CN116241569A - Horizontal bearing sealing structure - Google Patents
Horizontal bearing sealing structure Download PDFInfo
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- CN116241569A CN116241569A CN202310531697.4A CN202310531697A CN116241569A CN 116241569 A CN116241569 A CN 116241569A CN 202310531697 A CN202310531697 A CN 202310531697A CN 116241569 A CN116241569 A CN 116241569A
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- Prior art keywords
- ring
- sealing
- bearing
- face
- stationary
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3268—Mounting of sealing rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3464—Mounting of the seal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/44—Free-space packings
- F16J15/447—Labyrinth packings
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sealing Of Bearings (AREA)
Abstract
The invention relates to the field of mechanical sealing, in particular to a horizontal bearing sealing structure, a driving shaft is matched with a bearing box through a bearing, a movable ring is coaxially fixed on the driving shaft, a stationary ring is arranged at the end part of the bearing box, the stationary ring is mutually abutted with the end surface of the movable ring to form a sealing end surface, and the abutting surface of the stationary ring and/or the movable ring is a conical surface; the invention can obtain the optimal contact area of the sealing end surface, so that the bearing box can not generate larger friction power consumption under the working condition of high rotating speed, the leakage is avoided, and the bearing can reliably operate.
Description
Technical Field
The invention relates to the field of mechanical sealing, in particular to a horizontal bearing sealing structure.
Background
The seal means a device for preventing fluid leakage, which is formed by at least one pair of end surfaces perpendicular to the rotation axis and kept in contact and relatively slide under the action of fluid pressure and the elasticity (or magnetic force) of a compensation mechanism and the cooperation of an auxiliary seal. The mechanical seal is used as the heart of the dynamic equipment, the reliable operation of the mechanical seal has very important significance, and the friction pair of the sealing surface is used as the key part of the mechanical seal, which is the core of the research.
Dynamic sealing of a horizontal bearing box high-speed oil lubrication bearing is always a technical problem, and leakage is serious under the working conditions of high rotating speed, high and low fluctuation of the rotating speed and fluctuation of oil temperature; especially under the high-rotation-speed working condition, when the contact area of the sealing end face is overlarge, the friction power consumption can be greatly improved, and the sealing failure, the bearing box lubricating oil leakage and the bearing oil shortage failure are caused by the rise of the temperature of the sealing end face, so that the problem to be solved is urgently.
Disclosure of Invention
In order to avoid and overcome the technical problems in the prior art, the invention provides a horizontal bearing sealing structure. The invention can obtain the optimal contact area of the sealing end surface, so that the bearing box can not generate larger friction power consumption under the working condition of high rotating speed, the leakage is avoided, and the bearing can reliably operate.
In order to achieve the above purpose, the present invention provides the following technical solutions:
a horizontal bearing sealing structure is characterized in that a driving shaft is matched with a bearing box through a bearing, a movable ring is coaxially fixed on the driving shaft, a static ring is arranged at the end part of the bearing box, the static ring is mutually abutted with the end surface of the movable ring to form a sealing end surface, and the abutting surface of the static ring and/or the movable ring is a conical surface;
area of contact of the sealing end faceAThe method comprises the following steps:
wherein:Wmaximum friction power consumption is designed for the sealing end face;
fis the friction coefficient of the sealing end face;
ggravitational acceleration;
vis the average linear velocity of the sealing end face;
hthe thickness of the liquid film is the thickness of the liquid film at the sealing end face;
d m is the average diameter of the sealing end face;
P j is the seal chamber pressure;
Sthe gap coefficient of the sealing end face;
Qthe highest leakage is designed for the sealing end face.
As a further scheme of the invention: sealing teeth are arranged on the matching surfaces of the movable ring and the static ring in a staggered manner, and each sealing tooth is enclosed with each other to form a labyrinth sealing cavity, and one end of the labyrinth sealing cavity, which is far away from the bearing, forms a sealing end surface; oil return holes are formed in the sealing teeth at the bottom of the static ring along the axis direction of the parallel driving shaft, and the height of each oil return hole is higher than the height of the lubricating oil surface in the bearing box.
As still further aspects of the invention: a shaft shoulder for axially positioning the bearing inner ring is arranged on the shaft body of the driving shaft in the sealing cavity, and an end cover for compressing the static ring is arranged on the bearing box; two ends of the movable ring are respectively abutted with the stationary ring and the bearing inner ring.
As still further aspects of the invention: a compression ring is arranged between the stationary ring and the bearing outer ring, the outer ring surface of the compression ring is used for sealing the contact surface between the bearing box and the end cover, the compression ring is radially provided with a step surface, and two ends of the stationary ring are respectively abutted with the step surface and the end cover.
