Shaft end sealing device for low-speed heavy-load equipment

Abstract

The utility model discloses a shaft end sealing device for low-speed heavy-load equipment, which comprises a first sealing assembly, a second sealing assembly, a sealing box and a shaft sleeve, the first sealing assembly is provided with a first moving ring arranged on the shaft sleeve and a first static ring arranged on the sealing box. A sealing protrusion which extends towards the first movable ring and abuts against the first movable ring is arranged on the outer side of the first static ring, a fluid lubricating groove is formed in the inner side of the end face of the sealing protrusion, and the inner side of the fluid lubricating groove is an open end. The fluid lubricating groove is formed in the inner side of the end face of the sealing convex, and the inner side of the fluid lubricating groove is an open end, so that lubricating fluid can be sucked into the end face in time during operation; under the low-speed and heavy-load working condition, heat generated by friction can be rapidly taken away by a large amount of lubricating fluid, the temperature of the sealing face is effectively reduced, and the overall operation efficiency and stability of equipment are improved. Lubricating fluid is sucked between the end faces, stable and sufficient lubricating media are continuously provided for the sealing faces of the movable ring and the static ring, and it is guaranteed that relative movement between the sealing faces is always in a good lubricating state.

Description

TECHNICAL FIELD

[0001] The utility model belongs to the technical field of shaft end sealing, specifically relates to a shaft end sealing device for low-speed heavy load equipment. BACKGROUND

[0002] As one of the key equipment in petroleum chemical industry, chemical fiber and pharmaceutical production, the sealing performance of low-speed heavy load equipment plays a vital role in the safety and stability of the entire production process. In order to effectively prevent the occurrence of leakage during the operation of such equipment, a mechanical sealing device is usually equipped inside the equipment. However, under the special working conditions of low speed (linear speed below 2m / s) and heavy load, the ordinary contact type mechanical seal exposes a series of serious problems. Long-term low-speed operation causes continuous accumulation of heat between the friction pairs, which in turn causes fluid vaporization between the friction pairs, resulting in dry friction of the sealing surface, aggravating the wear degree of the sealing surface, and even causing the sealing surface to collapse in extreme cases, seriously damaging the integrity and functionality of the sealing device.

[0003] At the same time, during the operation of the equipment, due to the inevitable swing of the shaft during rotation, relative motion occurs between the dynamic ring and the dynamic ring seat. In the connection structure of the dynamic ring and the dynamic ring seat, the dynamic ring pin groove and the dynamic ring transmission pin frequently fit and separate, and under the repeated action of long time and high frequency, the dynamic ring pin groove and the transmission pin are subjected to a certain degree of wear and damage. The existence of these problems, whether it is dry friction, wear, collapse of the sealing surface, or wear and damage of the dynamic ring connection structure, has a very adverse effect on the performance of the mechanical seal, greatly shortens the service life of the mechanical seal, increases the equipment maintenance cost and downtime risk, and in severe cases may cause production accidents, posing a major threat to the production efficiency and safety of the enterprise.

[0004] The above information disclosed in the background is only used to increase the understanding of the background of the present application, and therefore it can include prior art known to those skilled in the art. SUMMARY

[0005] The utility model discloses in view of the above problems in the prior art, propose a kind of shaft end sealing device for low-speed heavy load equipment, fluid lubrication groove is strengthened cooling and lubrication, improve the overall operation efficiency and stability of equipment.

[0006] To achieve the above utility model purposes, the utility model adopts the following technical solutions to be realized:

[0007] A kind of shaft end sealing device for low-speed heavy load equipment, comprising:

[0008] First sealing assembly, it is located between sealing box and shaft sleeve;

[0009] The first sealing assembly has a first dynamic ring arranged on the shaft sleeve, and a first static ring arranged on the sealing box;

[0010] A sealing convex extending towards the first dynamic ring is arranged on the outside of the first static ring and abuts against the first dynamic ring, and a fluid lubrication groove is arranged on the inner side of the end surface of the sealing convex, and the inner side of the fluid lubrication groove is an open end.

[0011] In some embodiments of the present application, a plurality of fluid lubrication grooves are arranged on the circumference of the end surface of the sealing convex, and the area between two adjacent fluid lubrication grooves is a dam area, and the ratio of the circumferential dimension of the inner side of the fluid lubrication groove to the circumferential dimension of the inner side of the dam area is 0.8-2.

