A shaft seal sleeve with high sealing performance

Abstract

The application discloses a shaft seal sleeve with high sealing performance, which comprises a shaft seal sleeve body; a vertical shaft seal sleeve mounting hole is arranged at the center position of the shaft seal sleeve body; two sealing ring grooves are arranged on the outer wall of the upper part of the shaft seal sleeve body; a drainage boss is arranged around the outer wall of the lower part of the shaft seal sleeve body; a first drainage groove is arranged on the inner side of the top of the drainage boss; a slope oil guide groove is arranged on the outer wall of the drainage boss; an upper concave oil guide ring groove is arranged on the outer side of the bottom of the drainage boss; a plurality of blade variable-width full-through oil guide drainage grooves are arranged on the top of the drainage boss and are connected with the first drainage groove; and a plurality of blade equal-width full-through oil guide drainage grooves are arranged on the bottom of the drainage boss and are connected with the oil guide ring groove. The full-through oil guide drainage groove formed by two groups of different specifications of inclined blades can significantly improve the sealing performance of the turbocharger compressor end.

Description

Technical Field

[0001] This invention relates to the field of fluid machinery turbocharger technology, and in particular to a shaft seal with high sealing performance. Background Technology

[0002] The turbocharger is a crucial component of a turbocharged engine. Its function is to provide the engine with more compressed air, allowing it to burn more fuel, thereby generating more power, improving fuel economy, and reducing harmful components in exhaust emissions. Due to its energy-saving and environmentally friendly effects, turbocharging technology has been widely adopted in the engine industry. Currently, turbochargers play a vital role in engine miniaturization, reducing fuel consumption, and lowering pollutant emissions.

[0003] When the engine is idling for a long time or operating at low speed, the turbocharger may experience low boost pressure or even negative pressure in the compressor, which can easily lead to oil leakage. Therefore, it is necessary to improve the compressor's ability to withstand negative pressure in turbochargers.

[0004] The shaft seal is an important component of the compressor end of a turbocharger. It is a dynamic sealing structure that works in conjunction with other compressor components to ensure both stable rotation of the rotor shaft and sealing of the turbocharger compressor end.

[0005] To improve the sealing performance of compressors, existing technologies typically increase the number of sealing rings installed in the shaft seal groove of the compressor. For example... Figure 1a , Figure 1b As shown, a compressor shaft seal sleeve has a shaft seal sleeve mounting hole 1. Its main body includes two sealing ring grooves 2 for installing sealing rings, and its bottom surface is a thrust bearing mating surface 3 (for contacting the thrust bearing in the compressor end of the turbocharger). However, given the small size of the turbocharger, its compressor end sealing structure is extremely compact, and the existing method can no longer meet the need for further improvement in compressor sealing performance.

[0006] Therefore, there is an urgent need to develop a technology that can further improve the sealing performance of compressors under the condition of shaft seal structure in compact turbocharger compressors. Summary of the Invention

[0007] The purpose of this invention is to address the technical deficiencies of existing technologies by providing a shaft seal sleeve with high sealing performance.

[0008] Therefore, the present invention provides a shaft seal sleeve with high sealing performance, comprising a shaft seal sleeve body;

[0009] A vertically penetrating shaft seal mounting hole is provided at the center of the shaft seal body;

[0010] The upper radial outer wall of the shaft seal sleeve body is provided with a sealing ring groove.

[0011] The lower radial outer wall of the shaft seal body is surrounded by outwardly protruding drainage bosses;

[0012] The top inner side of the drainage boss is provided with a recessed first drainage groove around the circumference of the shaft seal body;

[0013] The radial perimeter of the drainage boss is surrounded by a concave, sloping oil guide groove.

[0014] The bottom outer side of the drainage boss is provided with an upwardly recessed oil guide ring groove along the circumferential direction;

[0015] Among them, the top four edges of the drainage boss are evenly distributed with multiple upward-protruding oblique blades along the circumferential direction;

[0016] Between any two adjacent variable-width inclined blades, there is a blade variable-width full-through oil guide groove;

[0017] The variable width full-through oil guide groove of this blade is a groove with the same width at the inlet and outlet;

[0018] The blade has a variable width, fully-through oil guide groove that is connected to the first guide groove.

