WO2012079881A1 - Ensemble palier pour un turbocompresseur et turbocompresseur - Google Patents

Ensemble palier pour un turbocompresseur et turbocompresseur Download PDF

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Publication number
WO2012079881A1
WO2012079881A1 PCT/EP2011/070048 EP2011070048W WO2012079881A1 WO 2012079881 A1 WO2012079881 A1 WO 2012079881A1 EP 2011070048 W EP2011070048 W EP 2011070048W WO 2012079881 A1 WO2012079881 A1 WO 2012079881A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
bearing
turbocharger
turbine wheel
rolling
Prior art date
Application number
PCT/EP2011/070048
Other languages
German (de)
English (en)
Inventor
Heiko Schmidt
Peter Solfrank
Christopher Mitchell
André KUCKUK
Thomas Motz
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to CN201180060643XA priority Critical patent/CN103261716A/zh
Priority to US13/994,260 priority patent/US20130272854A1/en
Publication of WO2012079881A1 publication Critical patent/WO2012079881A1/fr

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Classifications

    • 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
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/02—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for connecting two abutting shafts or the like
    • F16D1/027—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for connecting two abutting shafts or the like non-disconnectable, e.g. involving gluing, welding or the like
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
    • F16D1/068—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving gluing, welding or the like
    • 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
    • F05D2240/54—Radial 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • 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

Definitions

  • the invention relates to a bearing arrangement for a turbocharger, comprising a bearing housing, a bearing arranged inside the bearing housing with an outer bearing ring and a number of rolling elements, and a rotatably mounted within the bearing housing, axially extending shaft.
  • the invention relates to a turbocharger with an aforementioned bearing assembly.
  • a turbocharger is usually used to increase the performance of internal combustion engines through the use of exhaust gas energy.
  • the turbocharger consists of a compressor and a turbine, which are connected to each other via a shaft mounted within a bearing housing shaft.
  • the turbine In operation, the turbine is rotated by an exhaust gas flow and drives the compressor via the shaft, which sucks and compresses air.
  • the compressed air is conducted into the engine, whereby a large amount of air enters the cylinders due to the increased pressure during the intake stroke.
  • the oxygen content required for the combustion of fuel increases accordingly, so that more oxygen enters the combustion chamber of the engine at each intake stroke.
  • this increase allows the use of a more powerful motor with approximately the same dimensions or, alternatively, allows for a reduction in engine dimensions, ie, a comparable performance for smaller and lighter machines.
  • a first object of the invention to provide a comparison with the prior art improved bearing assembly that allows for easy installation and low cost secure storage of a shaft in a turbocharger.
  • a second object of the invention is to provide a turbocharger with such a bearing assembly.
  • the first object of the invention is achieved by a bearing arrangement for a turbocharger, comprising a bearing housing extending in an axial direction, a roller bearing arranged inside the bearing housing with an outer bearing ring and a number of rolling elements, and a housing rotatably mounted within the bearing housing axially extending shaft.
  • the shaft comprises a rolling body raceway for guiding the rolling bodies.
  • the inner bearing rings are pushed onto the shaft and must be pressed onto them so that no rotation relative to the shaft is possible during operation.
  • the bearing rings are compressed in such a way that the axial distance between the rolling element raceways is shortened and thus the shaft clearance is changed. Furthermore, the diameter of the WälzSystemonnebahnen and thus the bearing clearance change.
  • the inner bearing rings when they are pressed in, they may be misaligned on the shaft. It is possible, for example, that they do not align coaxially with the shaft and with respect to one another, which can lead to an undesired setting at the axial contact points between the bearing rings or the bearing seats both during balancing and during later operation.
  • the balancing quality can vary over the life of the warehouse deteriorate and lead to increased wear of the bearing components. In any case, such a trouble-free function of a turbocharger can not be guaranteed.
  • the invention finally recognizes that the aforementioned problems can be overcome, surprisingly, when the shaft comprises a rolling body raceway for guiding the rolling bodies.
  • the use of separately mounted inner bearing rings can be dispensed with altogether. In other words, the shaft itself assumes the function of the inner bearing ring, so that a safe mounting of the shaft in a turbocharger can be achieved by such a design with low cost and assembly costs.
  • the shaft can be made of different materials, in particular temperature-stable and corrosion-resistant materials are suitable.
  • the shaft may for example be made in one piece by means of a forming process, a machining process or a casting process.
  • a multi-part production is possible.
  • the rolling body raceway is in this case integrated into the lateral surface of the shaft and can be introduced, for example, directly in the production of the shaft in one step in the lateral surface.
  • the rolling body raceway can be subsequently introduced into the lateral surface in a step subsequent to the manufacture of the shaft main body.
  • the shaft is rotatably mounted in the installed state within a bearing housing.
