CN109790848A - Turbocharger with oil-free hydrostatic bearing - Google Patents
Turbocharger with oil-free hydrostatic bearing Download PDFInfo
- Publication number
- CN109790848A CN109790848A CN201680089607.9A CN201680089607A CN109790848A CN 109790848 A CN109790848 A CN 109790848A CN 201680089607 A CN201680089607 A CN 201680089607A CN 109790848 A CN109790848 A CN 109790848A
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- CN
- China
- Prior art keywords
- bearing
- turbocharger
- compressor
- hydrostaticjournal
- vibration damper
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/18—Lubricating arrangements
- F01D25/22—Lubricating arrangements using working-fluid or other gaseous fluid as lubricant
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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
- F04D29/051—Axial thrust balancing
- F04D29/0513—Axial thrust balancing hydrostatic; hydrodynamic thrust 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
- F04D29/0516—Axial thrust balancing balancing pistons
-
- 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
- F04D29/057—Bearings hydrostatic; hydrodynamic
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
- F16C32/0614—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings
- F16C32/0622—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings via nozzles, restrictors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/50—Bearings
- F05D2240/53—Hydrodynamic or hydrostatic bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
- F16C2360/24—Turbochargers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A kind of turbocharger for internal combustion engine, the compressed air that the turbocharger is supplied by the compressor (11) of turbocharger, by hydrostatic bearing (the 15,16) support on radial and axial direction, and sufficiently high pressure is pressurized to support the rotor of turbocharger to the compressed air by individual booster compressor (17).Turbocharger hydrostatic bearing (15,16) generates damping action using wire mesh or distributing frcition damper (33,41).
Description
Government Licensing Rights
The agreement that the present invention is FA86500-14-M-2470 according to the contract number that United States Air Force is authorized, in U.S. government's branch
Hold lower completion.U.S. government has certain rights in the invention.
Technical field
The present invention relates generally to turbocharger, and relate more specifically to have the oil-free static pressure with mechanical damper
The turbocharger of bearing.
Background technique
Turbocharger using the hot gas of discharge as driving force come the air of compressed supply to engine.Engine row
Device of air drives turbine, and the turbine drives compressor is by the air supply of compression to engine.Since air compresses, improve
The performance of engine.
The turbocharger of the prior art needs to depend on using the axis support system of oil-lubricated bearing, the oil-lubricated bearing
The viscosity of the fluid of fluid dynamic film is provided within the bearing.The compressor that component on axis generally includes the one end for being installed to axis turns
The turbine rotor of son and the other end for being installed to axis.
During turbocharger operation, compressor and turbine can generate significant radial force and axial force, they
It is reacted in shell by journal bearing and axial thrust bearing.This is usually realized by pressurization oil lubrication system,
To remove heat and reduce rolling resistance.For turbocharger, lubricating system needs oil cooler and pump to mention for bearing
For enough pressure, while preventing oily coking.If oil pressure loses loss or oil is polluted by internal combustion (IC) machine, the performance meeting of bearing
Decline since lubrication or cooling loss occurs, catastrophic failure occurs so as to cause turbocharger bearing system.In order to anti-
Only oily coking, some advanced high-temperature turbine boosters are in bear box using additional coolant system further to drop
The temperature of low bearing and bearing fluid.But individual bearing lubrication system also will increase the weight of aircraft simultaneously, and weight pair
It is vital for the aircraft of such as unpiloted aviation aircraft or UAV etc.
Summary of the invention
Invention advantageously provides a kind of turbocharger, the air supply for that will compress to internal combustion engine.The turbine
Booster includes by turbine driven compressor and in the radial and axial directions by the rotor of hydrostatic bearing support.It comes from
The compressed air of compressor is directed to booster compressor, this can increase the pressure for hydrostatic bearing.The booster compressor
It can be driven by the power transmission shaft of I/C engine or the separate motors of such as motor.
