Self-adaptive mechanical sealing structure used under working conditions of high temperature, high pressure and vibration

Abstract

The invention relates to a self-adaptive mechanical sealing structure used under the working conditions of high temperature, high pressure and vibration, and relates to the technical field of rotating shaft sealing. A self-adaptive mechanical sealing structure used under high-temperature, high-pressure and vibration working conditions comprises a main end face sealing structure, a second end face sealing structure and a third end face sealing structure, the main end face sealing structure comprises a driving ring fixed to a shaft body, a main static ring arranged on the shaft body in a sleeving mode at intervals and a main static ring base used for supporting and fixing the main static ring, and a first suction groove is formed in the side, right facing the main static ring, of the driving ring; the axial compensation structure comprises a corrugated pipe arranged on the shaft body in a sleeving mode, a corrugated pipe seat supported and positioned at one end of the corrugated pipe and a corrugated pipe cover arranged on the periphery of the corrugated pipe in a sleeving mode, the other end of the corrugated pipe is positioned through a main static ring seat, glands are arranged at the end, away from the corrugated pipe, of the corrugated pipe seat at intervals, and memory alloy pins are connected between the glands and the corrugated pipe seat; an auxiliary end face sealing structure is arranged on the shaft body on one side of the gland. The sealing device has the effect of sealing three different media at the same time under the working conditions of high temperature, high pressure and vibration.

Description

Technical Field

[0001] The invention belongs to the field of rotary shaft sealing, and in particular relates to an adaptive mechanical sealing structure used under high temperature, high pressure and vibration conditions. Background Art

[0002] Sealing technology plays a vital role in modern industry and is widely used in petrochemical, power generation, shipbuilding, aerospace and other fields. The main function of sealing is to prevent fluid or gas leakage and ensure the normal operation and safety of equipment.

[0003] Mechanical seal is a widely used rotating dynamic seal structure, usually including moving ring, stationary ring, spring, auxiliary seal ring and other components. The moving ring and stationary ring move relative to each other to form a sealing surface, while the spring and auxiliary seal ring provide the necessary elasticity and compensation function to ensure the tight fit of the sealing surface under vibration. Mechanical seals use the combination of fluid pressure and elastic elements to achieve efficient sealing effects and are widely used in various complex working conditions.

[0004] This sealing structure performs well under normal working conditions and can effectively prevent fluid leakage. However, as the equipment is increasingly used in high temperature, high pressure and complex vibration environments, it exposes many problems under these harsh working conditions. This ultimately manifests as the lack of reliability and adaptability of mechanical seals under high temperature, high pressure and vibration conditions.

[0005] Specifically, high temperature environment will lead to stress relaxation of the compensation structure, which will reduce the end face fit level and affect the stability of the oil film, and eventually cause leakage. In addition, the temperature that increases too quickly in a short period of time will also cause the polymer ring (usually a rubber ring) of the auxiliary seal to expand or age, resulting in failure, which has a serious impact on production efficiency and safety. Taking the petrochemical industry as an example, its equipment often works in a medium of hundreds of degrees Celsius. If the sealing structure cannot effectively cope with high temperatures, it will cause leakage accidents, which will lead to shutdowns or even fires or explosions, causing huge economic losses and environmental pollution.

[0006] Under high pressure conditions, the sealing end face needs to withstand greater pressure. Traditional end face matching is difficult to form a stable oil film, which in turn causes greater wear. In addition, higher medium pressure may cause the O-ring to be squeezed or misaligned, and affect the positioning accuracy of the spring. This may lead to a decrease in sealing reliability. Due to the high medium pressure, the decline in the level of sealing matching will significantly increase the leakage and affect work efficiency.

[0007] Vibration is common in drilling and mining operations, which places higher demands on the compensation capability of the sealing system. Under vibration conditions, conventional elastomer or spring compensation is prone to misalignment or slippage, or even separation risk. This reduces the reliability of the seal, which in turn restricts the performance of the equipment under vibration conditions.

