CN211039390U - Combined high-temperature high-pressure high-speed sealing bearing - Google Patents
Combined high-temperature high-pressure high-speed sealing bearing Download PDFInfo
- Publication number
- CN211039390U CN211039390U CN201920062053.4U CN201920062053U CN211039390U CN 211039390 U CN211039390 U CN 211039390U CN 201920062053 U CN201920062053 U CN 201920062053U CN 211039390 U CN211039390 U CN 211039390U
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- bearing
- ring
- radial
- teeth
- labyrinth seal
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- 238000007789 sealing Methods 0.000 title claims description 26
- 230000003068 static effect Effects 0.000 claims description 16
- 238000000034 method Methods 0.000 claims description 7
- 238000010438 heat treatment Methods 0.000 claims description 6
- 239000000945 filler Substances 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 4
- 230000006378 damage Effects 0.000 abstract description 3
- 239000007788 liquid Substances 0.000 abstract 1
- 238000009423 ventilation Methods 0.000 abstract 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 4
- 238000012856 packing Methods 0.000 description 4
- 239000002699 waste material Substances 0.000 description 3
- 238000005192 partition Methods 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 210000004907 gland Anatomy 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
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Abstract
The utility model provides a high-speed sealed bearing of combination formula high temperature high pressure, mainly by terminal surface radial labyrinth seal, thrust bearing and radial bearing constitute, radially set up the quiet ring and the thrust bearing of annular tooth outside the preceding terminal surface of T type inner circle, radial bearing is being set up along the axial, П type outer lane's rear end inboard radially sets up the rotating ring of annular tooth, when T type inner circle and П type outer lane assemble, the quiet ring of annular tooth and the rotating ring convex-concave cooperation form terminal surface radial labyrinth seal, thrust bearing has prevented that the axial float of axle makes radial labyrinth seal card die, radial bearing has eliminated the destruction of axial radial load to radial labyrinth seal, obtain the better bearing structural style of sealed effect, the mountable is at turbine, compressor, air-blower, ventilation blower, heat-separating centrifuge and oil pump, sealed gas or liquid on the rotation axis such as water pump.
Description
Technical Field
The invention relates to the field of mechanical equipment, in particular to a non-contact sealing structure of a rotating shaft.
Background
The rotary shaft seal belongs to one of mechanical basic elements with precision and complex structure, and is a key part of equipment such as various pumps, reaction synthesis kettles, turbine compressors, submersible motors and the like. Although the rotary shaft seal has a plurality of forms such as gasket seal, packing seal, mechanical seal, non-contact seal and the like, the labyrinth seal in the non-contact seal is that a plurality of annular seal teeth which are arranged in sequence are arranged around a rotary shaft, a series of cut-off gaps and expansion cavities are formed between the teeth, and the sealed medium generates throttling effect when passing through the gaps of the zigzag labyrinth to achieve the purpose of leakage resistance. Because the clearance exists between the rotor and the casing of the labyrinth seal, the labyrinth seal has no solid contact, does not need lubrication, allows thermal expansion, adapts to the occasions of high temperature, high pressure and high rotating speed frequency, and is widely used for sealing shaft ends and all stages of steam turbines, gas turbines, compressors and blowers.
Among the four labyrinth seal structures of smooth, zigzag, stepped and honeycomb, the zigzag effect is the best in terms of sealing, and the stepped, honeycomb second, the least good is the smooth type. However, in terms of strength, the integral comb teeth sheet and the insertion type comb teeth sheet have high strength, but are difficult to process; the high-low type is convenient for processing and has low strength. In the high-speed rotating shaft of high-pressure centrifugal compressor and high-temperature steam turbine, where it is extended from two ends of cylinder and the rotating shaft is passed through the central hole of partition plate, in order to prevent friction collision between rotating component and static component, a proper gap must be left, and because the pressure difference of gas is existed in the front and rear of said gap, it must make leakage pass through said gap, and the interstage seal between intermediate partition plate and rotating shaft only needs small leakage quantity of gas. Therefore, the radial zigzag labyrinth seal has the best sealing performance, is easy to process, and is the best sealing selection for high-temperature and high-pressure fluid high-speed rotating equipment.
The leakage amount of the radial zigzag labyrinth seal is proportional to the size of the throttling tooth gap, and from the viewpoint of sealing performance, it is desirable that the throttling tooth gap is as small as possible, because the leakage amount of the labyrinth seal is increased, which results in a large amount of energy waste. However, if the throttling tooth gap is designed to be small, in the process of starting and stopping rotation of equipment with long rotating shafts, such as a steam turbine, a gas turbine and the like, the rotating speed of the rotating shaft needs to pass through more than one critical rotating speed in the process of changing, and the vibration of the rotating shaft is increased rapidly near the critical rotating speed, so that the comb teeth and the rotating shaft are rubbed or even collided, the throttling tooth gap is enlarged, and even the labyrinth seal may lose the sealing effect due to the breakage of the comb teeth. In addition, the axial play of the shaft causes the radial labyrinth seal to seize due to high pressure differential. Therefore, for those devices with large shaft runout during starting and stopping rotation, one has to design the throttling tooth gap of the labyrinth to be large, thereby causing large energy waste during the operation of the device. For large turbines, 40% of the identifiable efficiency losses are due to excessive gland clearances.
