Container type high-temperature-resistant and high-pressure-resistant three-end-face mechanical sealing device

Abstract

The utility model relates to a packaging type high-temperature-resistant and high-pressure-resistant three-end-face mechanical sealing device which is sequentially provided with an inner cavity, a middle cavity and an end cover from a medium side to an atmosphere side, the inner cavity is connected with an equipment main body through a screw, the middle cavity is connected with the inner cavity through a screw, and the end cover is connected with the middle cavity through a screw. The end cover is connected with the middle cavity through a screw; a shaft sleeve is arranged at the axis of the sealing device, is mounted on the outer side of the main shaft and synchronously rotates with the main shaft; two first friction sealing pairs are arranged in the inner cavity, and a second friction sealing pair is arranged in the middle cavity. According to the sealing device, leakage of high-temperature and high-pressure poisonous media can be well isolated, the application range of mechanical sealing pressure can be greatly widened, and the cost of the sealing device can be greatly reduced.

Description

Technical Field

[0001] This utility model relates to the field of mechanical seal technology, specifically to a containerized high-temperature and high-pressure three-end mechanical seal device. Background Technology

[0002] High temperature, high pressure, and toxic or harmful media have long been problems plaguing the mechanical seal industry. The main difficulties lie in the following aspects: 1. High temperature conditions affect the selection of auxiliary seals (such as O-rings) and cause thermal deformation of components, affecting the seal performance; 2. High pressure conditions place high demands on the pressure-bearing capacity of mechanical seal components, especially the friction pair composed of dynamic and static rings. High pressure causes end-face deformation, further affecting its sealing performance; 3. For toxic or harmful conditions, leakage of media must be avoided, therefore, at least a double-end-face mechanical seal is required in terms of structure; 4. Even with a double-end-face mechanical seal, there is a large pressure difference between the sealing pair and the atmospheric side, which can easily cause leakage of the isolation liquid (gas), placing high demands on the precision of the mechanical seal end cap and greatly increasing the sealing cost.

[0003] If these three operating conditions occur simultaneously, it poses new challenges to the design of mechanical seals. Conventional mechanical seal layout schemes will not be able to meet the requirements of field use conditions. Therefore, it is necessary to design a mechanical seal device that can withstand high temperature and high pressure and can operate normally under toxic and harmful media conditions. Summary of the Invention

[0004] The purpose of this utility model is to overcome the defects of the existing technology and provide a containerized high temperature and high pressure resistant three-end mechanical seal device.

[0005] To achieve the purpose of this utility model, this application provides the following technical solution.

[0006] In a first aspect, this application provides a cartridge-type high-temperature and high-pressure three-end mechanical seal device. The sealing device is installed on the outside of the main shaft and connected to the main body of the equipment. The sealing device is provided with an inner cavity, an intermediate cavity, and an end cover in sequence from the medium side to the atmosphere side. The inner cavity is connected to the main body of the equipment by screws. The intermediate cavity is connected to the inner cavity by screws. The end cover is connected to the intermediate cavity by screws. A bushing is provided at the shaft center of the sealing device. The bushing is installed on the outside of the main shaft and rotates synchronously with the main shaft. Two pairs of first friction sealing pairs are provided in the inner cavity, and a pair of second friction sealing pairs are provided in the intermediate cavity.

[0007] In this application, two pairs of first friction seals are arranged in the inner cavity near the medium side, and a separating fluid is circulated between the two pairs of friction seals. The pressure of the separating fluid is 2-3 Bar higher than the medium pressure, that is, high-pressure fluid is used to seal high-temperature, high-pressure, or toxic media, which can effectively prevent media leakage. At the same time, in order to prevent high-pressure fluid from leaking into the atmosphere, a set of second friction seals is arranged in the middle cavity. A buffer solution (with a pressure much lower than the pressure of the separating fluid) is circulated between the second pair of friction seals and the third pair of friction seals. The buffer solution flows in and out, providing a certain back pressure to the second pair of friction seals. This reduces the actual pressure difference that the second pair of friction seals bears, which can greatly improve the applicable pressure range of the mechanical seal. On the other hand, it carries away heat and reduces the temperature of the sealing end face.

