CN213235142U - Novel turbine rotor shaft and turbocharger - Google Patents
Novel turbine rotor shaft and turbocharger Download PDFInfo
- Publication number
- CN213235142U CN213235142U CN202021973213.XU CN202021973213U CN213235142U CN 213235142 U CN213235142 U CN 213235142U CN 202021973213 U CN202021973213 U CN 202021973213U CN 213235142 U CN213235142 U CN 213235142U
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- Prior art keywords
- floating bearing
- turbine rotor
- lubricating
- rotor shaft
- lubricated
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- 238000007667 floating Methods 0.000 claims abstract description 78
- 230000001050 lubricating effect Effects 0.000 claims abstract description 34
- 239000003921 oil Substances 0.000 claims abstract description 20
- 239000010687 lubricating oil Substances 0.000 claims abstract description 17
- 239000000945 filler Substances 0.000 abstract description 9
- 230000000694 effects Effects 0.000 abstract description 8
- 238000012546 transfer Methods 0.000 abstract description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 3
- 238000005461 lubrication Methods 0.000 description 13
- 238000005516 engineering process Methods 0.000 description 5
- 230000006872 improvement Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000004044 response Effects 0.000 description 4
- 230000001052 transient effect Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
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- 239000007790 solid phase Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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Abstract
The utility model relates to a novel turbine rotor axle and turbo charger, including axostylus axostyle and the turbine rotor who is connected on the axostylus axostyle, the overcoat has the floating bearing on the axostylus axostyle, offers the oil filler point that is used for water conservancy diversion lubricating oil on the floating bearing, is equipped with lubricated surface on the axostylus axostyle, and the internal surface clearance fit of lubricated surface and floating bearing is equipped with a plurality of parallel arrangement's recess on the lubricated surface, recess and oil filler point intercommunication, when the axostylus axostyle is rotatory for the floating bearing. The grooves which are arranged in parallel are arranged on the lubricating surface of the shaft rod, so that the hydrodynamic pressure effect on the surface of a friction pair of the turbine rotor shaft and the floating bearing can be enhanced, the friction loss of the friction pair of the turbine rotor shaft and the floating bearing is effectively reduced, and the energy transfer efficiency of the turbine rotor shaft and the mechanical efficiency of the turbocharger are effectively improved.
Description
Technical Field
The utility model relates to a turbo charger field especially relates to a novel turbine rotor axle and turbo charger.
Background
Turbocharging is a technique for converting the residual energy in the engine exhaust into increased engine power efficiency. The technology not only can obviously improve the dynamic property of the engine and reduce the fuel consumption of the engine, but also can effectively reduce harmful components in the exhaust gas discharged by the engine, and has the effects of energy conservation and environmental protection. Meanwhile, the technology is also an important means for recovering the engine power in the plateau area, so that the engine can meet the operation requirements of different altitudes. Therefore, turbocharger technology has become a trend in engines.
The mechanical efficiency of the turbocharger is improved, the acceleration and transient response characteristics of the automobile can be obviously improved, and the emission of harmful tail gas of the automobile can be effectively reduced. However, the operation friction loss of the turbocharger in the prior art, particularly the small turbocharger, is large, and the internal friction loss can reach and exceed 15% of the power generated by the turbine. Under the same conditions, the total efficiency of the supercharger can be improved by 5-7% by adopting the advanced antifriction technology, and can be improved by 20% even under the condition of smaller turbine tail gas flow, and the data is very considerable. The increased overall turbocharger efficiency provides a greater air flow to pressure ratio at low engine speeds, thereby greatly improving the operating characteristics of the engine.