Hydrostatic bearing is oil-free and other than the compressed air from compressor and booster compressor without any other
Fluid allows higher temperature exposure and limits the total weight of turbocharger, (wherein weighs for use in lightweight aircraft
Measure most important to its performance), such as unmanned aviation aircraft (UAV).
Hydrostatic bearing includes the bearing of journals set on turbine pump center, which has cantilevered compressor and turbine
Machine.Wherein the bearing of journals inhibits to vibrate using mechanical or frcition damper.Mechanical damper can be loopful shape damper or
Around the circumferentially spaced arch damper of bearing.Also distributing frcition damper can be used, have complete in arrangement
Ring in pellet shapes component.
Detailed description of the invention
When considered in conjunction with the accompanying drawings, it by reference to detailed description below, will be better understood of the invention more complete
Meaning and its adjoint advantage and feature, in which:
Fig. 1 shows the schematic diagram of the turbocharger with oil-free hydrostatic bearing of the invention；
Fig. 2 shows the viewgraph of cross-section of the turbocharger with oil-free hydrostatic bearing of the invention；
Fig. 3 shows the viewgraph of cross-section of turbocharger of the invention, and wherein turbocharger has band static thrust
The oilless bearing and mechanical damper of bearing；
Fig. 4 shows the turbocharger with oilless bearing and mechanical damper of the invention (with dummy piston)
Viewgraph of cross-section；
Fig. 5 shows the cross section view of the turbocharger with oilless bearing and distributing frcition damper of the invention
Figure；
Fig. 6 shows the viewgraph of cross-section of the distributing frcition damper in the turbocharger of Fig. 5；
Fig. 7 shows the cross-sectional side view of a frcition damper with complete annular shape；
Fig. 8 shows the second embodiment of frcition damper, wherein three segmental arcs are arranged around shell；And
Fig. 9 shows the flow schematic diagram for entering and leaving the fluid of hydrostatic bearing and dummy piston.
Specific embodiment
The present invention relates to a kind of turbocharger, with oil-free hydrostatic bearing and mechanical or distributing frcition damper.
The gas of compressor discharge is used as the working fluid of the hydrostatic bearing with booster compressor, to realize enough stream within the bearing
Body dead load ability and damping.The present invention is cold by omitting the temperature sensitivity oil lubricant in prior art turbocharger, oil
But device, oil pump and bear box cooling system improve reliability and durability.This is by utilizing the compression from compressor
Gas (air) carrys out support shaft in a manner of hydrostatic pressure and realizes.In order to reduce the total power consumption of system, bearing feed system
It is pressurized by turbocharger compressor, is then boosted using oil-free positive displacement compressor by system to required work pressure in advance
Power, the oil-free positive displacement compressor directly pass through the driving of accessory drive axis 18 or are driven by miniature motor 19.In any one
In the case of, total power consumption is all relatively small, so that the influence to internal combustion (IC) machine performance is minimum.
Fig. 1 shows the schematic diagram of the turbocharger with oil-free hydrostatic bearing.The turbocharger includes compressor
11 and turbine 12, the compressor 11 and turbine 12 connect with shared rotor 13.Rotor 13 is by one or more radial static pressure
Bearing 15 is supported with one or more axial flow of fluid static pressure (or thrust) bearings 16 in the axial direction in radial directions.
The hot gas that internal combustion (IC) machine 14 is discharged is supplied to turbine 12, which drives compressor by rotor 13
11 with compressed air.Then by the air delivery of compression to engine 14.A part of compressed air from compressor 11 is arranged
It is supplied to booster compressor 17 out and by booster compressor entrance, the compressed air for being supplied to booster compressor 17 can will press
Power is increased sufficiently to support the amount of rotor 13 in a manner of hydrostatic pressure.The outlet of booster compressor 17 and one or more static pressure
The smooth body connection of bearing 16.
Booster compressor 17 can directly be driven by engine 14 by the compression cylinder in accessory drive axis 18, engine
It is dynamic, or driven by the separate motors of such as motor 19.
Hydrostatic fluid foil bearing is capable of providing many advantages, makes it particularly suited for high-speed turbine booster shaft/rotor
Support system.These advantages include: that can support heavy load；Hydrostatic bearing bearing capacity is that Fluid pressure acts in bearing area
Pressure drop function；Since surface does not contact, so the service life is long (theory unlimited)；And very big rigidity and damping are
Number, so as to provide accurate positioning and control.
Compressed air is used to replace oil as applying the working fluid in the hydrostatic bearing of turbocharger to additionally provide
The advantages of such as eliminating lubricant failure problem, allows the higher operating temperature of turbine inlet.Oily overheat is prevented due to eliminating
Required cooling duct, it also reduces the thermal stress in bear box.With the increase of operating temperature in lean burn internal combustion engine, need
The bearing of higher temperature is wanted to support the rotor of turbocharger.The small aircraft of such as unmanned plane etc is required to bear
Due to the bearing of the more high load of motor-driven generation, this is motor-driven including lasting high G turning and the operation in turbulent air.This
Outside, it will not be rubbed after bearing removing due to internal part, so hydrostatic bearing is not needed using advanced coating, because
This, it might even be possible to the high-temperature material including ceramics is used as bearing material.Static pressure axis in high pressure turbocharger application
Hold major advantage is to the boost pressures provided using turbocharger compressor to promote small-sized oilless (oil free) compressor in advance
The pressure of entrance, to maximize the load capacity under all turbocharger service conditions.Bearing can light a fire it in IC machine
It is preceding or be lifted in the moment of igniting, it is operated with being realized in entire working range without abrasion.
Another remarkable advantage that hydrostatic bearing provides is that they can provide accurate allowance control.This is for maximizing
The efficiency of turbocharger is even more important, and medium-small diameter is equal without cover compressor and turbine (on its radial and axial direction)
Need to minimize gap to reduce leakage.The accurate control of the axis of this rigidity and damping to height, so that static pressure axis
It holds and is very suitable to apply in unmanned air line turbocharger.
Fig. 2 shows the viewgraph of cross-section of the turbocharger with oil-free hydrostatic bearing of Fig. 1.The turbocharger packet
Include suction port of compressor 21 and compressor outlet 22, turbine inlet 23 and turbine outlet 24, one or more bearings of journals 25,
Thrust bearing 26, pivot journal 27, bear box 28, bearing gas supply accessory 29, V-belt 30 and seal area 31.The turbocharging
Device includes cantilevered compressor and turbine element and the sealing element for sealing bearing bore, and wherein turbine element is in being located at
Bearing in heart shell.Thrust bearing 26 is located at the center of axis, to provide symmetrical ventilation for each hydrostaticjournal bearing 25
Hole.The turbine design of Fig. 2 simplifies bearing bore component.Bearing is full symmetric relative to the central plane of thrust bearing 26 and sets
Meter, thus provides component reuse, this turbocharger for facilitating the existing production to not hydrostatic bearing is sold
After upgrade.Pressure-feed air bearing in Fig. 2 is substituted for the bear box of prior art turbocharger.
Fig. 3 shows turbocharger, has the machinery being located between bear box 28 and hydrostaticjournal bearing 25
Damper 33.The mechanical friction damper is metal mesh type.Static pressure thrust bearing 34 is located at left side, axial rub retainer
35 are located at right side.
Fig. 4 is shown similar to the turbocharger in Fig. 3, but has dummy piston chamber in the left side of turbocharger
36.Mechanical friction damper 33 is then located on position identical with the mechanical damper 33 in Fig. 3.
The turbocharger of the embodiment of Fig. 5 uses the distributing frcition damper arranged in a manner of complete circle.These
Frcition damper is pellet shapes element or sphere made of ceramics or metal material, by rubbing against one another in a limited space
And generate damping.Fig. 6 is shown in which the detailed view of a distributing frcition damper 41, the distributing frcition damper 41
With sealing element 42, snap ring component 43, sealing element or cover board 44 and for compressing frcition damper 41 in a limited space
Spring 45.A gap 47 is formed between bear box 28 and floating journal bearings 25.Axle journal 46 is floating in shell 28.Dispersion
Formula frcition damper 41 is formed by pellet shapes component, when bearing journal floats (bearing is supported on the ground by damper),
Pellet shapes component can then occupy the complete circle space between bearing and shell.These spherical components can be metal or ceramic
, and damper is played the role of to generate damping by phase mutual friction.Distributing frcition damper behaves as
Incompressible fluid and simulation oil squeeze-film damping device.
Two frcition dampers 33 used in embodiment shown in Fig. 3 and Fig. 4 are by the netted material of metal wire knitted
The complete 360 degree of annular friction dampers formed, as produced by Metex Corporation (www.metexcorp.com)
Shock and vibration isolator).Fig. 7 is shown between the bearing of journals 25 on fixed bear box and inner surface on the outer surface
Loopful shape frcition damper 33 side view.The frcition damper 33 is circular ring shape.Fig. 8 shows the of frcition damper
Two embodiments, which use three arch portions 51, they are equally spacedly arranged around the bearing of journals 25.
Fig. 9 shows the flow schematic diagram in air supply and ventilating system.High-pressure spray enters centre bore by accessory 29.
Then it flows into the center cavity in bearing journal 25 and gap 47.When needed, sub-fraction high-pressure spray will by gap 47 to
Damper 41 or damper 33 provide coolant.And most of high-pressure spray then shunts in bearing journal 25；Most of stream high pressure
Half in stream will be transmitted to the bearing for being located at compressor side, and the other half then flows to the bearing positioned at turbine side.When quiet
After last item holds middle offer lift, high-pressure spray by from the central part of hydrostatic bearing exit into runner 27 and bearing journal 25 it
Between in the low pressure chamber 50 that is formed, the chamber 51 between runner 27 and axis 13 is then entered by a series of apertures 60 in runner 27.
After entering chamber 51, high-pressure spray flows through a series of apertures 61 in runner 27 and escapes into turbine flow path 24,
And it is finally discharged.The air can provide cooling for the rear side of turbine rotor 12.The other half then transit chamber of bearing high-pressure spray
52 leave and are discharged to environmental pressure by control hole 62.
Air-flow in one-direction thrust bearing 34 or thrust piston 36 separates across hole 63 and enters from center pressure fittings 29
Chamber 53.Chamber 53 promotes thrust bearing or thrust piston moves air through hole 64 and enters thrust chamber 54.Sub-fraction air-flow is from chamber
54 release in compressor.And most of air-flow then releases in chamber 52 and is discharged by aperture 62.
It will be understood by those skilled in the art that the content that the present invention is not limited to have been particularly shown and described above.In addition, on unless
Face is mentioned in contrast, it should be noted that, all attached drawings are not drawn on scale.Do not depart from the scope of the present invention and
In the case where spirit, various modifications can be carried out according to the above instruction and variation, and scope and spirit of the present invention are only by appended power
The limitation that benefit requires.
Claims (according to the 19th article of modification of treaty)
1. a kind of turbocharger for internal combustion engine, comprising:
Compressor, compressed air is to assist the burning in internal combustion engine；
Turbine drives compressor using the hot gas of internal combustion engine discharge；
Rotor is connected between the compressor of turbocharger and turbine；
First hydrostaticjournal bearing and the second hydrostaticjournal bearing, for radially and rotatably supporting rotor；
First vibration damper, between bear box and the first hydrostaticjournal bearing；Second vibration damper is located at bearing
Between shell and second fluid hydrostaticjournal bearing；
Booster compressor with entrance and exit, the entrance of the booster compressor are connected to the outlet of compressor, and the increasing
The outlet of pressure compressor is connected to the first hydrostatic bearing and the second hydrostatic bearing, to support rotor；And
The booster compressor is by the pressure boost of the compressed air from compressor to higher to support rotor.
2. turbocharger according to claim 1, wherein the rotor includes static pressure axial thrust bearing, the axis
Axial thrust bearing is supplied with the compressed air of the booster compressor.
3. turbocharger according to claim 1, wherein the booster compressor is driven by the power transmission shaft of internal combustion engine
It is dynamic.
4. turbocharger according to claim 1, wherein the booster compressor is by motor drive.
5. turbocharger according to claim 1, wherein the booster compressor is the additional pressure in the internal combustion engine
Contracting cylinder.
6. turbocharger according to claim 1, wherein in first vibration damper and the second vibration damper
Each be wire mesh damper.
7. turbocharger according to claim 1, in which: first vibration damper includes multiple element, multiple
Element be enclosed between first hydrostaticjournal bearing and the bear box formed it is intracavitary；And
Second vibration damper includes multiple element, and the multiple element is enclosed in second hydrostaticjournal bearing and axis
Hold formed between shell it is intracavitary.
8. turbocharger according to claim 7, wherein in first vibration damper and the second vibration damper
The multiple element of each is ceramic spherical and is made of ceramics.
9. turbocharger according to claim 7, wherein in first vibration damper and the second vibration damper
The multiple element of each is metal ball shaped and consists of metal.
10. turbocharger according to claim 6, wherein the wire mesh damper is circular ring shape damper.
11. turbocharger according to claim 6, in which:
First vibration damper includes multiple arch, and the multiple arch surrounds the first hydrostaticjournal bearing circumferentially cloth
It sets；And
Second vibration damper includes multiple arch, and the multiple arch surrounds the second hydrostaticjournal bearing circumferentially cloth
It sets.
12. turbocharger according to claim 6, wherein the wire mesh damper is cooling using cooling air,
The cooling air is also used to cool down first hydrostaticjournal bearing and the second hydrostaticjournal bearing.
13. turbocharger according to claim 1, wherein be used for first hydrostaticjournal bearing and the second static pressure
The compressed air of the bearing of journals is also used to the hub side of cooling turbine rotor.
Claims (13)
1. a kind of turbocharger for internal combustion engine, comprising:
Compressor, compressed air is to assist the burning in internal combustion engine；
Turbine drives compressor using the hot gas of internal combustion engine discharge；
Rotor is connected between the compressor of turbocharger and turbine；
First hydrostaticjournal bearing and the second hydrostaticjournal bearing, for radially and rotatably supporting rotor；
First vibration damper, between bear box and the first hydrostaticjournal bearing；Second vibration damper is located at bearing
Between shell and second fluid hydrostaticjournal bearing；
Booster compressor has the entrance for being connected to compressor and is connected to the first hydrostatic bearing and the second hydrostatic bearing to support
The outlet of rotor；And
The booster compressor is by the pressure boost of the compressed air from compressor to the higher pressure that can support rotor.
2. turbocharger according to claim 1, wherein the rotor includes static pressure axial thrust bearing, the increasing
Compressor is pressed to supply compressed air to the static pressure axial thrust bearing.
3. turbocharger according to claim 1, wherein the booster compressor is driven by the power transmission shaft of internal combustion engine
It is dynamic.
4. turbocharger according to claim 1, wherein the booster compressor is by motor drive.
5. turbocharger according to claim 1, wherein the booster compressor is the additional pressure in the internal combustion engine
Contracting cylinder.
6. turbocharger according to claim 1, wherein in first vibration damper and the second vibration damper
Each be wire mesh damper.
7. turbocharger according to claim 1, in which: first vibration damper includes multiple element, multiple
Element be enclosed between first hydrostaticjournal bearing and the bear box formed it is intracavitary；And
Second vibration damper includes multiple element, and the multiple element is enclosed in second hydrostaticjournal bearing and axis
Hold formed between shell it is intracavitary.
8. turbocharger according to claim 7, wherein in first vibration damper and the second vibration damper
The multiple element of each is ceramic spherical and is made of ceramics.
9. turbocharger according to claim 7, wherein in first vibration damper and the second vibration damper
The multiple element of each is metal ball shaped and consists of metal.
10. turbocharger according to claim 6, wherein the wire mesh damper is circular ring shape damper.
11. turbocharger according to claim 6, in which:
First vibration damper includes multiple arch, and the multiple arch surrounds the first hydrostaticjournal bearing circumferentially cloth
It sets；And
Second vibration damper includes multiple arch, and the multiple arch surrounds the second hydrostaticjournal bearing circumferentially cloth
It sets.
12. turbocharger according to claim 6, wherein the wire mesh damper is cooling using cooling air,
The cooling air is also used to cool down first hydrostaticjournal bearing and the second hydrostaticjournal bearing.
13. turbocharger according to claim 1, wherein be used for first hydrostaticjournal bearing and the second static pressure
The compressed air of the bearing of journals is also used to the hub side of cooling turbine rotor.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2016/044056 WO2018022015A1 (en) | 2016-07-26 | 2016-07-26 | Turbocharger with oil-free hydrostatic bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN109790848A true CN109790848A (en) | 2019-05-21 |
Family
ID=56682257
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680089607.9A Pending CN109790848A (en) | 2016-07-26 | 2016-07-26 | Turbocharger with oil-free hydrostatic bearing |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP3491250A1 (en) |
| JP (1) | JP2019527316A (en) |
| KR (1) | KR20190028541A (en) |
| CN (1) | CN109790848A (en) |
| WO (1) | WO2018022015A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113074023A (en) * | 2021-04-12 | 2021-07-06 | 哈尔滨工业大学 | Oil-free lubrication high-power-density zero-steam leakage steam turbine |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110043561A (en) * | 2019-04-25 | 2019-07-23 | 西安交通大学 | A kind of pressure applied to turbocharger automatically supplies gas-static bush(ing) bearing |
| CN110080874A (en) * | 2019-04-25 | 2019-08-02 | 西安交通大学 | A kind of pressure applied to turbocharger automatically supplies gas-static thrust slide bearing |
| DE102019127456A1 (en) * | 2019-10-11 | 2021-04-15 | Atlas Copco Energas Gmbh | Method for operating a turbo machine |
| CN113027922B (en) * | 2021-03-12 | 2021-12-07 | 山东赛马力发电设备有限公司 | High-speed air suspension bearing |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61126327A (en) * | 1984-11-22 | 1986-06-13 | Nissan Motor Co Ltd | Pneumatic bearing device in turbocharger |
| CN1217764A (en) * | 1995-09-18 | 1999-05-26 | 涡轮动力系统有限公司 | Turbocharging system with internally-fitted assisting electric motor and cooling system thereof |
| JP2009236068A (en) * | 2008-03-28 | 2009-10-15 | Ihi Corp | Supercharger |
| CN201396194Y (en) * | 2009-05-11 | 2010-02-03 | 马惠秋 | Turbocharger supported by static pressure gas bearing with self-lubricating sliding supercharge flow channel groove |
| DE102010006843A1 (en) * | 2010-02-03 | 2011-08-04 | Eble, Markus, 70199 | Turbocharger, particularly exhaust gas turbocharger for internal combustion engine, has turbine, compressor and rotor in housing, where rotor has shaft with compressor wheel of compressor and turbine wheel of turbine |