As still further aspects of the invention: a compression ring sealing ring is arranged between the compression ring and the static ring, and a steel paper pad is arranged at the contact surface of the end cover and the bearing box.
As still further aspects of the invention: and a spring is axially arranged between the movable ring and the bearing inner ring, and applies elastic force towards the end cover to the movable ring so as to enable the movable ring to be abutted with the end face of the stationary ring.
As still further aspects of the invention: and a moving ring sealing ring is arranged at the contact surface of the moving ring and the driving shaft.
Compared with the prior art, the invention has the beneficial effects that:
1. according to the invention, the end surfaces of the stationary ring and the movable ring are designed into conical surfaces, so that the end surfaces are abutted to reduce the contact area of the sealing end surfaces, the optimal contact area of the sealing end surfaces meeting the design leakage amount requirement and the design maximum friction power consumption requirement can be obtained by constructing a sealing end surface contact area calculation formula, the increase of heating value caused by overlarge sealing end surface contact area is avoided, the friction damage such as scratches generated when the stationary ring and the movable ring work due to overlarge sealing end surface contact area is also avoided, the bearing box can not generate larger friction power consumption under the working condition of high rotating speed, the leakage is avoided, and the bearing is reliable in operation.
2. The static ring and the moving ring form a labyrinth seal structure, lubricating oil in the bearing box is prevented from leaking through the labyrinth seal cavity, and when the moving ring rotates and the lubricating oil entering the labyrinth seal cavity contacts the moving ring seal teeth, the lubricating oil can be thrown out onto the static ring under the action of centrifugal force and finally flows to the oil return hole, and flows back into the bearing box through the oil return hole.
3. According to the invention, the static ring is pressed and positioned by the cooperation of the end cover and the bearing, so that the static ring is prevented from axially moving along the driving shaft; the compression ring compresses the bearing and the stationary ring, and the position of the compression ring corresponds to the contact surface of the end cover and the bearing box, so that leakage of the contact surface of the end cover and the bearing box is reduced, and the compression ring sealing ring and the vulcanized paper pad can further reduce leakage of the contact surface of the end cover and the bearing box under the cooperation.
4. According to the invention, the spring is arranged between the movable ring and the bearing inner ring, and the elastic force is applied to the movable ring through the spring, so that the end face of the movable ring is always abutted against the end face of the static ring, and the leakage quantity at the sealing end face is reduced.
Drawings
Fig. 1 is a schematic structural view of the present invention.
In the figure:
1. a drive shaft; 2. a bearing;
3. a moving ring; 31. a spring; 32. a moving ring seal ring;
4. a stationary ring; 41. an oil return hole;
5. an end cap; 51. a compression ring; 511. a step surface;
52. a compression ring seal ring; 53. a steel paper pad;
6. and a bearing box.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Referring to fig. 1, in the embodiment of the present invention, a horizontal bearing sealing structure is provided, a driving shaft 1 is in bearing fit with a bearing housing 6 through a bearing 2, an inner cavity of the bearing housing 6 forms a sealing cavity, and lubricating oil for lubricating the bearing 2 is injected into the bottom of the housing.
The driving shaft 1 is provided with a shaft shoulder, and the bearing 2 is abutted with the shaft shoulder after being pushed axially along the driving shaft 1.
The end face of the bearing box 6 is sealed by an end cover 5, a vulcanized paper pad 53 is arranged between the end cover 5 and the bearing box 6, and the end cover 5 and the bearing box 6 are fixed by bolts. The end cover 5 is provided with two right-angle end cover steps, the end cover steps of the adjacent bearings 2 are provided with compression rings 51, and the cross section of each compression ring 51 is T-shaped. The two ends of the compression ring 51 are respectively abutted against the outer ring of the bearing 2 and the end cover step of the end cover 5 adjacent to the bearing 2, and the end cover 5 compresses and fixes the bearing 2 through the compression ring 51 so as to avoid axial movement of the bearing.
The end cover 5 is far away from the end cover step of the bearing 2 and is provided with a stationary ring 4, two ends of the stationary ring 4 are respectively abutted with a radial step surface 511 of the compression ring 51 and the end cover step of the end cover 5 far away from the bearing 2, and a compression ring sealing ring 52 is arranged at the contact surface of the stationary ring 4 and the compression ring 51.
A movable ring 3 is coaxially fixed on the driving shaft 1, two ends of the movable ring 3 are respectively abutted against the stationary ring 4 and the inner ring of the bearing 2, and a movable ring sealing ring 32 is arranged at the contact surface of the movable ring 3 and the driving shaft 1. The end surfaces of the moving ring 3 and the static ring 4 far away from the bearing 2 are conical, and the conical surfaces of the moving ring 3 and the static ring 4 are in abutting fit to form a sealing end surface so as to prevent the lubricating oil of the bearing box 6 from leaking.
