CN109751255B - Centrifugal compressor using static and dynamic pressure mixed radial gas bearing - Google Patents
Centrifugal compressor using static and dynamic pressure mixed radial gas bearing Download PDFInfo
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- CN109751255B CN109751255B CN201910089280.0A CN201910089280A CN109751255B CN 109751255 B CN109751255 B CN 109751255B CN 201910089280 A CN201910089280 A CN 201910089280A CN 109751255 B CN109751255 B CN 109751255B
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- 230000003068 static effect Effects 0.000 title abstract description 11
- 239000011888 foil Substances 0.000 claims abstract description 48
- 230000000149 penetrating effect Effects 0.000 claims abstract description 4
- 230000001050 lubricating effect Effects 0.000 claims description 5
- 238000000034 method Methods 0.000 abstract description 9
- 238000005299 abrasion Methods 0.000 abstract description 4
- 230000002035 prolonged effect Effects 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 10
- 230000000694 effects Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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Abstract
The invention discloses a centrifugal compressor using static and dynamic pressure mixed radial gas bearing, which relates to the technical field of centrifugal compressor design, and comprises a shell and also comprises: the radial bearing is fixedly arranged in the shell, a boss A and a wave foil A are arranged on an inner ring of the radial bearing, the wave foil A is arranged on two sides of the boss A, a top foil A is arranged above the wave foil A, the height of the boss A is lower than the height of a working surface of the top foil A, a through hole A penetrating through the radial bearing is formed in the boss A, and an air supply channel corresponding to the through hole A is formed in the shell; a stator disposed within the housing; and the rotor is rotatably arranged in the radial bearing and corresponds to the stator. The invention has the advantages that the friction and the abrasion between the top foil of the dynamic pressure bearing and the rotating shaft in the starting process and the variable load process can be reduced by matching the static and dynamic pressure bearings, and the service life of the compressor is prolonged.
Description
Technical Field
The invention relates to the technical field of centrifugal compressor design, in particular to a centrifugal compressor using a static-dynamic pressure mixed radial gas bearing.
Background
The centrifugal compressor needs to realize high speed and miniaturization thereof, and an oil-lubricated rolling bearing and a sliding bearing cannot run at high speed, which is a main technical bottleneck of high speed of the compressor. The gas bearing has the characteristic of high-speed stable operation and is a core technology for realizing high speed of the compressor.
In recent years, gas bearing technology has gradually begun to be applied to centrifugal compressors. The gas bearing includes a static pressure gas bearing and a dynamic pressure gas bearing. The static pressure gas bearing has stable starting and stopping process and large bearing capacity, but has poor stability (air hammer) at high speed and needs stable external gas supply; the dynamic pressure gas bearing has high stability under a high-speed working condition, does not need external gas supply, but can cause damage to the surface of the bearing in the starting and stopping process, has certain starting and stopping frequency limitation, and influences the use of the compressor.
The existing static pressure gas bearing needs high pressure gas supplied from the outside, the matching equipment is complex and high in cost, the collision and abrasion phenomenon exists in the starting and stopping process, the requirement on the friction and abrasion performance of the material of the bearing is high, and the service life of the bearing is finally influenced.
Disclosure of Invention
The invention aims to increase a gas static pressure bearing, reduce bearing friction and prolong the service life of the bearing, and designs a centrifugal compressor using a static-dynamic pressure mixed radial gas bearing.
In order to achieve the above object, according to an aspect of the present invention, a centrifugal compressor using a static-dynamic pressure hybrid radial gas bearing includes a housing, and further includes: the radial bearing is fixedly arranged in the shell, a boss A and a wave foil A are arranged on an inner ring of the radial bearing, the wave foil A is arranged on two sides of the boss A, a top foil A is arranged above the wave foil A, the height of the boss A is lower than the height of a working surface of the top foil A, a lubricating layer is coated on the surface of the boss A, a through hole A penetrating through the radial bearing is formed in the boss A, a counter sink is arranged on the outer side of the through hole A, and an air supply channel corresponding to the through hole A is formed in the shell; a stator disposed within the housing; the rotor is rotatably arranged in the radial bearing and corresponds to the stator; still further, the motor also comprises a thrust disc arranged on the rotor; the pair of thrust bearings are arranged in the shell and positioned on two sides of the thrust disc, a boss B and a wave foil B are arranged on one opposite side of each thrust bearing, the boss B and the wave foil B are arranged along the radial direction of each thrust bearing, the wave foil B is arranged on two sides of the boss B, a top foil B is arranged above the wave foil B, and the height of the boss B is lower than the height of the working surface of the top foil B; the side of the thrust bearing is provided with a channel B, the boss B is provided with a through hole B communicated with the channel B, and the shell is provided with an air supply channel communicated with the channel B.