[0008] In modern production operations, in addition to facing constant factors, the sealing system also needs to maintain a high degree of robustness under dynamic conditions. The most significant influence is the ambient temperature. During the continuous operation of the equipment, the ambient temperature will increase with the working time. In special working conditions (such as drilling operations), as the well depth increases, the operating temperature of the equipment may rise sharply in a short period of time. This requires the sealing system to have higher adaptability and lower sensitivity to temperature changes. In traditional mechanical sealing structures, in order to resist stress relaxation under dynamic high temperatures, the system is generally provided with matching requirements and cooling rates that take into account the highest temperature during assembly and startup. Therefore, the end face sealing performance is excessive at the beginning of the operation, which squeezes the maximum life of the parts and reduces the operating efficiency. Even if the cooling oil circulation rate is adjusted according to the cavity temperature in some structures, the stress relaxation problem cannot be avoided, and a more complex electronic control system is required, which increases the equipment cost.

[0009] In summary, developing a new type of adaptive mechanical seal structure that can adapt to dynamic ambient temperature while maintaining good service performance under high temperature, high pressure and vibration conditions not only has important technological innovation and application value, but also has a far-reaching impact on improving the safety and efficiency of industrial production. Summary of the invention

[0010] We hope to improve the mechanical seal reliability of the mechanical seal structure under high temperature, high pressure and vibration conditions as well as its stability when facing dynamic temperature.

[0011] The present application provides an adaptive mechanical seal structure for high temperature, high pressure and vibration conditions, which adopts the following technical solution: An adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions, comprising: The main end face sealing structure comprises an active ring sleeved and fixed on the shaft body along the axial direction, a main static ring sleeved on the shaft body at intervals, and a main static ring seat for supporting and fixing the main static ring, and a first suction groove is provided on the side of the active ring facing the main static ring; An axial compensation structure, comprising a bellows sleeved on the shaft body, a bellows seat supported and positioned at one end of the bellows, and a bellows cover sleeved on the periphery of the bellows, the other end of the bellows being positioned by the main static ring seat, a gland being spaced apart at one end of the bellows seat away from the bellows, and a memory alloy pin being connected between the gland and the bellows seat; A secondary end face sealing structure is arranged on the shaft body at the side of the gland away from the bellows seat.

[0012] By adopting the above technical solution, the first suction groove can form a negative pressure, and the lubricating oil is sucked to the interface between the active ring and the main static ring during high-speed rotation, and a stable lubricating oil film is formed, which can not only reduce the wear under high-speed rotation and enhance the bearing capacity of the lubricating oil film under high-pressure conditions, but also reduce the direct contact of the main static ring surface with external contaminants.

[0013] The axial compensation structure is used to provide a clamping force for the main end face and provide elastic compensation when the shaft body vibrates axially. Compared with traditional springs, the repeated deformation of the bellows is more stable and has a better elastic compensation ability for axial vibration. In addition, its stress relaxation degree is lower in high temperature environment and its permanent deformation degree is lower under high pressure. This makes the equipment more stable under the coupling conditions of vibration, high temperature and high pressure, and more robust to changes in operating conditions.

[0014] In response to dynamic ambient temperature, the memory alloy pin can actively generate stable axial extension when the temperature rises, and actively generate stable axial contraction when the temperature drops. On the one hand, it compensates for the stress relaxation of the bellows and adjusts the sealing contact load; on the other hand, it increases the size of the lubrication oil outlet channel and adjusts the circulation rate.

[0015] Optionally, the secondary end face sealing structure comprises a secondary dynamic ring sleeved on the shaft body along the axial direction, and a W-shaped secondary static ring sleeved on the shaft body at intervals, and a secondary static ring seat is arranged on the outer side of the W-shaped secondary static ring; The auxiliary dynamic ring is located between the W-shaped auxiliary static ring and the pressure cover. The auxiliary dynamic ring is provided with a second suction groove on the side facing the W-shaped auxiliary static ring. The auxiliary dynamic ring can rotate with the shaft.

