Rotary ring and double-cavity mechanical seal

Abstract

The application discloses a dynamic ring, which comprises a dynamic ring body, an installation part arranged on one side of the dynamic ring body, and a gear ring groove with a gear ring friction surface arranged on the other side of the dynamic ring body; a rough wall surface is arranged on the inner wall surface of the gear ring groove; long-short type blade radiating fins are arranged below the gear ring friction surface; the cross sections of the radiating fins are all trapezoidal; the radiating fins are sequentially stacked from small to large along the axial direction according to the size of the radian, and the design principle of the fins is met. The application also discloses a double-cavity mechanical seal, which is a double-cavity double-end-face sealing structure, has double sealing cavities and a dynamic ring flushing sealing isolation cavity, greatly improves the sealing performance and the flushing efficiency, and enables the sealing structure to bear certain axial and radial runout through the interaction of compression springs and compensation springs. The sealing structure has the advantages of simple structure, convenient disassembly and maintenance, and long service life.

Description

Technical Field

[0001] This invention relates to the field of mechanical seal technology, specifically a dynamic ring and dual-cavity mechanical seal. Background Technology

[0002] Mechanical seals are devices used for shaft sealing of rotating fluid machinery. They mainly consist of compensating springs, rotating rings, stationary rings, and stationary ring seats. The rotating rings and stationary rings cooperate to form a dynamic friction pair. Effectively cooling the dynamic friction surfaces is a necessary condition for ensuring the normal operation of mechanical seals, and existing technologies cannot solve this problem.

[0003] Mechanical seals can be classified into single-face seals and multi-face seals based on the number of sealing pairs. A single-face seal consists of a pair of sealing faces and does not require an external sealing fluid supply system, but it must be equipped with a self-flushing system. It is easy to manufacture and disassemble and has a simple structure. A multi-face seal has two or more pairs of sealing faces and requires the introduction of sealing fluid for sealing, lubrication, flushing, and cooling. Compared with a single-face mechanical seal, the biggest advantage of a multi-face seal is that it has an additional sealing face, which reduces leakage and the stress on the sealing face is more reasonable. The disadvantages are that it is more difficult to manufacture, has a more complex structure, and is larger in size. Once a seal leakage occurs, it is extremely difficult to troubleshoot. Summary of the Invention

[0004] This invention provides a dynamic ring and a dual-chamber mechanical seal. The dynamic ring can flush and cool the dynamic friction pair of the rotating dynamic and stationary rings and the isolation chamber, which can improve flushing efficiency, provide better sealing, and has a simple structure, is easy to disassemble and maintain, and has a long service life.

[0005] The technical solution adopted to achieve the above-mentioned objectives of this invention is as follows:

[0006] A rotating ring has a mounting portion on one side of its body, which includes a keyway and a compression spring cavity. A compression spring can be installed in the compression spring cavity. The keyway and the compression spring are used to form a fixed connection with the rotating ring seat. The other side of the rotating ring body is a gear-shaped friction surface with two sets of gear-shaped grooves. The inner wall of the gear-shaped grooves is rough. Below the gear-shaped friction surface are long and short blade heat sinks that are evenly distributed radially along the rotating ring body. The long and short blade heat sinks are designed and stacked using the rib design principle.

[0007] There are four sets of flat keyways and compression spring cavities, which are evenly distributed along the radial direction of the moving ring body. There are two sets of gear annular grooves, and the axis of the gear annular grooves coincides with the axis of the moving ring.

[0008] Furthermore, the ratio of the depth of the gear annular groove to the width of the moving ring is 1:3. The ratio of the inner diameter of the gear annular groove to the diameter of the moving ring body is 5:6. The ratio of the outer diameter of the gear annular groove to the diameter of the moving ring body is 9:10. The ratio of the depth of the gear annular groove to the width of the moving ring body is 2:5.

[0009] Below the gear-shaped friction surface of the moving ring body, there are long and short blade heat sinks, which are designed based on the fin principle.

[0010] Furthermore, the ratio of the blade root width to the width of the moving ring body of the long and short blade heat sink is 1:70, and the ratio of the blade tip width to the blade root width is 1:4. Its thickness varies uniformly along the blade curvature direction. The long and short blade heat sinks are stacked sequentially along the axial direction of the moving ring body in descending order of curvature to form long and short blade heat sink groups. The ratio of the stacking spacing of the long and short blade heat sink groups to the width of the moving ring is 1:34. There are eight long and short blade heat sink groups in total, each group consisting of nine long and short blades. The long and short blade heat sink groups formed after stacking are uniformly distributed radially along the moving ring body. The angle β of each stacked blade group is 50°, and the angle α between each stacked blade group is 45°.