[0019] Among them, the bottom perimeter of the drainage boss has multiple downward-protruding oblique blades of equal width evenly distributed along the circumferential direction;

[0020] Between any two adjacent oblique blades of equal width, there is a blade-wide, fully-through oil guide groove of equal width;

[0021] The blades have a full-width, continuous oil guide groove that is connected to the oil guide ring groove.

[0022] As can be seen from the technical solution provided by the present invention above, compared with the prior art, the present invention provides a shaft seal with high sealing performance. As an important component of the compressor end of a turbocharger, it can significantly improve the sealing performance of the compressor end of the turbocharger through a full-through oil guide groove composed of two sets of inclined blades of different specifications, which has significant practical significance and application value.

[0023] This invention provides a compressor shaft seal sleeve. Through the arrangement design of two sets of different blade structures on the shaft seal sleeve, the lubricating oil flowing through the shaft seal sleeve can be quickly carried away from the compressor end, reducing the degree of lubricating oil accumulation in the compressor shaft seal sleeve area, thereby improving the sealing performance of the compressor.

[0024] By applying this invention, it is possible to fully utilize its function of improving the compressor end sealing performance in compact turbochargers under the condition of limited space at the compressor end structure. Attached Figure Description

[0025] Figure 1a This is a three-dimensional structural diagram of an existing turbocharger compressor shaft seal sleeve, specifically a diagram viewed from above.

[0026] Figure 1b This is a schematic diagram of the three-dimensional structure of an existing turbocharger compressor shaft seal sleeve, that is, a schematic diagram viewed from bottom to top;

[0027] Figure 2a The first three-dimensional structural schematic diagram of the shaft seal sleeve with high sealing performance provided by the present invention is shown in the first embodiment, that is, the schematic diagram when viewed from top to bottom.

[0028] Figure 2b The second three-dimensional structural diagram of the shaft seal sleeve with high sealing performance provided by the present invention is a schematic diagram of the first embodiment, that is, a schematic diagram viewed from bottom to top.

[0029] Figure 3a The first schematic diagram of the geometric structure design of the shaft seal sleeve with high sealing performance provided by the present invention is a schematic diagram viewed from below.

[0030] Figure 3b The second schematic diagram shows the geometric structure design of a shaft seal sleeve with high sealing performance provided by the present invention, according to Embodiment 1.

[0031] Figure 3c The geometric structure design diagram three of the embodiment one of the shaft seal sleeves with high sealing performance provided by the present invention is a top view.

[0032] Figure 4a The first three-dimensional structural diagram of the shaft seal sleeve with high sealing performance provided by the present invention is a schematic diagram of the second embodiment, that is, a schematic diagram viewed from top to bottom;

[0033] Figure 4b The second three-dimensional structural schematic diagram of the shaft seal sleeve with high sealing performance provided by the present invention is a schematic diagram viewed from bottom to top.

[0034] Figure 5a The first schematic diagram of the geometric structure design of the shaft seal sleeve with high sealing performance provided by the present invention is a schematic diagram viewed from below.

[0035] Figure 5b The second schematic diagram shows the geometric structure design of a shaft seal sleeve with high sealing performance provided by the present invention, according to Embodiment 2.

[0036] Figure 5c The geometric structure design diagram of the shaft seal sleeve with high sealing performance provided by the present invention is shown in Figure 3 of Embodiment 1.

[0037] In the figure, 1 is the shaft seal mounting hole, 2 is the sealing ring groove, and 3 is the thrust bearing mating surface;

[0038] 401 is a variable width inclined blade, 402 is a variable width full-through oil guide channel, and 403 is a sloped oil guide channel.

[0039] 501 is an equal-width inclined blade, 502 is an equal-width full-through oil guiding groove, and 503 is an oil guiding ring groove.

[0040] Where Da is the minimum distribution diameter of the variable width oblique blade, Db is the maximum distribution diameter of the variable width oblique blade, Dc is the minimum distribution diameter of the equal width blade, and Dd is the maximum distribution diameter of the equal width oblique blade.

[0041] d1 is the first width of the variable width inclined blade, d2 is the first width of the variable width inclined blade, d3 is the width of the constant width inclined blade, d4 is the height of the variable width inclined blade, d5 is the height of the constant width inclined blade, and d6 is the width of the connecting oil guide ring groove.