[0016] By adopting the above technical solution, the second suction groove can form a negative pressure, and the lubricating oil is allowed to be sucked to the interface between the secondary dynamic ring and the W-shaped secondary static ring during high-speed rotation, thereby forming a more stable lubricating oil film, which can reduce wear under high-speed rotation, enhance the bearing capacity of the lubricating oil film under high-pressure conditions, and reduce the direct contact of the main static ring surface with external contaminants.

[0017] Optionally, a radial compensation structure is further included, which includes a spring with one end radially arranged on the auxiliary static ring seat, an L-shaped spring seat is arranged at the other end of the spring, and a sealing end cover is sleeved and fixed on the outer side of the L-shaped spring seat; The W-shaped auxiliary static ring is connected to the vertical arm of the L-shaped spring seat close to the outer side surface of the shaft body.

[0018] By adopting the above technical solution, the spring is positioned axially by the L-shaped spring seat and radially by the sealing end cover and the secondary static ring seat. The sealing end cover is used to help position and tighten the secondary end face seal. When the shaft body vibrates radially, elastic compensation is performed to ensure that the secondary end face seal does not misalign. During the operation of the equipment, the axial and radial compensation mechanisms work together to ensure that the complex vibration of the rotating shaft does not affect the stable operation of the sealing system.

[0019] Optionally, a shaft sleeve is provided on the bellows cover, and the sealing end cover and the shaft sleeve are fixedly connected to the pressure cover.

[0020] By adopting the above technical solution, the shaft sleeve is used to seal the main end face.

[0021] Optionally, the sealing end cover is provided with an oil inlet channel, the shaft sleeve is provided with an oil outlet channel, a temperature sensor is provided on the oil outlet channel, and the shaft sleeve and the oil outlet channel are arranged on both sides of the shaft body; The oil outlet passage is connected to a filtering device, the filtering device is connected to a circulation device, and the circulation device is connected to the oil inlet passage.

[0022] By adopting the above technical solution, when the oil temperature measured by the temperature sensor exceeds the preset temperature value, the monitoring system controls the lubricating oil to be output from the oil outlet channel to the filtering device for filtration, enters the circulation device for cooling, and after cooling is completed, flows back to the oil inlet channel and enters the chamber of the sealing structure.

[0023] Optionally, the sealing end cover is L-shaped, and a self-lubricating combined sealing structure is arranged between one side and the shaft body, which includes a graphite ring sleeved on the shaft body and a first metal X-shaped ring sleeved on the graphite ring, and the axial ends of the graphite ring are clamped on the first metal X-shaped ring.

[0024] By adopting the above technical solution, the first metal X-ring uses high temperature resistant metal materials to replace the traditional polymer elastomer ring, provides elastic compensation in high temperature environment, and is designed as a special X-shaped cross section to ensure that its performance at high temperature is not significantly degraded, and elastic deformation and sealing can be completed through the deformation of the "foot" support at both ends of the X-shape. The modified structure of the graphite ring and the first metal X-ring is assembled, so that it has better wear resistance and self-lubrication while retaining elastic compensation, so it can be used in oil-deficient conditions.

[0025] Optionally, a turbine is sleeved and fixed on the shaft body, and the turbine is fixedly connected to a side of the auxiliary dynamic ring away from the W-shaped auxiliary static ring; A threaded sleeve is connected to the side of the turbine away from the auxiliary dynamic ring, and the threaded sleeve is sleeved on the shaft body; One end of the gland is a sleeve portion arranged along the shaft body, and the sleeve portion is located between the bellows and the threaded sleeve.

[0026] By adopting the above technical solution, the threaded sleeve forms a threaded channel for oil delivery, so that the lubricating oil is stably pumped from the oil inlet channel to the main end face and the oil outlet channel in one direction. The sleeve portion can prevent the corrugated pipe from contacting the threaded sleeve when it is deformed by vibration, thereby affecting the rotation of the threaded sleeve.

[0027] Optionally, the turbine includes a plurality of conical surfaces, and a plurality of blades are evenly spaced apart from each other on the conical surfaces.

