Double-end-face sealing structure and salt mining pump thereof
Through the relative movement of the moving and static rings in the double-end sealing structure and the compensation of the axial pressure provided by the spring, the problem of seal leakage during potassium salt mining is solved, the stable operation and long life of the salt pump is achieved, and the maintenance cost is reduced.
Patent Information
- Application Number
- CN202422498150.1
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-10-15
- Publication Date
- 2025-08-12
- Estimated Expiration
- 2034-10-15
AI Technical Summary
The existing sealing technology cannot effectively resist the erosion and corrosion of ore slurry during potassium salt mining, resulting in frequent leakage, affecting the stability and service life of the salt mining pump. In addition, traditional sealing methods are difficult to adapt to the changes in the sealing surface gap caused by pump body vibration in harsh environments.
Using a double-end sealing structure, two-stage dynamic seals are achieved through the relative movement of the first moving ring and the first static ring and the relative movement of the second moving ring and the second static ring, and axial pressure is provided by the first compensation spring and the second compensation spring respectively, so that the moving ring and the static ring are closely fitted to ensure the sealing effect.
It improves the operating stability and service life of salt harvesting pumps, reduces maintenance costs, and promotes technological progress and sustainable development of the potassium salt mining industry.
Smart Images
Figure CN223215754U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of salt mining pump seals, in particular to a double-end face seal structure and a salt mining pump thereof. Background Art
[0002] In the potash mining industry, salt pumps, as key equipment, are responsible for transporting mixed potassium salt slurry containing different concentrations (5% to 40%) from the bottom of the salt lake to the processing system. However, in this process, the complex characteristics of the slurry pose a huge challenge to the stable operation of the salt pumps. Specifically, the particle size distribution of the material in the slurry is wide (0 to 50 mm), and the hardness of the salt ore is as high as 3.0. This unevenness and high hardness directly lead to violent vibrations in the salt pump during operation, which not only affects the service life of the pump, but also increases energy consumption and maintenance costs.
[0003] Furthermore, brine, as a supersaturated salt solution, is prone to crystallization, making the pump body and sealing components extremely susceptible to corrosion from the crystallized salt, exacerbating seal wear and failure. Brine is also highly corrosive, further shortening the service life of seals. Further complicating matters, the salt pumps are installed in the bilge of the salt mining vessel. The frequent movement of the salt mining vessel within the salt lake creates a harsh and volatile working environment. This, coupled with the lack of fresh water supply on board, limits the effective application of traditional sealing technologies.
[0004] Currently, the sealing methods widely used in the chemical industry, such as packing seals, mechanical seals, soft packing seals, and spiral seals, all demonstrate significant inadequacy in handling these special operating conditions. These sealing methods frequently leak, either because they are unable to effectively resist the erosion and corrosion of the slurry or because they struggle to adapt to changes in the sealing surface gap caused by pump vibration. According to statistics, the leakage interval of salt pumps using existing sealing technology generally does not exceed seven days. This not only leads to high maintenance costs but also seriously affects the continuity and efficiency of salt mining operations. Furthermore, leaking slurry and brine also deteriorate the working environment in the cabin, posing a threat to personnel health and equipment safety.
[0005] In view of the above technical background, there is an urgent need for a salt pump sealing device to solve the sealing problem faced in the potash mining process. Utility Model Content
[0006] The purpose of the utility model is to provide a double-end face sealing structure and a salt mining pump thereof to solve the problems existing in the above-mentioned prior art, and to realize two-stage dynamic sealing by utilizing the relative movement of the first dynamic ring and the first static ring and the relative movement of the second dynamic ring and the second static ring, and to provide axial pressure through the first compensation spring and the second compensation spring respectively so that the first dynamic ring and the first static ring are tightly fitted and the second dynamic ring and the second static ring are tightly fitted, thereby ensuring the sealing effect.
[0007] To achieve the above purpose, the present invention provides the following solutions:
[0008] The utility model provides a double-end face sealing structure, including a first sleeve, a second sleeve, a third sleeve, a fourth sleeve, a first compensation spring and a second compensation spring, the first sleeve is used for sealing connection to the transmission shaft, and a first dynamic ring is installed on the first sleeve; the second sleeve is used for sealing connection to the machine seal cover, and a first static ring for sliding sealing with the first dynamic ring is installed on the second sleeve; the third sleeve is located in a cavity between the first sleeve and the second sleeve, the third sleeve is connected to the first sleeve, and a second dynamic ring is installed on the third sleeve; the fourth sleeve is used for sealing connection to the machine seal cover, and a second static ring for sliding sealing with the second dynamic ring is installed on the fourth sleeve; the first compensation spring is used to provide axial pressure between the first dynamic ring and the first static ring; the second compensation spring is used to provide axial pressure between the second dynamic ring and the second static ring.
[0009] In one embodiment, one end of the first compensation spring abuts against the fourth sleeve, and the other end of the first compensation spring abuts against the second sleeve.
[0010] In one embodiment, an end cover with a central opening is further included, wherein the first axial surface side of the end cover is used for sealing connection with the machine seal cover, the second axial surface side of the end cover is sealed connected with the fourth sleeve, and the inner diameter side of the end cover is sealed connected with the second sleeve.
[0011] In one embodiment, a coolant outlet and a coolant inlet are radially provided on the end cover, the first sleeve, the second sleeve and the fourth sleeve form a cooling chamber, and the coolant outlet and the coolant inlet are connected to the cooling chamber.
[0012] In one embodiment, a spiral groove is provided on the outer diameter side of the third sleeve, and the spiral groove is used to generate power for the flow of the coolant.
[0013] In one embodiment, the third sleeve is provided with a mounting groove for accommodating the second compensation spring, one end of the second compensation spring abuts against the third sleeve, and the other end of the second compensation spring abuts against the second movable ring.
[0014] In one embodiment, an expansion sleeve is further included, wherein a portion of the first sleeve extending out of the fourth sleeve is connected to the expansion sleeve, and the expansion sleeve is used to fasten the first sleeve to the transmission shaft.
[0015] In one embodiment, a fifth sleeve is further included, which is used to be sleeved between the inner diameter side of the first sleeve and the outer diameter side of the transmission shaft. The fifth sleeve and the transmission shaft, as well as the fifth sleeve and the first sleeve, are sealed.
[0016] The present utility model also provides a salt mining pump, including an impeller, a machine seal cover and the double-end face sealing structure as described above, wherein the impeller is used to be installed on a transmission shaft; the machine seal cover is used to be sealed and connected to the pump casing; the first sleeve is sealed and connected to the transmission shaft, the second sleeve and the fourth sleeve are sealed and connected to the machine seal cover, the second dynamic ring is sealed and connected to the first sleeve, and the second static ring is sealed and connected to the fourth sleeve.
[0017] In one embodiment, there is a first gap between the impeller and the mechanical seal cover, and a second gap between the inner diameter side of the mechanical seal cover and the double-end face sealing structure, the first gap is 30mm~40mm, and the second gap is 35mm~40mm; the first gap and the second gap are connected through a tapered channel, and the opening angle of the tapered channel is 70°~80°.
[0018] Compared with the prior art, the utility model has achieved the following technical effects:
[0019] The utility model realizes two-stage dynamic sealing by utilizing the relative movement of the first dynamic ring and the first static ring and the relative movement of the second dynamic ring and the second static ring, and provides axial pressure through the first compensation spring and the second compensation spring respectively so that the first dynamic ring and the first static ring are in close contact with each other, and the second dynamic ring and the second static ring are in close contact with each other, thereby ensuring the sealing effect, improving the operating stability and service life of the salt mining pump, reducing maintenance costs, and promoting technological progress and sustainable development of the potash mining industry. BRIEF DESCRIPTION OF THE DRAWINGS
[0020] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.
[0021] Figure 1 This is a schematic diagram of the installation of a double-end sealing structure in an embodiment of the present utility model;
[0022] Figure 2 This is a schematic diagram of a double-end face sealing structure in an embodiment of the present utility model;
[0023] Figure 3 for Figure 2 Enlarged view of point A in the middle;
[0024] Figure 4 for Figure 2 Enlarged view of point B in the middle;
[0025] Among them, 1. impeller; 2. mechanical seal cover; 3. double end face seal structure; 4. expansion joint; 5. transmission shaft; 6. limit block; 7. first screw; 8. second screw;
[0026] 31. First sleeve; 311. First dynamic ring; 32. Second sleeve; 321. First static ring; 33. Third sleeve; 331. Second dynamic ring; 332. Spiral groove; 34. Fourth sleeve; 341. Second static ring; 35. Fifth sleeve; 36. End cover; 37. First compensation spring; 38. Second compensation spring.
[0027] 41. First compression sleeve; 42. Second compression sleeve; 43. Arc sleeve; 44. Third screw;
[0028] 91. Coolant tank; 92. Liquid level gauge; 93. Inlet valve; 94. Connecting pipe. DETAILED DESCRIPTION
[0029] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.
[0030] The purpose of the utility model is to provide a double-end face sealing structure and a salt mining pump thereof to solve the problems existing in the prior art, and to realize two-stage dynamic sealing by utilizing the relative movement of the first dynamic ring and the first static ring and the relative movement of the second dynamic ring and the second static ring, and to provide axial pressure through the first compensation spring and the second compensation spring respectively so that the first dynamic ring and the first static ring are tightly fitted and the second dynamic ring and the second static ring are tightly fitted, thereby ensuring the sealing effect.
[0031] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific implementation methods.
[0032] like Figures 1 to 4As shown, the present invention provides a double-end face sealing structure, including a first sleeve 31, a second sleeve 32, a third sleeve 33, a fourth sleeve 34, a first compensation spring 37, and a second compensation spring 38. The first sleeve 31 is used for sealing connection to the transmission shaft 5. To ensure sealing, an O-ring can be provided between the first sleeve 31 and the transmission shaft 5. The O-ring can be distributed in one or more rows in the axial direction. The first sleeve 31 can be directly attached to the transmission shaft 5 or connected through other sleeves. A first dynamic ring 311 is mounted on the first sleeve 31. The first dynamic ring 311 can be mounted on the radially outer side or axial side of the first sleeve 31. The first sleeve 31 is provided with an annular groove for accommodating the first dynamic ring 311. An O-ring can be provided in the annular groove to prevent leakage. Driven by the transmission shaft 5, the first dynamic ring 311 rotates with the first sleeve 31. The second sleeve 32 is sealed against the mechanical seal 2. The second sleeve 32 can be connected directly to the mechanical seal 2 or through the end cap 36. To ensure a tight seal, an O-ring is installed between the second sleeve 32 and the mechanical seal 2, or between the second sleeve 32 and the end cap 36. The mechanical seal 2 is connected to the pump casing to facilitate installation and removal of the impeller 1. The second sleeve 32 is mounted with a first stationary ring 321 for sliding sealing with the first dynamic ring 311. The first stationary ring 321 can be mounted radially outward or axially on the second sleeve 32. The second sleeve 32 is provided with an annular groove to accommodate the first stationary ring 321. An O-ring can be installed in the annular groove to prevent leakage. Since the second sleeve 32 remains stationary relative to the mechanical seal 2, the first stationary ring 321 also remains stationary relative to the mechanical seal 2. The first dynamic ring 311 and the first stationary ring 321 form a first mechanical seal friction pair, capable of maintaining a seal while in relative motion.
[0033] In addition to the first mechanical seal friction pair, a second mechanical seal friction pair consisting of a second dynamic ring 331 and a second static ring 341 is also provided. Specifically, the third sleeve 33 is located in the cavity between the first sleeve 31 and the second sleeve 32. The third sleeve 33 is connected to the first sleeve 31. The second dynamic ring 331 is mounted on the third sleeve 33. The second dynamic ring 331 can be mounted on the radially outer side or axial side of the third sleeve 33. The third sleeve 33 is provided with an annular groove to accommodate the second dynamic ring 331. An O-ring can be provided in the annular groove to prevent leakage. The fourth sleeve 34 is used for sealing connection to the mechanical seal cover 2. The fourth sleeve 34 can be connected to the mechanical seal cover 2 directly or through the end cover 36. To ensure sealing, an O-ring is provided between the fourth sleeve 34 and the mechanical seal cover 2 or between the fourth sleeve 34 and the end cover 36. Mounted on the fourth sleeve 34 is a second stationary ring 341, which provides a sliding seal with the second dynamic ring 331. The second stationary ring 341 can be mounted radially outward or axially on the fourth sleeve 34. The fourth sleeve 34 includes an annular groove to accommodate the second stationary ring 341, which can be fitted with an O-ring to prevent leakage. Because the fourth sleeve 34 remains stationary relative to the mechanical seal cover 2, the second stationary ring 341 also remains stationary relative to the mechanical seal cover 2. The second dynamic ring 331 and the second stationary ring 341 form a second mechanical seal friction pair, capable of maintaining a seal while in relative motion.
[0034] One end of the first compensation spring 37 abuts the end of the second sleeve 32 away from the first static ring 321, and the other end of the first compensation spring 37 abuts the mechanical seal 2. Note that this abutment can be made directly or indirectly against the fourth sleeve 34 connected to the mechanical seal 2. The first compensation spring 37 provides axial pressure between the first dynamic ring 311 and the first static ring 321, ensuring a tight fit between the first dynamic ring 311 and the first static ring 321, ultimately improving the sealing effect. One end of the second compensation spring 38 abuts the second dynamic ring 331, and the other end of the second compensation spring 38 abuts the third sleeve 33. The second compensation spring 38 provides axial pressure between the second dynamic ring 331 and the second static ring 341, ensuring a tight fit between the second dynamic ring 331 and the second static ring 341, ultimately improving the sealing effect.
[0035] In one embodiment, one end of the first compensation spring 37 abuts against the fourth sleeve 34 , the other end of the first compensation spring 37 abuts against the second sleeve 32 , and the fourth sleeve 34 is directly or indirectly fixedly connected to the mechanical cover 2 .
[0036] In one embodiment, an end cap 36 with a central opening is further included. The first axial surface of the end cap 36 is used for sealing connection with the machine seal cover 2. An O-ring may be disposed between the end cap 36 and the machine seal cover 2 to enhance the sealing effect. Furthermore, the end cap 36 may be fastened to the machine seal cover 2 via first screws 7, which are evenly distributed circumferentially. The second axial surface of the end cap 36 is sealed to the fourth shaft sleeve 34. An O-ring may be disposed between the end cap 36 and the fourth shaft sleeve 34 to enhance the sealing effect. Furthermore, the fourth shaft sleeve 34 may be fastened to the end cap 36 via second screws 8, which are evenly distributed circumferentially. The inner diameter side of the end cap 36 is sealed to the second shaft sleeve 32. An O-ring may be disposed between the end cap 36 and the second shaft sleeve 32 to enhance the sealing effect.
[0037] In one embodiment, a coolant outlet and a coolant inlet are radially disposed on the end cap 36. The first, second, and fourth shaft sleeves 31, 32, and 34 form a cooling chamber. The coolant outlet and the coolant inlet communicate with each other, allowing coolant to enter the cooling chamber through the coolant inlet, thereby cooling the first and second mechanical seal friction pairs. The coolant inlet and the coolant outlet are connected to a coolant tank 91 via a connecting pipe 94 (which can be a metal hose). The coolant tank 91 is connected to the coolant inlet via an inlet valve 93. The coolant tank 91 may also be equipped with a matching liquid level gauge 92, which displays the coolant content within the tank 91. The liquid level gauge 92 can be a magnetic flap level gauge.
[0038] In one embodiment, a coolant (antifreeze) is used to cool and lubricate the friction pair, and the problem of no fresh water supply for salt mining ships is solved by taking advantage of the antifreeze's low freezing point in winter and low volatility in summer.
[0039] In one embodiment, the third sleeve 33 is located in the cooling chamber, and a spiral groove 332 is provided on the outer diameter side of the third sleeve 33. The spiral groove 332 is located in the cooling chamber. The spiral groove 332 can form a driving force for the flow of coolant under the rotation of the third sleeve 33. The coolant is pumped by the spiral groove 332 to self-circulate between the cooling chamber and the coolant tank 91, without the need for a separate external circulating water pump.
[0040] In one embodiment, the third sleeve 33 is provided with a mounting groove for accommodating the second compensation spring 38, one end of the second compensation spring 38 abuts the third sleeve 33, and the other end of the second compensation spring 38 abuts the second dynamic ring 331. A pad may also be provided between the second compensation spring 38 and the second dynamic ring 331.
[0041] In one embodiment, an expansion sleeve 4 is further included. The portion of the first sleeve 31 extending beyond the fourth sleeve 34 is connected to the expansion sleeve 4. The expansion sleeve 4 is used to secure the first sleeve 31 to the drive shaft 5, so that rotation of the drive shaft 5 drives rotation of the first sleeve 31. The expansion sleeve 4 can be a tapered sleeve. This tapered structure allows axial pressure to be converted into radial pressure to compress the first sleeve 31 and the drive shaft 5.