  • the bearing housing is preferably hollow-cylindrical. det. Due to the high loads during operation of a turbocharger, temperature-resistant and corrosion-resistant metallic materials are particularly suitable for producing the bearing housing.
  • the bearing housing is formed in particular with a receiving bore for the other components of the bearing assembly, such as the rolling bearing.
  • the rolling bearing or the individual rolling bearing components are expediently made of temperature and corrosion resistant materials, such as hardened steels or ceramics.
  • the common types of bearings are basically used, such as cylindrical roller bearings or tapered roller bearings.
  • Particularly suitable are ball bearings, such as in particular double row angular contact ball bearings.
  • two axially spaced WälzEffbahnen are introduced in the lateral surface of the shaft.
  • the rolling bearing is further formed with at least one outer bearing ring, on whose inner circumference a rolling body raceway is introduced, which also serves to guide and position the rolling bodies.
  • at least one outer bearing ring on whose inner circumference a rolling body raceway is introduced, which also serves to guide and position the rolling bodies.
  • the outer bearing rings for example, abut each other and thus prevent axial displacement of the bearings on the shaft.
  • the outer bearing rings for example, by means of a spring member axially spaced apart.
  • a gap for example as a circumferential outer race ring gap formed for a so-called Quetschölfilm.
  • the quenching oil film assumes the function of the vibration damper and prevents unwanted contact between the outer bearing ring and the bearing housing.
  • a number of supply bores can be introduced within the bearing housing, via which oil from the engine oil circuit can be metered into the intermediate space.
  • the supply holes are for this purpose in particular with a number of the outer circumference of the outer bearing ring encircling grooves in a communicating connection. Accordingly, the grooves can be supplied with oil via the supply bores.
  • the oil can distribute in the axial direction over the circumference of the outer bearing ring, so that forms a uniform oil film between the outer bearing ring and the inner wall of the bearing housing.
  • the number of supply bores and the grooves is in principle not limited and can for example be adapted to the dimensions of the bearing housing and the thickness of the quenching oil film.
  • an outlet bore is preferably additionally introduced into the bearing housing, which is communicatively connected to a drain groove running around the outer bearing ring on its outer circumference. In this way it is ensured that the oil supplied via the supply bore to the intermediate space can flow away continuously.
  • the outer bearing rings can be guided by an additional support ring in the bearing housing.
  • the carrier ring is embedded in the intermediate space.
  • the carrier ring preferably has on its outer circumference a number of circumferential grooves which, in the installed state, communicate with the supply bores of the bearing housing in a communicating manner.
  • the quenching oil film is then formed correspondingly in the space between the outer periphery of the carrier ring and the inner wall of the bearing housing.
  • a carrier ring is suitably introduced in this introduced on its outer circumference drainage communicating with an outlet bore in connection and allows corresponding to the oil drain.
  • securing elements can be used.
  • securing elements which withstand the forces acting during operation of a turbocharger and which enable a rotation-proof arrangement of the outer bearing ring within the bearing housing.
  • the security elements may be formed, for example, as backup pins or securing bolts that can be inserted into holes provided for this purpose within the bearing housing.
  • the securing elements can be designed as springs, which can then engage, for example, in recesses or grooves provided for this purpose.
  • the shaft consists of a steel, at least in the region of the rolling body track.
  • different steels or metallic materials can be used here.
  • an alloyed bearing steel is suitable.
  • a roller bearing steel type 81 MoCrV42-16 can be used, which in particular due to its temperature stability and corrosion resistance, the necessary conditions for use in turbochargers.
  • the properties of the metallic material or of the rolling bearing steel can be influenced by the choice of the alloy components or by the composition. In principle, it is possible here to manufacture the entire shaft from a rolling bearing steel. Alternatively, a rolling bearing steel can also be used only at the points of the rolling body raceways.
  • the shaft is composed of a number of axially adjacent shaft sections.
  • the individual shaft sections can be welded together prior to assembly of the bearing assembly.
  • the multi-part design allows, for example, the controlled introduction of recesses in the shaft. These recesses provide an air volume within the shaft which, when the shaft is installed in the turbocharger, reduces the heat conduction from the turbine wheel to the rolling bearing.
  • the shaft sections can be made of different materials.
  • the shaft sections in which the WälzSystemterrorismbahnen are introduced preferably made of a bearing steel, which has the necessary stability.
  • requirement-specific material and correspondingly less expensive shaft material can be used.
  • welding methods are suitable in this case in particular because, when used, it is also possible to use materials with different physical properties, such as, for example, Steel with aluminum, to connect.
  • the shaft comprises an inner recess.
  • the inner recess may be formed as a cavity that provides an additional volume of air.
  • the recess can serve for receiving so-called welding ejection, which occurs when the shaft is connected to the turbine wheel or even when several shaft sections are connected to one another and can then be caught within the recesses.