[0012] In some embodiments of the present application, the depth of the fluid lubrication groove is 0.5-1.5 mm.

[0013] In some embodiments of the present application, the ratio of the radial dimension of the sealing convex to the radial dimension of the fluid lubrication groove is 2-3.

[0014] In some embodiments of the present application, the circumferential maximum dimension of the fluid lubrication groove is the central angle corresponding to the open end.

[0015] In some embodiments of the present application, the first sealing assembly has a first spring seat, an installation slot is arranged on the sealing box, the outer side of the first spring seat is located in the installation slot, and a gland abuts against one end of the first spring seat close to the atmosphere side.

[0016] In some embodiments of the present application, a second sealing assembly close to the atmosphere side is further included, and the first sealing assembly and the second sealing assembly are arranged in series in the axial direction.

[0017] The second sealing assembly includes a second dynamic ring movably arranged on the shaft sleeve, and a second spring seat fixedly arranged on the shaft sleeve, an extension along extending towards the second dynamic ring is arranged on the outer diameter side of the second spring seat, and the extension along is sleeved on the outer side of the second dynamic ring.

[0018] In some embodiments of the present application, a transmission pin arranged in the radial direction is arranged between the extension along and the second dynamic ring, an axially arranged transmission pin groove is arranged on the second dynamic ring, and the transmission pin is movably located in the transmission pin groove in the axial direction.

[0019] In some embodiments of the present application, the transmission pin has a first transmission part located in the transmission pin groove, and the ratio of the axial length of the transmission pin groove to the axial length of the first transmission part is 1.5-3.

[0020] In some embodiments of the present application, the ratio of the axial length of the transmission pin groove to the distance from the first transmission part to the second dynamic ring seal end face is 3-4.

[0021] In some embodiments of the present application, the transmission pin further has a second transmission part outside the first transmission part, the axial dimension of the second transmission part is smaller than that of the first transmission part, and the second transmission part is arranged on the extension.

[0022] In some embodiments of the present application, a mounting hole matched with the second transmission part is arranged on the extension, and the second transmission part is fixed in the mounting hole.

[0023] In some embodiments of the present application, the second sealing assembly further comprises a second static ring fixed on the gland, and a radial anti-rotation pin is arranged between the second static ring and the gland.

[0024] Compared with the prior art, the advantages and positive effects of the present application are as follows: a fluid lubrication groove is arranged inside the sealing convex end face, and the inside of the fluid lubrication groove is an open end, so that the lubricating fluid can be timely absorbed into the end face gap during operation; the heat generated due to friction can be rapidly taken away by a large amount of lubricating fluid under low-speed heavy-load working conditions, the temperature of the sealing surface is effectively reduced, a series of problems such as fluid vaporization, dry friction of the sealing surface, wear and even edge collapse caused by heat accumulation are avoided, the service life of the sealing device is greatly prolonged, the equipment downtime caused by sealing failure is reduced, and the overall operation efficiency and stability of the equipment are improved. The lubricating fluid is absorbed into the end face gap, continuously providing stable and sufficient lubricating medium for the dynamic and static ring sealing surfaces, and ensuring that the relative movement between the sealing surfaces is always in a good lubrication state.

[0025] Other characteristics and advantages of the present application will become more apparent after reading the specific implementation manner of the present application in combination with the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0026] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed in the embodiments will be briefly introduced as follows. Obviously, the drawings in the following description are some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without creative labor on the basis of these drawings.

[0027] Figure 1 The structure schematic diagram of an embodiment of the shaft end sealing device for low-speed heavy-load equipment proposed in the present application is shown in the figure.

[0028] Figure 2 The structure schematic diagram of an embodiment of the shaft end sealing device for low-speed heavy-load equipment proposed in the present application is shown in the figure. Figure 1 The enlarged structure schematic diagram of the A area in the figure.