[0028] By adopting the above technical solution, the blades are used to stir the lubricating oil so that the lubricating oil is stably pumped unidirectionally from the oil inlet channel to the main end surface and the oil outlet channel.

[0029] Optionally, a second annular metal X-shaped ring is embedded on the inner ring surface of the active ring.

[0030] By adopting the above technical solution, the second metal X-shaped ring is made of high temperature resistant metal material, which not only ensures that its performance does not deteriorate significantly at high temperatures, but also the deformation of the "foot" supports at both ends of the X-shaped ring can complete elastic deformation and sealing. At the same time, the X-shaped ring is open at both ends, and can undergo secondary deformation when it is subjected to synchronous medium pressure on both sides, thereby achieving self-sealing.

[0031] Optionally, the middle portion of the memory alloy pin is configured to be spring-shaped, and both ends are respectively cylindrical.

[0032] By adopting the above technical solution, the middle part is set to be spring-shaped, and the memory alloy column pin shrinks and expands more at high temperatures, thereby increasing the gap size, which is beneficial to further compress the bellows and compensate for the stress relaxed at high temperatures.

[0033] In summary, the present application includes at least one of the following beneficial technical effects: Through the specific design of main and auxiliary end faces, metal X-shaped rings, W-shaped auxiliary static rings, memory alloy pins, lubrication systems, etc., it is possible to achieve simultaneous sealing of three different media under high temperature, high pressure and vibration conditions. This design not only maintains good stability under harsh conditions, but also has higher adaptability under dynamic temperature; a self-lubricating combined sealing structure is designed to assist the system in completing dynamic sealing, thereby improving the overall sealing effect and stability. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 is a cross-sectional view of an adaptive mechanical seal structure for high temperature, high pressure and vibration conditions embodying the present application; Figure 2 It is a schematic diagram of the structure of the active ring embodying the present application; Figure 3is a schematic diagram of a memory alloy pin embodying the present application; Figure 4 It is a schematic diagram of the structure of the W-shaped auxiliary static ring of the present application; Figure 5 Schematic diagram of a lubricating fluid circulation monitoring system embodying the present application Figure 6 is a front view of a worm gear embodying the present application; Figure 7 is a side view of a worm gear embodying the present application; Figure 8 is a schematic diagram of a metal X-shaped ring embodying the present application; Fig. 9 It is a schematic diagram of the self-lubricating combined sealing structure of the present application.

[0035] Description of reference numerals: 1. Shaft body; 2. Sealing end cover; 3. Shaft sleeve; 4. Temperature sensor; 5. Filtering equipment; 6. Circulation equipment; 7. Threaded sleeve; 8. Stop pin; 20. Oil inlet channel; 30. Oil outlet channel; 11. Active ring; 12. Main static ring; 13. Main static ring seat; 111. First suction groove; 112. Second metal X-shaped ring; 21. bellows; 22. bellows seat; 23. bellows cover; 24. gland; 241. sleeve; 25. memory alloy pin; 31. Auxiliary dynamic ring; 311. Second suction groove; 32. W-shaped auxiliary static ring; 33. Auxiliary static ring seat; 34. Turbine; 41. Spring; 42. L-shaped spring seat; 51. Graphite ring; 52. First metal X-shaped ring. DETAILED DESCRIPTION

[0036] The following is combined with Figure 1-Figure 9 This application is described in further detail.

[0037] The embodiment of the present application discloses an adaptive mechanical sealing structure for use under high temperature, high pressure and vibration conditions.

[0038] See also Figure 1 , Figure 2 and Figure 3 , an adaptive mechanical seal structure for high temperature, high pressure and vibration working conditions, including a main end face seal structure, an axial compensation structure and a secondary end face seal structure arranged in sequence along the length direction of the shaft body 1. The mechanical seal structure can be used in high temperature, high pressure and vibration working environments, where the high temperature refers to a temperature higher than 150°C, the high pressure refers to a pressure greater than 20MPa, and the vibration refers to a vibration with a frequency greater than 50Hz.

