; 1802. Shaft hole. Detailed Implementation

[0058] The specific embodiments of the present invention will now be described with reference to the accompanying drawings.

[0059] like Figures 1-14 As shown, the ultra-high pressure vessel sealing structure and opening / closing method for deep-earth and deep-sea environment simulation described in this embodiment includes four main parts: a first ultra-high pressure vessel 2, a second ultra-high pressure vessel 3, a sealing structure, and an opening / closing device.

[0060] The first ultra-high pressure vessel 2 and the second ultra-high pressure vessel 3 are arranged symmetrically, and their end structures are mostly the same.

[0061] The end features of the first ultra-high pressure vessel 2 and the second ultra-high pressure vessel 3 are as follows: identical end flange 201 and end flange 301 are provided in sequence, as well as cylindrical section 202 and cylindrical section 302. One side of the cylindrical section is connected to the main body of the vessel, and the other side is connected to the end flange.

[0062] The mating surfaces 203 of the first end flange 201 and the second end flange 301 are perpendicular to the central axes of the first cylindrical section 202 and the second cylindrical section 302; the connecting surface 204 of the first end flange 201 and the first cylindrical section 202 is a conical surface, and the included angle β between the connecting surface 204 and the mating surface 203 is 3±1°; in addition to having the same features as the first end flange 201, the second end flange 301 also has a sealing groove 303 at the center of its end face, and a bracket 4 is installed inside the sealing groove 303.

[0063] Specifically, a recessed sealing groove 303 is opened at the center of the inner side of the second end flange 301. A bracket 4 is installed in the sealing groove 303. One end of the bracket 4 is sealed with the first ultra-high pressure vessel 2 through the end face O-ring 6, and the other end of the bracket 4 is sealed with the second ultra-high pressure vessel 3 through the radial O-ring 5.

[0064] The sealing structure includes a bracket 4, a radial O-ring 5, an end face O-ring 6, and a sealing groove 303.

[0065] The bracket 4 is a ring structure, with its axial height slightly less than the depth of the sealing groove 303. The outer circle 404 of the bracket 4 and the inner circle of the sealing groove 303 are clearance-fitted. A radial groove 401 is formed on one side of the outer circle 404, and a radial O-ring 5 is installed in the radial groove 401. An end face groove 402 is formed on the other end face 403, and an end face O-ring 6 is installed in the end face groove 402. Its structural features are as follows: the depth and width of the radial groove 401 are designed according to relevant O-ring groove standards; the bottom of the end face groove 402 is flat, the upper ring surface is circular, and the lower ring surface is conical. The conical surface and the bracket 4 share a common centerline, and the conical angle is 2γ, where γ is between 10° and 20°. The diameter D of the intersection circle of the conical surface and the end face 403 needs to be slightly larger than the inner diameter C of the end face O-ring 6. The depth h of the end face groove 402 is determined by the following formula: To ensure appropriate O-ring compression, the upper annular diameter D+2k of the end face groove 402 is determined by the following formula: kh≥πd 2 / 4, the k value calculated according to the above formula needs to be rounded to the nearest value.

[0066] Specifically,

[0067] The working principle of the sealing structure is:

[0068] The radial groove 401 end face bears the internal pressure P of the two containers, causing the end face 403 of the bracket 4 to tend to press tightly against the abutment surface 203. The higher the value of P, the smaller the gap between the end face 403 and the abutment surface 203, ensuring that the end face O-ring 6 will not be squeezed out from the gap between the two surfaces. Similarly, the end face groove 402 upper ring surface bears the internal pressure P of the two containers, causing the outer circle 404 of the bracket 4 to tend to press tightly against the inner circle of the sealing groove 303 as the value of P increases. The higher the value of P, the smaller the gap between the outer circle 404 and the inner circle of the sealing groove 303, ensuring that the radial O-ring 5 will not be squeezed out from the gap between the two surfaces, thereby achieving a seal between the two containers.