[0029] Figure 3 For Figure 1 Enlarged structural diagram of the middle B area;

[0030] Figure 4 Partial structural diagram of the sealing convex end face;

[0031] Wherein, the first moving ring 3; the first static ring 4; the sealing convex 41; the fluid lubrication groove 411; the dam area 412; the first pushing ring 7; the first spring 8; the first spring seat 9; the second spring seat 10; the extension along 11; the mounting hole 111; the second spring 12; the second pushing ring 13; the transmission pin 15; the first transmission part 151; the second transmission part 152; the second moving ring 16; the transmission pin groove 161; the second static ring 17; the anti-rotation pin 19;

[0032] The sealing box 20; the mounting groove 21; the shaft sleeve 30; the gland 40. DETAILED DESCRIPTION

[0033] In order to make the purpose, technical scheme and advantages of the embodiments of the utility model clearer, the technical scheme in the embodiments of the utility model will be clearly and completely described below in combination with the drawings in the embodiments of the utility model.

[0034] In the description of the utility model, it needs to be explained that the position relationship or location relationship indicated by the terms "upper", "lower", "left", "right" and the like is based on the position relationship shown in the drawings, and the direction close to the rotation axis is "inner", and vice versa is "outer". The terms are only for the convenience of describing the utility model and simplifying the description, and are not indicative or suggestive of the devices or elements indicated having a specific orientation, being constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the utility model. In addition, the terms "first", "second", "third" are only for the purpose of description, and cannot be understood as indicative or suggestive of relative importance; the features limited by "first", "second" can explicitly or implicitly include one or more of the features. In the description of the utility model, the meaning of "multiple" is two or more than two, unless otherwise specifically limited.

[0035] In the utility model, unless otherwise specifically specified and limited, the terms "mounting", "connection", "connection", "fixing" and the like should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the communication or interaction relationship between two elements. For ordinary skilled in the art, the specific meaning of the above terms in the utility model can be understood according to the specific situation.

[0036] In the present application, unless otherwise explicitly specified and limited, the first feature is "on" or "under" the second feature, which can include direct contact between the first and second features, or indirect contact between the first and second features through another feature therebetween. Moreover, the first feature "on", "above" and "over" the second feature includes the first feature directly above and obliquely above the second feature, or only indicates that the first feature is higher than the second feature in horizontal height. The first feature "under", "below" and "under" the second feature includes the first feature directly below and obliquely below the second feature, or only indicates that the first feature is lower than the second feature in horizontal height.

[0037] The disclosure below provides many different embodiments or examples for implementing different structures of the present application. In order to simplify the disclosure of the present application, the components and settings of specific examples are described below. Of course, they are only examples, and the purpose is not to limit the present application. In addition, the present application can repeatedly refer to numbers and / or letters in different examples, and such repetition is for the purpose of simplification and clarity, which itself does not indicate the relationship between the various embodiments and / or settings discussed. In addition, the present application provides various specific examples of processes and materials, but those skilled in the art can realize the application of other processes and / or the use of other materials.

[0038] As far as possible, the various aspects and features described and illustrated in the specification can be applied individually, and these individual aspects can be the subject of a divisional application.

[0039] Referring to Figures 1-4 It is an embodiment of the shaft end sealing device for low-speed heavy-load equipment provided by the present application, and the shaft end sealing device for low-speed heavy-load equipment comprises: a first sealing assembly arranged between a sealing box 20 and a shaft sleeve 30, the first sealing assembly has a first dynamic ring 3 arranged on the shaft sleeve 30 and a first static ring 4 arranged on the sealing box 20, and the first static ring 4 is fixed on a spring seat 9 through an anti-rotation pin. A sealing protrusion 41 extending towards the first dynamic ring 3 is arranged on the outer side of the first static ring 4, and the sealing protrusion 41 abuts against the first dynamic ring 3. A fluid lubrication groove 411 is arranged on the inner side of the end surface of the sealing protrusion 41, and the inner side of the fluid lubrication groove 411 is an open end.

[0040] The sealing protrusion 41 is arranged to reduce the contact area between the first static ring 4 and the first dynamic ring 3 and reduce friction.

[0041] By opening the fluid lubrication groove 411 in the inner side of the sealing convex 41 end face, and the inner side is an open end, the lubricating fluid can be sucked into the end face in time during operation; the heat generated by friction can be quickly taken away by a large amount of lubricating fluid under low-speed heavy-load working conditions, effectively reducing the temperature of the sealing surface, avoiding a series of problems such as fluid vaporization, dry friction of the sealing surface, wear and even edge collapse caused by heat accumulation, greatly prolonging the service life of the sealing device, reducing the equipment downtime caused by sealing failure, and improving the overall operation efficiency and stability of the equipment. The lubricating fluid is sucked into the end face, continuously providing stable and sufficient lubricating medium for the dynamic and static ring sealing surface, ensuring that the relative movement between the sealing surfaces is always in a good lubricated state.