Disclosure of Invention
The invention aims to overcome the defects of the existing labyrinth seal technology, and provides a combined high-temperature high-pressure high-speed seal bearing, which utilizes a thrust bearing to prevent axial movement of a shaft from blocking a radial labyrinth seal, and solves the problem of ultra-large differential pressure sealing of high-pressure fluid; the radial bearing is utilized to eliminate the damage of the radial load or vibration of the shaft to the radial labyrinth seal, reduce the throttling tooth clearance as much as possible and improve the sealing performance; through the integrated combination of the end face radial labyrinth seal, the thrust bearing and the radial bearing, the bearing with the sealing function is formed, the occupied space is small, the size of a host is reduced, the structure is simplified, the bearing is easier to position, the leakage rate of a sealing system is effectively reduced, the heat efficiency loss of a steam turbine is reduced, the energy waste of equipment in the operation process is reduced, and the service life of the labyrinth seal is prolonged.
The technical scheme of the invention is as follows:
the invention provides a combined high-temperature high-pressure high-speed sealed bearing, which mainly comprises a braided heat exchange tube bank, branch tubes, a header tube, thin tubes, a shell and the like, wherein the head parts of one ends of the branch tubes and the header tube are closed, and the other ends of the branch tubes and the header tube are used as open ends; splayed thin tube connecting tubes are symmetrically arranged on two sides of the radial middle lower part of the branch tube, and the adjacent thin tube connecting tubes on each side in the axial direction are arranged in a vertically staggered manner; the two ends of each thin tube are respectively connected with the corresponding thin tube connecting tubes of the inlet branch tube and the outlet branch tube in a socket joint manner, and the thin tubes on the two sides of the branch tubes are woven in a staggered manner through the middle isolating rods to form a group of tube rows which are continuously arranged in an 8 shape in an alternating manner; branch pipe connecting pipes which are arranged in a vertically staggered manner are respectively arranged on one side of the collecting pipes of the inlet and the outlet and are connected with the opening ends of the corresponding branch pipe rows in a socket joint manner to form a woven filler type heat exchange core body; and the heat exchange core body is arranged in the shell in a mode of hot and cold fluid countercurrent or cross flow to form the shell-and-tube ultrahigh-temperature ultrahigh-pressure heat exchanger.
The invention provides a combined high-temperature high-pressure high-speed sealed bearing, which mainly comprises an end face radial labyrinth seal, a thrust bearing and a radial bearing, wherein a static ring with annular teeth and the thrust bearing are sequentially arranged on the outer side of the front end face of a T-shaped inner ring along the radial direction, the radial bearing with the outer diameter not smaller than the diameter of the front end face is arranged on the inner side of the front end face along the axial direction, a moving ring with the annular teeth is arranged on the inner side of the rear end face of an П -shaped outer ring along the radial direction, the number of teeth of the moving ring is one more than that of the static ring, the T-shaped inner ring and a П -shaped outer ring are assembled to form the sealed bearing, the static ring with the moving ring are in concave-convex matching to form the end face.
The thrust bearing and the radial bearing are firstly installed on the T-shaped inner ring by thermal expansion in a heating mode, and then the П -type outer ring is installed on the T-shaped inner ring by thermal expansion in a heating mode.
The bottom surface of the annular groove of each static ring is provided with or not provided with a packing layer.
The number of teeth of the static ring is 3-35, the number of teeth used for interstage sealing before and after the impeller is 3-6, and the number of teeth used for shaft end sealing is 6-35.
The outer wheel of the sealed bearing may or may not have a flange.
Drawings
Fig. 1 is a schematic view of the overall structure of the combined high-temperature high-pressure high-speed sealed bearing of the invention.
Fig. 2 is a structural schematic diagram of an П -type outer ring of the combined high-temperature high-pressure high-speed sealed bearing of the invention.
Fig. 3 is a schematic view of an assembly structure of a T-shaped inner ring of the combined high-temperature high-pressure high-speed sealed bearing of the invention.
The drawing of the attached drawing is provided with a T-shaped inner ring 1, a front end face 2, a static ring 3, a thrust bearing 4, a radial bearing 5, an outer ring 6, an П -shaped outer ring, a rear end face 7, a dynamic ring 8 and a flange 9.
Detailed Description
The invention is further described below with reference to the following figures and examples.
