Dual seal pull apart valve for marine oil and gas manifold based on cryogenic fluid safety trip technology

Abstract

This invention relates to the field of breakaway valve technology, and in particular to a dual-seal breakaway valve for marine oil and gas manifolds based on cryogenic fluid safety breakaway technology. It addresses the shortcomings of existing breakaway valves, which are mostly single-seal structures, resulting in insufficient sealing redundancy after breakaway and leading to delayed or premature pressure relief responses under different environments. This invention achieves sealing redundancy by using a sealing seat and sealing element in conjunction with a conical valve core to form a dual-seal structure. A snap-fit ​​assembly locks the conical valve core to prevent displacement due to seawater impact. A delivery channel and pressure valve release evaporated gas from sealing chamber A into sealing chamber B for passive pressure relief. The push block and push ring inclined surface work together to perform secondary compression on the sealing ring to compensate for cryogenic contraction. An intelligent pressure relief protection control system estimates the evaporation rate using both seawater temperature and the rate of pressure rise in chamber A, and coordinates the timing and rhythm of pressure relief with the capacity of chamber B, enabling adaptive adjustment of the pressure relief strategy according to marine conditions.

Description

Technical Field

[0001] This invention relates to the field of breakaway valve technology, and in particular to a marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology. Background Technology

[0002] Offshore breakaway valves are safety disconnect devices installed on oil and gas transmission hoses between ships. Their function is to automatically disconnect the hose when it experiences abnormal tension during transmission, simultaneously closing the valve cores at both ends to cut off the fluid passage and prevent oil and gas leakage into the sea. In ship-to-ship STS (Self-Transportation System) operations, the hose may be subjected to tensile loads exceeding design limits due to wind, waves, ocean currents, and ship drift. Without breakaway valve protection, the hose would directly break, leading to a large-scale oil and gas leak and potentially causing serious accidents such as fires, explosions, and marine pollution. Breakaway valves, through a preset break point within a safe tensile force range, preemptively disconnect and seal, transforming a catastrophic leak into a controllable emergency shutdown. They are an indispensable final-level safety barrier for offshore oil and gas transmission pipelines.

[0003] Chinese patent application CN221922418U discloses a breakaway valve comprising two symmetrically arranged valve body seats joined together. Each valve body seat includes a main valve body, a secondary valve body, a valve core, a support frame, and a spring. The main valve body contains a main valve cavity, and the support frame and valve core are located within the main valve cavity, with the support frame supporting the valve core. The spring is located between the support frame and the valve core. The main valve body and the secondary valve body are connected and fixed by several first bolts and nuts, and when the main valve body and the secondary valve body are connected and fixed, the support frame is pressed tightly. When installing the breakaway valve, the spring, support frame, and valve core are first connected. Then, the support frame and valve core are directly placed into the main valve cavity of the main valve body. The connection and fixation of the main valve body and the secondary valve body presses the support frame, thus achieving fixed installation. Therefore, the breakaway valve has a simple overall structure, is easy to install, and has a low cost.

[0004] The aforementioned and existing related technologies often suffer from the following defects: Existing breakaway valves mostly adopt a single-seal structure, and the sealing reliability lacks redundancy after breakage. After breakage, the low-temperature fluid trapped in the sealing cavity continues to evaporate and increase in pressure due to seawater heating. Relying solely on a mechanical safety valve with a fixed opening pressure for pressure relief results in a mismatch between the pressure relief timing and the evaporation rate. In tropical seas, the response may be too late, potentially causing overpressure and damaging parts, while in polar seas, it may trigger prematurely, wasting pressure relief resources. Furthermore, the valve lacks the ability to sense the evaporation rate, and the pressure relief action always lags behind the actual risk, leading to poor sealing performance of the breakaway valve. Summary of the Invention

[0005] The technical problem to be solved by this invention is that, in the prior art, most breakaway valves are single-seal structures, which means that after breakaway, they cannot provide sealing redundancy protection, resulting in the disadvantage of too late or too early pressure relief response under different environments. To this end, we propose a marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety breakaway technology.

[0006] To achieve the above objectives, this application adopts the following technical solution: a marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology, including a female valve body, a male valve body provided on one side of the female valve body of the signal conversion module, a conical valve core and a sealing element provided inside the female and male valve bodies of the signal conversion module, a valve stem fixedly installed inside the conical valve core and the sealing element of the signal conversion module, a sealing seat fixedly installed on the inner wall of the conical valve core of the signal conversion module, a housing fixedly installed on one side of the conical valve core of the signal conversion module, a snap-fit ​​assembly for improving the sealing effect of the conical valve core fixedly installed on the inner wall of the conical valve core of the signal conversion module, a rectangular groove opened on the surface of the conical valve core of the signal conversion module, and a storage groove opened on the surface of the housing of the signal conversion module;

[0007] The signal conversion module snap-fit ​​assembly includes a snap-fit ​​block with a conical valve core inner wall fixedly installed. The signal conversion module snap-fit ​​block is adapted to a rectangular groove. A groove is opened on the surface of the signal conversion module snap-fit ​​block. A rotating shaft is movably arranged inside the groove. A snap-fit ​​plate A is fixedly installed on the outer surface of the rotating shaft. A torsion spring is fixedly installed on the outer surface of the rotating shaft. Two sets of torsion springs are provided, and the two sets of torsion springs are located on both sides of the snap-fit ​​plate A.