[0042] In some embodiments of the present application, a plurality of fluid lubrication grooves 411 are opened in the circumferential direction of the sealing convex 41 end face, and the area between the two adjacent fluid lubrication grooves 411 is a dam area 412. The ratio of the circumferential dimension of the inner diameter side of the fluid lubrication groove 411 to the circumferential dimension of the inner diameter side of the dam area 412 is 0.8-2. Opening a plurality of fluid lubrication grooves 411 in the circumferential direction of the sealing convex 41 end face can suck in lubricating fluid from multiple positions during equipment operation. The plurality of fluid lubrication grooves 411 are also conducive to heat dissipation, meaning that there are more channels to circulate and exchange heat, which can more efficiently reduce the temperature of the sealing surface. The ratio of the circumferential dimension of the inner diameter side of the fluid lubrication groove 411 to the circumferential dimension of the inner diameter side of the dam area 412 is 0.8-2. The dam area 412 plays an important role in preventing fluid leakage during sealing. If the size of the fluid lubrication groove 411 is too large, the sealing ability of the dam area 412 may be weakened; if the size of the fluid lubrication groove 411 is too small, the amount of lubricating fluid sucked in will also be affected. By reasonable size ratio, it can ensure that enough lubricating fluid enters the sealing surface, and maintain good sealing performance, so that the sealing device reaches a balance between lubrication and sealing, two important functions.

[0043] In some embodiments of the present application, the depth of the fluid lubrication groove 411 is 0.5-1.5 mm, and the depth of the fluid lubrication groove 411 is the axial dimension. The ratio of the radial dimension a of the sealing convex 41 to the radial dimension a' of the fluid lubrication groove is 2-3. When the depth of the fluid lubrication groove 411 is in the range of 0.5-1.5 mm, an appropriate amount of lubricating fluid can be stored, ensuring that the lubricating fluid can be stably and uniformly distributed between the sealing surfaces under low-speed heavy-load working conditions, effectively reducing the friction coefficient. During equipment operation, heat is generated by the friction of the sealing surfaces, and the lubricating fluid plays a key role in heat dissipation. The depth of 0.5-1.5 mm allows the lubricating fluid to have a suitable inventory and flow space in the groove, and when the sealing surface generates heat by friction, the heat can be more efficiently transferred to the lubricating fluid, which can dissipate the heat in time through its own flow and heat exchange with the outside. If the depth is too shallow, the contact area for heat transfer is small, and the heat dissipation efficiency is low; if the depth is too large, it may affect the normal circulation of the fluid and the heat transfer path, which is not conducive to rapid heat dissipation. This depth range helps to maintain the appropriate temperature of the sealing surface and avoid problems such as damage to the sealing surface caused by heat accumulation. By setting the ratio of the radial dimension a of the sealing convex 41 to the radial dimension a' of the fluid lubrication groove to be 2-3, it is ensured that the sealing convex 41 has sufficient sealing capacity to prevent fluid leakage, and the fluid lubrication groove 411 can smoothly absorb and distribute lubricating fluid, achieving good lubrication effect, so that the two complement each other during the entire equipment operation process, and together improve the overall performance of the sealing device, meeting the strict requirements of low-speed heavy-load equipment on sealing.

[0044] In some embodiments of the present application, the circumferential maximum dimension of the fluid lubrication groove 411 is the central angle corresponding to the open end, ensuring that the fluid lubrication groove 411 can smoothly absorb lubricating fluid. The central angle corresponding to the open end of the fluid lubrication groove 411 can maximize the contact with the lubricating fluid source during equipment operation, and can quickly capture and absorb lubricating fluid between the sealing surfaces during relative motion of the sealing surfaces. Under low-speed heavy-load working conditions, this efficient absorption capacity is particularly important, because the equipment operates at low speed, and if the lubricating fluid cannot be quickly and abundantly absorbed, the sealing surfaces are likely to generate dry friction due to lack of lubrication, leading to accelerated wear of the sealing surfaces and shortening the service life of the sealing device. A larger circumferential opening angle ensures that lubricating fluid can be continuously introduced, maintaining a good lubrication state, reducing the frictional resistance between the sealing surfaces, reducing energy consumption, and improving the smoothness of equipment operation.