[0042] h1 is the maximum height of the variable width inclined blade arrangement area, h2 is the maximum height of the constant width inclined blade arrangement area, α is the tilt angle of the variable width inclined blade, and β is the tilt angle of the constant width inclined blade. Detailed Implementation

[0043] 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.

[0044] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0045] In the description of this patent, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "setting" should be interpreted broadly. For example, they can refer to a fixed connection or setting, a detachable connection or setting, or an integral connection or setting. Those skilled in the art can understand the specific meaning of the above terms in this patent according to the specific circumstances.

[0046] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0047] Example 1.

[0048] See Figure 2a , Figure 2b , Figure 3a , Figure 3b , Figure 3c The present invention provides a shaft seal sleeve with high sealing performance, including a shaft seal sleeve body 100;

[0049] A vertically penetrating shaft seal mounting hole 1 is provided at the center of the shaft seal body 100;

[0050] It should be noted that shaft seal mounting hole 1 is used to install the turbine shaft at the compressor end of the turbocharger;

[0051] The upper radial outer wall of the shaft seal body 100 is provided with two sealing ring grooves 2 spaced vertically.

[0052] The lower radial outer wall of the shaft seal body 100 is provided with outwardly protruding drainage bosses 200.

[0053] The top inner side of the drainage boss 200 is provided with a recessed first drainage groove 201 around the shaft seal body 100.

[0054] The radial periphery of the drainage boss 200 is surrounded by a concave sloping oil guide groove 403.

[0055] The bottom outer side of the drainage boss 200 is provided with an upwardly recessed oil guide ring groove 503 along the circumferential direction.

[0056] In this invention, specifically, the bottom surface of the center part of the drainage boss 200 is the thrust bearing mating surface 3.

[0057] In this invention, specifically, the top periphery of the drainage protrusion 200 is uniformly distributed with multiple upwardly protruding inclined blades 401 along the circumferential direction.

[0058] Between any two adjacent variable-width inclined blades 401, there is a blade variable-width full-through oil guiding groove 402;

[0059] The variable width full-through oil guide groove 402 of the blade is a groove with the same width at the inlet and outlet;

[0060] The blade has a variable width, fully-through oil guide groove 402, which is connected to the first guide groove 201.

[0061] In practice, the variable width full-through oil guide groove 402 of the blade is a groove with different widths at the inlet and outlet (i.e., the openings on the inner and outer sides).

[0062] In practice, the inlet width of the variable width full-through oil guide channel 402 is smaller than its outlet width.

[0063] In practice, the blade variable width full-through oil guide groove 402 has openings on both the inner and outer sides (i.e., it is not sealed).

[0064] It should be noted that for specific implementation details, please refer to [link / reference]. Figure 3c As shown, between any two adjacent variable width inclined blades 401, there is a blade variable width full-through oil guide groove 402 with a first width of d1, a second width of d2, and a depth of d4 (i.e., the height d4 of the variable width inclined blade 401 at the same time).

[0065] Where d1 > 2 × d2;

[0066] The first width d1 is the width of the outer end opening (i.e., the outlet) of the variable width full-through oil guide groove 402 of the blade;

[0067] The second width, d2, is the width of the inner end opening (i.e., the inlet) of the variable width full-through oil guide groove 402 of the blade.

[0068] It should be noted that, for the present invention, the purpose of setting the variable width inclined blade 401 is to create a pressure difference between the two ends of the variable width full-through oil guiding groove 402 with a first width of d1 and a second width of d2, so that the lubricating oil flows through the self-priming channel with a second width of d2 (i.e., the inner end opening of the variable width full-through oil guiding groove 402) to the oil discharge channel with a first width of d1 (i.e., the outer end opening of the variable width full-through oil guiding groove 402), so that the lubricating oil near the sealing ring groove 2 and the sealing ring assembled thereon is drawn out of the shaft seal sleeve, thereby improving the sealing performance of the shaft seal sleeve.