[0011] Furthermore, the ratio of the radius of the long and short blade heat sink to the width of the moving ring is 2:3 to 1:1, the arc of the long and short blade heat sink is 2.5-16 rad, the angle of the long and short blade heat sink is 15-69°, and the ratio of the mounting diameter of the long and short blade heat sink to the diameter of the moving ring is 4:5.

[0012] A dual-chamber mechanical seal includes the aforementioned rotating ring, impeller gland, sealing housing, sealing gland, shaft sleeve, drive shaft, stationary ring, and rotating ring assembly. The drive shaft is installed between the impeller gland and the sealing gland and extends from the sealing gland. The dual-chamber mechanical seal is spatially symmetrical, with an isolation chamber formed between the stationary ring, rotating ring, and shaft sleeve, and two sealing chambers formed between the stationary ring, shaft sleeve, rotating ring, rotating ring assembly, sealing gland, and sealing housing.

[0013] The double-chamber mechanical seal has a stationary ring at the end away from the sealing gland, and a rotating ring and rotating ring assembly are provided on the side of the stationary ring closer to the sealing gland. The gear-shaped friction surface of the rotating ring is in direct contact with the stationary friction surface of the stationary ring, forming a rotating dynamic seal friction pair. The rotating ring assembly is fixedly connected to the bushing by a second fixing bolt, and the rotating ring assembly and the bushing are fixedly connected to the drive shaft by fixing bolts.

[0014] Along the drive shaft, from left to right, the rotating ring body, key, compression spring, rotating ring washer, compensating spring, and compensating spring washer are arranged sequentially. The rotating ring assembly, away from the gear annular friction surface and near the sealing cover, is fixed to the bushing by bolts, forming a secondary sealing cavity between itself, the stationary ring, the bushing, and the housing. One end of the rotating ring assembly has a sliding mounting groove for mounting the rotating ring, compensating spring, key, rotating ring washer, and compensating spring washer. A keyway is provided on the sliding mounting groove. The rotating ring body and the rotating ring seat are fixedly connected in a relatively static manner by the key. A compression spring cavity is provided below the key.

[0015] Furthermore, the upper left corner of the flat key has a flat key angle γ, wherein the flat key angle γ = 5° to 15°.

[0016] Furthermore, three sets of compression springs are evenly arranged inside the compression spring cavity, and a mounting threaded hole is provided at the contact part between the flat key and the moving ring seat. There are a total of four sets of mounting threaded holes, which are evenly distributed along the radial direction of the moving ring body.

[0017] The compression spring provides a radial force to the flat key, ensuring it remains precisely fitted against the inner wall of the rotating ring seat. This prevents leaking media from entering the compensation spring cavity through the mounting threaded hole, ensuring the compensation spring is in a relatively sealed state. The compression spring also provides axial compensation to the dynamic seal friction surface, simultaneously providing an axial force to ensure the rotating ring body and the rotating ring seat remain relatively stationary as they rotate with the drive shaft. Furthermore, it ensures that the gear-ring friction surface of the rotating ring body and the static friction surface of the stationary ring remain in contact during relative rotation. The dynamic seal friction surface includes both the gear-ring friction surface and the static friction surface. The interaction between the compression spring and the compensation spring also allows the dual-cavity mechanical seal to accommodate certain axial and radial runout.

[0018] The stationary ring is directly fixed to the sealing shell by fixing bolts, dividing the sealing cavity into two chambers, left and right. The left sealing cavity is the first sealing cavity, and the right sealing cavity forms the second sealing cavity. The left sealing cavity is the main sealing cavity, and the right sealing cavity is the secondary sealing cavity. The left sealing cavity contains the leakage medium, and the right sealing cavity, while forming the second sealing protection, can also act as an auxiliary seal to prevent external impurities from entering the main sealing cavity.

[0019] An isolation cavity is formed between the stationary ring, the rotating ring, and the bushing. The stationary ring and the sealing housing are provided with flushing holes that communicate with the isolation cavity. The dynamic seal friction surface and the long and short blade heat sink can be flushed directly through the flushing holes, which greatly improves the flushing efficiency.