Spring grooves are uniformly formed in the annular surface of the stationary ring 4 along the circumferential direction, the groove length direction of each spring groove is parallel to the axial direction of the driving shaft 1, and springs 31 are arranged in each spring groove; one end of the spring 31 abuts against the inner ring of the bearing 2, and the other end of the spring 31 abuts against the groove bottom surface of the spring groove, so that an elastic force is applied to the movable ring 3 in a direction away from the bearing 2, so that the end surface of the movable ring 3 abuts against the end surface of the stationary ring 4.
In order to improve the sealing effect, the matching surfaces of the movable ring 3 and the stationary ring 4 are staggered with sealing teeth, and each sealing tooth is matched to form a labyrinth seal-shaped structure, and the labyrinth seal cavity is S-shaped. Oil return holes 41 are formed in sealing teeth at the bottom of the stationary ring 4 along the axis direction parallel to the driving shaft 1, the oil return holes 41 of the sealing teeth are positioned on the same straight line, and the height of the bottom surface of each oil return hole 41 is higher than that of the lubricating oil in the bearing box 6.
In order to makeThe sealing effect is optimal, and the contact area of the sealing end faceAThe method comprises the following steps:
wherein:Wmaximum friction power consumption is designed for the sealing end face;
fis the friction coefficient of the sealing end face;
ggravitational acceleration;
vis the average linear velocity of the sealing end face;
hthe thickness of the liquid film is the thickness of the liquid film at the sealing end face;
d m is the average diameter of the sealing end face;
P j is the seal chamber pressure;
Sthe gap coefficient of the sealing end face;
Qthe highest leakage is designed for the sealing end face.
With a deep groove ball bearing with an inner diameter of 70mm,
after the deep groove ball bearing with the inner diameter of 70mm is arranged in the bearing box in a cantilever horizontal layout, the leakage amount, the friction power consumption and the service life are tested. The lubrication mode is oil lubrication, namely great wall No. 32 engine oil is adopted, and the lubricating oil is added to the horizontal center line of the ball at the lower side of the deep groove ball bearing under the static condition.
The test object is the sealing structure of the present invention, and the sealing structure in the comparative example is the conventional lip seal, labyrinth seal, and mechanical seal. The sealing structure and the existing sealing mechanism of the invention are tested for leakage amount, friction power consumption and service life under five working conditions of 1500rpm, 3000rpm, 4500rpm, 6000rpm and > 6000 rpm.
Table 1:
as shown in table 1, it can be seen that the leakage amount of the sealing structure of the present invention is lower than that of each existing sealing structure under the working conditions of different rotation speeds, and the sealing structure of the present invention can still work normally without failure under the high rotation speed.
Table 2:
as can be seen from table 2, under the working conditions of different rotation speeds, the friction power consumption of the sealing structure can be kept at a low position, a large heating value can not be generated, the sealing structure can be normally used under the working conditions of high rotation speeds, the lip seal and the mechanical seal always have a large heating value, and the lip seal and the mechanical seal can be quickly failed after the rotation speed is increased and cannot be used; while conventional labyrinth seals have little friction power consumption at low speeds, once the speed is increased, the mechanical seal can leak severely and cannot be used.
Table 3:
as shown in Table 3, it can be seen that under the working conditions of different rotation speeds, the service life of the sealing structure of the invention can be always maintained at the standard value of more than or equal to 24000 hours, and the existing sealing structure can rapidly leak and lose efficacy after the rotation speed is increased.
By combining the data, under the working condition of high rotating speed, the invention can still prevent leakage, can not generate larger friction power consumption during working, has long service life, and can ensure that the bearing can stably operate under the working condition of different rotating speeds.
The basic principles of the present application have been described above in connection with specific embodiments, however, it should be noted that the advantages, benefits, effects, etc. mentioned in the present application are merely examples and not limiting, and these advantages, benefits, effects, etc. are not to be considered as necessarily possessed by the various embodiments of the present application. Furthermore, the specific details disclosed herein are for purposes of illustration and understanding only, and are not intended to be limiting, as the application is not intended to be limited to the details disclosed herein as such.
The block diagrams of the devices, apparatuses, devices, systems referred to in this application are only illustrative examples and are not intended to require or imply that the connections, arrangements, configurations must be made in the manner shown in the block diagrams. As will be appreciated by one of skill in the art, the devices, apparatuses, devices, systems may be connected, arranged, configured in any manner. Words such as "including," "comprising," "having," and the like are words of openness and mean "including but not limited to," and are used interchangeably therewith. The terms "or" and "as used herein refer to and are used interchangeably with the term" and/or "unless the context clearly indicates otherwise. The term "such as" as used herein refers to, and is used interchangeably with, the phrase "such as, but not limited to.