  • a recess can also be made in the turbine wheel. The same applies to a multi-part design of the shaft for the individual shaft sections, which can also be formed in each case with a recess. As a result, the internal air volume increases further and the thermal conductivity is further reduced.
  • the shaft on the front side a shaft journal for centering and attachment to a turbine wheel.
  • the shaft journal is preferably designed as a pin extending in the axial direction, which in the inserted Built state in the bore of a turbine wheel can intervene.
  • a connection between them is possible, which simplify the subsequent welding process.
  • the formation of a pin on the turbine wheel is possible, which then engages in a bore on the end face of the shaft.
  • the outer bearing ring comprises a spray oil hole for lubricant application of the rolling bearing.
  • the spray oil holes are in this case connected to the grooves in the outer ring. The oil can pass from the grooves through the spray oil holes in the storage room and be used in this way for lubrication and cooling.
  • the shaft comprises on its outer circumference a number of grooves for positioning of sealing elements.
  • the grooves can be introduced into the outer circumference of the shaft both on the compressor side and on the turbine side, so that a sealing effect is achieved on both sides of the shaft. In this way, the required lubrication of the positioned inside the bearing housing bearing can be ensured, which is achieved for example via spray oil holes.
  • the shaft comprises an oil separator.
  • the oil separator may for example be attached to the shaft as a separate component or integrated into the shaft.
  • the oil separator is designed as one which operates by utilizing the centrifugal force principle.
  • the second object of the invention is achieved by a turbocharger, comprising a compressor wheel, a turbine wheel, and a bearing assembly according to the aforementioned embodiments, wherein the Compressor and the turbine are arranged at the opposite ends of the shaft. It is provided that the shaft is welded to the turbine wheel.
  • the turbine wheel of the turbine of a turbocharger is set in rotation by an exhaust gas flow and drives the compressor via the shaft.
  • the compressor draws in air and compresses it.
  • the compressor operates continuously and is characterized by low pressure increase and a high volume throughput.
  • the compressed air is directed into the engine, whereby a large amount of air enters the cylinders due to the increased pressure during the intake stroke.
  • the oxygen content required for the combustion of fuel increases accordingly, so that more oxygen enters the combustion chamber of the engine at each intake stroke.
  • the shaft is welded to the turbine wheel.
  • different welding methods are suitable.
  • Friction welding allows a secure connection of components both with the same and with different material combinations. This is a pressure welding process, whereby the heating of the parts to be joined takes place by mechanical friction. The heating is usually generated by a movement between a rotating and a stationary component, which are combined under force without additional material.
  • the shaft can also be connected to the turbine wheel by means of an electron beam welding method.
  • This method for example, due to the high energy density, which is introduced into the welding zone, allows the joining of a variety of different materials, such as high-melting metals.
  • the electron Beam welding enables high welding speeds with extremely deep and narrow seams. Due to the small seam widths and the high parallelism, the delay can be kept extremely small.
  • a laser beam welding is conceivable, which can connect components with high welding speed, narrow and slim weld shape and low thermal distortion. The laser beam welding is usually performed without feeding a filler material.
  • the turbine wheel is pressed onto the shaft.
  • This process is expediently preceded by the welding process.
  • the shaft is formed on the turbine side, for example, with a shaft journal extending in the axial direction, which is pressed into a bore in the turbine wheel.
  • a connection between the shaft and the turbine wheel is possible even before welding, so that the two components subsequently only have to be welded together at the preferably planar contact points.
  • the turbine wheel with a pin and the shaft can be formed with a bore on its end face, so that the shaft is pressed in the turbine wheel.
  • the compressor wheel is expediently fastened to the shaft by means of a nut.
  • the compressor wheel is pushed onto the shaft during assembly and finally jammed there by means of the nut. In this way, a secure connection between the compressor and the shaft is guaranteed.
  • the bearing components of the bearing cartridge can be preassembled and pushed starting from the turbine side into the bearing housing. This allows a delivery of the storage cartridge with less effort and a low installation costs for the customer. Further advantageous embodiments can be found in the directed to the bearing assembly subclaims that can be analogously transmitted to the turbocharger.
  • FIG. 1 to 4 each show a turbocharger with a bearing assembly in a longitudinal section.
  • FIG. 1 shows a turbocharger 1 having a bearing assembly 3.
  • the turbocharger has a compressor wheel 5 and a turbine wheel 7 disposed at opposite ends of a shaft 9 extending in the axial direction.
  • the shaft 9 is part of the bearing assembly 3 and rotatably mounted within a likewise axially extending bearing housing 1 1.
  • the bearing arrangement 3 comprises a rolling bearing 13 arranged inside the bearing housing 11 with two axially adjacent outer bearing rings 15, 17.