[0039] The main end face sealing structure includes an active ring 11, a main static ring 12 and a main static ring seat 13 for supporting and fixing the main static ring 12, which are sequentially sleeved along the length direction of the shaft body 1. The active ring 11 is fixedly connected to the shaft body 1 and rotates with the shaft body 1, and the main static ring 12 is spaced apart from the shaft body 1 and does not rotate with the shaft body 1. A first suction groove 111 is radially arranged on the active ring 11 at the interval between the main static ring 12 and the shaft body 1, and the width of the first suction groove 111 is greater than the aforementioned interval and extends radially.

[0040] Due to the presence of the first suction groove 111, the lubricating oil is allowed to be sucked to the interface between the active ring 11 and the main static ring 12 during high-speed rotation, thereby forming a more stable lubricating oil film at the contact interface between the active ring 11 and the main static ring 12, effectively reducing the direct contact of the surface of the main static ring 12 with external pollutants. It also helps to reduce wear and loss under high-speed rotation and enhance the bearing capacity of the lubricating oil film under high-pressure conditions. It can be applied to high-speed and high-pressure rotating machinery and highly polluted environments, such as mud pumps and mining equipment, and can significantly improve the sealing reliability.

[0041] According to different working conditions, the structural parameters of the first suction groove 111 can be adjusted. The material of the main static ring 12 is graphite, and the material of the active ring 11 is metal, which can ensure easy assembly and enhance the wear resistance of the end face seal in a particle environment.

[0042] The axial compensation structure includes a bellows 21 sleeved on the shaft body 1, with a certain space between the two without contact. One end of the bellows 21 is positioned by the main static ring seat 13, and the other end of the bellows 21 is supported and positioned by the bellows seat 22. A bellows cover 23 is sleeved on the outer periphery of the bellows 21, and the bellows cover 23 radially limits the bellows 21 and the main static ring seat 13.

[0043] The bellows cover 23 and the main static ring seat 13 are designed as axial limiters, which stipulate the maximum compression degree of the bellows 21 while ensuring low friction reciprocating motion, which is beneficial to prevent the compression of the bellows 21 from exceeding the limit under high pressure and high amplitude vibration, and ensure that the axial supporting force of the end face meets the requirements.

[0044] The axial compensation structure is used to provide a clamping force for the main end face and to provide elastic compensation when the shaft body vibrates axially. During assembly, the resilience of the bellows 21 is pressed against the main static ring seat 13, which is then transmitted to the main static ring 12 by the main static ring seat 13, and then transmitted to the active ring 11 by the main static ring 12, thereby pre-compressing the active ring 11. During the operation of the equipment, the main static ring 12 remains stationary, and the active ring 11 rotates together with the shaft body 1. During high-speed rotation, the lubricating oil is allowed to be sucked to the interface between the active ring 11 and the main static ring 12 to form a lubricating oil film, and the two cooperate to form a rotating dynamic seal.

[0045] Compared with traditional springs, the bellows 21 has more stable repeated deformation and better axial vibration elastic compensation capability. In addition, it has lower stress relaxation in high temperature environment and lower permanent deformation under high pressure. This makes the equipment more stable under the coupling conditions of vibration, high temperature and high pressure, and more robust to changes in operating conditions.

[0046] A gland 24 is arranged at one end of the bellows seat 22 away from the bellows 21, and a memory alloy pin 25 is connected between the gland 24 and the bellows seat 22. The memory alloy pin 25 is assembled in the holes of the gland 24 and the bellows seat 22, and plays a dynamic supporting role while assisting positioning.

[0047] The two ends of the memory alloy pin 25 are cylindrical, and the middle part is set to be spring-shaped. When the temperature rises, a stable axial extension occurs actively, and when the temperature drops, a stable axial shortening occurs actively. At room temperature, there is a gap between the assembled gland 24 and the bellows seat 22 for the flow of lubricating oil. At high temperatures, the memory alloy pin 25 has a greater contraction and expansion, which increases the gap size, which is conducive to further compressing the bellows 21 and compensating for its stress relaxation at high temperatures. On the other hand, the gap size is increased at high temperatures, the oil circulation rate is accelerated, and the cooling effect is improved. This design enhances the adaptability of the sealing system in high-temperature applications, ensures the stability of the sealing contact, and actively adjusts the cavity temperature, thereby improving the life of the equipment.