[0008] The signal conversion module sealing seat is compatible with the sealing element. A base plate is fixedly installed on the inner wall of the signal conversion module mother valve body. A pressure spring is provided on the outer surface of the signal conversion module valve stem. One side of the signal conversion module sealing element is fixedly installed with one end of the pressure spring, and the other end of the signal conversion module pressure spring is fixedly installed with the surface of the base plate.

[0009] Preferably, a sealing cavity A is formed between the conical valve core and the sealing seat, and a sealing cavity B is formed between the sealing seat of the signal conversion module and the hose connecting the female valve body. Pressure relief protection structures are fixedly installed on the outer surfaces of both the female and male valve bodies of the signal conversion module. These pressure relief protection structures include a conveying plate on the outer surface of the female valve body, a sliding plate inside the female valve body, and a conveying channel inside the conveying plate. One end of the conveying channel is connected to sealing cavity A, and the other end is connected to sealing cavity B. A pressure valve is installed at the connection point between the conveying channel and sealing cavity B. A baffle plate is movably installed inside the sliding plate. Two sets of baffle plates are provided, one set located inside sealing cavity A and the other inside sealing cavity B. A magnetic plate B is fixedly installed on the surface of the baffle plate, located at the center of the baffle plate. A conveying hole is provided on the surface of the baffle plate, and the conveying hole is compatible with both ends of the conveying channel.

[0010] Preferably, the base plate has a rod hole inside, which is adapted to the valve stem. Pressure sensors are fixedly installed inside both the A and B sealing cavities of the signal conversion module. A temperature sensor is installed at one end of the pressure relief protection structure of the signal conversion module. An intelligent pressure relief protection control system is installed inside the mother valve body of the signal conversion module. A storage groove is opened on one side of the outer shell of the signal conversion module. The snap-fit ​​assembly of the signal conversion module is on the same horizontal line as the storage groove. A rod groove is opened on one side of the outer shell of the signal conversion module, which is adapted to the valve stem. A magnetic plate A is fixedly installed on the outer surface of the outer shell of the signal conversion module. The magnetic plate A of the signal conversion module is magnetically attracted to the magnetic plate B located inside the A sealing cavity.

[0011] Preferably, the card block has a slot inside, a push plate is slidably arranged inside the slot of the signal conversion module, a lever is provided at one end of the signal conversion module card A, a card B is movably arranged on the lower surface of the signal conversion module card block, a lever is also provided at one end of the signal conversion module card B, the two sets of signal conversion module levers are in contact, the signal conversion module push plate is located on one side of the two sets of signal conversion module levers, and a pressing plate is fixedly installed on the outer surface of the signal conversion module push plate.

[0012] Preferably, a positioning plate is fixedly installed on the outer surface of the mother valve body, and a triggering component for triggering the reset of the snap-fit ​​assembly is fixedly installed at one end of the conical valve core of the signal conversion module. The triggering component of the signal conversion module includes a rectangular plate fixedly installed on the outer surface of one end of the conical valve core. A movable groove is opened inside the rectangular plate of the signal conversion module. A compression spring is fixedly installed on the inner wall of the movable groove of the signal conversion module. One end of the compression spring of the signal conversion module is fixedly installed on one side of the extrusion plate. The compression spring of the signal conversion module is located on the outer surface of the push plate. The push plate of the signal conversion module is movably connected to the rectangular plate.

[0013] Preferably, a ramp A is provided on one side of the sealing seat, a sealing groove A is provided inside the sealing seat of the signal conversion module, a push ring is movably provided on the inner wall of the sealing groove A of the signal conversion module, a ramp B is provided on one side of the push ring of the signal conversion module, a sliding groove is provided inside the sealing seat of the signal conversion module, a magnet A is fixedly installed on the top of the sliding groove of the signal conversion module, a push block is provided inside the sliding groove of the signal conversion module, a magnet B is fixedly installed on the top of the push block of the signal conversion module, the magnet B and the magnet A are magnetically repelled, an inclined surface A and an inclined surface B are provided on one side of the push block of the signal conversion module, the inclined surface A of the signal conversion module is in contact with the ramp B, and an arc plate is fixedly installed on one side of the push block of the signal conversion module.

[0014] Preferably, a slope C is provided on one side of the seal, and the slope C of the signal conversion module fits with the slope A. A sealing groove B is provided on one side of the seal of the signal conversion module, and a sealing ring is provided inside the sealing groove B. A slope D is provided at one end of the seal of the signal conversion module, and the slope D of the signal conversion module matches the slope B. An inner hole is provided inside the seal of the signal conversion module, and the inner hole of the signal conversion module matches the valve stem. A magnetic plate C is fixedly installed on the outer surface of the seal of the signal conversion module, and the magnetic plate C of the signal conversion module and the magnetic plate B inside the sealing cavity B are magnetically attracted.

[0015] Preferably, the intelligent pressure relief protection control system includes a sensing and acquisition module, a central decision-making module, and a communication and reporting module, wherein:

[0016] The sensing and acquisition module is used to collect pressure data of sealing chamber A and sealing chamber B, as well as seawater ambient temperature data on the outer surface of the main valve body, and convert analog signals into digital signals for output.