Further, the number of the bosses a is two, and the number of the bump foils a is three.
Further, the number of the radial bearings is two, and the radial bearings are respectively arranged at two ends of the rotor.
Still further, the shell is including casing, first support, casing, second support and the apron that sets gradually, journal bearing sets up on first support, the stator fixed set up in on the casing, be equipped with air feed channel on first support and the second support.
Further, the number of the bosses B is eight, and the number of the bump foils B is eight.
Further, the surface of the boss B is coated with a lubricating layer.
Furthermore, the side surface of the thrust bearing is provided with an annular groove.
Furthermore, the thrust bearing is arranged between the cover plate and the second support, and an air supply channel is arranged on the second support.
The invention has the beneficial effects that: by using the static and dynamic pressure bearings in a matched manner, the friction and the abrasion between the dynamic pressure bearing top foil and the rotating shaft in the starting process and the variable load process can be reduced, and the service life of the compressor is prolonged; the pressure of the working surface of the bearing can be effectively improved by using the two bearings simultaneously, so that the bearing capacity of the bearing is improved; through the mixed use of static and dynamic pressure bearings, the static pressure bearing is used in the starting process of the compressor, and the compressor is switched to the dynamic pressure bearing to operate after running stably, so that the respective advantages of the two bearings are taken into account, and the overall performance of the compressor is improved.
Drawings
FIG. 1 is a schematic diagram of a compressor according to the present application;
FIG. 2 is a schematic view of the radial bearing of the present application;
FIG. 3 is an enlarged partial schematic view at A in FIG. 2;
FIG. 4 is a cross-sectional structural view of the journal bearing;
FIG. 5 is a schematic structural view of a thrust plate of the present application;
FIG. 6 is a schematic front view of the structure of FIG. 5;
FIG. 7 is a schematic left side view of the structure of FIG. 6;
FIG. 8 is a schematic cross-sectional view at B-B in FIG. 6;
fig. 9 is a partially enlarged schematic view at C in fig. 7.
In the above figures, 1, a housing; 10. a gas supply channel; 11. a housing; 12. a first bracket; 13. a housing; 14. a second bracket; 15. a cover plate; 2. a radial bearing; 21. a boss A; 22. a bump foil A; 23. a top foil A; 24. a through hole A; 3. a stator; 4. a rotor; 5. a thrust plate; 6. a thrust bearing; 61. a boss B; 62. a bump foil B; 63. a top foil B; 64. a channel B; 65. and a through hole B.
Detailed Description
To further illustrate the technical means and effects of the present invention adopted to achieve the predetermined objects, the following detailed description of the embodiments, structures, features and effects according to the present invention with reference to the accompanying drawings and preferred embodiments is as follows:
a centrifugal compressor using a static-dynamic pressure hybrid radial gas bearing, as shown in fig. 1 to 9, includes a housing 1, a radial bearing 2, a stator 3, and a rotor 4.
As shown in fig. 2 to 4, the radial bearings 2 are fixedly provided in the housing 1, the number of the radial bearings 2 is two, and the radial bearings 2 are provided at both ends of the rotor 4, respectively. The inner ring of the radial bearing 2 is provided with a boss A21 and a wave foil A22, the wave foil A22 is arranged on two sides of the boss A21, a top foil A23 is arranged above the wave foil A22, and the height of the boss A21 is lower than the height of the working surface of the top foil A23, so that the boss A21 is prevented from contacting with the shaft of the rotor 4 in normal operation. The boss a21 is provided with a through hole a24 penetrating the radial bearing 2, the housing 1 is provided with a gas supply passage 10 corresponding to the through hole a24, and gas or liquid can be injected into the housing 1 from the gas supply passage 10 through the through hole a 24. For convenience of use, a counter bore may be provided at the outer side of the through hole a 24. In the figure, the number of the bosses a21 is two, and the number of the bump foils a22 is three, so that the input rate of gas or liquid is increased. Preferably, the surfaces of the boss A21 and the top foil A23 are coated with a lubricating layer to avoid surface damage during contact friction.
As shown in fig. 1, the stator 3 is disposed inside the housing 1. A rotor 4 is rotatably disposed within the radial bearing 2, the rotor 4 corresponding to the stator 3.