[0042] In one embodiment, a fifth sleeve 35 is further included. The fifth sleeve 35 is used to be sleeved between the inner diameter side of the first sleeve 31 and the outer diameter side of the transmission shaft 5. The fifth sleeve 35 and the transmission shaft 5 as well as the fifth sleeve 35 and the first sleeve 31 are sealed. The sealing connection can use an O-ring to seal the gaps between the impeller 1, the first sleeve 31, the fifth sleeve 35 and the transmission shaft 5 to avoid leakage.
[0043] In one embodiment, the expansion connection sleeve 4 includes an arc sleeve 43 and a first compression sleeve 41 and a second compression sleeve 42 located on both sides of the arc sleeve 43. The inner diameter side of the first compression sleeve 41 and the second compression sleeve 42 is provided with a semi-arc that matches the outer diameter side of the arc sleeve 43. The first compression sleeve 41 and the second compression sleeve 42 are connected by a compression screw. The compression screw adopts a third screw 44. By rotating the third screw 44, the axial position between the first compression sleeve 41 and the second compression sleeve 42 can be adjusted, and the pressure is converted into radial pressure under the cooperation of the semi-arc and the arc sleeve 43, thereby pressing the first sleeve 31 onto the drive shaft 5 or disassembling it when repair / replacement is needed.
[0044] In one embodiment, the first dynamic ring 311 and the second dynamic ring 331 are made of cemented carbide YWN8, and the first stationary ring 321 and the second stationary ring 341 are made of cemented carbide YWN6. The main components of YWN8 and YWN6 include tungsten carbide (WC) and cobalt (Co), and may sometimes also contain nickel (Ni). This type of alloy has the advantages of high hardness, wear resistance, high temperature resistance, low linear expansion coefficient, low friction coefficient, and good assembly performance. It has good wear resistance, corrosion resistance, long service life, and good toughness and service life. In addition, YWN8 has higher strength and hardness than YWN6, and YWN8 has better impact resistance and vibration resistance than YWN6, but YWN8 has lower wear resistance than YWN6.
[0045] In one embodiment, the machine seal cover 2, the end cover 36 and the expansion connection sleeve 4 are made of S22053 material; the first compensation spring 37 and the second compensation spring 38 are made of Hastelloy C-276; the O-ring is made of fluorosilicone rubber; and each screw is made of A4-80.
[0046] Recombination Figures 1 to 4As shown, the present invention also provides a salt extraction pump, comprising an impeller 1, a mechanical seal cover 2, and the double-end seal structure 3 described above. The impeller 1 is used to be mounted on a drive shaft 5, which is located inside the pump casing. The drive shaft 5 transmits power to the impeller 1. The mechanical seal cover 2 is used to seal the pump casing. The first shaft sleeve 31 is sealed to the drive shaft 5. The second shaft sleeve 32 and the fourth shaft sleeve 34 are sealed to the mechanical seal cover 2. The second dynamic ring 331 is sealed to the first shaft sleeve 31, and the second static ring 341 is sealed to the fourth shaft sleeve 34. A first mechanical seal friction pair consisting of the first dynamic ring 311 and the first static ring 321 and a second mechanical seal friction pair consisting of the second dynamic ring 331 and the second static ring 341 are formed. The double-end seal structure 3 completes the sealing of the drive shaft 5 passing through the mechanical seal cover 2.
[0047] In one embodiment, there is a first gap between the impeller 1 and the mechanical cover 2, such as Figure 1 As shown in S, there is a second gap between the inner diameter side of the mechanical seal cover 2 and the double end face sealing structure 3, as shown in Figure 1 The first clearance S is 30mm~40mm, and the second clearance is 35mm~40mm. Figure 1 As shown, the salt slurry enters the first gap and the second gap between the outer side of the first mechanical seal friction pair and the mechanical seal cover 2 along the slurry leakage direction. The centrifugal force of the impeller 1 in the salt pump is used to quickly throw out the salt slurry in the first gap and the second gap, and at the same time, the heat generated by the first mechanical seal friction pair is also taken away.
[0048] In one embodiment, the first gap and the second gap are connected through a tapered channel, and the opening angle of the tapered channel is as follows: Figure 1 The open structure of the conical channel makes it easy for large-diameter salt ore to enter the outside of the first mechanical seal friction pair, and also makes it easy to use the centrifugal force of the impeller 1 to throw the large-diameter salt ore away from the outside of the first mechanical seal friction pair.