In the prior art, a turbine rotor shaft in a turbocharger is a smooth metal shaft, the turbine rotor shaft is mounted in a bearing body of the turbocharger, the turbine rotor shaft is in a high-speed rotating state when the turbocharger works, and a floating bearing of the turbocharger enters an oil cavity of the bearing body through a lubricating oil inlet of the bearing body and finally reaches a lubricating oil inlet above the floating bearing. The floating bearing is isolated from the turbine rotor shaft through lubricating oil, a thin oil film is formed, and friction loss of rotation of the turbine rotor shaft is reduced. However, when the turbocharger runs at a high speed, the friction loss between the sealing ring and the sealing sleeve or the annular groove of the turbine rotor shaft is small, the friction loss between the turbine rotor shaft and the floating bearing friction pair is large, and the service life of the turbocharger can be shortened along with the long-term use of the turbine rotor shaft, so that the optimization and improvement of the lubrication condition of the turbine rotor shaft and the floating bearing friction pair are effective ways for reducing the running friction loss of the turbocharger, the running friction loss of the conventional turbocharger is reduced, and the supercharging effect of the turbocharger and the transient response characteristic of an engine can be further improved.
At present, the main method for reducing the friction loss of a turbine rotor shaft and a floating bearing friction pair of a turbocharger is to optimize the design of a floating bearing, for example, a certain convergent oil wedge is arranged in an inner hole of the floating bearing as disclosed in chinese patent CN102852976A, so that the friction loss is reduced by improving the lubricating effect, but the method has the following disadvantages: the machining process of the local oil wedge of the inner hole of the floating bearing is complex and the cost is high.
Since the turbine rotor shaft of the turbocharger and the support surface of the floating bearing constitute a friction pair, the friction loss is closely related to the surface state of the turbine rotor shaft and the surface state of the floating bearing respectively.
Accordingly, the inventors provide a novel turbine rotor shaft and turbocharger.
SUMMERY OF THE UTILITY MODEL
(1) Technical problem to be solved
The embodiment of the utility model provides two novel turbine rotor shafts, be equipped with the recess that a plurality of parallel article were gone and are set up through the lubricated surface on the axostylus axostyle, and the oil filler point intercommunication on recess and the floating bearing, when making the axostylus axostyle rotatory for the floating bearing, the clearance between lubricating oil packing recess and lubricated surface and the floating bearing internal surface, can strengthen the fluid dynamic pressure effect on turbine rotor shaft and the vice surface of floating bearing friction, effectively reduce the vice friction loss of turbine rotor shaft and floating bearing's friction, effectively improve turbine rotor shaft energy transfer efficiency and turbo charger's mechanical efficiency.
(2) Technical scheme
In a first aspect, the embodiment of the utility model provides a turbine rotor shaft, this turbine rotor shaft include the axostylus axostyle and be connected turbine rotor on the axostylus axostyle, the overcoat has the floating bearing on the axostylus axostyle, offer the oil filler point that is used for water conservancy diversion lubricating oil on the floating bearing, be equipped with lubricated surface on the axostylus axostyle, lubricated surface with the internal surface clearance fit of floating bearing, be equipped with a plurality of parallel arrangement's recess on the lubricated surface, the recess with the oil filler point intercommunication, the axostylus axostyle for when the floating bearing is rotatory, lubricating oil fills the recess and lubricated surface with clearance between the floating bearing.
Further, the lubricated surfaces include a first lubricated surface and a second lubricated surface, the floating bearings include a first floating bearing and a second floating bearing, an inner surface of the first floating bearing is in clearance fit with the first lubricated surface, the second floating bearing is in clearance fit with the second lubricated surface, and the inner surface of the first floating bearing covers the first lubricated surface and the inner surface of the second floating bearing covers the second lubricated surface.
Further, the first lubricated surface is spaced apart from the second lubricated surface, and the second lubricated surface is located between the first lubricated surface and the turbine rotor.
Furthermore, the shaft rod is further provided with a connecting surface for connecting the first lubricating surface and the second lubricating surface, and a limiting sleeve for spacing the first floating bearing and the second floating bearing is sleeved outside the connecting surface.
Further, an external thread is arranged at one end, far away from the turbine rotor, of the shaft rod.
Furthermore, the depth of the groove is more than or equal to 3 mu m and less than or equal to hp and less than or equal to 30 mu m, and the width of the groove is more than or equal to 30 mu m and less than or equal to d and less than or equal to 150 mu m.
Further, the area and the area density of the first lubricating surface and the second lubricating surface are the same, and the area density, namely the ratio of the concave area formed by the grooves on the lubricating surfaces to the lubricating surfaces is sp equal to 15% -35%.
Further, the included angle between the tangent of the groove on the lubricating surface and the axis of the shaft rod is more than or equal to 30 degrees and less than or equal to 150 degrees.
Further, the groove is of a continuous spiral line type or an interrupted line type.
In a second aspect, there is provided a turbocharger employing the first aspect, the turbocharger comprising a turbine rotor shaft.
A large number of theories and experimental researches show that the smoother the surface of the friction pair is, the better the surface is, the surface of the friction pair with certain microscopic geometrical morphology is not only beneficial to storing lubricating oil, but also easier to form a lubricating oil film between the surfaces of the friction pair, so that the surface of the friction pair does not have hard solid phase contact, and the aim of reducing friction and wear is achieved. The microscopic geometrical morphology of the surface of the friction pair has important influence on the tribological performance of the friction pair, the surface texture technology can change the geometrical morphology of the surface, and the purpose of improving the contact mode and the lubrication state of the surface is achieved, so that the frictional wear performance of the surface of the friction pair is improved, researches show that under the working conditions of low load and high relative speed, the lubrication antifriction effect of optimally designed microgrooves is remarkable, and the maximum average friction coefficient of the texture surface can be reduced by 64% compared with the maximum smooth surface.
(3) Advantageous effects
To sum up, the utility model discloses a lubricated surface on the axostylus axostyle is equipped with a plurality of parallel arrangement's recess, and the oil filler hole intercommunication on recess and the floating bearing, when making the axostylus axostyle rotatory for the floating bearing, the clearance between lubricating oil packing recess and lubricated surface and the floating bearing internal surface, can strengthen the fluid dynamic pressure effect on friction pair surface, can show improvement oil film bearing capacity, reduce the swing of turbine rotor shaft, effectively keep apart friction pair surface, reduce the friction loss between turbine rotor shaft and floating bearing, improve turbo charger's mechanical efficiency, transient response characteristic, reliability and life, reduce the hysteresis of turbine.
Meanwhile, under poor lubrication conditions such as when the turbine rotor shaft is just started or just stops moving, the lubricating oil stored in the groove overflows under the driving of friction force, the lubricating liquid required by the surface of the friction pair is supplemented, and therefore effective lubrication on the peripheral surface of the turbine rotor shaft is formed.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments of the present invention will be briefly described below, and it is obvious that the drawings described below are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
Fig. 1 is a schematic structural view of a turbine rotor shaft according to the present invention.
FIG. 2 is another schematic view of a turbine rotor shaft according to the present invention.
Fig. 3 is an enlarged view of a in fig. 2.
Fig. 4 is a cross-sectional view B-B of fig. 2.
In the figure:
6-floating bearing; 7-a limiting sleeve; 31-an axle rod; 32-a turbine rotor; 33-a first lubricated surface; 34-a second lubricated surface; 35-a groove; 36-a connecting surface; 61-oil hole; 62-a first floating bearing; 63-second floating bearing.
Detailed Description
The following describes embodiments of the present invention in further detail with reference to the accompanying drawings and examples. The following detailed description of the embodiments and the accompanying drawings are provided to illustrate the principles of the invention, but are not intended to limit the scope of the invention, i.e., the invention is not limited to the embodiments described, but covers any modifications, substitutions and improvements in the parts, components and connections without departing from the spirit of the invention.
It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present application will be described in detail below with reference to the embodiments with reference to the attached drawings.
Fig. 1 is the utility model discloses a turbine rotor shaft's structural schematic diagram, as shown in fig. 1, this turbine rotor shaft includes axostylus axostyle 31 and the turbine rotor 32 on connecting the axostylus axostyle 31, the overcoat has floating bearing 6 on the axostylus axostyle 31, the oil filler point 61 that is used for water conservancy diversion lubricating oil has been offered on the floating bearing 6, be equipped with lubricated surface on the axostylus axostyle 31, lubricated surface and floating bearing 6's internal surface clearance fit, be equipped with a plurality of parallel arrangement's that parallel on the lubricated surface recess 35, recess 35 and oil filler point 61 intercommunication, when axostylus axostyle 31 is rotatory for floating bearing 6, the.
The utility model discloses a lubricated surface on the axostylus axostyle is equipped with the recess that a plurality of article row settings side by side, and the oil filler point on recess and the floating bearing intercommunication, when making the axostylus axostyle rotatory for the floating bearing, the clearance between lubricating oil filling recess and lubricated surface and the floating bearing internal surface, can strengthen the fluid dynamic pressure effect on friction pair surface, can show improvement oil film bearing capacity, reduce the swing of turbine rotor shaft, effective isolation friction pair surface, reduce the friction loss between turbine rotor shaft and floating bearing, improve the energy transfer efficiency of turbine pivot, transient response characteristic, reliability and life, reduce turbine pivot hysteresis.
As a preferred embodiment, fig. 2 is another structural schematic diagram of a turbine rotor shaft according to an embodiment of the present invention, as shown in fig. 1 and fig. 2, the lubrication surfaces include a first lubrication surface 33 and a second lubrication surface 34, the floating bearing 6 includes a first floating bearing 62 and a second floating bearing 63, an inner surface of the first floating bearing 62 is in clearance fit with the first lubrication surface 33, the second floating bearing 63 is in clearance fit with the second lubrication surface 34, an inner surface of the first floating bearing 62 covers the first lubrication surface 33 and an inner surface of the second floating bearing 63 covers the second lubrication surface 34, and an end of the shaft 31 away from the turbine rotor 32 is provided with an external thread for connecting with an external lock nut. The inner surface of the first floating bearing and the inner surface of the second floating bearing are respectively covered with the first lubricating surface and the second lubricating surface, namely the groove is covered, so that lubricating oil in the groove overflows under the driving of friction force, lubricating liquid required by the surface of a friction pair is supplemented, sufficient lubrication on the lubricating surfaces and the inner surface of the floating bearing is formed, the lubricating oil stored in the groove is extruded to form an extrusion oil film due to the radial rotation of a turbine rotor shaft, the rigidity of the oil film is increased, the dry friction phenomenon between the floating bearing and a turbine rotating shaft during high-speed operation is effectively avoided, and the abrasion on the turbine rotating shaft is reduced.
As another preferred embodiment, as shown in FIGS. 3 and 4, the grooves 35 have a depth of 3 μm. ltoreq. hp.ltoreq.30 μm and a width of 30 μm. ltoreq. d.ltoreq.150. mu.m, and the grooves 35 have a continuous spiral line type or a discontinuous line type.
As other alternative embodiments.
Preferably, as shown in FIG. 2, the first lubricated surface 33 is spaced apart from the second lubricated surface 34, and the second lubricated surface 34 is located between the first lubricated surface 33 and the turbine rotor 32.
Preferably, as shown in fig. 1 and 2, the shaft 31 is further provided with a connecting surface 36 for connecting the first lubricating surface 33 and the second lubricating surface 34, and the connecting surface 36 is externally sleeved with a stop collar 7 for spacing the first floating bearing 62 and the second floating bearing 63.
Preferably, as shown in fig. 2, the first lubricating surface 33 and the second lubricating surface 34 have the same area and area density, and the area density, i.e., the ratio sp of the depressed area formed by the grooves 35 on the lubricating surfaces to the lubricating surfaces is 15% -35%.
Preferably, as shown in FIG. 3, the angle α of a tangent n to the groove 35 at the lubricating surface, which is a straight line formed by the groove 35 in its length direction perpendicular to the radial direction of the shaft 31, is 30 DEG or more and 150 DEG or less to the axis m of the shaft 31.