[0008] Specifically, for toxic and harmful media, the most effective mechanical seal arrangement to prevent leakage is to use a double-end mechanical seal with a separator fluid in between. The separator fluid pressure should be 2-3 bar higher than the medium pressure, so that the medium can be sealed with a separator fluid that is higher than the medium pressure. However, if the medium pressure itself is high, then the required pressure of the isolation fluid must be even higher. For example, assuming the medium pressure is 100 bar, then the isolation fluid pressure must be at least 102~103 bar. For the first pair of friction pairs (the first friction sealing pair near the medium side), the internal and external pressure difference is 2~3 bar. Obviously, the pressure requirement of the first pair of friction pairs is relatively low. However, if there is no third pair of friction pairs, the internal and external pressure difference of the second pair of friction pairs is 102~103 bar. This places very high demands on the pressure-bearing capacity of the second pair of friction pairs (another pair of first friction sealing pairs). Similarly, if the medium pressure is even higher, the corresponding isolation fluid pressure needs to be increased, causing the internal and external pressure difference borne by the second pair of friction pairs to increase further. However, the pressure-bearing capacity of dynamic and static rings made of different materials has its limits. High pressure not only puts forward higher requirements for the selection of materials for dynamic and static rings, but also, the higher the pressure, the more heat is generated by the dynamic and static rings during operation, causing thermal deformation of the dynamic and static rings, thereby affecting the sealing performance. This application adds a third pair of friction pairs (i.e., the second friction sealing pair). A buffer solution (with a pressure lower than the isolation fluid) is introduced between the second and third pairs of friction pairs. Using the example above, assuming the isolation fluid pressure is 102~103 bar and the buffer solution pressure is 50 bar, the pressure difference between the inside and outside of the second pair of friction pairs is reduced to about 50 bar, and the pressure difference between the inside and outside of the third pair of friction pairs is also 50 bar. Thus, for the three pairs of sealing end faces, the maximum pressure difference between the inside and outside of each pair of sealing end faces is about 50 bar, which greatly reduces the pressure range that the dynamic and static rings can withstand. Furthermore, the design of the three-end face mechanical seal can improve the overall seal's adaptability to the medium pressure range (for example, if the medium pressure is 150 bar, the isolation fluid pressure is 152~153 bar, and the buffer solution pressure is given as 75 bar, the maximum pressure difference between each pair of sealing end faces is about 75 bar). At the same time, the buffer solution enters and exits, which can remove the heat generated by the friction of the sealing end faces, avoid thermal deformation of the dynamic and static rings caused by heat, and improve the overall performance of the seal.

[0009] In one embodiment of the first aspect, a first mounting chamber is coaxially provided in the middle of the inner cavity, and an integral convex ring is provided outwardly in the middle of the bushing. The convex ring is located in the first mounting chamber, wherein a pair of first friction sealing pairs are installed between the convex ring and the front end face of the first mounting chamber, and another pair of first friction sealing pairs are installed between the convex ring and the rear end face of the first mounting chamber. In this application, the rear end face of the first mounting chamber can be closed or open. "Closed" means that the rear end of the inner cavity has a partition, and the partition serves as the rear end face of the first mounting chamber; "open" means that the front end face of the intermediate cavity serves as the rear end face of the first mounting chamber.

[0010] In one embodiment of the first aspect, the first friction sealing pair includes a first stationary ring, a first rotating ring, a first spring, and a first push ring assembly.

[0011] The first stationary ring is connected to the front or rear end face of the first mounting chamber via a pin. A first spring and a first push ring assembly are sequentially arranged between the front or rear end face of the first mounting chamber and the first stationary ring. The first spring pushes the first stationary ring to abut against the first rotating ring. The contact surfaces of the first stationary ring and the first rotating ring are hard-on-hard, meaning their contact surface materials are very hard, such as silicon carbide on silicon carbide + CVD. Furthermore, micron-sized fluid grooves can be formed on their contact surfaces to create a highly rigid liquid film, which isolates the medium and reduces wear between the first rotating ring and the first stationary ring. The remaining components, such as the first spring, the first push ring assembly, and the pin, are all conventional features in the art.

[0012] The front and rear ends of the convex ring are provided with holes and grooves, the shape of which matches the first moving ring, and the sidewall of the hole and groove is connected to the first moving ring through a convex recess.