[0069] This embodiment solves the problem that traditional O-rings are more easily squeezed out as the pressure increases. The radial O-ring 5 and the end face O-ring 6 only need to be selected with higher hardness and appropriate wire diameter to withstand pressure of 300MPa, which greatly improves the pressure range of traditional O-rings. At the same time, the sealing structure of this invention obviously inherits the advantages of traditional O-ring seals.

[0070] This embodiment solves the problem that traditional seals are easy to fall off from the groove. On the other hand, as long as the contact surface 203 completely covers the end face groove 402, a seal can be achieved. This greatly reduces the design difficulty of the automated opening and closing device. The automated opening and closing device only needs to achieve tight contact between the ends of the two containers. It is not necessary to ensure high coaxiality between the ends of the two containers during the tight contact process. This makes it possible to realize the automated opening and closing of ultra-high containers.

[0071] The opening and closing device includes: a clamp assembly, a clamp drive mechanism, a first end flange 201, a second end flange 301, a first cylindrical section 202, a second cylindrical section 302, and corresponding connection surfaces of the end flanges and cylindrical sections.

[0072] The clamp assembly includes: a first clamp 1, a second clamp 7, a threaded block, and a pin. The two clamps have completely identical structural features. Taking the first clamp 1 as an example, ... Figure 5 and Figure 6 as well as Figure 10 , Figure 11 and Figure 12 As shown, a single clamp has a pair of top double ears 106 at its top, and a through top pin hole 107 on each top double ear 106; the middle part is a semi-circular ring-shaped body 108, inside which a first cylindrical hole 101, a first transition elliptical groove 102, a second cylindrical hole 103, a second transition elliptical groove 104 and a third cylindrical hole 105 are arranged in sequence; a clamp first conical surface 112 is provided between the first cylindrical hole 101 and the first transition elliptical groove 102, the conical surface and the first cylindrical hole 101 share the same center line, and the angle α between the generatrix of the conical surface and the bottom surface of the conical surface is 3±1°; similarly, the same clamp second conical surface 113 is also provided between the third cylindrical hole 105 and the second transition elliptical groove 104; a bottom double ear 109 is provided at the bottom, and a sliding base plate 111 is provided on the end face of the double ear, and a through bottom pin hole 110 is also provided on the double ear.

[0073] Taking the first clamp 1 as an example, the assembly relationship of the clamp components is as follows:

[0074] Two upper pins 19 pass through the top pin hole 107 and are inserted into the two pin holes 1802 on the end face of the upper threaded block 18. Two lower pins 21 pass through the bottom pin hole 110 and are inserted into the two pin holes on the end face of the lower threaded block 20. The upper threaded block 18 and the lower threaded block 20 have completely identical structural features.

[0075] The clamp drive mechanism includes a first vertical plate 8, a second vertical plate 9, a base plate 10, a slide rail 11, an upper lead screw 12, a lower lead screw 13, an upper motor 14, an upper reducer 15, a lower motor 16, a lower reducer 17, an upper limit plate 23, and a lower limit plate 22.

[0076] The specific assembly relationship is as follows: the base plate 10 is a rectangular structure, the first upright plate 8 is welded to one side of the base plate 10, the second upright plate 9 is welded to the other side of the base plate 10, the upper limit plate 23 is screwed to the upper part of the two upright plates, the lower limit plate 22 is screwed to the bottom of the two upright plates, the upper screw 12 and the lower screw 13 are respectively inserted into the holes of the upper limit plate 23 and the lower limit plate 22, the upper motor 14 is connected to the upper reducer 15 and fixed to the upper part of the second upright plate 9, and is connected to one end of the upper screw 12 through a flexible coupling, the lower motor 16 is connected to the lower reducer 17 and fixed to the lower part of the second upright plate 9, and is connected to one end of the lower screw 13 through a flexible coupling, and the slide rail 11 is screwed onto the base plate 10.

[0077] The assembly relationship between the clamp assembly and the clamp drive mechanism is as follows:

[0078] The upper screw 12 has a first-side threaded engagement with the upper screw block 18 of the first clamp 1 and a second-side threaded engagement with the upper screw block 18 of the second clamp 7. The sliding base plate 111 of the first clamp 1 is installed in the groove of the slide rail 11 and can move along the groove. The lower screw 13 has a first-side threaded engagement with the lower screw block 20 of the first clamp 1 and a second-side threaded engagement with the lower screw block 20 of the second clamp 7. The bottom of the second clamp 7 is installed in the groove of the slide rail 11 and can move along the groove.