[0017] The central decision module is used to detect the seawater ambient temperature based on the temperature sensor installed on the outer surface of the mother valve to determine the evaporation driving force, obtain the actual evaporation gas production rate based on the pressure rise rate of the A sealing chamber, predict the withstand time of the B sealing chamber based on the pressure rise rate of the B sealing chamber and the evaporation gas production rate, and jointly schedule the pressure relief action based on the evaporation gas production rate and the withstand time.

[0018] The communication reporting module is used to output pressure, temperature and system status data to an external monitoring system.

[0019] Preferably, the sensing and acquisition module includes a pressure sensor, a temperature sensor, and a signal conversion module, wherein:

[0020] Pressure sensors are used to collect real-time pressure data from sealing chambers A and B, respectively.

[0021] Temperature sensor used to collect seawater ambient temperature data on the outer surface of the main valve body;

[0022] The signal conversion module is used to convert analog signals from sensors into digital signals and output them to the central decision-making module.

[0023] Preferably, the central decision-making module includes a microprocessor, an evaporation rate estimation module, a capacity prediction module, and a pressure relief scheduling module, wherein:

[0024] The evaporation rate estimation module is used to determine the evaporation driving force based on the seawater ambient temperature collected by the temperature sensor, and to obtain the actual evaporation gas production rate based on the pressure rise rate of sealed chamber A. It employs a dual-parameter driven evaporation rate estimation model, and its estimation formula is as follows: ,in Let h be the evaporation gas production rate, and h be the heat transfer coefficient between the inner wall of the sealed cavity A and the trapped cryogenic fluid. Let A be the heat exchange area of ​​the inner wall of the sealed cavity. The temperature of the seawater environment is collected by a temperature sensor. To retain the boiling point temperature of cryogenic fluids, The rate of pressure rise in sealed cavity A. To preset the reference pressure rise rate, This is a correction factor;

[0025] The capacity prediction module is used to estimate the evaporation gas production rate output by the module based on the pressure rise rate and evaporation rate of the B sealing cavity, and to predict the time that the B sealing cavity can withstand.

[0026] The pressure relief scheduling module uses the evaporation gas production rate output by the evaporation rate estimation module and the withstand time of the B-sealed cavity output by the capacity margin prediction module as joint decision inputs. It employs an environmentally adaptive safety margin model and a pressure relief rhythm control algorithm, where the dynamic threshold of the safety margin is: ,in Based on the basic safety margin time, For temperature sensitivity coefficient, Preset reference seawater temperature;

[0027] Pressure relief activation condition: When < Generate start command at time, The time that the B-sealed cavity can withstand is determined by the output of the margin prediction module.

[0028] Pressure relief rhythm control: Duration of a single opening of the pressure relief valve ,in Based on the opening time, The evaporation gas production rate output by the evaporation rate estimation module is used to estimate the evaporation rate. For reference evaporation rate;

[0029] Pressure relief closure condition: When the pressure in sealing chamber B drops to... A shutdown command is generated at that time, in which Based on security pressure, This is the temperature regulation coefficient.

[0030] The technical effects and advantages of this invention are as follows:

[0031] In this invention, a double-sealing structure is formed by the sealing seat and the sealing element in conjunction with the conical valve core. After the valve breaks off, the two seals close sequentially to provide redundant protection.

[0032] A sealing cavity A is formed between the conical valve core and the sealing seat, and a sealing cavity B is formed between the sealing seat and the hose. A delivery channel and a pressure valve are set between the two cavities, so that after the low temperature fluid in cavity A is trapped and evaporated and pressurized, it will automatically be discharged into the larger cavity B to achieve passive pressure relief.

[0033] By using pressure and temperature sensors in conjunction with the microprocessor-based evaporation rate estimation and depressurization scheduling module, the evaporation and gas production rate is estimated using two parameters: seawater temperature and the rate of pressure rise in chamber A. Combined with the capacity of chamber B, the timing of depressurization is scheduled, replacing the fixed threshold mechanical safety valve, and achieving adaptive adjustment of early depressurization in tropical regions and delayed depressurization in polar regions.

[0034] The sealing ring is subjected to secondary compression by the inner push block of the sealing seat and the inclined surface of the push ring, which compensates for the low-temperature shrinkage gap and ensures the second sealing effect at ultra-low temperatures. Attached Figure Description

[0035] The disclosure of this invention is illustrated with reference to the accompanying drawings. It should be understood that the drawings are for illustrative purposes only and are not intended to limit the scope of protection of this invention. In the drawings, the same reference numerals are used to refer to the same parts:

[0036] Figure 1 This is a schematic diagram of the overall structure of the present invention;

[0037] Figure 2 This is a schematic diagram of the internal structure of the mother valve body of the present invention. Figure One ;

[0038] Figure 3 This is a schematic diagram of the internal structure of the mother valve body of the present invention. Figure Two ;

[0039] Figure 4 This is a schematic diagram of the disassembled structure of the sealing seat of the present invention;

[0040] Figure 5 This is a schematic diagram of the disassembled structure of the sealing element of the present invention;

[0041] Figure 6 This is a schematic diagram of the disassembled structure of the conical valve core of the present invention;

[0042] Figure 7This is a schematic diagram of the disassembled structure of the snap-fit ​​assembly of the present invention;

[0043] Figure 8 This is a diagram of the overall architecture of the present invention;

[0044] Figure 9 This is a flowchart of the overall modules of the present invention.

[0045] Legend: 1. Female valve body; 11. Conical valve core; 111. Rectangular groove; 112. Housing; 113. Stem groove; 114. Receiving groove; 115. Magnetic plate A; 116. Valve stem; 117. Pressure spring; 12. Base plate; 13. Sealing cavity A; 14. Sealing cavity B; 15. Stem hole; 16. Slide plate; 17. Pressure sensor; 18. Temperature sensor; 2. Male valve body; 3. Pressure relief protection structure; 31. Conveying plate; 32. Conveying channel; 33. Baffle plate; 34. Conveying hole; 35. Magnetic plate B; 4. Positioning plate; 5. Trigger assembly; 51. Rectangular plate; 52. Movable groove; 53. Compression 6. Spring; 7. Sealing seat; 8. Ramp A; 9. Sealing groove A; 10. Slide groove; 11. Magnet A; 12. Push ring; 13. Ramp B; 14. Push block; 15. Magnet B; 16. Surface A; 17. Arc plate; 18. Surface B; 19. Sealing element; 10. Ramp C; 10. Sealing groove B; 11. Ramp D; 12. Inner hole; 13. Magnet plate C; 14. Sealing ring; 15. Snap-fit ​​assembly; 16. Snap-fit ​​block; 17. Groove; 18. Plate groove; 19. Push plate; 10. Extrusion plate; 10. Snap plate A; 11. Rotating shaft; 12. Torsion spring; 13. Paddle plate; 14. Snap plate B. Detailed Implementation

[0046] It is readily understood that, based on the technical solution of this invention, those skilled in the art can propose various interchangeable structural methods and implementations without altering the essential spirit of the invention. Therefore, the following detailed embodiments and accompanying drawings are merely illustrative examples of the technical solution of this invention and should not be considered as the entirety of the invention or as limitations or restrictions on the technical solution of this invention.

[0047] Reference Figures 1-9 As shown, this invention provides a technical solution: a double-seal breakaway valve for marine oil and gas manifolds based on cryogenic fluid safety disconnection technology, comprising: a female valve body 1, with a male valve body 2 connected to one side of the female valve body 1. In the transport state, the two valve bodies are joined together to form a complete fluid channel. A conical valve core 11 and a sealing element 7 are jointly disposed inside the female valve body 1 and the male valve body 2. The conical valve core 11 is frustoconical in shape and is slidably installed along the axis of the female valve body 1, used to inwardly reset and seal the fluid channel upon disconnection. The sealing element 7 is installed inside the conical valve core 11 and coaxially arranged with the valve stem 116. The valve stem 116 passes through the center of the conical valve core 11 and the sealing element 7 and is fixedly connected, providing guiding support for the sliding of both.

[0048] The sealing seat 6 is fixedly embedded in the inner wall of the conical valve core 11, located between the conical valve core 11 and the sealing element 7. When the breakage occurs, the sealing element 7 is driven by the pressure spring 117 to fit with the sealing seat 6, forming the first seal. The pressure spring 117 is fitted on the outer surface of the valve stem 116, with one end abutting against the back of the sealing element 7 and the other end abutting against the bottom plate 12 fixed to the inner wall of the mother valve body 1. The bottom plate 12 has a rod hole 15 in the center for the valve stem 116 to pass through. The pressure spring 117 always applies a pre-tightening force to the sealing element 7 toward the sealing seat 6 to ensure that the sealing element 7 can quickly reset and fit after the breakage.

[0049] The outer casing 112 is fixedly installed on one side of the conical valve core 11 and moves together with the conical valve core 11. The outer casing 112 has a receiving groove 114 on its surface, which is used to receive the latching block 81 of the latching assembly 8 extending from the rectangular groove 111 after the valve core 11 is broken. The conical valve core 11 has a rectangular groove 111 on its surface, which is opened around the circumference of the conical valve core 11, so that the latching block 81 can pass through and unfold and lock in the receiving groove 114.

[0050] The latching assembly 8 is fixedly installed on the inner wall of the conical valve core 11, including a latching block 81. The size of the latching block 81 is adapted to the rectangular groove 111, and it can pass through the rectangular groove 111 into the storage groove 114. A groove 82 is formed on the surface of the latching block 81. A latching plate A85 is movably hinged inside the groove 82 via a rotating shaft 86. Two sets of torsion springs 87 are fitted on the outer surface of the rotating shaft 86. The two sets of torsion springs 87 are located on both sides of the latching plate A85. One end of the torsion spring 87 abuts against the inner wall of the groove 82, and the other end abuts against the latching plate A85. When the latching block is engaged, the latching assembly 8 is engaged with the receiving groove 114. When plate A85 is pressed into groove 82 by external force, torsion spring 87 stores energy. After the external force disappears, torsion spring 87 releases, causing plate A85 to spring open. When conical valve core 11 breaks off and resets, block 81 passes through rectangular groove 111 and enters receiving groove 114. At this time, plate A85 loses the pressure of the rectangular groove 111 wall and is springed open by torsion spring 87. The outer end of plate A85 abuts against the inner wall of receiving groove 114, locking conical valve core 11 in the closed position to prevent the conical valve core 11 from shifting due to seawater impact and affecting the sealing effect.