[0048] See also Figure 1 and Figure 4 The secondary end face sealing structure includes a secondary dynamic ring 31 which is sequentially sleeved on the shaft body 1 along the axial direction and a W-shaped secondary static ring 32 which is sleeved on the shaft body 1 at intervals. The side of the W-shaped secondary static ring 32 away from the shaft body 1 is supported and fixed by a secondary static ring seat 33. During assembly, the W-shaped secondary static ring 32 is pressed against the secondary dynamic ring 31 by self-deformation. The secondary dynamic ring 31 can rotate with the shaft body 1. During operation, the two move relative to each other and form a rotating dynamic seal. A second suction groove 311 is provided on the side of the secondary dynamic ring 31 facing the W-shaped secondary static ring 32. The function of the second suction groove 311 can refer to the function of the first suction groove 111, which reduces the wear and loss of the secondary end face.

[0049] The secondary dynamic ring 31 is located between the W-shaped secondary static ring 32 and the gland 24. The secondary end face sealing structure is applied to the secondary sealing end face, and the working principle is similar to that of the primary end face sealing structure.

[0050] The W-shaped secondary static ring 32 is made of metal material and is designed with a W-shaped cross section, so that it can have a compensation effect when axially compressed and produce a specified radial deformation, thereby saving additional axial springs and radial sealing rings on the secondary sealing end face.

[0051] The main and auxiliary end faces are designed to work together at both ends of the sealing structure to ensure that the lubricating medium in the cavity of the sealing structure does not leak while completing the sealing of different media at both ends. For example, the three media of air, lubricating oil and mud can be isolated simultaneously in the mud pump structure, providing additional safety redundancy for the operation of the equipment in complex environments.

[0052] The mechanical sealing structure also includes a radial compensation structure, which includes a spring 41 connected to the side of the auxiliary static ring seat 33 facing away from the shaft body 1, the other end of the spring 41 is inserted into the through hole of the horizontal arm of the L-shaped spring seat 42, and the outer side surface of the W-shaped auxiliary static ring 32 close to the shaft body 1 is connected to the vertical arm of the L-shaped spring seat 42.

[0053] The L-shaped spring seat 42 is sleeved with a sealing end cover 2, and the bellows cover 23 is sleeved with a shaft sleeve 3. The sealing end cover 2 and the shaft sleeve 3 are both fixedly connected to the gland 24. The sealing end cover 2 is used to support the end of the spring 41 inserted into the through hole of the cross arm of the L-shaped spring seat 42, and the sealing end cover 2 is used to help position and tighten the secondary end face seal.

[0054] The spring 41 is positioned axially by the L-shaped spring seat 42 and radially by the sealing end cover 2 and the secondary static ring seat 33. The spring 41 can perform elastic compensation when the shaft body 1 vibrates radially, thereby ensuring that the secondary end face sealing structure does not misalign. During the operation of the equipment, the axial compensation structure and the radial compensation mechanism work together to ensure that the complex vibration of the shaft body 1 does not affect the stable operation of the sealing system.

[0055] See also Figure 1 and Figure 5 The sealing end cover 2 is provided with an oil inlet channel 20, the shaft sleeve 3 is provided with an oil outlet channel 30, the oil outlet channel 30 is provided with a temperature sensor 4, and the shaft sleeve 3 and the oil outlet channel 30 are arranged on both sides of the shaft body 1. The oil outlet channel 30 is connected to a filter device 5 for filtering the wear debris and tiny pollutants carried by the lubricating oil, and the filter device 5 is connected to a circulation device 6 for cooling the lubricating oil and driving the lubricating oil, and the circulation device 6 is connected to the oil inlet channel 20.

[0056] The lubricating oil is input into the cavity from the oil inlet channel 20. When the temperature sensor 4 measures that the oil temperature exceeds a preset temperature value, the monitoring system controls the lubricating oil to be output from the oil outlet channel 30 to the filtering device 5 for filtration and enters the circulation device 6 for cooling.

[0057] See also Figure 1 , Figure 6 and Figure 7 The shaft body 1 is sleeved with a turbine 34, which is fixedly connected to the side of the secondary moving ring 31 away from the W-shaped secondary static ring 32. The side of the turbine 34 away from the secondary moving ring 31 is connected with a threaded sleeve 7, which is sleeved on the shaft body 1.

[0058] One end of the gland 24 is a sleeve portion 241 arranged along the shaft body 1, and the sleeve portion 241 is sleeved on the threaded sleeve 7 at intervals, which can prevent the bellows 21 from contacting the threaded sleeve 7 when it is deformed by vibration, thereby affecting the rotation of the threaded sleeve 7. The bellows seat 22, the bellows 21 and the main static ring seat 13 are sleeved on the sleeve portion 241 at intervals along the length direction of the shaft body 1. The other end of the gland 24 is a base, which is used to fix one end of the memory alloy pin 25.

[0059] The turbine 34 includes a plurality of conical surfaces, on which a plurality of blades are evenly spaced. The turbine 34 and the threaded sleeve 7 are mounted on the shaft 1 and rotate with it. The threaded sleeve 7 forms a threaded channel for oil delivery, and the blades are used for stirring, so that the lubricating oil is stably pumped from the oil inlet channel 20 to the main end face and the oil outlet channel 30 in a unidirectional manner. The design of this lubricating fluid circulation monitoring system enables the equipment to work more safely under high temperature and particle conditions, such as oil and gas engineering and ship engineering.

[0060] See also Figure 1 , Figure 8 and Fig. 9 The sealing end cover 2 is L-shaped, and a self-lubricating combined sealing structure is arranged between one side and the shaft body 1, which includes a graphite ring 51 sleeved on the shaft body 1 and a first metal X-shaped ring 52 sleeved on the graphite ring 51, and the axial ends of the graphite ring 51 are clamped on the first metal X-shaped ring 52. The modified structure of the graphite ring 51 and the first metal X-shaped ring 52 is combined and assembled, so that it has better wear resistance and self-lubrication while retaining elastic compensation, so it can be used in oil-deficient conditions.

[0061] A second metal X-shaped ring 112 is embedded in the inner ring surface of the active ring 11, and the second metal X-shaped ring 112 is sleeved on the shaft body 1. The second metal X-shaped ring 112 and the first metal X-shaped ring 52 are both made of high-temperature resistant metal materials and are designed as special X-shaped cross-sections. Not only does it ensure that its performance at high temperatures is not significantly degraded, but also elastic deformation and sealing can be achieved through the deformation of the "foot" supports at both ends of the X-shaped. In addition, the X-shaped is open at both ends, and can undergo secondary deformation when it is subjected to synchronous medium pressure on both sides, thereby achieving self-sealing.

[0062] The second metal X-ring 112 is designed as a static seal in the mechanical seal to fill the sealing gap. The self-lubricating combined seal structure at the sealing end cover 2 is designed as a dynamic seal to help complete the rotary dynamic seal.

[0063] A stop pin 8 is fixedly connected between the L-shaped spring seat 42 and the sealing end cover 2 to prevent relative rotation between the components.

[0064] The above are all preferred embodiments of the present application, and the protection scope of the present application is not limited thereto. Therefore, any equivalent changes made according to the structure, shape, and principle of the present application should be included in the protection scope of the present application.

Claims

1. An adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions, characterized in that: include: A main end face sealing structure, comprising an active ring (11) sleeved and fixed on a shaft body (1) along an axial direction, a main static ring (12) sleeved and fixed on the shaft body (1) at intervals, and a main static ring seat (13) for supporting and fixing the main static ring (12), wherein a first suction groove (111) is provided on a side of the active ring (11) directly facing the main static ring (12); An axial compensation structure, comprising a bellows (21) sleeved on the shaft body (1), a bellows seat (22) supporting and positioning one end of the bellows (21), and a bellows cover (23) sleeved on the periphery of the bellows (21); the other end of the bellows (21) is positioned by the main stationary ring seat (13); a gland (24) is spaced apart from the end of the bellows seat (22) away from the bellows (21); a memory alloy pin (25) is connected between the gland (24) and the bellows seat (22); A secondary end face sealing structure is provided on the shaft body (1) at the side of the gland (24) facing away from the bellows seat (22).