[0045] In some embodiments of the present application, the first sealing assembly further has a first spring seat 9, a first push ring 7 abutting against the first static ring 4, a first spring 8 located between the first push ring 7 and the first spring seat 9, and a mounting notch 21 formed on the sealing box 20, the outer side of the first spring seat 9 being located in the mounting notch 21, and the gland 40 abutting against one end of the first spring seat 9 close to the atmosphere side. By arranging the first spring seat 9 to be abutted between the sealing box 20 and the gland 40, the firmness of the first spring seat 9 is improved.

[0046] In some embodiments of the present application, a second sealing assembly close to the atmosphere side is further included, the first sealing assembly and the second sealing assembly are arranged in series in the axial direction, and the second sealing assembly is located between the shaft sleeve 30 and the gland 40. The second sealing assembly includes a second dynamic ring 16 movably arranged on the shaft sleeve 30, a second spring seat 10 fixedly arranged on the shaft sleeve 30, an extension 11 extending in the direction of the second dynamic ring 16 arranged on the outer diameter side of the second spring seat 10, and the extension 11 is sleeved on the outer side of the second dynamic ring 16. A transmission pin 15 radially arranged between the extension 11 and the second dynamic ring 16 is used to transmit the torque between the extension 11 and the second dynamic ring 16. The transmission pin 15 is radially arranged between the extension 11 and the second dynamic ring 16, and during the operation of the equipment, when the shaft sleeve 30 rotates, the second spring seat 10 and the extension 11 fixedly arranged thereon also rotate, and the torque is accurately transmitted to the second dynamic ring 16 through the transmission pin 15, so as to ensure the synchronous rotary motion of the second dynamic ring 16 and the shaft sleeve 30. The extension 11 is sleeved on the outer side of the second dynamic ring 16, and such a layout makes the entire second sealing assembly more compact in the radial direction, thereby improving the integration and space utilization of the equipment.

[0047] In some embodiments of the present application, an axially arranged transmission pin groove 161 is formed on the second dynamic ring 16, and the transmission pin 15 is axially movable in the transmission pin groove 161. The transmission pin 15 has a first transmission part 151 located in the transmission pin groove 161, and the ratio of the axial length c of the transmission pin groove 161 to the axial length c' of the first transmission part 151 is 1.5-3. In the sealing state, due to the low rotation speed and large load, the rotating shaft will have a certain swing during rotation, and a large torque will be generated between the second dynamic ring 16 and the second spring seat 10, and the transmission pin groove 161 and the transmission pin 15 will frequently stick together and separate. If a common transmission pin is used to transmit a large impact load, the transmission pin is prone to wear and deformation, and the sealing ring is also prone to edge collapse and wear or even breakage. To ensure the reliability of the transmission mechanism, the ratio of the axial length c of the transmission pin groove 161 to the axial length c' of the first transmission part 151 is 1.5-3, which ensures that the transmission pin 15 has sufficient contact area in the transmission pin groove 161 to transmit torque, effectively reducing the impact force of the transmission pin 15 on the second dynamic ring 16, thereby preventing the second dynamic ring 16 from cracking due to frequent impact, and effectively ensuring the sealing effect of the mechanical seal. The ratio of the axial length c of the transmission pin groove 161 to the distance c''' from the first transmission part 151 to the sealing end surface of the second dynamic ring 16 is 3-4.

[0048] In some embodiments of the present application, the transmission pin 15 further has a second transmission part 152 located outside the first transmission part 151, the axial dimension of the second transmission part 152 is smaller than that of the first transmission part 151, and the second transmission part 152 is arranged on the extension edge 11. The second transmission part 152 is arranged on the extension edge 11, and its smaller axial dimension allows it to be more accurately fitted with the structure of the extension edge 11. While the extension edge 11 provides mounting and torque transmission support for the transmission pin 15, the smaller second transmission part 152 can be more tightly and accurately embedded in the corresponding mounting position of the extension edge 11, reducing problems such as looseness and shaking caused by excessive fitting clearance, improving the tightness and stability of the connection between the transmission pin 15 and the extension edge 11, and thereby enhancing the structural stability of the entire sealing assembly, allowing it to maintain accurate fitting between components and maintain good sealing effect during long-term operation, especially in the face of equipment vibration, shaft swing, and other situations.