[0013] In one embodiment of the first aspect, two retaining rings are inserted into the side wall of the first mounting chamber. The retaining rings are arranged coaxially with the main shaft. The outer periphery of the retaining rings abuts against the side wall of the first mounting chamber, and the inner periphery of each of the two retaining rings abuts against the outer wall of one of the first stationary rings.

[0014] A distribution ring is provided between the two retaining rings, with its front and rear ends respectively abutting against the two retaining rings, and uniform through holes are provided on the distribution ring.

[0015] The inner cavity has an inlet channel and an outlet channel for the isolation liquid on its side wall, and both the inlet channel and the outlet channel are connected to the first installation chamber.

[0016] In one embodiment of the first aspect, the distribution ring includes two side rings and an isolation ring disposed between the two side rings, wherein the side rings and the isolation ring are integrally formed; the two side rings respectively abut against two retaining rings.

[0017] The isolation ring has uniformly spaced through holes and is coaxially arranged with the main shaft. The isolation ring divides the space of the first mounting chamber located between the two retaining rings into an outer cavity space and an inner cavity space. The contact surfaces of the two first stationary rings and the first moving ring are located within the inner cavity space. The isolation fluid inlet channel and the isolation fluid outlet channel communicate with the outer cavity space. The purpose of setting the distribution ring is to ensure more uniform distribution of the isolation fluid entering between the first stationary ring and the first moving ring.

[0018] In one embodiment of the first aspect, the tail of the intermediate cavity is coaxially provided with a second mounting chamber, and the second friction sealing pair is disposed in the second mounting chamber; the second friction sealing pair includes a second stationary ring, a second moving ring, a short bushing, a second spring, and a second push ring assembly.

[0019] The short bushing rotates synchronously with the second rotating ring via a set screw. The short bushing has a groove that matches the second rotating ring. A second spring and a second push ring assembly are sequentially arranged between the short bushing and the second rotating ring. The second spring pushes the second rotating ring to abut against the second stationary ring. The contact surfaces of the second rotating ring and the second stationary ring are also hard-on-hard. Alternatively, micron-sized fluid grooves can be formed on their contact surfaces to create a buffer solution film, which can prevent leakage of the isolation fluid and reduce wear between them.

[0020] The second stationary ring is connected to the end cap via an anti-rotation pin.

[0021] In one embodiment of the first aspect, the intermediate cavity is provided with a buffer inlet channel and a buffer outlet channel, both of which are connected to the second mounting chamber.

[0022] In one embodiment of the first aspect, the inner cavity also includes an independent cooling chamber, and the inner cavity has a cooling water inlet channel and a cooling water outlet channel, both of which communicate with the cooling chamber. The cooling water chamber, cooling water inlet channel, and cooling water outlet channel are primarily for sealing high-temperature media, and preferably, the cooling chamber is located on the side of the inner cavity closer to the main body of the equipment. During processing, an annular groove can be formed on the inner cavity, and a sealing cap can be placed at one end of the annular groove and welded to the inner cavity, thereby forming an independent, sealed cooling chamber (the so-called sealed means that it is not connected to other spaces except for communication with the cooling water inlet channel and the cooling water outlet channel).

[0023] Compared with the prior art, the beneficial effects of this utility model are as follows:

[0024] (1) The main seal consists of two pairs of friction pairs (a pair of dynamic and static rings forming a pair of friction pairs, i.e. the first friction sealing pair) arranged back to back. The dynamic and static rings are paired in a hard-to-hard manner to improve the pressure bearing capacity of the friction pairs. The two pairs of friction pairs are connected by a separating fluid. The pressure of the separating fluid is 2~3 Bar higher than the pressure of the medium. The high-pressure fluid is used to seal the low-pressure medium to prevent the medium from leaking out.

[0025] (2) Arrange a single-end mechanical seal (i.e., the second friction seal pair) near the atmosphere. Buffer solution (its pressure is much lower than the isolation fluid pressure) is introduced between the second pair of friction pairs and the third pair of friction pairs. The buffer solution enters and exits, providing a certain back pressure to the second pair of friction pairs. This reduces the actual pressure difference borne by the second pair of friction pairs. On the other hand, it removes heat and lowers the temperature of the sealing end face.

[0026] (3) A cooling water jacket is provided near the medium side, and cooling water enters and exits, taking away some of the heat transferred from the medium. Attached Figure Description

[0027] Figure 1 This is a schematic diagram of the sealing device of this application.

[0028] In the attached drawings, 1 is the first stationary ring, 2 is the first moving ring, 3 is an O-ring, 4 is the first push ring assembly, 5 is a sealing ring, 6 is an O-ring, 7 is a bushing, 8 is a metal spiral wound gasket, 9 is an inner cavity, 10 is a distribution ring, 11 is a retaining ring, 12 is a pin sleeve, 13 is an intermediate cavity, 14 is a short bushing, 15 is a set screw, 16 is a second spring, 17 is an O-ring, 18 is the second push ring assembly, 19 is an O-ring, 20 is the second moving ring, 21 is an anti-detachment ring, 22 is the second mounting chamber, 23 is the second stationary ring, 24 is an O-ring, and 25 is... End cap, 26 is anti-rotation pin, 27 is locking disc assembly, 28 is positioning plate, 29 is screw, 30 is O-ring, 31 is first spring, 32 is inner cavity space, 33 is outer cavity space, 34 is through hole, 35 is side ring, 36 is isolation ring, 37 is first mounting chamber, 38 is cooling chamber, 39 is main shaft, 40 is equipment body, CI is cooling water inlet channel, CO is cooling water outlet channel, LBI is isolation fluid inlet channel, LBO is isolation fluid outlet channel, BI is buffer solution inlet channel, and BO is buffer solution outlet channel. Detailed Implementation

[0029] Unless otherwise defined, the technical or scientific terms used in this specification and claims shall have the ordinary meaning understood by one of ordinary skill in the art to which this invention pertains. All values ​​listed herein, ranging from the minimum to the maximum, refer to all values ​​obtained by incrementing the minimum and maximum values ​​by one unit when the difference between the minimum and maximum values ​​is more than two units.

[0030] The following describes specific embodiments of this utility model. It should be noted that, in order to provide a concise description, this specification cannot provide a detailed description of all features of the actual embodiments. Without departing from the spirit and scope of this utility model, those skilled in the art can modify and substitute the embodiments of this utility model, and the resulting embodiments are also within the protection scope of this utility model.

[0031] This patent proposes a modular, high-temperature, high-pressure, three-end-face mechanical seal device for use with high-temperature, high-pressure, and toxic / hazardous media. Its basic structure is as follows: The main seal consists of two pairs of friction pairs (one pair consisting of a dynamic and a static ring) arranged back-to-back, with the dynamic and static rings rigidly paired, such as silicon carbide to silicon carbide + CVD. A separating fluid flows between the two pairs of friction pairs, with the pressure of the separating fluid being 2-3 Bar higher than the medium pressure. This high-pressure fluid seals the low-pressure medium, preventing leakage. A single-end-face mechanical seal (i.e., the third pair of friction pairs) is arranged near the atmosphere. A buffer solution (with a pressure much lower than the separating fluid pressure) flows between the second and third pairs of friction pairs. The buffer solution flows in and out, providing back pressure to the second pair of friction pairs, reducing the pressure difference between their ends, and carrying away heat to lower the temperature of the sealing end face. A cooling water jacket is located near the medium side, with cooling water flowing in and out to remove some of the heat transferred from the medium. The three pairs of friction pairs are arranged sequentially within the sealing cavity, and the sealing cavity and shaft sleeve are assembled into a single unit by positioning plates.

[0032] For toxic and hazardous media, this patent employs a back-to-back double-end mechanical seal as the main seal, using an isolation fluid with a pressure 2-3 kg higher than the medium pressure to seal the medium and ensure no leakage. For high-pressure conditions, this patent uses high-pressure resistant dynamic and static rings as the main seal, with a hard-to-hard mating material selection. It also includes a third pair of friction pairs, with a buffer solution flowing between the second and third pairs, effectively providing back pressure to the second pair and reducing the pressure difference across them. For high-temperature conditions, this patent incorporates a cooling water jacket for the medium, allowing cooling water to flow in and out, carrying away some of the heat transferred from the medium. Additionally, a buffer solution flows between the second and third pairs of friction pairs, carrying away heat and reducing the temperature of the sealing surfaces. Example

[0033] The embodiments of this utility model will be described in detail below. These embodiments are implemented based on the technical solution of this utility model and provide detailed implementation methods and specific operation processes. However, the protection scope of this utility model is not limited to the following embodiments. Example

[0034] A containerized high-temperature and high-pressure resistant three-end mechanical seal device, the structure of which is as follows: Figure 1 As shown, the sealing device is installed on the outside of the main shaft 39 and connected to the equipment body 40. The sealing device, from the medium side to the atmosphere side, consists of an inner cavity 9, an intermediate cavity 13, and an end cap 25. The inner cavity 9 is connected to the equipment body 40 by screws (the screws are not shown in the figure). The intermediate cavity 13 is connected to the inner cavity 9 by screws (the screws are not shown in the figure). The end cap 25 is connected to the intermediate cavity 13 by screws. A bushing 7 is provided at the shaft center of the sealing device. The bushing 7 is installed on the outside of the main shaft 39 and rotates synchronously with the main shaft 39. The inner cavity 9 has two pairs of first friction sealing pairs, and the intermediate cavity 13 has one pair of second friction sealing pairs. Specifically…

[0035] A first mounting chamber 37 is coaxially located in the center of the inner cavity 9. An integral convex ring is provided outward from the center of the bushing 7. The convex ring is located in the first mounting chamber 37. Two first moving rings 2 are mounted on the convex ring. The convex ring has a hole groove that matches the shape of the first moving ring 2, and a recess is provided in the groove. The recess plays a transmission role, so that the first moving ring 2 and the bushing 7 rotate synchronously. A sealing ring 5 is provided on the contact surface between the first moving ring 2 and the convex ring. The sealing ring 5 plays a static sealing role between the first moving ring 2 and the bushing 7 (convex ring). The first moving ring 2, the bushing 7, and the sealing ring 5 rotate together with the main shaft 39, as the rotating parts of the two pairs of first friction sealing pairs.

[0036] In this embodiment, the tail end face of the first mounting chamber 37 is in an open state. Specifically, one of the first springs 31 is installed in the spring hole of the inner cavity 9 and acts on the first push ring assembly 4. The first push ring assembly 4 is in contact with the back of the first stationary ring 1. Under the force of the first spring 31, the first push ring assembly 4 and the first stationary ring 1 can move axially within the first mounting chamber 37 and maintain contact with the first moving ring 2. An anti-rotation pin is provided between the first stationary ring 1 and the inner cavity 9. A pin sleeve 12 is provided at the connection between the anti-rotation pin and the inner cavity 9. The anti-rotation pin plays a radial anti-rotation role, that is, it prevents the first stationary ring 1 from rotating. This part is the stationary part of one of the first friction sealing pairs. In addition, an O-ring 3 is provided at the connection between the first push ring assembly 4 and the inner cavity 9.

[0037] The stationary part of the other first friction seal pair has the same structure, but its installation position is different because the tail end face of the first mounting chamber 37 is in the open state. Specifically, the first spring 31 is installed in the spring hole on the front end face of the intermediate cavity 13 and acts on the first push ring assembly 4. The first push ring assembly 4 is in contact with the back of the first stationary ring 1. Under the force of the first spring 31, the first push ring assembly 4 and the first stationary ring 1 can move axially at the balance diameter of the intermediate cavity 13 and maintain contact with the first moving ring 2. An anti-rotation pin is provided between the first stationary ring 1 and the intermediate cavity 13. A pin sleeve 12 is provided at the connection between the anti-rotation pin and the intermediate cavity 13. The anti-rotation pin plays a radial anti-rotation role, that is, it prevents the first stationary ring 1 from rotating. This part is the stationary part of the second first friction seal pair. In addition, an O-ring 3 is also provided at the connection between the first push ring assembly 4 and the intermediate cavity 13.