[0020] By employing the above technical solutions, the beneficial effects of the present invention are as follows:

[0021] 1. The moving ring provided by the present invention has a gear-shaped friction surface, which reduces the area of ​​the dynamic sealing friction surface. The gear-shaped groove wall is a rough wall, which increases the heat exchange area and can achieve a better cooling effect.

[0022] 2. The dynamic ring provided by the present invention has long and short blade heat sinks, which are stacked axially and evenly distributed radially. The cross-section of the blades is designed as a trapezoidal structure, which has good thermal conductivity and can quickly remove the heat generated by the dynamic friction pair.

[0023] 3. In this invention, the rotating ring and the rotating ring seat are fixedly connected by a flat key. There is a compression spring below the flat key, which works in conjunction with the compensation spring. While fixing the rotating ring, the compensation spring can compensate the friction surface axially and radially, achieving a better sealing effect. It can also prevent particles from entering the sealing chamber of the compensation spring and causing accumulation. The interaction between the compression spring and the compensation spring can also enable the device to adapt to a certain radial and axial runout, always keeping the sealing surface in contact and preventing mechanical seal failure.

[0024] 4. The double-cavity double-end-face sealing structure provided by the present invention is symmetrical, simple and lightweight, easy to maintain, and can achieve a good sealing effect.

[0025] 5. In this invention, a sealed isolation cavity is formed between the dynamic ring, the stationary ring, and the bushing. The stationary ring and the sealing housing have flushing holes that connect to the isolation cavity, which can directly assist in flushing the dynamic seal friction surface and the long and short blade heat sink, thus achieving a better cooling effect.

[0026] To make the above and other objects, features and advantages of the present invention more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 The diagram shows the dynamic ring structure provided by this invention;

[0029] Figure 2 A partial sectional view of the dynamic ring provided by this invention;

[0030] Figure 3 for Figure 2 Enlarged schematic diagram of the structure at point A in the middle;

[0031] Figure 4 for Figure 1Enlarged schematic diagram of the structure at point B;

[0032] Figure 5 for Figure 2 Enlarged schematic diagram of the structure at point C;

[0033] Figure 6 A half-sectional view of the dual-cavity mechanical seal provided by the present invention;

[0034] Figure 7 for Figure 6 Enlarged schematic diagram of the structure at point D.

[0035] The reference numerals in the above figures are as follows: 1. Moving ring body; 2. Mounting part; 3. Gear annular friction surface; 4. Gear annular groove; 5. Annular inner wall surface; 6. Long and short blade heat sink; 7. Axis centerline; 8. Static friction surface; 9. Anti-rotation pin; 10. Static ring; 11. Isolation cavity; 12. Bushing; 13. Moving ring washer; 14. Compensating spring; 15. First fixing bolt; 16. Moving ring seat; 17. Second fixing bolt; 18. Flat keyway; 19. Compression spring; 20. Compression spring cavity; 21. Sliding mounting groove; 22. Compensating spring washer; 23. Sealing gland; 24. Third fixing bolt; 25. Sealing housing; 26. Fourth fixing bolt; 27. Flushing fluid inlet; 28. Fifth fixing bolt; 29. ​​Impeller gland; 30. Drive shaft; 31. Flushing fluid outlet; 32. Left sealing cavity; 33. Right sealing cavity. Detailed Implementation

[0036] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0037] It should be noted that in the description of this invention, the terms "first," "second," etc., are used only for descriptive purposes and to distinguish similar objects; there is no order between them, nor should they be construed as indicating or implying relative importance. Furthermore, in the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0038] Example: Combining Figure 1-7As shown, Embodiment 1 discloses a moving ring. The moving ring body 1 has a mounting part 2 on one side, the mounting part 2 has a flat keyway 18 and a compression spring cavity 20. The other side of the moving ring body 1 is a gear ring friction surface 3. Two sets of gear ring grooves 4 are opened on the gear ring friction surface 3. The annular inner wall surface 5 of the gear ring groove 4 is a rough wall surface. Below the gear ring friction surface 3, there are long and short blade heat sinks 6 designed and stacked according to the rib design principle and evenly distributed along the radial direction of the moving ring.

[0039] like Figure 7 As shown, the mounting part 2 of the moving ring body 1 is provided with a flat keyway 18 and a compression spring cavity 20. Optionally, there are four sets of flat keyways 18 and compression spring cavities 20, which are evenly distributed along the radial direction of the moving ring body 1.

[0040] like Figure 3 As shown, the annular inner wall 5 of the gear annular groove 4 is a rough wall surface. The gear annular groove 4 is formed on the gear annular friction surface 3, which reduces the area of ​​the gear annular friction surface 3. The rough inner wall 5 increases the heat dissipation area, thus enhancing heat conduction. Two sets of gear annular grooves 4 are formed on the gear annular friction surface 3, and the axis 7 of the two sets of gear annular grooves 4 coincides with the axis of the moving ring.

[0041] Optionally, the ratio of the depth of the gear annular groove 4 to the width of the moving ring body 1 is 1:3. The ratio of the inner diameter of the gear annular groove 4 to the diameter of the moving ring body is 5:6. The ratio of the outer diameter of the gear annular groove 4 to the diameter of the moving ring body is 9:10. The ratio of the width to the depth of the gear annular groove 4 is 2:5.

[0042] like Figure 4 As shown, below the gear annular friction surface 3, there are long and short blade heat sinks 6 that are evenly distributed radially along the moving ring body 1. The long and short blade heat sinks 6 are designed according to the rib principle and impeller design principle.

[0043] Optionally, the ratio of the radius of the long and short blade heat sink 6 to the width of the moving ring is 2:3 to 1:1. The arc of the long and short blade heat sink 6 is 2.5-16 rad. The angle of the long and short blade heat sink 6 is 15-69°. The ratio of the mounting diameter of the long and short blade heat sink 6 to the diameter of the moving ring is 4:5.

[0044] The ratio of the width of the blade root of the long and short blade heat sink 6 to the width of the moving ring body 1 is 1:70, and the ratio of the blade tip width to the blade root width is 1:4. The thickness of the long and short blade heat sink 6 varies uniformly along its blade curvature direction. The long and short blade heat sink 6 are stacked sequentially along the axial direction of the moving ring body 1 in order of decreasing curvature to form a long and short blade heat sink group. The ratio of the stacking spacing of the long and short blade heat sink 6 to the width of the moving ring is 1:34. There are eight long and short blade heat sink groups in total, and each group has nine long and short blades. The long and short blade heat sink groups formed by stacking the long and short blade heat sinks are uniformly distributed along the radial direction of the moving ring body. The angle β of each stacked blade group is 50°, and the angle α between each stacked blade group is 45°. The long and short blade heat sink 6 enhances thermal conductivity and, as it rotates with the drive shaft 30, increases the heat exchange efficiency between the annular friction surface 3 of the moving ring gear and the flushing fluid. The cross-section of the long and short blade heat sink 6 is trapezoidal. Starting from the moving friction pair, the heat sinks are arranged from large to small along the axial direction according to the size of the arc, which conforms to the fin design principle and can increase convective heat transfer.

[0045] Example 2 discloses a dual-cavity mechanical seal, such as Figure 6 As shown, the mechanical seal is installed between the drive shaft 30 and the sealing cover 23, and is placed on the bushing 12. The drive shaft 30 is installed between the impeller cover 29 and the sealing cover 23, and extends out from the sealing cover 23. The dual-chamber mechanical seal includes a rotating ring body 1, a rotating ring assembly, and a stationary ring 10. An isolation chamber 11 is formed between the stationary ring 10, the rotating ring body 1, and the bushing 12. Two sealing chambers are formed between the stationary ring 10, the bushing 12, the rotating ring body 1, the rotating ring assembly, the sealing cover 23, and the sealing housing 25.

[0046] A stationary ring 10 is provided at one end of the sealing gland 23, away from the dual-chamber mechanical seal. A rotating ring and a rotating ring assembly are provided on the side of the stationary ring 10 closest to the sealing gland 23. Along the drive shaft, from left to right, the rotating ring assembly consists of a rotating ring body 1, a flat key 18, a compression spring 19, a rotating ring washer 13, a compensating spring 14, and a compensating spring washer 22. The rotating ring assembly is fixedly connected to the bushing 12 by a second fixing bolt 17, and the rotating ring assembly and bushing 12 are fixedly connected to the drive shaft 30 by a first fixing bolt 15.

[0047] One end of the moving ring assembly has a sliding mounting groove 21 for mounting the moving ring body 1 and the compensating spring 14. The mounting part 2 and the sliding mounting groove 21 are provided with a flat keyway 18. The moving ring body 1 and the moving ring seat 16 are fixedly connected to each other in a relatively static manner through the flat keyway 18.

[0048] Optionally, the upper left corner of the parallel key 18 has a parallel key angle γ, wherein the parallel key angle γ = 5-15°.

[0049] Below the flat key 18 is a compression spring cavity 20, within which three sets of compression springs 19 are evenly arranged. Above the flat key 18, at the contact point with the moving ring seat 16, are four sets of mounting threaded holes, evenly distributed radially. The three sets of compression springs evenly arranged within the compression spring cavity provide a radial force to the flat key 18, ensuring that the flat key 18 remains precisely fitted against the inner wall of the moving ring seat 16. This prevents leaking media from entering the compensation spring cavity 20 through the mounting threaded holes, thus preventing the entry and accumulation of media and particulate matter. The compensating spring 14 ensures a relatively sealed state, while the compression spring 19 provides axial compensation and an axial force to the dynamic seal friction surface. This ensures that the moving ring body 1 and the moving ring seat 16 remain relatively stationary as they rotate with the drive shaft 30. Simultaneously, it ensures that the gear-ring friction surface 3 of the moving ring body 1 and the static friction surface 8 of the stationary ring 10 remain in contact during relative rotation. The dynamic seal friction surface includes the gear-ring friction surface 3 and the static friction surface 8. The interaction between the compression spring 19 and the compensating spring 14 also allows the seal to adapt to certain axial and radial runout.

[0050] The stationary ring 10 is directly fixedly connected to the sealing housing 25 by the fourth fixing bolt 26, dividing the sealing cavity into two chambers 32 and 33. The left sealing chamber 32 is the first sealing chamber, and the right sealing chamber 33 forms the second sealing chamber. The left sealing chamber 32 is the main sealing chamber, and the right sealing chamber 33 is the secondary sealing chamber. The left sealing chamber 32 contains the leakage medium, while the right sealing chamber 33, while forming a second sealing protection, can also act as an auxiliary seal to prevent external impurities from entering the main sealing chamber. The gear-shaped friction surface 3 of the moving ring body 1 abuts against the stationary friction surface 8 of the stationary ring 10, forming a dynamic friction pair that can rotate relative to each other. An isolation cavity 11 is formed between the moving ring body 1, the stationary ring 10, and the bushing 12. The stationary ring 10 and the sealing housing 25 are provided with flushing holes 27 that communicate with the isolation cavity 11. The mechanical seal can directly flush the dynamic sealing friction surface 3 and the long and short blade heat sink 6 through the flushing holes, greatly improving the flushing efficiency.

[0051] The sealing device is symmetrical in space and has fourteen sets of sealing rubber rings distributed in key parts such as the dynamic ring body 1, the stationary ring 10, and the bushing 12. It can effectively prevent media leakage. The sealing device has a simple and compact structure and is easy to disassemble and maintain.

[0052] The working process of this invention is as follows:

[0053] The motor connected to the drive shaft 30 is started, and the drive shaft 30 drives the bushing 12, the rotating ring body 1, and the rotating ring assembly, which are fixedly connected to it, to begin rotating. The drive shaft 30 is equipped with a stationary ring anti-rotation pin 9, which can further prevent the stationary ring 10 from sliding relative to each other. The stationary ring 10 is directly fixedly connected to the sealing housing 25 through the fourth fixing bolt 26, dividing the sealing cavity into two chambers 32 and 33. The left sealing 32 is the first sealing cavity, and the right sealing cavity 33 forms the second sealing cavity. During operation, the left sealing cavity 32 is the main sealing cavity, and the right sealing cavity 33 is the secondary sealing cavity. The left sealing cavity 32 is the leakage medium sealing cavity. When the left sealing cavity 32 fails, the right sealing cavity 33 forms a secondary sealing cavity on the basis of the auxiliary seal, which constitutes a second sealing guarantee. While preventing the internal medium from leaking, it can also ensure that external air and other impurities can enter the main sealing cavity.

[0054] The rotating ring body 1 rotates with the drive shaft 30. The gear ring friction surface 3 of the rotating ring body 1 abuts against the static friction surface 8 of the stationary ring 10, forming a dynamic friction pair that rotates relative to each other. Lubricating oil is installed in the gear ring groove 4 to ensure that the oil film on the dynamic sealing friction surface remains intact when the rotating ring body 1 and the stationary ring 10 rotate relative to each other, thereby extending the service life of the sealing device.

[0055] An isolation cavity 11 is formed between the rotating ring body 1, the stationary ring 10, and the bushing 12. When the rotating rings rotate relative to each other, the heat generated by the relative rotation of the rotating rings can be directly introduced into the rotating ring isolation cavity 11 through the long and short blade heat sink below the gear ring friction surface 3 of the rotating ring body 1. The stationary ring 10 and the sealing housing 25 are provided with a 27 that communicates with the isolation cavity 11. During operation, the flushing fluid enters the rotating ring isolation cavity 11 through the flushing hole 27 and directly flushes the dynamic sealing friction surface 3 and the long and short blade heat sink 6. After flowing out through the flushing fluid outlet 31 and entering the external heat exchange device for cooling, it enters the isolation cavity 11 through the flushing fluid inlet 27 for heat exchange. This cycle is repeated, which greatly improves the flushing efficiency.

[0056] During operation, the compression spring 19 always provides a radial thrust to the flat key 18, ensuring that the upper surface of the flat key is in precise contact with the rotating ring seat 16. The compensation spring 14 always provides an axial thrust to the rotating ring body 1 and the flat key 18, ensuring that the end face of the rotating ring mounting part 2 and the right end face of the flat key 18 are in contact with the rotating ring gasket 13. The compensation spring cavity 20 always maintains a self-sealing state. When wear occurs on the dynamic seal friction surface, the axial thrust provided by the compensation spring 14 can push the flat key 18 to move axially along the flat key's angle, further compressing the compression spring 19 to push the rotating ring body 1 for axial compensation. When axial or radial runout occurs, the compensation spring 14 and the compression spring 19 can also react quickly. The compensation spring 14 provides axial compensation, and the compression spring 19 provides radial compensation. As the wear of the dynamic seal friction surface gradually increases, the radial thrust provided by the compression spring 19 will also gradually increase, effectively preventing sealing failure caused by medium leakage due to wear of the sealing surface.

[0057] The embodiments described above are preferred embodiments of the present invention, but the present invention is not limited to the above embodiments. Any obvious improvements, substitutions or modifications that can be made by those skilled in the art without departing from the essence of the present invention shall fall within the protection scope of the present invention.

[0058] Specific embodiments have been used to illustrate the principles and implementation methods of this invention. The descriptions of the embodiments above are only for the purpose of helping to understand the method and core ideas of this invention. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the ideas of this invention. Therefore, the content of this specification should not be construed as a limitation of this invention.

Claims

1. A dynamic ring, characterized in that, The device includes a rotating ring body (1), one side of which is provided with a mounting part (2), and the other side is a gear annular friction surface (3); the gear annular friction surface (3) is provided with at least two sets of gear annular grooves (4), and the annular inner wall surface (5) of the gear annular groove (4) is a rough wall surface; the mounting part (2) is provided with a flat key (18), a compression spring cavity (20) and mounting grooves for the flat key (18), and multiple mounting grooves for the flat key (18), the compression spring cavity (20) and the flat key (18) are evenly distributed along the radial direction of the rotating ring body (1); the gear annular groove (4) is provided with at least two sets of gear annular grooves (4), and the gear annular groove (5 ... The ratio of the depth to the width of the moving ring body (1) is 1:3; two sets of gear annular grooves (4) are provided, and the axis of both sets of gear annular grooves (4) coincides with the axis (7) of the moving ring; the ratio of the inner diameter of the gear annular groove (4) to the diameter of the moving ring body (1) is 5:6, and the ratio of its outer diameter to the diameter of the moving ring body (1) is 9:10; the ratio of the width to the depth of the gear annular groove (4) is 2:5; the inner sidewall of the moving ring body (1) is provided with long and short blade heat sinks (6) evenly distributed along its axial direction, and the long and short blade heat sinks (6) adopt... The design is based on the principle of fin design and superposition; the ratio of the width of the blade root of the long and short blade heat sink (6) to the width of the moving ring body (1) is 1:70, and the ratio of the width of the blade tip to the width of the blade root is 1:4; the thickness of the long and short blade heat sink (6) varies uniformly along its blade curvature direction, and the long and short blade heat sink (6) are superimposed sequentially along the axial direction of the moving ring body (1) in order of decreasing curvature to form a long and short blade heat sink group; the ratio of the superposition spacing of the long and short blade heat sink group to the width of the moving ring body (1) is 1:34, and the long and short blade heat sink group Eight groups are set up, each group containing nine long and short blades. The long and short blade heat sink groups formed by stacking the long and short blade heat sinks (6) are evenly distributed along the radial direction of the moving ring body (1). The angle β of each stacked blade is 50°, and the angle α between each stacked blade is 45°. The ratio of the radius of the long and short blade heat sink (6) to the width of the moving ring body (1) is 2:3 to 1:1, its arc is 2.5 to 16 rad, and its angle is 15° to 69°. The ratio of the installation diameter of the long and short blade heat sink (6) to the diameter of the moving ring body (1) is 4:

5.

2. A dual-cavity mechanical seal, wherein the dual-cavity mechanical seal is a dual-cavity, dual-end-face sealing structure, characterized in that, The system includes the dynamic ring body (1), impeller rear cover plate (29), sealing housing (25), sealing gland (23), bushing (12), drive shaft (30), stationary ring (10), and dynamic ring assembly as described in claim 1. The stationary ring (10) is provided at one end of the dual-cavity mechanical seal away from its sealing gland (23). The dynamic ring body (1) and the dynamic ring assembly are provided on the side of the stationary ring (10) close to the sealing gland (23). The gear ring friction surface (3) of the dynamic ring body (1) is in direct contact with the static friction surface (8) of the stationary ring (10) to form a dynamic sealing friction pair that can rotate relative to each other. The dynamic ring assembly is fixedly connected to the bushing (12) by a second fixing bolt (17), and the dynamic ring assembly and the bushing (12) are fixedly connected to the drive shaft (30) by a first fixing bolt (15).

3. The dual-cavity mechanical seal according to claim 2, characterized in that, The moving ring assembly includes a flat key (18), a moving ring washer (13), a compensating spring (14), a moving ring seat (16), and a compensating spring washer (22). The end of the moving ring assembly away from the gear annular friction surface (3) is fixedly connected to the bushing (12) by a fixing bolt (17). The end of the moving ring assembly near the stationary ring (10) is provided with a sliding mounting groove (21) for mounting the moving ring body (1), the compensating spring (14), the flat key (18), the moving ring washer (13), and the compensating spring washer (22).

4. The dual-cavity mechanical seal according to claim 3, characterized in that, The key (18) has a key angle γ, which is 5°~15°. The moving ring assembly is arranged sequentially along the drive shaft (30). The moving ring body (1) and the moving ring seat (16) are fixedly connected by the key (18). The inner side of the key (18) is provided with a compression spring cavity (20). The contact part between the key (18) and the moving ring seat (16) is provided with a mounting thread hole. There are four sets of mounting thread holes, which are evenly distributed along the radial direction of the moving ring body (1). Compression springs (19) are evenly arranged in the compression spring cavity (20). The compression spring (19) is used to provide a radial force to the flat key (18) so that the flat key (18) always remains in contact with the inner wall surface of the moving ring seat (16). The compression spring (19) is used to provide axial compensation for the dynamic sealing friction pair and at the same time provide an axial force to the dynamic sealing friction pair to ensure that the moving ring body (1) and the moving ring seat (16) always remain relatively stationary during the rotation with the transmission shaft (30). At the same time, it can ensure that the gear ring friction surface (3) of the moving ring body (1) and the static friction surface (8) of the stationary ring (10) always remain in contact during the relative rotation.

5. The dual-cavity mechanical seal according to claim 2, characterized in that, The stationary ring (10) and the sealing housing (25) are fixedly connected by the fourth fixing bolt (26), dividing the sealing cavity into a left sealing cavity (32) and a right sealing cavity (33). The left sealing cavity (32) is the first sealing cavity, and the right sealing cavity (33) forms the second sealing cavity. The left sealing cavity (32) contains the leakage medium. The right sealing cavity (33) forms the second sealing protection and can also act as an auxiliary seal to prevent external impurities from entering the left sealing cavity (32).

6. The dual-cavity mechanical seal according to claim 2, characterized in that, An isolation cavity (11) is formed between the stationary ring (10), the moving ring body (1) and the bushing (12). The stationary ring (10) and the sealing housing (25) are provided with a flushing hole (27) that communicates with the isolation cavity (11). The moving sealing friction pair and the long and short blade heat sink (6) can be flushed directly through the flushing hole.

Images