[0079] A further feature of the clamp drive mechanism is that the upper motor 14 and the lower motor 16 are driven by the same driver. The upper lead screw 12 and the lower lead screw 13 have threads with opposite directions and the same pitch on both sides. The upper lead screw 12 achieves spatial positioning by means of two threaded connections in the upper screw blocks 18 of the two clamps. The upper limit plate 23 only plays a coarse limiting role for the upper lead screw 12. Similarly, the lower lead screw 13 achieves spatial positioning by means of two threaded connections in the lower screw blocks 20 of the two clamps. The lower limit plate 22 only plays a coarse limiting role for the lower lead screw 13. The advantages of this feature are: the upper and lower motors are driven by the same driver, which can reduce the synchronization error between the upper motor 14 and the lower motor 16 caused by using different drivers. Furthermore, after the upper reducer 15 and the lower motor 16 are reduced according to the reduction ratio, the error is further reduced significantly. This ensures that the difference between the moving distance of the upper screw block 18 and the moving distance of the lower screw block 20 per unit time when the clamp moves is minimal. This better maintains the vertical state necessary for the long-term repeated opening and closing of the first clamp 1 and the second clamp 7, and avoids the clamp tilting and causing the upper screw 12 and the lower screw 13 to tilt, resulting in the screw jamming.

[0080] The upper wire block 18 adopts a rectangular wire block body 1801. The axial center of the wire block body 1801 has a shaft hole 1082, and the radial center of the wire block body 1801 has a screw hole.

[0081] The working principle of the opening and closing device is as follows:

[0082] After the upper motor 14 and the lower motor 16 are driven by the same driver, they begin to rotate, driving the upper reducer 15 and the lower reducer 17 respectively, which in turn drives the upper lead screw 12 and the lower lead screw 13 to rotate, thereby realizing the movement of the first clamp 1 and the second clamp 7 along the slide rail 11. When the motor rotates forward, the first clamp 1 and the second clamp 7 move relative to each other, and the first conical surface 112 of the clamp and the connecting surface 204 of the first ultra-high pressure vessel 2 gradually fit together, and the second conical surface 113 of the clamp and the connecting surface of the second ultra-high pressure vessel 3 gradually fit together, thereby realizing the clamping of the first ultra-high pressure vessel 2 and the second ultra-high pressure vessel 3. In this process, assuming that the output torque of the reducer is T, the thrust generated by the clamp when it moves is given by the formula, where P is the lead of the lead screw (i.e., the linear distance moved by the lead screw per revolution), and is the transmission efficiency between the lead screw and the clamp assembly. Then, the normal force of the clamp acting on the connecting surface 204 of the first ultra-high pressure vessel 2 is Ftanβ, which can be further decomposed into The forces consist of axial and radial components. Under the action of the axial component, the clamp pushes the floating container to move towards the fixed container until the flanges at the ends of the two containers are tightly abutted. The radial component is distributed circumferentially along the center of the first container connection surface 204. At the same time, there is also a sliding friction force generated by the normal force Ftanβ on the surface of the connection surface 204 of the first ultra-high pressure container 2, which is also distributed circumferentially along the center of the first container connection surface 204. During the actual operation of the opening and closing device, since the output torque T of the upper reducer 15 and the lower reducer 17 is not completely consistent, the resultant force of the radial component and the friction force is not completely zero. Therefore, during the process of the two containers tightly abutting at the ends, it is necessary to design a suitable cone angle β to reasonably balance the radial resultant force and the axial component. While ensuring that the radial position of the floating container does not deviate, the axial component should be increased as much as possible so that when the two containers are sealed abutting, the compression ratio of the end face O-ring 6 can be fully realized, thereby ensuring the seal.

[0083] When the motor reverses, the first clamp 1 and the second clamp 7 move in opposite directions, the first conical surface 112 of the clamp and the connecting surface 204 of the first ultra-high pressure vessel 2 gradually separate, the second conical surface 113 of the clamp and the corresponding connecting surface of the second ultra-high pressure vessel 3 gradually separate, and the flanges at the ends of the two vessels return to a free contact state, thereby realizing the separation of the first ultra-high pressure vessel 2 and the second ultra-high pressure vessel 3.

[0084] The opening and closing device designed in this embodiment has been tested and verified that when the clamp assembly achieves the clamping or loosening between the first ultra-high pressure vessel 2 and the second ultra-high pressure vessel 3, the related forces between the first conical surface 112 of the clamp, the second conical surface 113 of the clamp, and the end connection surface 204 of the vessel will not cause deviation in the radial position of the first and second ultra-high pressure vessels, nor will the clamp tilting or screw tilting cause the screw to jam. It can realize the repeated clamping and loosening of the two ultra-high pressure vessels.

[0085] The above description is an explanation of the present invention and not a limitation thereof. The scope of the present invention is defined by the claims. Within the scope of protection of the present invention, any form of modification may be made.

Claims

1. A sealing structure for an ultra-high pressure vessel used for simulating deep-earth and deep-sea environments, characterized in that: It includes a first ultra-high pressure vessel (2) and a second ultra-high pressure vessel (3). The first ultra-high pressure vessel (2) is provided with a first cylindrical section (202) and a first end flange (201) is provided at its end. The second ultra-high pressure vessel (3) is provided with a second cylindrical section (302), and its end is provided with a second end flange (301); A recessed sealing groove (303) is provided at the center of the inner side of the second end flange (301). A bracket (4) is installed in the sealing groove (303). One end of the bracket (4) is sealed to the first ultra-high pressure vessel (2) through an end face O-ring (6), and the other end of the bracket (4) is sealed to the second ultra-high pressure vessel (3) through a radial O-ring (5).

2. The ultra-high pressure vessel sealing structure for deep-earth and deep-sea environment simulation as described in claim 1, characterized in that: The bracket (4) adopts a circular structure.

3. The ultra-high pressure vessel sealing structure for deep-earth and deep-sea environment simulation as described in claim 1, characterized in that: The bracket (4) has a transverse convex shape in cross section. An outer circle (404) is formed on the outermost ring of the bracket (4). An end face (403) is formed on one side of the outer circle (404), and an end face groove (402) for installing the end face O-ring (6) is provided on it. The outer circle (404) and the inner circle of the sealing groove (303) are in clearance fit. A radial groove (401) for installing the radial O-ring (5) is provided on the other side of the outer circle (404).

4. The ultra-high pressure vessel sealing structure for deep-earth and deep-sea environment simulation as described in claim 3, characterized in that: The depth and width of the radial groove (401) are matched with the wire diameter of the radial O-ring (5).

5. The ultra-high pressure vessel sealing structure for deep-earth and deep-sea environment simulation as described in claim 3, characterized in that: The upper ring surface of the end face groove (402) is a circular surface, and the lower ring surface of the end face groove (402) is a conical surface. The conical surface and the bracket (4) share the same center line. The cone angle of the conical surface is 2γ, and γ is taken as 10°-20°. The depth and width of the end face groove (402) match the wire diameter of the end face O-ring (6).

6. A method for opening and closing an ultra-high pressure vessel for simulating deep-earth and deep-sea environments as described in claim 1, characterized in that: The opening and closing device includes a base plate (10), on the upper surface of which a slide rail (11) is fixed. A pair of oppositely arranged first clamps (1) and second clamps (7) are installed on the slide rail (11). The first clamps (1) and second clamps (7) hold the first ultra-high pressure vessel (2) and the second ultra-high pressure vessel (3). A first vertical plate (8) is vertically installed at one end of the base plate (10), and a second vertical plate (9) is vertically installed at the other end of the base plate (10). Upper limit plates (23) and lower limit plates (22) are installed at the upper and lower ends of the first vertical plate (8) and the second vertical plate (9). The two ends of the upper screw (12) are inserted into the limit holes of the upper limit plate (23), and the two ends of the lower screw (13) are inserted into the limit holes of the lower limit plate (22). An upper motor (14) and an upper reducer (15) are installed above the outer side of the second vertical plate (9) to drive the upper screw (12) to rotate. A lower motor (16) and a lower reducer (17) are installed below the outer side of the second vertical plate (9) to drive the lower screw (13) to rotate. The upper and lower ends of the first clamp (1) and the second clamp (7) pass through the upper screw (12) and the lower screw (13) respectively. During operation, the upper motor (14) and the lower motor (16) rotate, driving the upper reducer (15) and the lower reducer (17) respectively, which in turn drive the upper lead screw (12) and the lower lead screw (13) to rotate, realizing the movement of the first clamp (1) and the second clamp (7) along the slide rail (11). When the motor rotates forward, the first clamp (1) and the second clamp (7) move relative to each other, and the two clamps gradually fit with the end flanges of the two ultra-high pressure vessels, pushing the floating dynamic vessel to move towards the fixed vessel, realizing the tight contact of the end flanges of the two ultra-high pressure vessels, thereby realizing the clamping of the first ultra-high pressure vessel (2) and the second ultra-high pressure vessel (3). When the motor rotates in reverse, the first clamp (1) and the second clamp (7) move in opposite directions, and the two clamps gradually disengage from the end flanges of the two ultra-high pressure vessels, and the end flanges of the two ultra-high pressure vessels return to the free contact state, thereby realizing the disengagement of the first ultra-high pressure vessel (2) and the second ultra-high pressure vessel (3).

7. The opening and closing method of the ultra-high pressure vessel for deep-earth and deep-sea environment simulation as described in claim 6, characterized in that: The first clamp (1) and the second clamp (7) have the same structure. The first clamp (1) has a pair of top double ears (106) at the top. The top double ears (106) have a top pin hole (107). The upper thread block (18) is installed using the upper pin (19). The upper thread block (18) matches the upper thread rod (12). The middle part of the first clamp (1) is a semi-circular ring-shaped body (108). The bottom double ears (109) extend below the semi-circular ring-shaped body (108). The bottom double ears (109) have a bottom pin hole (110). The lower thread block (20) is installed using the lower pin (21). The lower thread block (20) matches the lower thread rod (13). The bottom double ears (109) have a sliding base plate (111) at the bottom.

8. The opening and closing method of the ultra-high pressure vessel for deep-earth and deep-sea environment simulation as described in claim 7, characterized in that: The semi-circular body (108) has a first cylindrical hole (101), a first transition elliptical groove (102), a second cylindrical hole (103), a second transition elliptical groove (104), and a third cylindrical hole (105) arranged sequentially from one end to the other. A clamping first conical surface (112) is provided between the first cylindrical hole (101) and the first transition elliptical groove (102). The clamping first conical surface (112) and the first cylindrical hole (101) share the same center line. The angle α between the generatrix and the bottom surface of the conical surface is 3±1°. A clamping second conical surface (113) is provided between the third cylindrical hole (105) and the second transition elliptical groove (104). The two conical surfaces have the same characteristics.

9. The opening and closing method of the ultra-high pressure vessel for deep-earth and deep-sea environment simulation as described in claim 8, characterized in that: The outer end faces of the first end flange (201) and the second end flange (301) form abutment surface (203). The connection surface (204) of the first end flange (201) and the first cylindrical section (202) adopts a conical surface. The included angle β between the connection surface (204) and the abutment surface (203) is 3±1°. When the first clamp (1) tightens or loosens the two ultra-high pressure vessels, the first conical surface (112) of the clamp and the connection surface (204), the second conical surface (113) of the clamp and the corresponding connection surface of the second ultra-high pressure vessel (3) gradually fit together or separate. The tightening or loosening process of the second clamp (7) is the same and synchronous.

10. The opening and closing method of the ultra-high pressure vessel for deep-earth and deep-sea environment simulation as described in claim 7, characterized in that: The upper wire block (18) adopts a rectangular wire block body (1801). The axial center of the wire block body (1801) is provided with a shaft hole (1082), and the radial center of the wire block body (1801) is provided with a screw hole.

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