[0038] Two retaining rings 11 are inserted into the side wall of the first mounting chamber 37. The retaining rings 11 are coaxially arranged with the main shaft 39. The outer periphery of the retaining rings 11 abuts against the side wall of the first mounting chamber 37, and the inner periphery of the two retaining rings 11 abuts against the outer wall of a first stationary ring 1, respectively. A distribution ring 10 is provided between the two retaining rings 11. The distribution ring 10 includes two side rings 35 and an isolation ring 36 disposed between the two side rings 35. The side rings 35 and the isolation ring 36 are integrally formed. The two side rings 35 abut against the two retaining rings 11, respectively. The isolation ring 36 has uniformly distributed through holes 34. The isolation ring 36 is coaxially arranged with the main shaft 39, and the isolation ring 36 divides the space of the first mounting chamber 37 located between the two retaining rings 11 into an outer cavity space 33 and an inner cavity space 32. The abutting surfaces of the two first stationary rings 1 and the first moving ring 2 are located in the inner cavity space 32. The isolation liquid inlet channel and the isolation liquid outlet channel are connected to the outer cavity space 33. The inner cavity 9 has a separating fluid inlet channel LBI and a separating fluid outlet channel LBO on its side wall. Both the separating fluid inlet channel LBI and the separating fluid outlet channel LBO are connected to the first installation chamber 37.

[0039] In addition, an independent cooling chamber 38 is provided in the inner cavity 9 near the medium side, and the inner cavity 9 is provided with a cooling water inlet channel CI and a cooling water outlet channel CO, both of which are connected to the cooling chamber 38.

[0040] A second mounting chamber 22 is coaxially provided at the tail end of the intermediate cavity 13, and a second friction sealing pair is disposed within the second mounting chamber 22. The second friction sealing pair includes a second stationary ring 23, a second rotating ring 20, a short bushing 14, a second spring 16, and a second push ring assembly 18. Specifically, the short bushing 14 rotates synchronously with the bushing 7 via a set screw 15. The short bushing 14 has a groove that matches the second rotating ring 20, and the second spring 16 and the second push ring assembly 18 are sequentially arranged between the short bushing 14 and the second rotating ring 20. The second spring 16 pushes the second rotating ring 20 to abut against the second stationary ring 23. The second rotating ring 20 and the short bushing 14 are driven by a groove, so that the second rotating ring 20 and the short bushing 14 rotate synchronously. An O-ring 17 is provided at the connection between the short bushing 14 and the bushing 7, and an O-ring 19 is provided between the second rotating ring 20 and the short bushing 14. Additionally, an anti-disengagement ring 21 is provided on the short bushing 14 to prevent the second rotating ring 20 from disengaging from the groove in the short bushing 14. This part is the rotating part of the second friction seal pair.

[0041] The second stationary ring 23 is installed on the end cover 25 and is prevented from rotating by the anti-rotation pin 26 installed on the end cover 25. The O-ring 24 plays a static sealing role between the second stationary ring 23 and the end cover 25. This part is the stationary part of the second friction seal pair.

[0042] A buffer inlet channel BI and a buffer outlet channel BO are provided on the intermediate cavity 13. Both the buffer inlet channel BI and the buffer outlet channel BO are connected to the second mounting chamber 22.

[0043] The locking disc assembly 27 locks the bushing 7 to the main shaft 39, causing the rotating part to rotate together with the main shaft 39. The positioning plate 28 and screw 29 connect the bushing 7 and the end cover 25, integrating the entire sealing assembly into a single unit. In addition, metal spiral wound gaskets 8 are provided between the inner cavity 9 and the main body 40 and the intermediate cavity 13, an O-ring 30 is provided between the end cover 25 and the intermediate cavity 13, and an O-ring 6 is provided between the bushing 7 and the main shaft 39.

[0044] The above description of the embodiments is intended to enable those skilled in the art to understand and apply this application. It will be apparent to those skilled in the art that various modifications can be easily made to these embodiments, and the general principles described herein can be applied to other embodiments without creative effort. Therefore, this application is not limited to the embodiments described herein, and any improvements and modifications made by those skilled in the art based on the disclosure of this application without departing from the scope and spirit of this application are within the scope of this application.