A combined high-temperature high-pressure high-speed sealing bearing mainly comprises an end face radial labyrinth seal, a thrust bearing (4) and a radial bearing (5), wherein a static ring (3) and the thrust bearing (4) with annular teeth are sequentially arranged on the outer side of a front end face (2) of a T-shaped inner ring (1) in the radial direction, the radial bearing (5) with the outer diameter not smaller than the diameter of the front end face (2) is arranged on the inner side of the front end face (2) in the axial direction, a movable ring (8) with the annular teeth is arranged on the inner side of a rear end face (7) of an П -shaped outer ring (6) in the radial direction, the number of teeth of the movable ring (8) is one more than that of the static ring (3), the T-shaped inner ring (1) and a П -shaped outer ring (6) are assembled to form the sealing bearing, the static ring (3) and the movable ring (8) with the annular teeth are in concave-convex matching to form the end face radial labyrinth seal.
The thrust bearing (4) and the radial bearing (5) are firstly installed on the T-shaped inner ring (1) by thermal expansion in a heating mode, and then the П -shaped outer ring (6) is installed on the T-shaped inner ring (1) by thermal expansion in a heating mode.
The bottom surface of the annular groove of each static ring (3) is provided with or not provided with a packing layer.
The number of teeth of the static ring (3) is 3-35, the number of teeth used for interstage sealing before and after the impeller is 3-6, and the number of teeth used for shaft end sealing is 6-35.
The outer wheel of the sealed bearing may or may not have a flange (9).
In conclusion, the combined high-temperature high-pressure high-speed sealing bearing provided by the invention solves the problem of ultra-large differential pressure sealing of a high-pressure high-temperature fluid high-speed rotating shaft by combining the end surface radial labyrinth seal, the thrust bearing, the radial bearing and the flange, the use pressure is higher than 40MPa, the temperature is higher than 800 ℃, and particularly, the bottom surface of the annular groove of each static ring is additionally provided with the packing layer, so that the leakage amount can be reduced by 2 orders of magnitude. Meanwhile, the combined high-temperature high-pressure high-speed sealing bearing only occupies 1/3-1/2 of a common high-speed rotating shaft sealing system, the damage rate is greatly reduced during abnormal operation, the service life is prolonged by more than 1 time, the installation and the disassembly are convenient, and the manufacturing cost is lower. In addition, the outer wheel of the sealing bearing is provided with a flange, so that the structure of the main machine is simplified, the size of the main machine is reduced, and the sealing bearing is easier to position and install.
Claims (5)
1. The combined high-temperature high-pressure high-speed sealed bearing is characterized in that a static ring and a thrust bearing with annular teeth are sequentially arranged on the outer side of the front end face of a T-shaped inner ring along the radial direction, a radial bearing with the outer diameter not smaller than the diameter of the front end face is axially arranged on the inner side of the front end face, a moving ring with annular teeth is radially arranged on the inner side of the rear end face of an П -shaped outer ring, the number of teeth of the moving ring is one more than that of the static ring, the T-shaped inner ring and a П -shaped outer ring are assembled to form a sealed bearing, the static ring and the moving ring of the annular teeth are in concave-convex fit to form end face radial labyrinth seal, the thrust bearing serves.
2. The combined high-temperature high-pressure high-speed sealed bearing of claim 1, wherein the thrust bearing and the radial bearing are first installed on the T-shaped inner ring by thermal expansion through a heating method, and then the П -type outer ring is installed on the T-shaped inner ring by thermal expansion through a heating method.
3. The combined high-temperature high-pressure high-speed sealed bearing of claim 1, wherein the bottom surface of the annular groove of each stationary ring is provided with or without a filler layer.
4. The combined high-temperature high-pressure high-speed sealing bearing as claimed in claim 1, wherein the number of teeth of the stationary ring is 3-35, the number of teeth of the interstage seals at the front and rear of the impeller is 3-6, and the number of teeth of the shaft end seals is 6-35.
5. The combined high temperature, high pressure and high speed sealed bearing of claim 1, wherein the outer wheel of the sealed bearing is with or without a flange.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920062053.4U CN211039390U (en) | 2019-01-15 | 2019-01-15 | Combined high-temperature high-pressure high-speed sealing bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920062053.4U CN211039390U (en) | 2019-01-15 | 2019-01-15 | Combined high-temperature high-pressure high-speed sealing bearing |
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| Publication Number | Publication Date |
|---|---|
| CN211039390U true CN211039390U (en) | 2020-07-17 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920062053.4U Withdrawn - After Issue CN211039390U (en) | 2019-01-15 | 2019-01-15 | Combined high-temperature high-pressure high-speed sealing bearing |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109595257A (en) * | 2019-01-15 | 2019-04-09 | 中国石油大学(华东) | Combined high-temperature high-pressure high-speed sealing bearing |
-
2019
- 2019-01-15 CN CN201920062053.4U patent/CN211039390U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109595257A (en) * | 2019-01-15 | 2019-04-09 | 中国石油大学(华东) | Combined high-temperature high-pressure high-speed sealing bearing |
| CN109595257B (en) * | 2019-01-15 | 2024-03-12 | 中国石油大学(华东) | Combined high-temperature high-pressure high-speed sealing bearing |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20200717 Effective date of abandoning: 20240312 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20200717 Effective date of abandoning: 20240312 |
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| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |