CN108180159B - Self-adaptive correction thrust bearing of turbocharger - Google Patents
Self-adaptive correction thrust bearing of turbocharger Download PDFInfo
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- CN108180159B CN108180159B CN201711176144.2A CN201711176144A CN108180159B CN 108180159 B CN108180159 B CN 108180159B CN 201711176144 A CN201711176144 A CN 201711176144A CN 108180159 B CN108180159 B CN 108180159B
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- disc
- positioning pin
- floating bearing
- turbocharger
- thrust bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/051—Axial thrust balancing
Abstract
The invention provides a self-adaptive correction thrust bearing of a turbocharger, which comprises a fixed disc and a floating bearing disc, wherein the fixed disc is fixed on the floating bearing disc; the floating bearing disc is embedded in an inner hole of the fixed disc, and the floating bearing disc and the fixed disc are connected together in a ball type universal joint mode; the fixed disc and the floating bearing disc limit the rotation of the floating bearing disc along with the supercharger rotor through circumferential positioning pins arranged along the radial direction of the fixed disc and the floating bearing disc. The self-adaptive correction thrust bearing of the turbocharger can self-adaptively adjust the fitting degree of the plane of the thrust plate and the working surface of the thrust bearing, and further effectively avoid supercharger faults caused by the fitting degree difference of the plane of the thrust plate and the working surface of the thrust bearing.
Description
Technical Field
The invention belongs to the field of turbochargers, and particularly relates to a self-adaptive correction thrust bearing structure of a turbocharger.
Background
When the turbocharger works, the gas acting force on the turbine impeller and the air acting force on the compressor impeller are unbalanced to form an axial force. This axial force is taken up by the thrust bearing. Thrust bearings are typically provided at the compressor end, depending on the operating conditions and structural arrangement of the turbocharger. Therefore, the compressor end is provided with a thrust bearing for bearing axial load in addition to a bearing for bearing radial load. Thrust bearings not only affect the mechanical efficiency of the turbocharger, but also have a significant impact on the reliability and service life of the turbocharger.
A typical one-piece thrust bearing, which is currently used more frequently in turbochargers, is shown in fig. 1-3.
The integral thrust bearing has simple structure. On the front and rear working faces, there are four (or six) oil grooves, respectively. Four (or six) fan-shaped oil wedge bearing planes are formed, and each fan-shaped working surface is provided with a 0.25-1-degree inclined plane along the circumferential direction or an oil inlet hole at the grooving position. Two thrust plates corresponding to the front and back working faces of the thrust bearing form a bearing structure for bearing axial load. The working surface of the thrust plate is smooth. And is a rotator symmetrical to the axis.
The integral thrust bearing has higher requirements on processing and assembly, if the processing precision or the assembly quality is poor, the plane of the thrust plate is not well attached to the working surface of the thrust bearing, the normal work of the thrust bearing can be damaged, the thrust bearing can be seriously abraded, and even the whole turbocharger can be damaged. In addition, because the floating ring bearing has a certain gap, the center line of the shaft neck is not perpendicular to the plane of the thrust plate in the running process of the supercharger, the plane of the thrust plate is not well attached to the working surface of the thrust bearing, and the thrust bearing is easy to damage. Therefore, a novel thrust bearing is urgently needed, and the fitting degree of the plane of the thrust plate and the working surface of the thrust bearing can be adjusted in a self-adaptive mode.
Disclosure of Invention
In view of this, the present invention provides a turbocharger adaptive correction thrust bearing to overcome the problem that in the prior art, the contact degree between the thrust plate plane and the thrust bearing working surface can be adaptively adjusted, so as to effectively avoid supercharger faults caused by the contact difference between the thrust plate plane and the thrust bearing working surface.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a turbocharger self-adaptive correction thrust bearing comprises a fixed disc and a floating bearing disc; the floating bearing disc is embedded in an inner hole of the fixed disc, and the floating bearing disc and the fixed disc are connected together in a ball type universal joint mode; the fixed disc and the floating bearing disc limit the rotation of the floating bearing disc along with the supercharger rotor through circumferential positioning pins arranged along the radial direction of the fixed disc and the floating bearing disc.