Claims

1. A cartridge-type high-temperature and high-pressure resistant three-end-face mechanical seal device, wherein the seal device is installed on the outside of the main shaft and connected to the main body of the equipment, characterized in that, The sealing device is provided with an inner cavity, an intermediate cavity, and an end cap in sequence from the medium side to the atmosphere side. The inner cavity is connected to the main body of the device by screws, the intermediate cavity is connected to the inner cavity by screws, and the end cap is connected to the intermediate cavity by screws. A bushing is provided at the axis of the sealing device. The bushing is installed on the outside of the main shaft and rotates synchronously with the main shaft. Two pairs of first friction sealing pairs are provided in the inner cavity, and a pair of second friction sealing pairs are provided in the intermediate cavity.

2. The containerized high-temperature and high-pressure three-end mechanical seal device as described in claim 1, characterized in that, The inner cavity is coaxially provided with a first mounting chamber in the middle, and the bushing is provided with an integral convex ring in the middle. The convex ring is located in the first mounting chamber. One pair of the first friction seals is installed between the convex ring and the front end face of the first mounting chamber, and another pair of the first friction seals is installed between the convex ring and the tail end face of the first mounting chamber.

3. The containerized high-temperature and high-pressure three-end mechanical seal device as described in claim 2, characterized in that, The first friction seal pair includes a first stationary ring, a first rotating ring, a first spring, and a first push ring assembly, wherein, The first stationary ring is connected to the front end face or the rear end face of the first mounting chamber by a pin, and a first spring and a first push ring assembly are sequentially provided between the front end face or the rear end face of the first mounting chamber and the first stationary ring. The first spring pushes the first stationary ring to abut against the first moving ring. The front and rear ends of the convex ring are provided with holes and grooves, the shape of which matches the first moving ring, and the sidewall of the hole and groove is connected to the first moving ring through a convex recess.

4. The containerized high-temperature and high-pressure three-end mechanical seal device as described in claim 3, characterized in that, Two retaining rings are inserted into the side wall of the first mounting chamber. The retaining rings are arranged coaxially with the main shaft. The outer periphery of the retaining rings abuts against the side wall of the first mounting chamber, and the inner periphery of the two retaining rings abuts against the outer wall of one of the first stationary rings. A distribution ring is provided between the two retaining rings, with the front and rear ends of the distribution ring abutting against the two retaining rings respectively, and uniform through holes are provided on the distribution ring; The inner cavity has an inlet channel and an outlet channel for the isolation liquid on its side wall, and both the inlet channel and the outlet channel are connected to the first installation chamber.

5. The containerized high-temperature and high-pressure three-end mechanical seal device as described in claim 4, characterized in that, The distribution ring includes two side rings and an isolation ring disposed between the two side rings, wherein the side rings and the isolation ring are integrally formed; the two side rings respectively abut against two retaining rings; The isolation ring has uniformly spaced through holes. The isolation ring is coaxially arranged with the main shaft. The isolation ring divides the space of the first mounting chamber located between the two retaining rings into an outer cavity space and an inner cavity space. The contact surfaces of the two first stationary rings and the first moving ring are located in the inner cavity space. The isolation liquid inlet channel and the isolation liquid outlet channel are connected to the outer cavity space.

6. The containerized high-temperature and high-pressure three-end mechanical seal device as described in claim 1, characterized in that, The rear end of the intermediate cavity is coaxially provided with a second mounting chamber, and the second friction sealing pair is disposed in the second mounting chamber; the second friction sealing pair includes a second stationary ring, a second moving ring, a short bushing, a second spring, and a second push ring assembly, wherein... The short bushing rotates synchronously with the bushing via a set screw. The short bushing has a groove that matches the second moving ring. A second spring and a second push ring assembly are sequentially provided between the short bushing and the second moving ring. The second spring pushes the second moving ring to abut against the second stationary ring. The second stationary ring is connected to the end cap via an anti-rotation pin.

7. The containerized high-temperature and high-pressure three-end mechanical seal device as described in claim 6, characterized in that, The intermediate cavity is provided with a buffer inlet channel and a buffer outlet channel, both of which are connected to the second mounting chamber.

8. The containerized high-temperature and high-pressure three-end mechanical seal device as described in claim 1, characterized in that, The inner cavity also has an independent cooling chamber, and the inner cavity is provided with a cooling water inlet channel and a cooling water outlet channel, both of which are connected to the cooling chamber.

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