[0069] In specific implementation, the pressure in the first oil discharge channel with a width of d1 (i.e., the outer end opening of the variable width full-through oil guide groove 402) is P1, and the pressure in the second self-priming channel with a width of d2 (i.e., the inner end opening of the variable width full-through oil guide groove 402) is P2. The two have the following relationship:

[0070] P1×d1×d4=P2×d2×d4, formula (1);

[0071] Simplifying Formula 1, we get:

[0072] P2≥2×P1, formula (2);

[0073] As a result, the pressure in the self-priming channel with a second width of d2 is greater than the pressure in the oil discharge channel with a first width of d1. The lubricating oil flowing through the compressor end shaft seal is drawn into the oil guide ring groove 503 by the variable width full-pass oil guide groove 402 formed by multiple variable width inclined blades 401. Then, the oil guide ring 503 guides the lubricating oil to drain away from the compressor shaft seal, thereby improving the sealing performance of the compressor.

[0074] In specific implementation, the tilting direction of the variable width inclined blade 401 is backward tilting along the rotation direction X of the shaft sleeve;

[0075] In specific implementation, the tilt angle of each variable width inclined blade 401 is α;

[0076] The value of α satisfies the condition: 0°≤α≤65°;

[0077] It should be noted that the number N1 of the variable width inclined blades 401 can be freely selected according to the size of the shaft seal specification, and the following relationship should be met: the sum of the volumes of the variable width inclined blades should not be greater than the total volume of the arrangement area, and the height d4 of the variable width inclined blades should not exceed the maximum height h1 of the arrangement area of ​​the variable width inclined blades. In order to ensure structural reliability, it is usually necessary to satisfy h1≥2×d4. From this, the following relationship is derived:

[0078] π[(Db / 2) 2 -(Da / 2) 2 > N1[(d1+d2) / 2][(Db / 2)-(Da / 2)] / cos(α), formula (3);

[0079] Rearranging formula (3) yields:

[0080] N1<πcos(α)(Da+Db) / (d1+d2), formula (4);

[0081] Among them, see Figure 3cAs shown, Da is the minimum distribution diameter of the variable width inclined blade 401, Db is the maximum distribution diameter of the variable width inclined blade 401, d1 is the first width (outer oil discharge end opening width, i.e., outlet width) of the blade variable width full-through oil guiding channel 402 formed by two adjacent variable width inclined blades 401, d2 is the second width (inner oil suction end opening width, i.e., inlet width) of the blade variable width full-through oil guiding channel 402 formed by two adjacent variable width inclined blades, and α is the tilt angle of the variable width inclined blade 401.

[0082] Formula (4) gives the upper limit of the design of the number of variable width inclined blades of the shaft seal. When the structural dimensions are sufficient, the number of variable width inclined blades should be arranged as much as possible, that is, the N1 value should be the maximum value. However, the N1 value should be selected after comprehensive consideration of the limitations of structural reliability, production process and production cost.

[0083] In practice, the maximum diameter end face (i.e. the outermost end face with the largest width) of the variable width inclined blade 401 is provided with a sloping oil guide ring groove 403, which is conducive to guiding the lubricating oil out of the shaft seal sleeve.

[0084] In specific implementation, the slope angle of the inclined oil guide ring groove 403 is 15° to 45°;

[0085] For specific implementation details, see [link to implementation details]. Figure 3b The blade height d4 of the variable width inclined blade 401 shall not exceed the maximum height h1 of the arrangement area of ​​the variable width inclined blade 401, and shall satisfy the following relationship:

[0086] h1≥2×d4.

[0087] In this invention, specifically, the bottom periphery of the drainage protrusion 200 is evenly distributed with multiple downward-protruding oblique blades 501 of equal width along the circumferential direction.

[0088] Between any two adjacent equal-width inclined blades 501, there is a blade equal-width full-through oil guiding groove 502;

[0089] The blade-width, full-through oil guiding groove 502 is connected to the oil guiding ring groove 503.

[0090] In practice, the blade's equal-width, fully-through oil guiding groove 502 is a groove with the same width at both the inlet and outlet (i.e., the openings on both the inner and outer sides).

[0091] In practice, the inner and outer sides of the blade-width, fully-through oil guiding groove 502 are open (i.e., not sealed).

[0092] For specific implementation details, see [link to implementation details]. Figure 3aBetween any two adjacent equal-width inclined blades 501, there is a blade equal-width full-through oil guiding groove 502 with a width of d3 and a height of d5, which is connected to the oil guiding ring groove 503;

[0093] In practice, the connecting width of the oil guide ring groove is d6.