[0049] In one embodiment, the double seal structure 3 is installed as follows: first, position the stopper 6 over the shoulder of the drive shaft 5, loosen the expansion joint 4, and position the double seal structure 3 over the drive shaft 5, pressing against the stopper 6. The first screw 7 is connected to the mechanical seal cover 2. The drive shaft 5 is then connected to the impeller 1 of the salt pump to form an integrated structure, which is then docked with the pump casing of the salt pump. The coolant inlet and outlet are connected to the coolant tank 91 using connecting pipes 94, and an appropriate amount of coolant is added. The salt pump is then cranked, the expansion joint 4 is tightened, and the inlet valve 93 is opened.
[0050] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only intended to help understand the method and core concept of the present invention. At the same time, those skilled in the art will find that the specific implementation methods and application scopes may vary based on the concept of the present invention. In summary, the contents of this specification should not be construed as limiting the present invention.
Claims
1. A double-end sealing structure, characterized in that: include: a first sleeve, the first sleeve being used for sealingly connecting to the transmission shaft, and a first dynamic ring being mounted on the first sleeve; a second sleeve, the second sleeve being used for sealing connection to the machine seal cover, and the second sleeve being provided with a first stationary ring for sliding sealing with the first dynamic ring; a third shaft sleeve, the third shaft sleeve being located in the cavity between the first shaft sleeve and the second shaft sleeve, the third shaft sleeve being connected to the first shaft sleeve, and a second dynamic ring being mounted on the third shaft sleeve; a fourth sleeve, the fourth sleeve being used for sealing connection to the machine cover, and the fourth sleeve being provided with a second static ring for sliding sealing with the second dynamic ring; a first compensation spring, the first compensation spring being used to provide axial pressure between the first dynamic ring and the first static ring; and a second compensation spring, wherein the second compensation spring is used to provide axial pressure between the second dynamic ring and the second static ring.
2. The double-end face sealing structure according to claim 1, characterized in that: One end of the first compensation spring abuts against the fourth shaft sleeve, and the other end of the first compensation spring abuts against the second shaft sleeve.
3. The double-end face sealing structure according to claim 2, characterized in that: It also includes an end cover with a central opening, wherein the first axial surface side of the end cover is used for sealing connection with the machine seal cover, the second axial surface side of the end cover is sealed connected with the fourth sleeve, and the inner diameter side of the end cover is sealed connected with the second sleeve.
4. The double-end sealing structure according to claim 3, characterized in that: The end cover is radially provided with a coolant outlet and a coolant inlet. The first shaft sleeve, the second shaft sleeve and the fourth shaft sleeve form a cooling chamber. The coolant outlet and the coolant inlet are connected to the cooling chamber.
5. The double-end sealing structure according to claim 4, characterized in that: A spiral groove is provided on the outer diameter side of the third sleeve, and the spiral groove is used to generate power for the flow of coolant.
6. The double-end sealing structure according to claim 1, characterized in that: The third sleeve is provided with a mounting groove for accommodating the second compensation spring. One end of the second compensation spring abuts against the third sleeve, and the other end of the second compensation spring abuts against the second movable ring.
7. The double-end sealing structure according to claim 1, characterized in that: It also includes an expansion connecting sleeve, wherein the portion of the first sleeve extending out of the fourth sleeve is connected to the expansion connecting sleeve, and the expansion connecting sleeve is used to fasten the first sleeve to the transmission shaft.
8. The double-end sealing structure according to claim 7, characterized in that: It also includes a fifth sleeve, which is used to be sleeved between the inner diameter side of the first sleeve and the outer diameter side of the transmission shaft. The fifth sleeve and the transmission shaft are sealed and connected to each other as well as to the first sleeve.
9. A salt mining pump, characterized in that: include: an impeller, the impeller being mounted on a transmission shaft; A machine sealing cover, the machine sealing cover is used for sealingly connecting with the pump casing; And the double-end face sealing structure according to any one of claims 1 to 8, wherein the first sleeve is sealed and connected to the transmission shaft, the second sleeve and the fourth sleeve are sealed and connected to the machine cover, the second dynamic ring is sealed and connected to the first sleeve, and the second static ring is sealed and connected to the fourth sleeve.
10. The salt mining pump according to claim 9, characterized in that: There is a first gap between the impeller and the mechanical seal cover, and a second gap between the inner diameter side of the mechanical seal cover and the double-end face sealing structure. The first gap is 30mm~40mm, and the second gap is 35mm~40mm; the first gap and the second gap are connected through a tapered channel, and the opening angle of the tapered channel is 70°~80°.