[0049] In some embodiments of the present application, a mounting hole 111 matched with the second transmission part 152 is formed on the extension edge 11, and the second transmission part 152 is fixedly arranged in the mounting hole 111. Forming a mounting hole 111 matched with the second transmission part 152 on the extension edge 11 allows for accurate positioning of the second transmission part 152.

[0050] In some embodiments of the application, the second sealing assembly further comprises a second static ring 17 fixed on the gland 40, a second push ring 13 for pushing the second dynamic ring 16, and a second spring 12 arranged between the second spring seat 10 and the second push ring 13, and a radial anti-rotation pin 19 arranged between the second static ring 17 and the gland 40.

[0051] The above embodiments are only used to illustrate the technical solutions of the present application, but not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, the technical solutions recorded in the foregoing embodiments can still be modified by those of ordinary skill in the art, or some technical features thereof can be replaced equivalently; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions claimed by the present application.

Claims

1. A shaft end sealing device for low speed heavy duty equipment, characterized by The utility model relates to a kind of sealing device, including: First sealing assembly, it is arranged between sealing box and shaft sleeve; The first sealing assembly has first dynamic ring, first static ring is arranged on the shaft sleeve; Sealing convex is arranged on the outside of the first static ring and extends to the first dynamic ring and abuts on the first dynamic ring, fluid lubrication groove is opened in the inner side of the end face of the sealing convex, and the inner side of the fluid lubrication groove is open end.

2. The shaft end seal apparatus of claim 1, wherein, A plurality of fluid lubrication grooves are opened in the circumferential direction of the end face of the sealing convex, and the area between the two adjacent fluid lubrication grooves is dam area, and the ratio of the circumferential dimension of the inner diameter side of the fluid lubrication groove to the circumferential dimension of the inner diameter side of the dam area is 0.8-2.

3. The shaft end seal apparatus of claim 1 wherein, The depth of the fluid lubrication groove is 0.5-1.5mm, and the ratio of the radial dimension of the sealing convex to the radial dimension of the fluid lubrication groove is 2-3.

4. The shaft end seal apparatus of claim 1 wherein, The first sealing assembly has a first spring seat, and a mounting slot is opened on the sealing box, the outer side of the first spring seat is located in the mounting slot, and the gland abuts on one end of the first spring seat close to the atmosphere side.

5. The shaft end seal apparatus of claim 1 wherein, The circumferential maximum dimension of the fluid lubrication groove is the central angle corresponding to the open end.

6. A shaft end sealing arrangement according to any one of claims 1 to 5, characterised in that, Also including second sealing assembly close to atmosphere side, first sealing assembly and second sealing assembly are arranged in series in axial direction; The second sealing assembly includes a second dynamic ring movably arranged on the shaft sleeve, a second spring seat fixedly arranged on the shaft sleeve, and an extension along arranged on the outer diameter side of the second spring seat and extending to the second dynamic ring, the extension along is sleeved on the outer side of the second dynamic ring, and a transmission pin arranged in radial direction is arranged between the extension along and the second dynamic ring.

7. A shaft end sealing arrangement according to claim 6, characterised in that An axially arranged transmission pin groove is opened on the second dynamic ring, and the transmission pin is movably located in the transmission pin groove in axial direction.

8. The shaft end seal apparatus of claim 7, wherein, The transmission pin has a first transmission part located in the transmission pin groove, and the ratio of the axial length of the transmission pin groove to the axial length of the first transmission part is 1.5-3.

9. The shaft end seal apparatus of claim 8, wherein, The ratio of the axial length of the transmission pin groove to the distance from the first transmission part to the sealing end face of the second dynamic ring is 3-4.

10. The shaft end seal apparatus of claim 8, wherein, The transmission pin also has a second transmission part located on the outer side of the first transmission part, and the axial dimension of the second transmission part is smaller than the axial dimension of the first transmission part, and the second transmission part is arranged on the extension along.

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