| DE102012024845A1 (en) * | 2012-12-19 | 2014-06-26 | Daimler Ag | Storage arrangement for rotor on housing of exhaust gas turbocharger for internal combustion engine of vehicle, has storage unit that has support element which is formed from wire mesh for damping vibrations of rotor |
| CN104454992A (en) * | 2014-09-30 | 2015-03-25 | 湖南大学 | Elastic radial air bearing |
| CN105003593A (en) * | 2015-07-17 | 2015-10-28 | 厦门理工学院 | Hybrid bearing supporting shock absorber used for cone shaft |
| CN105452689A (en) * | 2013-08-20 | 2016-03-30 | 申克罗泰克有限责任公司 | Aerostatic bearing for a rotor, in particular in a balancing machine |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6125542U (en) * | 1984-07-20 | 1986-02-15 | 日産自動車株式会社 | Turbo gear bearing device |
| JPS6132532U (en) * | 1984-07-30 | 1986-02-27 | 日本精工株式会社 | Turbocharger bearing device |
| BRPI0504326A (en) * | 2005-10-11 | 2007-06-26 | Brasil Compressores Sa | aerostatic bearing fluid compressor, aerostatic bearing compressor control system and aerostatic bearing compressor control method |
| US8182206B2 (en) * | 2006-10-17 | 2012-05-22 | Borgwarner Inc. | Ring seals for gas sealing and vibration damping |
| JP2010174811A (en) * | 2009-01-30 | 2010-08-12 | Toyota Motor Corp | Bearing structure of turbocharger |
| JP2012177457A (en) * | 2011-02-28 | 2012-09-13 | Ntn Corp | Foil bearing |
-
2016
- 2016-07-26 EP EP16750560.1A patent/EP3491250A1/en not_active Withdrawn
- 2016-07-26 CN CN201680089607.9A patent/CN109790848A/en active Pending
- 2016-07-26 JP JP2019504013A patent/JP2019527316A/en active Pending
- 2016-07-26 KR KR1020197004853A patent/KR20190028541A/en not_active Application Discontinuation
- 2016-07-26 WO PCT/US2016/044056 patent/WO2018022015A1/en unknown
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61126327A (en) * | 1984-11-22 | 1986-06-13 | Nissan Motor Co Ltd | Pneumatic bearing device in turbocharger |
| CN1217764A (en) * | 1995-09-18 | 1999-05-26 | 涡轮动力系统有限公司 | Turbocharging system with internally-fitted assisting electric motor and cooling system thereof |
| JP2009236068A (en) * | 2008-03-28 | 2009-10-15 | Ihi Corp | Supercharger |
| CN201396194Y (en) * | 2009-05-11 | 2010-02-03 | 马惠秋 | Turbocharger supported by static pressure gas bearing with self-lubricating sliding supercharge flow channel groove |
| DE102010006843A1 (en) * | 2010-02-03 | 2011-08-04 | Eble, Markus, 70199 | Turbocharger, particularly exhaust gas turbocharger for internal combustion engine, has turbine, compressor and rotor in housing, where rotor has shaft with compressor wheel of compressor and turbine wheel of turbine |
| DE102012024845A1 (en) * | 2012-12-19 | 2014-06-26 | Daimler Ag | Storage arrangement for rotor on housing of exhaust gas turbocharger for internal combustion engine of vehicle, has storage unit that has support element which is formed from wire mesh for damping vibrations of rotor |
| CN105452689A (en) * | 2013-08-20 | 2016-03-30 | 申克罗泰克有限责任公司 | Aerostatic bearing for a rotor, in particular in a balancing machine |
| CN104454992A (en) * | 2014-09-30 | 2015-03-25 | 湖南大学 | Elastic radial air bearing |
| CN105003593A (en) * | 2015-07-17 | 2015-10-28 | 厦门理工学院 | Hybrid bearing supporting shock absorber used for cone shaft |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113074023A (en) * | 2021-04-12 | 2021-07-06 | 哈尔滨工业大学 | Oil-free lubrication high-power-density zero-steam leakage steam turbine |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3491250A1 (en) | 2019-06-05 |
| JP2019527316A (en) | 2019-09-26 |
| KR20190028541A (en) | 2019-03-18 |
| WO2018022015A1 (en) | 2018-02-01 |
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