It should be clear that the embodiments in this specification are described in a progressive manner, and the same or similar parts in the embodiments are referred to each other, and each embodiment focuses on the differences from the other embodiments. The present invention is not limited to the specific steps and structures described above and shown in the drawings. Also, a detailed description of known process techniques is omitted herein for the sake of brevity.
The above description is only an example of the present application and is not limited to the present application. Various modifications and alterations to this application will become apparent to those skilled in the art without departing from the scope of this invention. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the scope of the claims of the present application.
Claims (10)
1. The turbine rotor shaft is characterized by comprising a shaft rod (31) and a turbine rotor (32) connected to the shaft rod (31), wherein a floating bearing (6) is sleeved outside the shaft rod (31), an oil filling hole (61) used for guiding lubricating oil is formed in the floating bearing (6), a lubricating surface is arranged on the shaft rod (31), the lubricating surface is in clearance fit with the inner surface of the floating bearing (6), a plurality of parallel grooves (35) are formed in the lubricating surface, the grooves (35) are communicated with the oil filling hole (61), and when the shaft rod (31) rotates relative to the floating bearing (6), the lubricating oil fills the grooves (35) and gaps between the lubricating surface and the inner surface of the floating bearing (6).
2. The turbine rotor shaft according to claim 1, characterized in that the lubricated surfaces comprise a first lubricated surface (33) and a second lubricated surface (34), the floating bearing (6) comprises a first floating bearing (62) and a second floating bearing (63), an inner surface of the first floating bearing (62) is clearance fitted with the first lubricated surface (33), the second floating bearing (63) is clearance fitted with the second lubricated surface (34), and an inner surface of the first floating bearing (62) covers the first lubricated surface (33) and an inner surface of the second floating bearing (63) covers the second lubricated surface (34).
3. The turbine rotor shaft according to claim 2, wherein the first lubricating surface (33) is spaced apart from the second lubricating surface (34), and the second lubricating surface (34) is located between the first lubricating surface (33) and the turbine rotor (32).
4. The turbine rotor shaft according to claim 2, characterized in that the shaft (31) is further provided with a connecting surface (36) for connecting the first lubricating surface (33) with the second lubricating surface (34), and the connecting surface (36) is externally sleeved with a stop collar (7) for spacing the first floating bearing (62) and the second floating bearing (63).
5. A turbine rotor shaft according to claim 1, characterised in that the shaft (31) is provided with an external thread at its end remote from the turbine rotor (32).
6. The turbine rotor shaft according to claim 1, characterized in that the grooves (35) have a depth of 3 μm ≦ hp ≦ 30 μm and a width of 30 μm ≦ d ≦ 150 μm.
7. A turbine rotor shaft according to claim 2, characterised in that the first (33) and second (34) lubricating surfaces have the same area and area density, and the area density, i.e. the ratio sp of the recessed area formed by the grooves (35) at the lubricating surface, to the lubricating surface is 15-35%.
8. A turbine rotor shaft according to claim 7, characterised in that the tangent to the groove (35) at the lubricated surface encloses an angle of 30 ° ≦ α ≦ 150 ° with the axis of the shaft (31).
9. The turbine rotor shaft according to claim 1, characterized in that the groove (35) is of a continuous helical or discontinuous line type.
10. A turbocharger comprising a turbine rotor shaft according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021973213.XU CN213235142U (en) | 2020-09-03 | 2020-09-03 | Novel turbine rotor shaft and turbocharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021973213.XU CN213235142U (en) | 2020-09-03 | 2020-09-03 | Novel turbine rotor shaft and turbocharger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN213235142U true CN213235142U (en) | 2021-05-18 |
Family
ID=75873322
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202021973213.XU Expired - Fee Related CN213235142U (en) | 2020-09-03 | 2020-09-03 | Novel turbine rotor shaft and turbocharger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN213235142U (en) |
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2020
- 2020-09-03 CN CN202021973213.XU patent/CN213235142U/en not_active Expired - Fee Related
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| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20210518 |