[0051] The locking block 81 also has a groove 83 inside, and a push plate 84 is slidably arranged inside the groove 83. A pressing plate 841 is fixedly installed on the outer surface of the push plate 84. A lever plate 88 is provided at one end of the locking plate A85. A locking plate B89 is movably arranged on the lower surface of the locking block 81, and a lever plate 88 is also provided at one end of the locking plate B89. The two sets of lever plates 88 are in contact with each other. The push plate 84 is located on one side of the two sets of lever plates 88. When the female valve body 1 and the male valve body 2 are spliced, the push plate 84 is pushed first to move along the groove 83. The pressing plate 841 on the push plate 84 presses the two sets of lever plates 88, making... Two sets of levers 88 rotate counterclockwise, causing two sets of clamping plates A85 to rotate counterclockwise into the groove 82. Then, the conical valve core 11, along with the outer shell 112, disengages from the clamping block 81, enabling normal oil and gas transportation. When the female valve body 1 and the male valve body 2 are disconnected, the pressure spring 117 drives the sealing element 7 and the conical valve core 11 to reset. The rectangular groove 111 on the surface of the conical valve core 11 presses the levers 88 and clamping plates B89 back into the groove 82. When the clamping block 81 passes through the rectangular groove 111 and enters the receiving groove 114, the clamping plate A85 is springed open by the torsion spring 87 and clamps the conical valve core 11.

[0052] A positioning plate 4 is fixedly installed on the outer surface of the female valve body 1. A triggering component 5 for triggering the reset of the snap-fit ​​assembly 8 is fixedly installed at one end of the conical valve core 11. The triggering component 5 includes a rectangular plate 51 fixedly installed on the outer surface of one end of the conical valve core 11. A movable groove 52 is opened inside the rectangular plate 51. A compression spring 53 is fixedly installed on the inner wall of the movable groove 52. One end of the compression spring 53 is fixedly connected to one side of the pressing plate 841. The compression spring 53 is fitted onto the outer surface of the push plate 84, and the push plate 84 is movably connected to the rectangular plate 51. When the female valve body 1 is disconnected from the male valve body 2, the compression spring 53 releases its stored energy, driving the push plate 84 and the conical valve core 11 to reset synchronously.

[0053] A sealing cavity A 13 is formed between the conical valve core 11 and the sealing seat 6, and a sealing cavity B 14 is formed between the sealing seat 6 and the hose connected to the mother valve body 1. The pressure relief protection structure 3 includes a conveying plate 31 disposed on the outer surface of the mother valve body 1. A sliding plate 16 is provided inside the mother valve body 1. A conveying channel 32 is provided inside the conveying plate 31. One end of the conveying channel 32 is connected to the sealing cavity A 13, and the other end is connected to the sealing cavity B 14. A pressure valve is provided at the connection between the conveying channel 32 and the sealing cavity B 14. A baffle plate 33 is movably disposed inside the sliding plate 16. Two sets of baffle plates 33 are provided, one set located inside the sealing cavity A 13 and the other set located inside the sealing cavity B 14. A magnetic plate B35 is fixedly installed on the surface of the baffle plate 33. The magnetic plate B35 is located at the center of the baffle plate 33. A conveying hole 34 is provided on the surface of the baffle plate 33, and the conveying hole 34 is adapted to both ends of the conveying channel 32. When the breakaway valve is disconnected, the conical valve core 11 and the seal 7 reset, causing the slide plate 16 to move. The conveying hole 34 on the surface of the baffle plate 33 connects with the conveying channel 32. The gas in the A sealing cavity 13 enters the conveying channel 32 through the conveying hole 34. Due to the large temperature difference between the low-temperature fluid trapped in the A sealing cavity 13 and the valve body, the gas evaporates and is pressurized before entering the B sealing cavity 14 through the pressure valve. The space of the B sealing cavity 14 is larger than that of the A sealing cavity 13 and its temperature rises more slowly, thus providing pressure relief protection for the A sealing cavity 13. A magnetic plate A115 is fixedly installed on the outer surface of the outer shell 112. The magnetic plate A115 and the magnetic plate B35 located inside the A sealing cavity 13 are magnetically attracted. In the conveying state, the magnetic force keeps the baffle plate 33 so that the conveying hole 34 and the conveying channel 32 are misaligned and closed.

[0054] A ramp A61 is provided on one side of the sealing seat 6. A sealing groove A62 is formed inside the sealing seat 6. A push ring 65 is movably disposed on the inner wall of the sealing groove A62. A ramp B651 is provided on one side of the push ring 65. A sliding groove 63 is formed inside the sealing seat 6. A magnet A64 is fixedly installed on the top of the sliding groove 63. A push block 66 is movably disposed inside the sliding groove 63. A magnet B661 is fixedly installed on the top of the push block 66. The magnets B661 and A64 are magnetically repelled, and always exert a downward pushing force on the push block 66. An inclined surface A662 and an inclined surface B664 are provided on one side of the push block 66. The inclined surface A662 contacts the ramp B651. An arc-shaped plate 663 is fixedly installed on one side of the push block 66. When the seal 7 moves to fit against the sealing seat 6, the push block 66 is pressed upward along the slide groove 63. The rising push block 66 presses the slope B651 through the inclined surface A662, driving the push ring 65 to move outward radially, thus cooperating with the seal 7 to achieve double compression of the sealing ring 76.

[0055] One side of the seal 7 has a ramp C71 that fits into ramp A61. A sealing groove B72 is formed on one side of the seal 7, and a sealing ring 76 is installed inside the sealing groove B72. One end of the seal 7 has a ramp D73 that matches the inclined surface B664. An inner hole 74 is formed inside the seal 7, and the inner hole 74 matches the valve stem 116. A magnetic plate C75 is fixedly mounted on the outer surface of the seal 7, and the magnetic plate C75 is magnetically attracted to the magnetic plate B35 inside the sealing cavity 14. When the sealing seat 6 is reset, the sealing element 7, along with the sealing ring 76, merges with the sealing seat 6. The sealing ring 76 is located between the push ring 65 and the sealing groove B72. As the sealing element 7 is reset, the ramp D73 presses against the inclined surface B664, driving the push block 66 to rise and then press the push ring 65 radially outward through the inclined surface A662. The sealing ring 76, located between the push ring 65 and the sealing groove B72, is double-pressed by the push ring 65 and the sealing element 7, compensating for the shrinkage of the sealing ring 76 caused by the low temperature medium and preventing the formation of gaps.

[0056] Pressure sensors 17 are fixedly installed inside both sealing chamber A 13 and sealing chamber B 14. A temperature sensor 18 is installed at one end of the pressure relief protection structure 3. An intelligent pressure relief protection control system is installed inside the main valve body 1. The pressure sensors 17 are respectively embedded in the inner walls of sealing chamber A 13 and sealing chamber B 14 to collect pressure data in their respective chambers in real time; the temperature sensor 18 is installed on the outer surface of the main valve body 1 and is in direct contact with seawater to collect seawater ambient temperature data.

[0057] The intelligent pressure relief protection and control system includes a sensing and acquisition module, a central decision-making module, and a communication and reporting module.

[0058] The sensing and acquisition module includes a pressure sensor 17, a temperature sensor 18, and a signal conversion module. The pressure sensor 17 is installed on the inner walls of sealing chamber A 13 and sealing chamber B 14 to collect real-time pressure data from the two chambers respectively; the temperature sensor 18 is installed on the outer surface of the main valve body 1 to collect seawater ambient temperature data; the signal conversion module is installed inside the valve body to convert the analog signals output by the sensors into digital signals and output them to the central decision-making module.

[0059] The central decision-making module includes a microprocessor installed in a sealed wiring cavity inside the valve body. The microprocessor internally runs an evaporation rate estimation module, a capacity prediction module, and a pressure relief scheduling module. The evaporation rate estimation module determines the evaporation driving force based on the seawater ambient temperature collected by temperature sensor 18 and obtains the actual evaporation gas production rate based on the pressure rise rate of sealed cavity A 13. It employs a dual-parameter driven evaporation rate estimation model, and its estimation formula is as follows: ,in Let h be the evaporation gas production rate, and h be the heat transfer coefficient between the inner wall of sealed cavity 13 (A) and the trapped cryogenic fluid. The heat exchange area of ​​the inner wall of sealed cavity 13 is A. The temperature sensor 18 collects the seawater ambient temperature. To retain the boiling point temperature of cryogenic fluids, The rate of pressure rise in sealed cavity 13 (A) To preset the reference pressure rise rate, To correct for the error, the capacity prediction module estimates the evaporation gas production rate output by the module based on the pressure rise rate and evaporation rate of the B sealing cavity 14, and predicts the time that the B sealing cavity 14 can withstand. The pressure relief scheduling module uses the evaporation gas production rate output by the evaporation rate estimation module and the withstand time of the B-sealed cavity 14 output by the capacity margin prediction module as joint decision inputs. It adopts an environmental adaptive safety margin model and a pressure relief rhythm control algorithm, wherein the dynamic threshold of the safety margin is... , Based on the basic safety margin time, For temperature sensitivity coefficient, The pressure relief opening condition is when the preset reference seawater temperature is reached. Less than The opening command is generated in real time, and the duration of a single opening of the pressure relief valve in the pressure relief rhythm control is also specified. , Based on the opening time, Qref is the reference evaporation rate; the pressure relief and closing condition is when the pressure in seal chamber 14 of B drops to... Generate a shutdown command at the time. Based on the basic safety pressure, η is the temperature adjustment coefficient, and the drive push plate 84 and the conical valve core 11 are synchronously reset.