The housing 1 is mainly used for mounting. Regarding the structure of the housing 1, the present application provides a design solution, and the housing 1 includes a housing 11, a first bracket 12, a casing 13, a second bracket 14, and a cover plate 15, which are sequentially disposed. The radial bearing 2 is arranged on the first support 12, the stator 3 is fixedly arranged on the casing 13, and the first support 12 and the second support 14 are provided with air supply channels 10.
As shown in fig. 1, 5 to 9, a thrust disk 5 is provided on the rotor 4 for providing an axial force of the rotor 4. A pair of thrust bearings 6 are provided in the housing 1, the two thrust bearings 6 being located on either side of the thrust plate 5. The opposite side of the thrust bearing 6 is provided with a boss B61 and a wave foil B62, the boss B61 and the wave foil B62 are arranged along the radial direction of the thrust bearing 6, the wave foil B62 is arranged on the two sides of the boss B61, a top foil B63 is arranged above the wave foil B62, the height of the boss B61 is lower than the height of the working surface of the top foil B63, and the boss B61 is prevented from contacting with the side surface of the thrust disc 5 in normal operation. The side of the thrust bearing 6 is provided with a channel B64, the boss B61 is provided with a through hole B65 communicated with the channel B64, the shell 1 is provided with an air supply channel 10 communicated with the channel B64, and gas or liquid can be injected into the shell 1 from the air supply channel 10 through the channel B64 and the through hole B65. For convenience of use, an annular groove may be provided in the side surface of the thrust bearing 6, and the through hole B65 is provided in the annular groove. In the figure, the number of the bosses B61 is eight, and the number of the bump foils B62 is eight, so that the input rate of gas or liquid is increased. Preferably, the surfaces of the boss B61 and the top foil B63 are coated with a lubricating layer to avoid surface damage during contact friction. The thrust bearing 6 is arranged between the cover plate 15 and the second bracket 14, and the second bracket 14 is provided with the gas supply passage 10.
Before the compressor is started, high-pressure gas or liquid is supplied to the gas supply passage 10 of the compressor through an external gas supply device, and the high-pressure gas or liquid enters a gap between the rotor 4 and the radial bearing 2 through a through hole a24 formed in a boss a21, so that the rotor 4 is suspended in the radial bearing 2. The compressor is then started, with a progressive increase in the speed of rotation of the levitating rotor 4, whose dynamic pressure effect develops, the starting process of which is a hydrostatic bearing, when the rotor 4 can be levitated by the force generated by the radial bearing 2. And the external high-pressure gas or liquid supply is cut off, so that the compressor can stably work under the state that only the gas dynamic pressure bearing exists, namely the compressor is switched to the dynamic pressure bearing after stably running.
When the compressor load is increased and the dynamic pressure bearing can not meet the requirement of stable operation of the compressor, the load capacity of the bearing can be improved by supplying air to the radial bearing 2. When the compressor needs to be stopped, an external high-pressure gas or liquid channel is firstly opened to ensure that the bearing has enough bearing capacity, and then the rotating speed of the compressor is gradually reduced to stop.
When the axial load of the compressor is increased, high-pressure gas or liquid is supplied to the gas supply passage 10 by the external gas supply means, and the high-pressure gas or liquid enters the gap between the thrust disk 5 and the thrust bearing 6 through the passage B64 and the through hole B65, thereby balancing the axial load of the compressor.
The invention has been described above with reference to a preferred embodiment, but the scope of protection of the invention is not limited thereto, and various modifications can be made and equivalents can be substituted for elements thereof without departing from the scope of the invention, and features mentioned in the various embodiments can be combined in any way as long as there is no structural conflict, and any reference sign in the claims should not be construed as limiting the claim concerned, from which the embodiment is to be regarded as being exemplary and non-limiting in any way. Therefore, all technical solutions that fall within the scope of the claims are within the scope of the present invention.