It is also noted that in the apparatus, devices and methods of the present application, the components or steps may be disassembled and/or assembled. Such decomposition and/or recombination should be considered as equivalent to the present application.
The previous description of the disclosed aspects is provided to enable any person skilled in the art to make or use the present application. Various modifications to these aspects will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other aspects without departing from the scope of the application. Thus, the present application is not intended to be limited to the aspects shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
The foregoing description has been presented for purposes of illustration and description. Furthermore, this description is not intended to limit the embodiments of the application to the form disclosed herein. Although a number of example aspects and embodiments have been discussed above, a person of ordinary skill in the art will recognize certain variations, modifications, alterations, additions, and subcombinations thereof.
Claims (7)
1. The horizontal bearing sealing structure is characterized in that a driving shaft (1) is in bearing fit with a bearing box (6) through a bearing (2), a movable ring (3) is coaxially fixed on the driving shaft (1), a static ring (4) is arranged at the end part of the bearing box (6), the static ring (4) is abutted with the end surface of the movable ring (3) to form a sealing end surface, and the abutting surface of the static ring (4) and/or the movable ring (3) is a conical surface;
area of contact of the sealing end faceAThe method comprises the following steps:
fis the friction coefficient of the sealing end face;
ggravitational acceleration;
vis the average linear velocity of the sealing end face;
hthe thickness of the liquid film is the thickness of the liquid film at the sealing end face;
d m is the average diameter of the sealing end face;
P j is the seal chamber pressure;
Sthe gap coefficient of the sealing end face;
Qthe highest leakage is designed for the sealing end face.
2. The horizontal bearing sealing structure according to claim 1, wherein sealing teeth are arranged on the matching surfaces of the movable ring (3) and the stationary ring (4) in a staggered manner, the sealing teeth are enclosed with each other to form a labyrinth sealing cavity, and one end of the labyrinth sealing cavity, which is far away from the bearing (2), forms a sealing end surface; oil return holes (41) are formed in the sealing teeth at the bottom of the static ring (4) along the axial direction of the parallel driving shaft (1), and the height of the oil return holes (41) is higher than the height of the lubricating oil surface in the bearing box (6).
3. A horizontal bearing sealing structure according to claim 1 or 2, characterized in that the shaft body of the driving shaft (1) in the sealing cavity is provided with a shaft shoulder for positioning the inner ring of the bearing (2) along the axial direction, and the bearing box (6) is provided with an end cover (5) for compacting the stationary ring (4); two ends of the movable ring (3) are respectively abutted with the stationary ring (4) and the inner ring of the bearing (2).
4. A horizontal bearing sealing structure according to claim 3, characterized in that a pressing ring (51) is arranged between the stationary ring (4) and the outer ring of the bearing (2), the outer ring surface of the pressing ring (51) is used for sealing the contact surface between the bearing housing (6) and the end cover (5), the pressing ring (51) is radially provided with a step surface (511), and two ends of the stationary ring (4) are respectively abutted against the step surface (511) and the end cover (5).
5. A horizontal bearing sealing structure according to claim 4, characterized in that a press ring sealing ring (52) is arranged between the press ring (51) and the stationary ring (4), and a steel paper pad (53) is arranged at the contact surface of the end cover (5) and the bearing housing (6).
6. A horizontal bearing sealing structure according to claim 1 or 2, characterized in that a spring (31) is arranged axially between the moving ring (3) and the inner ring of the bearing (2), the spring (31) exerting an elastic force on the moving ring (3) in the direction of the end cap (5) so that the moving ring (3) abuts against the end face of the stationary ring (4).
7. A horizontal bearing seal arrangement according to claim 1 or 2, characterized in that a moving ring seal (32) is arranged at the contact surface of the moving ring (3) with the drive shaft (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310531697.4A CN116241569B (en) | 2023-05-12 | 2023-05-12 | Horizontal bearing sealing structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310531697.4A CN116241569B (en) | 2023-05-12 | 2023-05-12 | Horizontal bearing sealing structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN116241569A true CN116241569A (en) | 2023-06-09 |
| CN116241569B CN116241569B (en) | 2023-07-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310531697.4A Active CN116241569B (en) | 2023-05-12 | 2023-05-12 | Horizontal bearing sealing structure |
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| CN217558802U (en) * | 2022-06-10 | 2022-10-11 | 安徽宏翔农业机械有限公司 | Bearing seat for mounting rotary cultivator cutter shaft |
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| US5934684A (en) * | 1997-05-27 | 1999-08-10 | Brandon; Ronald Earl | Retractable segmented packing ring for fluid turbines having gravity springs to neutralize packing segment weight forces |
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| CN116241569B (en) | 2023-07-28 |
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