Furthermore, the wall surface of the inner hole of the fixed disc is an inner concave spherical surface, and the periphery of the excircle of the floating bearing disc is an outer convex spherical surface matched with the inner concave spherical surface; a gap is left between the concave spherical surface and the convex spherical surface.
Furthermore, at least one limiting groove is formed in the fixed disc in the circumferential direction.
Furthermore, a first positioning pin hole and a second positioning pin hole are respectively arranged in the fixed disc and the floating bearing disc along the radial direction; the first positioning pin hole corresponds to the second positioning pin hole in position, and a circumferential positioning pin is arranged in the first positioning pin hole and the second positioning pin hole; and a gap is reserved between the second positioning pin hole and the circumferential positioning pin to ensure that the floating bearing disc can freely swing within a certain range.
Furthermore, the diameter of the first positioning pin hole is smaller than that of the second positioning pin hole, and an internal thread which is matched and connected with the external thread of the circumferential positioning pin is arranged at the upper end of the first positioning pin hole.
Furthermore, a first oil duct is arranged on the fixed disc along the circumferential direction, and at least one second oil duct is arranged on the fixed disc along the radial direction; at least one third oil duct is arranged on the floating bearing disc along the radial direction, and the third oil duct corresponds to the second oil duct in position; the first oil duct, the second oil duct and the third oil duct are communicated with each other.
Furthermore, the tail end of a second oil duct is communicated with the inner circle of the fixed disc, and the second oil duct is communicated with the inner circle and the outer circle of the floating bearing disc; the second oil passage and the third oil passage have different diameters.
Further, an oil inlet groove is formed in the middle of the convex spherical surface of the floating bearing plate and is communicated with a second oil duct; the oil inlet groove is positioned right at the joint of the concave spherical surface and the convex spherical surface.
Further, the oil inlet groove is arranged along the circumferential direction.
Furthermore, a thrust bearing surface is arranged on the floating bearing disc.
Compared with the prior art, the self-adaptive correction thrust bearing of the turbocharger has the following advantages:
the self-adaptive correction thrust bearing of the turbocharger can automatically adjust the fitting degree of the plane of the thrust plate and the working surface of the thrust bearing under the action of axial force, and effectively avoids the thrust bearing fault caused by the difference of the fitting degree of the plane of the thrust plate and the working surface of the thrust bearing.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic view of a typical one-piece thrust bearing as is commonly used in turbochargers today;
FIG. 2 is a schematic structural view of a typical integral thrust bearing that is currently used in turbochargers;
FIG. 3 is a schematic illustration of a third exemplary thrust bearing of the unitary construction currently employed in turbochargers;
FIG. 4 is a front view of a turbocharger adaptive correction thrust bearing according to an embodiment of the present invention;
FIG. 5 is a cross-sectional side view of a turbocharger adaptive correction thrust bearing according to an embodiment of the present invention;
FIG. 6 is a cross-sectional side view of a stationary disk in a turbocharger adaptive correction thrust bearing according to an embodiment of the present invention;
FIG. 7 is a cross-sectional view taken along the line A-A in FIG. 6;
FIG. 8 is a front view of a floating carrier plate in a turbocharger adaptive correction thrust bearing according to an embodiment of the present invention;
FIG. 9 is a side view of a floating carrier plate in a turbocharger adaptive corrective thrust bearing according to an embodiment of the present invention;
FIG. 10 is a front cross-sectional view of a floating carrier plate in a turbocharger adaptive corrective thrust bearing in accordance with an embodiment of the present invention.
Description of reference numerals:
1-fixing the disc; 101-concave spherical surface; 102-a first dowel hole; 103-a first oil passage; 104-a second oil passage; 105-a limiting groove; 2-floating bearing plate; 201-convex spherical surface; 202-a second dowel hole; 2021-internal thread; 203-a third oil passage; 204-oil inlet tank; 3-circumferential positioning pins; 4-thrust bearing surface.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
As shown in fig. 4-10, a turbocharger self-adaptive correction thrust bearing comprises a fixed disc 1 and a floating bearing disc 2; the floating bearing disc 2 is embedded in an inner hole of the fixed disc 1 and is connected together in a ball type universal joint mode, and the floating bearing disc 2 can freely swing relative to the fixed disc 1; the fixed disc 1 and the floating bearing disc 2 limit the floating bearing disc 2 to rotate along with the supercharger rotor through a circumferential positioning pin 3 arranged along the radial direction of the fixed disc and the floating bearing disc.
The inner hole wall surface of the fixed disc 1 is an inner concave spherical surface 101, and the periphery of the outer circle of the floating bearing disc 2 is an outer convex spherical surface 201 matched with the inner concave spherical surface 101; a gap is left between the concave spherical surface 101 and the convex spherical surface 201.
The fixed disk 1 is provided with 2 limiting grooves 105 along the circumferential direction.
A first positioning pin hole 102 and a second positioning pin hole 202 are respectively arranged in the fixed disc 1 and the floating bearing disc 2 along the radial direction; the first positioning pin hole 102 corresponds to the second positioning pin hole 202 in position, and a circumferential positioning pin 3 is arranged in the first positioning pin hole 102 and the second positioning pin hole 202; a gap is left between the second positioning pin hole 202 and the circumferential positioning pin 3 to ensure that the floating bearing disc 2 can swing freely within a certain range.
The diameter of the first positioning pin hole 102 is smaller than that of the second positioning pin hole 202, and the upper end of the first positioning pin hole 102 is provided with an internal thread 2021 which is matched and connected with the external thread of the circumferential positioning pin 3.
A first oil passage 103 is arranged on the fixed disc 1 along the circumferential direction, and 2 second oil passages 104 are arranged along the radial direction; 2 third oil channels 203 are arranged on the floating bearing disc 2 along the radial direction, and the positions of the third oil channels 203 correspond to the positions of the second oil channels 104; the first oil passage 103, the second oil passage 104, and the third oil passage 203 communicate with each other.
The tail end of the second oil duct 104 is communicated with the inner circle of the fixed disc 1, and the second oil duct 104 is communicated with the inner circle and the outer circle of the floating bearing disc 2; the diameters of the second oil passage 104 and the third oil passage 203 are different to ensure that the oil intake amount is not affected when the floating carrier tray 2 swings.
An oil inlet groove 204 is arranged in the middle of the convex spherical surface 201 of the floating bearing disc 2, and the oil inlet groove 204 is communicated with the second oil duct 104. The oil inlet groove 204 is positioned right at the joint of the concave spherical surface 101 and the convex spherical surface 201 to ensure the lubrication of the spherical surfaces and prevent the floating bearing disc 2 and the fixed disc 1 from being clamped and blocked.
The oil inlet groove 204 is circumferentially arranged.
And the floating bearing disc 2 is provided with a thrust bearing surface 4.
The working process of the embodiment is as follows:
the fixed disc 1 and the floating bearing disc 2 are connected through the concave spherical surface 101 and the convex spherical surface 201, a proper gap is formed between the two spherical surfaces to ensure that the floating bearing disc 2 can swing freely, the circumferential positioning pins 3 are used for limiting the floating bearing disc 2 to rotate along with the supercharger rotor, and a certain gap is formed between the second positioning pin holes 202 on the floating bearing disc 2 and the circumferential positioning pins 3 to ensure that the floating bearing disc 2 can swing freely within a certain range.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (7)
1. An adaptively calibrated thrust bearing for a turbocharger, comprising: comprises a fixed disc (1) and a floating bearing disc (2); the floating bearing disc (2) is embedded in an inner hole of the fixed disc (1) and is connected with the fixed disc in a ball type universal joint mode; the fixed disc (1) and the floating bearing disc (2) limit the floating bearing disc (2) to rotate along with the supercharger rotor through circumferential positioning pins (3) arranged along the radial direction of the fixed disc and the floating bearing disc;
the inner hole wall surface of the fixed disc (1) is an inner concave spherical surface (101), and the periphery of the outer circle of the floating bearing disc (2) is provided with an outer convex spherical surface (201) matched with the inner concave spherical surface (101); a gap is reserved between the concave spherical surface (101) and the convex spherical surface (201);
the fixed disc (1) is provided with a first oil channel (103) along the circumferential direction and at least one second oil channel (104) along the radial direction; at least one third oil channel (203) is arranged on the floating bearing disc (2) along the radial direction, and the third oil channel (203) corresponds to the second oil channel (104); the first oil channel (103), the second oil channel (104) and the third oil channel (203) are communicated with each other;
the tail end of the second oil duct (104) is communicated with the inner circle of the fixed disc (1), and the second oil duct (104) is communicated with the inner circle and the outer circle of the floating bearing disc (2);
an oil inlet groove (204) is formed in the middle of the convex spherical surface (201) of the floating bearing disc (2), and the oil inlet groove (204) is communicated with the second oil duct (104); the oil inlet groove (204) is positioned right at the joint of the inner concave spherical surface (101) and the outer convex spherical surface (201).