[0094] It should be noted that, for the present invention, the purpose of setting the equal-width inclined blade 501 is to throw the lubricating oil in the oil guide ring groove 503 out of the shaft seal sleeve through the equal-width full-through oil guide groove 502 with a width of d3 and a height of d5, thereby reducing the accumulation of lubricating oil in the shaft seal sleeve and improving the sealing performance of the shaft seal sleeve.

[0095] In specific implementation, the tilting direction of the equal-width inclined blade 501 is forward tilting along the rotation direction of the shaft sleeve;

[0096] In specific implementation, the tilt angle of each equal-width inclined blade 501 is β;

[0097] The condition that β can be taken is: 0°≤β≤65°.

[0098] In specific implementation, the number N2 of equal-width inclined blades 501 can be freely selected according to the size of the shaft seal sleeve. The number of blades should satisfy the following relationship: the total volume of all equal-width inclined blades should not exceed the total volume of the arrangement area, and the specification of the equal-width full-through oil guide groove with a height of d5 should not exceed the maximum height h2 of the equal-width inclined blade arrangement area. To ensure structural reliability, it is usually necessary to satisfy h2≥2×d5, from which the following relationship is derived:

[0099] π[(Dd / 2) 2 -(Dc / 2) 2 ]>N2(d3 / 2)[(Dd / 2)-(Dc / 2)] / cos(α), formula (5);

[0100] Rearranging formula (5) yields:

[0101] N2<πcos(β)(Dc+Dd) / d3, formula (6);

[0102] Among them, see Figure 3a As shown, Dc is the minimum distribution diameter of the equal-width inclined blade 501, Dd is the maximum distribution diameter of the equal-width inclined blade 501, d3 is the width of the equal-width full-through oil guiding groove 502 of the blade, and β is the tilt angle of the equal-width inclined blade 501.

[0103] Formula (6) gives the upper limit of the design of the number of equal-width inclined blades 501 of the shaft seal sleeve. When the structural dimensions are sufficient, the number of equal-width inclined blades should be arranged as much as possible, that is, the N2 value should be taken as the maximum value. However, the N2 value should be selected after comprehensive consideration of the limitations of structural reliability, production process and production cost.

[0104] In this invention, specifically, the height d5 of the equal-width inclined blade 501 is not greater than twice the maximum height h2 of the area where the equal-width inclined blade 501 is arranged.

[0105] The height of the variable width inclined blade 401 shall not exceed twice the maximum height h1 of the area where the variable width inclined blade 401 is arranged.

[0106] In this invention, specifically, the width of the oil guide ring groove 503 is no greater than one-fifth of the width of the equal-width full-through oil guide channel 502.

[0107] In this invention, specifically, the blade type of the variable width inclined blade 401 includes any one of arc shape, triangle, trapezoid and parabola shape. The purpose is to make the pressure difference between the two ends of the first width d1 and the second width d2 of the variable width full-through oil guide groove 402 more diverse and stable by using blades composed of different blade types.

[0108] It should be noted that, for the present invention, for multiple variable-width oblique blades, an oil guide ring groove is provided on the end face of the blade with the largest diameter; for multiple equal-width oblique blades, an oil guide ring groove is provided on the end face of the blade with the smallest diameter.

[0109] Example 2.

[0110] For the present invention, see Embodiment 2, see Figure 4a , Figure 4b , Figure 5a , Figure 5b , Figure 5c The shapes of the variable-width oblique blade 401 and the constant-width oblique blade 501 have been adjusted, while the structural design requirements of other parts are the same as those in Embodiment 1 above.

[0111] Among them, the variable width inclined blade 401 is an irregular shape. In specific implementation, the shape of the variable width inclined blade 401 only needs to satisfy the following: the inlet width of the blade variable width full-pass oil guide groove 402 formed between two adjacent variable width inclined blades 401 is less than the outlet width.

[0112] In summary, this invention improves the sealing performance of the shaft seal sleeve by optimizing and adjusting its oil drainage structure. Specifically, it uses a design that arranges two sets of different blades (including variable-width inclined blades 401 and equal-width inclined blades 501) to form a full-pass oil guiding channel, which quickly carries the lubricating oil flowing through the shaft seal sleeve away from the compressor end, reducing the degree of lubricating oil accumulation in the compressor shaft seal sleeve area, thereby improving the compressor's sealing performance.