Claims (4)
1. A centrifugal compressor using a static-dynamic pressure hybrid radial gas bearing, comprising a casing (1), characterized by further comprising:
the radial bearing (2) is fixedly arranged in the shell (1), a boss A (21) and a wave foil A (22) are arranged on an inner ring of the radial bearing (2), the wave foil A (22) is arranged on two sides of the boss A (21), a top foil A (23) is arranged above the wave foil A (22), the height of the boss A (21) is lower than the height of a working surface of the top foil A (23), a lubricating layer is coated on the surface of the boss A (21), a through hole A (24) penetrating through the radial bearing (2) is arranged on the boss A (21), a counter bore is arranged on the outer side of the through hole A (24), and an air supply channel (10) corresponding to the through hole A (24) is arranged on the shell (1);
a stator (3) disposed within the housing (1); and
a rotor (4) rotatably disposed in the radial bearing (2) and corresponding to the stator (3); a thrust disc (5) is arranged on the rotor (4);
a pair of thrust bearings (6) is arranged in the shell (1), and the two thrust bearings (6) are respectively positioned on two sides of the thrust plate (5); a boss B (61) and a wave foil B (62) are arranged on one side opposite to the thrust bearing (6), and a top foil B (63) is arranged above the wave foil B (62); the side of thrust bearing (6) is equipped with passageway B (64), be equipped with on boss B (61) with through-hole B (65) that passageway B (64) are linked together, still be equipped with on shell (1) with passageway B (64) are linked together air feed channel (10).
2. The centrifugal compressor using a static-dynamic pressure mixing radial gas bearing according to claim 1, wherein the number of the bosses a (21) is two, and the number of the bump foils a (22) is three.
3. A centrifugal compressor using a static-dynamic pressure hybrid radial gas bearing according to claim 1, characterized in that the number of the radial bearings (2) is two, respectively provided at both ends of the rotor (4).
4. The centrifugal compressor using the static-dynamic pressure mixed radial gas bearing as claimed in claim 1, wherein the housing (1) comprises a housing (11), a first bracket (12), a casing (13), a second bracket (14) and a cover plate (15) which are sequentially arranged, the radial bearing (2) is arranged on the first bracket (12), the stator (3) is fixedly arranged on the casing (13), and the first bracket (12) and the second bracket (14) are provided with gas supply channels (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910089280.0A CN109751255B (en) | 2019-01-30 | 2019-01-30 | Centrifugal compressor using static and dynamic pressure mixed radial gas bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910089280.0A CN109751255B (en) | 2019-01-30 | 2019-01-30 | Centrifugal compressor using static and dynamic pressure mixed radial gas bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109751255A CN109751255A (en) | 2019-05-14 |
| CN109751255B true CN109751255B (en) | 2020-11-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910089280.0A Active CN109751255B (en) | 2019-01-30 | 2019-01-30 | Centrifugal compressor using static and dynamic pressure mixed radial gas bearing |
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| Country | Link |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112160915A (en) * | 2020-09-22 | 2021-01-01 | 珠海格力电器股份有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3366427A (en) * | 1965-11-01 | 1968-01-30 | Garrett Corp | Selectively pressurized foil bearing arrangements |
| CN103343775A (en) * | 2013-07-08 | 2013-10-09 | 上海大学 | Gas bearing integrated by dynamic pressure and static pressure |
| CN204164008U (en) * | 2014-10-27 | 2015-02-18 | 福建雪人股份有限公司 | A kind of centrifugal compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101070892B1 (en) * | 2004-06-15 | 2011-10-06 | 삼성테크윈 주식회사 | Air foil bearing and structure for supplying air into it |
| KR100963523B1 (en) * | 2008-10-23 | 2010-06-14 | 한국기계연구원 | Hybrid air foil journal bearings with external hydrostatic pressure supplies |
-
2019
- 2019-01-30 CN CN201910089280.0A patent/CN109751255B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3366427A (en) * | 1965-11-01 | 1968-01-30 | Garrett Corp | Selectively pressurized foil bearing arrangements |
| CN103343775A (en) * | 2013-07-08 | 2013-10-09 | 上海大学 | Gas bearing integrated by dynamic pressure and static pressure |
| CN204164008U (en) * | 2014-10-27 | 2015-02-18 | 福建雪人股份有限公司 | A kind of centrifugal compressor |
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| CN109751255A (en) | 2019-05-14 |
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Effective date of registration: 20231114 Address after: 214000 18-13 Zhenze Road, Xinwu District, Wuxi City, Jiangsu Province Patentee after: TAILINGTE COMPRESSOR WUXI Co.,Ltd. Address before: 1st Floor, No. 8 Jianshe North Street, Chenghua District, Chengdu City, Sichuan Province, 610051 Patentee before: Chengdu Situo Intellectual Property Services Co.,Ltd. Effective date of registration: 20231114 Address after: 1st Floor, No. 8 Jianshe North Street, Chenghua District, Chengdu City, Sichuan Province, 610051 Patentee after: Chengdu Situo Intellectual Property Services Co.,Ltd. Address before: 266000 Songling Road, Laoshan District, Qingdao, Shandong Province, No. 99 Patentee before: QINGDAO University OF SCIENCE AND TECHNOLOGY |