[0060] Working principle: When the breakaway valve breaks due to abnormal tension in the hose during delivery, the female valve body 1 and male valve body 2 first separate. Then, the pressure spring 117 releases the preload, driving the sealing element 7 to slide axially along the valve stem 116 and fit against the sealing seat 6 to form the first seal. At the same time, the pressure sensor 17 installed on the inner wall of sealing cavity A 13 and sealing cavity B 14 begins to collect the pressure data of the two cavities in real time. The temperature sensor 18 installed on the outer surface of the female valve body 1 synchronously collects the seawater ambient temperature data. The signal conversion module converts the sensor analog signal into a digital signal and outputs it to the microprocessor. Then, the conical valve core 11 is reset under the action of the pressure spring 117, driving the slide plate 16 to move so that the delivery hole 34 on the surface of the baffle plate 33 and the delivery channel 32 are switched from misalignment to connection. At this time, the low-temperature fluid trapped in sealing cavity A 13 evaporates and increases in pressure due to the temperature difference. The evaporation rate estimation module running in the microprocessor uses a dual-parameter driven evaporation rate estimation model based on the seawater ambient temperature collected by the temperature sensor 18 and the pressure rise rate of sealing cavity A 13. The module estimates the evaporation gas production rate and predicts the allowance based on the pressure rise rate and evaporation gas production rate in sealing chamber B. It then predicts the time that sealing chamber B can withstand. The pressure relief scheduling module uses the evaporation gas production rate and the tolerable time as joint decision inputs to calculate the dynamic threshold of the safety margin. ,when Less than An opening command is generated at any time, and the duration of a single opening of the pressure relief valve is specified. The pressurized gas enters the conveying channel 32 through the conveying hole 34 and passes through the pressure valve into the larger and slower-heating B sealing chamber 14. The pressure relief valve opens according to the opening command to discharge the gas from the B sealing chamber 14. When the pressure in the B sealing chamber 14 drops to... The pressure relief scheduling module generates a shutdown command and controls the pressure of the B sealing cavity 14 within a safe range through multiple opening and closing cycles. Then, the locking block 81 passes through the rectangular groove 111 and enters the receiving groove 114 on the surface of the outer shell 112. The locking plate A85 is pushed open by the torsion spring 87 and abuts against the inner wall of the receiving groove 114 to lock the conical valve core 11 and prevent displacement caused by seawater impact. Subsequently, when the seal 7 is reset, the ramp D73 squeezes the inclined surface B664 of the push block 66, causing the push block 66 to rise along the slide groove 63. The rising push block 66 squeezes the ramp B651 of the push ring 65 through the inclined surface A662, driving the push ring 65 to move radially outward. This applies a secondary compression to the sealing ring 76 located between the push ring 65 and the sealing groove B72, compensating for the contraction of the sealing ring 76 caused by the low temperature medium. At this point, the double seal is reliably closed, the pressure relief protection of the A sealing cavity 13 is completed, and the low temperature contraction of the sealing ring is compensated.

[0061] The technical scope of this invention is not limited to the content described above. Those skilled in the art can make various modifications and variations to the above embodiments without departing from the technical concept of this invention, and all such modifications and variations should fall within the protection scope of this invention.

Claims

1. A marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology, characterized in that, The device includes a female valve body, a male valve body on one side of the female valve body, a conical valve core and a sealing element inside the female and male valve bodies, a valve stem fixedly installed inside the conical valve core and the sealing element, a sealing seat fixedly installed on the inner wall of the conical valve core, a housing fixedly installed on one side of the conical valve core, a snap-fit ​​assembly for improving the sealing effect of the conical valve core fixedly installed on the inner wall of the conical valve core, a rectangular groove on the surface of the conical valve core, and a storage groove on the surface of the housing. The buckle assembly includes a buckle block fixedly installed on the inner wall of a conical valve core. The buckle block is adapted to a rectangular groove. A groove is opened on the surface of the buckle block. A rotating shaft is movably arranged inside the groove. A buckle plate A is fixedly installed on the outer surface of the rotating shaft. A torsion spring is fixedly installed on the outer surface of the rotating shaft. Two sets of torsion springs are provided, and the two sets of torsion springs are located on both sides of the buckle plate A. The sealing seat is adapted to the sealing element, a base plate is fixedly installed on the inner wall of the mother valve body, a pressure spring is provided on the outer surface of the valve stem, one side of the sealing element is fixedly installed with one end of the pressure spring, and the other end of the pressure spring is fixedly installed with the surface of the base plate.

2. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 1, characterized in that: A sealing cavity A is formed between the conical valve core and the sealing seat. A hose connecting the sealing seat and the female valve body forms a sealing cavity B. Pressure relief protection structures are fixedly installed on the outer surfaces of both the female and male valve bodies. The pressure relief protection structures include a conveying plate on the outer surface of the female valve body. A sliding plate is provided inside the female valve body. A conveying channel is provided inside the conveying plate. One end of the conveying channel is connected to the A sealing cavity, and the other end of the conveying channel is connected to the B sealing cavity. A pressure valve is provided at the connection between the conveying channel and the B sealing cavity. A baffle plate is movably installed inside the sliding plate. Two sets of baffle plates are provided. One set of baffle plates is located inside the A sealing cavity, and the other set of baffle plates is located inside the B sealing cavity. A magnetic plate B is fixedly installed on the surface of the baffle plate. The magnetic plate B is located at the center of the baffle plate. A conveying hole is provided on the surface of the baffle plate. The conveying hole is adapted to both ends of the conveying channel.

3. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 2, characterized in that: The base plate has a rod hole inside, which is adapted to the valve stem. Pressure sensors are fixedly installed inside both the A sealing cavity and the B sealing cavity. A temperature sensor is installed at one end of the pressure relief protection structure. An intelligent pressure relief protection control system is installed inside the mother valve body. A storage groove is opened on one side of the outer shell. The buckle assembly is on the same horizontal line as the storage groove. A rod groove is opened on one side of the outer shell, which is adapted to the valve stem. A magnetic plate A is fixedly installed on the outer surface of the outer shell. The magnetic plate A is magnetically attracted to the magnetic plate B located inside the A sealing cavity.

4. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 3, characterized in that: The card block has a groove inside, and a push plate is slidably arranged inside the groove. A lever plate is provided at one end of the card plate A. A card plate B is movably arranged on the lower surface of the card block. A lever plate is also provided at one end of the card plate B. The two sets of lever plates are in contact with each other. The push plate is located on one side of the two sets of lever plates. A pressing plate is fixedly installed on the outer surface of the push plate.

5. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 4, characterized in that: A positioning plate is fixedly installed on the outer surface of the mother valve body. A triggering component for triggering the reset of the snap-fit ​​assembly is fixedly installed at one end of the conical valve core. The triggering component includes a rectangular plate fixedly installed on the outer surface of one end of the conical valve core. A movable groove is opened inside the rectangular plate. A compression spring is fixedly installed on the inner wall of the movable groove. One end of the compression spring is fixedly installed on one side of the extrusion plate. The compression spring is located on the outer surface of the push plate. The push plate is movably connected to the rectangular plate.

6. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 5, characterized in that: The sealing seat has a ramp A on one side, a sealing groove A inside the sealing seat, a push ring movably disposed on the inner wall of the sealing groove A, a ramp B on one side of the push ring, a sliding groove inside the sealing seat, a magnet A fixedly installed on the top of the sliding groove, a push block disposed inside the sliding groove, a magnet B fixedly installed on the top of the push block, the magnet B and magnet A being magnetically repelled, an inclined surface A and an inclined surface B on one side of the push block, the inclined surface A contacting the ramp B, and an arc-shaped plate fixedly installed on one side of the push block.

7. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 6, characterized in that: The sealing element has a ramp C on one side, which fits with ramp A. A sealing groove B is provided on one side of the sealing element, and a sealing ring is provided inside the sealing groove B. A ramp D is provided at one end of the sealing element, which is adapted to the inclined surface B. An inner hole is provided inside the sealing element, which is adapted to the valve stem. A magnetic plate C is fixedly installed on the outer surface of the sealing element, and the magnetic plate C is magnetically attracted to the magnetic plate B inside the sealing cavity B.

8. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 7, characterized in that: The intelligent pressure relief protection and control system includes a sensing and acquisition module, a central decision-making module, and a communication and reporting module, wherein: The sensing and acquisition module is used to collect pressure data of sealing chamber A and sealing chamber B, as well as seawater ambient temperature data on the outer surface of the main valve body, and convert analog signals into digital signals for output. The central decision module is used to detect the seawater ambient temperature based on the temperature sensor installed on the outer surface of the mother valve to determine the evaporation driving force, obtain the actual evaporation gas production rate based on the pressure rise rate of the A sealing chamber, predict the withstand time of the B sealing chamber based on the pressure rise rate of the B sealing chamber and the evaporation gas production rate, and jointly schedule the pressure relief action based on the evaporation gas production rate and the withstand time. The communication reporting module is used to output pressure, temperature and system status data to an external monitoring system.

9. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 8, characterized in that: The sensing and acquisition module includes a pressure sensor, a temperature sensor, and a signal conversion module, wherein: Pressure sensors are used to collect real-time pressure data from sealing chambers A and B, respectively. Temperature sensor used to collect seawater ambient temperature data on the outer surface of the main valve body; The signal conversion module is used to convert analog signals from sensors into digital signals and output them to the central decision-making module.

10. The marine oil and gas manifold double-seal breakaway valve based on cryogenic fluid safety disconnection technology according to claim 8, characterized in that: The central decision-making module includes a microprocessor, an evaporation rate estimation module, a capacity prediction module, and a pressure relief scheduling module, wherein: The evaporation rate estimation module is used to determine the evaporation driving force based on the seawater ambient temperature collected by the temperature sensor, and to obtain the actual evaporation gas production rate based on the pressure rise rate of sealed chamber A. It employs a dual-parameter driven evaporation rate estimation model, and its estimation formula is as follows: ,in Let h be the evaporation gas production rate, and h be the heat transfer coefficient between the inner wall of the sealed cavity A and the trapped cryogenic fluid. Let A be the heat exchange area of ​​the inner wall of the sealed cavity. The temperature of the seawater environment is collected by a temperature sensor. To retain the boiling point temperature of cryogenic fluids, The rate of pressure rise in sealed cavity A. To preset the reference pressure rise rate, This is a correction factor; The capacity prediction module is used to estimate the evaporation gas production rate output by the module based on the pressure rise rate and evaporation rate of the B sealing cavity, and to predict the time that the B sealing cavity can withstand. The pressure relief scheduling module uses the evaporation gas production rate output by the evaporation rate estimation module and the withstand time of the B-sealed cavity output by the capacity margin prediction module as joint decision inputs. It employs an environmentally adaptive safety margin model and a pressure relief rhythm control algorithm, where the dynamic threshold of the safety margin is: ,in Based on the basic safety margin time, For temperature sensitivity coefficient, Preset reference seawater temperature; Pressure relief activation condition: When < Generate start command at time, The time that the B-sealed cavity can withstand is determined by the output of the margin prediction module. Pressure relief rhythm control: Duration of a single opening of the pressure relief valve ,in Based on the opening time, The evaporation gas production rate output by the evaporation rate estimation module is used to estimate the evaporation rate. For reference evaporation rate; Pressure relief closure condition: When the pressure in sealing chamber B drops to... A shutdown command is generated at that time, in which Based on security pressure, This is the temperature regulation coefficient.

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