[0113] In summary, compared with the prior art, the shaft seal provided by the present invention has high sealing performance. As an important component of the compressor end of a turbocharger, it can significantly improve the sealing performance of the compressor end of the turbocharger through a full-through oil guide groove composed of two sets of inclined blades of different specifications. It has significant practical significance and application value.

[0114] This invention provides a compressor shaft seal sleeve. Through the arrangement design of two sets of different blade structures on the shaft seal sleeve, the lubricating oil flowing through the shaft seal sleeve can be quickly carried away from the compressor end, reducing the degree of lubricating oil accumulation in the compressor shaft seal sleeve area, thereby improving the sealing performance of the compressor.

[0115] By applying this invention, it is possible to fully utilize its function of improving the compressor end sealing performance in compact turbochargers under the condition of limited space at the compressor end structure.

[0116] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A shaft seal sleeve with high sealing performance, characterized in that, Includes the shaft seal body (100); A vertically penetrating shaft seal mounting hole (1) is provided at the center of the shaft seal body (100). The upper radial outer wall of the shaft seal body (100) is provided with a sealing ring groove (2). The lower radial outer wall of the shaft seal body (100) is provided with outwardly protruding drainage bosses (200). The top inner side of the drainage boss (200) is provided with a recessed first drainage groove (201) around the shaft seal body (100). The radial periphery of the drainage boss (200) is surrounded by a concave, sloping oil guide ring groove (403). The bottom outer side of the drainage boss (200) is provided with an upwardly recessed oil guide ring groove (503) along the circumferential direction. Among them, the top four edges of the drainage boss (200) are evenly distributed with multiple upward-protruding oblique blades (401) along the circumferential direction. Between any two adjacent variable width inclined blades (401), there is a blade variable width full-through oil guide groove (402). The variable width full-through oil guide groove (402) of the blade is a groove with different widths at the inlet and outlet; The blade has a variable width full-through oil guide groove (402), which is connected to the first guide groove (201); Among them, the bottom periphery of the drainage boss (200) has multiple downward-protruding oblique blades (501) of equal width evenly distributed along the circumferential direction. Between any two adjacent equal-width oblique blades (501), there is a blade equal-width full-through oil guiding groove (502). The blade-width, full-through oil guide groove (502) is connected to the oil guide ring groove (503).

2. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The inlet width of the variable width full-through oil guide channel (402) is smaller than its outlet width.

3. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The tilting direction of the variable width inclined blade (401) is backward tilting along the rotation direction X of the shaft sleeve; The inclination direction of the equal-width inclined blade (501) is forward tilting along the rotation direction of the shaft sleeve.

4. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The tilt angle of each variable-width oblique blade (401) is α; The value of α satisfies the condition: 0°≤α≤65°.

5. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The number N1 of variable-width oblique blades (401) satisfies the following formula: N1<πcos(α)(Da+Db) / (d1+d2), formula (4); Where Da is the minimum distribution diameter of the variable width oblique blade (401), and Db is the maximum distribution diameter of the variable width oblique blade (401); d1 is the first width of the variable width full-through oil guide groove (402) of the blade, that is, the outlet width; d2 is the second width of the variable width full-through oil guide groove (402) of the blade, i.e., the inlet width; α is the tilt angle of the variable width oblique blade (401).

6. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The slope angle of the inclined oil guide ring groove (403) is 15°~45°.

7. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The tilt angle of each equal-width oblique blade (501) is β; The condition that β can be taken is: 0°≤β≤65°.

8. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The number N2 of equal-width oblique blades (501) satisfies the following formula: N2<πcos(β)(Dc+Dd) / d3, formula (6); Where Dc is the minimum distribution diameter of the equal-width inclined blade (501), Dd is the maximum distribution diameter of the equal-width inclined blade (501), d3 is the width of the equal-width full-through oil guide groove (502) of the blade, and β is the tilt angle of the equal-width inclined blade (501).

9. The shaft seal sleeve with high sealing performance as described in claim 1, characterized in that, The width of the oil guide ring groove (503) is not greater than one-fifth of the width of the blade-equal-width full-through oil guide channel (502).

10. The shaft seal sleeve with high sealing performance as described in any one of claims 1 to 9, characterized in that, The blade type of the variable width oblique blade (401) includes any one of the following: arc, triangle, trapezoid and parabolic.

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