2. The turbocharger adaptive correction thrust bearing of claim 1, wherein: at least one limiting groove (105) is formed in the fixed disc (1) in the circumferential direction.
3. The turbocharger adaptive correction thrust bearing of claim 1, wherein: a first positioning pin hole (102) and a second positioning pin hole (202) are respectively arranged in the fixed disc (1) and the floating bearing disc (2) along the radial direction; the first positioning pin hole (102) corresponds to the second positioning pin hole (202), and a circumferential positioning pin (3) is arranged in the first positioning pin hole (102) and the second positioning pin hole (202); and a gap is reserved between the second positioning pin hole (202) and the circumferential positioning pin (3) to ensure that the floating bearing disc (2) can freely swing within a certain range.
4. The turbocharger adaptive correction thrust bearing of claim 3, wherein: the diameter of the first positioning pin hole (102) is smaller than that of the second positioning pin hole (202), and an internal thread (2021) which is matched and connected with the external thread of the circumferential positioning pin (3) is arranged at the upper end of the first positioning pin hole (102).
5. The turbocharger adaptive correction thrust bearing of claim 1, wherein: the second oil passage (104) and the third oil passage (203) have different diameters.
6. The turbocharger adaptive correction thrust bearing of claim 1, wherein: the oil inlet groove (204) is arranged along the circumferential direction.
7. The turbocharger adaptive correction thrust bearing of claim 1, wherein: and a thrust bearing surface (4) is arranged on the floating bearing disc (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711176144.2A CN108180159B (en) | 2017-11-22 | 2017-11-22 | Self-adaptive correction thrust bearing of turbocharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711176144.2A CN108180159B (en) | 2017-11-22 | 2017-11-22 | Self-adaptive correction thrust bearing of turbocharger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108180159A CN108180159A (en) | 2018-06-19 |
| CN108180159B true CN108180159B (en) | 2020-09-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711176144.2A Active CN108180159B (en) | 2017-11-22 | 2017-11-22 | Self-adaptive correction thrust bearing of turbocharger |
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| Country | Link |
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| CN (1) | CN108180159B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58134221A (en) * | 1982-02-04 | 1983-08-10 | Toshiba Corp | Oil film control device for thrust bearing |
| CN101688555A (en) * | 2008-04-21 | 2010-03-31 | 德州润滑系统有限公司 | Self aligning bearing and seal assembly |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1182208A1 (en) * | 1984-02-13 | 1985-09-30 | Bruss I Inzh Zheleznodorozhnog | Creep support |
| FR2608700B1 (en) * | 1986-12-23 | 1989-04-28 | Graffenstaden Engrenages | COMBINED RADIAL AND AXIAL PAD BEARING |
| CN201539371U (en) * | 2009-07-14 | 2010-08-04 | 郭溪泉 | Static-dynamic pressure self-aligning spindle oil film bearing of wind driven generator |
| CN201560810U (en) * | 2009-11-20 | 2010-08-25 | 常州环能涡轮动力有限公司 | Turbocharger thrust bearing |
| CN202441482U (en) * | 2012-01-18 | 2012-09-19 | 山东富源动力设备有限公司 | Thrust bearing of turbocharger |
| CN104747590A (en) * | 2013-12-30 | 2015-07-01 | 常州环能涡轮动力股份有限公司 | Gasoline engine turbocharger novel thrust bearing |
-
2017
- 2017-11-22 CN CN201711176144.2A patent/CN108180159B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58134221A (en) * | 1982-02-04 | 1983-08-10 | Toshiba Corp | Oil film control device for thrust bearing |
| CN101688555A (en) * | 2008-04-21 | 2010-03-31 | 德州润滑系统有限公司 | Self aligning bearing and seal assembly |
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| Publication number | Publication date |
|---|---|
| CN108180159A (en) | 2018-06-19 |
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