2. The adaptive mechanical seal structure for high temperature, high pressure and vibration conditions according to claim 1, characterized in that: The secondary end face sealing structure comprises a secondary dynamic ring (31) sleeved on the shaft body (1) along the axial direction, and a W-shaped secondary static ring (32) sleeved on the shaft body (1) at intervals, wherein a secondary static ring seat (33) is provided on the outer side of the W-shaped secondary static ring (32); The auxiliary dynamic ring (31) is located between the W-shaped auxiliary static ring (32) and the pressure cover (24); a second suction groove (311) is provided on the side of the auxiliary dynamic ring (31) facing the W-shaped auxiliary static ring (32); and the auxiliary dynamic ring (31) is capable of rotating with the shaft body (1).

3. The adaptive mechanical seal structure for high temperature, high pressure and vibration conditions according to claim 2 is characterized in that: It also includes a radial compensation structure, which includes a spring (41) with one end radially arranged on the auxiliary static ring seat (33), the other end of the spring (41) is provided with an L-shaped spring seat (42), and the outer side of the L-shaped spring seat (42) is sleeved and fixed with a sealing end cover (2); The W-shaped auxiliary static ring (32) is connected to the vertical arm of the L-shaped spring seat (42) at an outer side surface close to the shaft body (1).

4. The adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions according to claim 3 is characterized in that: The bellows cover (23) is sleeved with a shaft sleeve (3), and the sealing end cover (2) and the shaft sleeve (3) are both fixedly connected to the gland (24).

5. The adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions according to claim 4, characterized in that: The sealing end cover (2) is provided with an oil inlet channel (20), the shaft sleeve (3) is provided with an oil outlet channel (30), a temperature sensor (4) is provided on the oil outlet channel (30), and the shaft sleeve (3) and the oil outlet channel (30) are arranged on both sides of the shaft body (1); The oil outlet passage (30) is connected to a filtering device (5), the filtering device (5) is connected to a circulation device (6), and the circulation device (6) is connected to the oil inlet passage (20).

6. The adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions according to claim 3, characterized in that: The sealing end cover (2) is L-shaped, and a self-lubricating combined sealing structure is provided between one side and the shaft body (1), comprising a graphite ring (51) sleeved on the shaft body (1) and a first metal X-shaped ring (52) sleeved on the graphite ring (51), wherein the two axial ends of the graphite ring (51) are clamped on the first metal X-shaped ring (52).

7. The adaptive mechanical seal structure for high temperature, high pressure and vibration conditions according to claim 2, characterized in that: A turbine (34) is sleeved and fixed on the shaft body (1), and the turbine (34) is fixedly connected to a side of the auxiliary dynamic ring (31) facing away from the W-shaped auxiliary static ring (32); A threaded sleeve (7) is connected to the side of the turbine (34) facing away from the auxiliary moving ring (31), and the threaded sleeve (7) is sleeved on the shaft body (1); One end of the gland (24) is a sleeve portion (241) arranged along the shaft body (1), and the sleeve portion (241) is located between the bellows (21) and the threaded sleeve (7).

8. The adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions according to claim 7, characterized in that: The turbine (34) comprises a plurality of conical surfaces, on which a plurality of blades are evenly spaced.

9. The adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions according to claim 1, characterized in that: An annular second metal X-shaped ring (112) is embedded on the inner ring surface of the active ring (11).

10. The adaptive mechanical seal structure for use under high temperature, high pressure and vibration conditions according to claim 1, characterized in that: The middle portion of the memory alloy pin (25) is arranged in a spring shape, and both ends are respectively in a cylindrical shape.

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