  • the outer bearing rings 15, 17 are spaced apart from one another by means of a prestressed spring element 19 arranged between them.
  • the rolling bearing 13 also has rolling elements 21 designed as balls, which are held in rows in cages 23, respectively.
  • the rolling elements 21 are each guided in rolling body raceways 25, 27, which are integrated in the lateral surface of the shaft 9.
  • the WälzSystemterrorismen 25, 27 are introduced directly in the manufacture of the shaft in one step in the lateral surface. This makes it possible to dispense with the use of separately mounted inner Lagerhnge, since the shaft 9 takes over the function of the inner bearing rings. As a result, the effort during assembly, in which the inner bearing rings must be pushed onto the shaft and pressed onto this reduced. Furthermore, the axial distance between the WälzConsequentlymaschinennenbahnen 25, 27 always the same size, so that the wave play does not change.
  • the entire shaft 9 is made in one piece from a temperature-resistant bearing steel. It is welded by means of a friction welding process with the turbine wheel 7, whereby a secure connection between the shaft 9 and the turbine wheel 7 is achieved.
  • the recesses 29, 31 provide an air volume, so that the heat conduction is reduced from that of a turbine wheel 7 to the rolling bearing 13 during operation of the turbocharger 1. Furthermore, they provide space for welding ejection during machining of the shaft.
  • the shaft 9 is connected to the compressor 5.
  • the compressor wheel 5 is pushed onto the shaft and clamped there by means of a nut 33.
  • sealing elements 37 seal against leakage and impurities both on the side of the compressor wheel 5 and on the side of the turbine wheel 7.
  • the bearing components can be pre-assembled and pushed starting from the turbine side into the bearing housing 11 become. Since the outer diameter of the outer bearing rings 15, 17 is slightly smaller than the inner diameter of the bearing housing 1 1, formed between the bearing housing 11 and the outer bearing rings 15, 17, a gap-shaped gap 39.
  • the space 39 is via supply bore 41 in the bearing housing 11 with oil acted upon, so that there forms a Quetschölfilm.
  • the supply bores 41, 42 communicate with grooves 43, 44 on the outer periphery of the outer races 15, 17 in communication. Furthermore, the oil from the grooves 43, 44, starting is distributed through connected with the grooves 43 spray oil holes 45, 46 in the camp and can be used for lubrication. To drain the oil, an outlet bore 47 is included.
  • an oil separator 49 is attached to the shaft 9 with centrifugal force principle.
  • FIG. 2 another turbocharger 61 is shown with a bearing assembly 63.
  • the turbocharger 61 has a compressor wheel 65 and a turbine wheel 67 disposed at opposite ends of an axially extending shaft 69.
  • the entire shaft 69 is also manufactured in one piece in FIG. 2 from a temperature-resistant steel.
  • turbocharger 61 in FIG. 2 Since the function and the individual components of the turbocharger 61 in FIG. 2 essentially correspond to those of the turbocharger 1 in FIG. 1, reference is here made to the detailed description and representation in FIG. 1, which can be transmitted analogously below.
  • the turbine wheel 67 is connected to the shaft 69 by means of electron beam welding.
  • the turbine wheel 67 is pressed onto the shaft 69.
  • the turbine wheel 67 has a corresponding bore 1 1 1, in which the formed on the end face of the shaft shaft journal 1 13 of the shaft is pressed.
  • the shaft journal 113 is formed as a pin extending in the axial direction.
  • the turbine wheel 67 and the shaft 69 are welded to the planar contact surfaces 15 of the turbine wheel 67 and the shaft 69 by an electron beam only.
  • the shaft 69 is clamped on the turbine wheel 67 opposite side with the compressor wheel 65 by means of a nut 93.
  • FIG. 3 shows another turbocharger 121 having a bearing assembly 123.
  • the turbocharger 121 also includes a compressor wheel 125 and a turbine wheel 127 disposed at opposite ends of a shaft 129 extending in the axial direction.
  • the shaft 129 is rotatably mounted within a likewise axially extending bearing housing 131.
  • the bearing assembly 123 a disposed within the bearing housing 131 rolling bearing 133 with two axially adjacent outer bearing rings 135, 137.
  • the outer bearing rings 135, 137 are spaced apart from each other by means of a preloaded spring element 139 arranged between them.
  • the rolling bearing 133 further has rolling elements 141 formed as balls, which are held in rows in cages 143, respectively.
  • the rolling elements 141 are each guided in rolling element raceways 145, 147, which are integrated in the lateral surface of the shaft 149.
  • a gap-shaped gap 159 is formed between the outer diameter of the outer bearing rings 135, 137 and the bearing housing 131, which is acted upon by two supply holes 161 in the bearing housing 131 with oil.
  • a quenching oil film forms in the intermediate space.
  • the supply bores 161, 162 communicate with grooves 163, 164 on the outer periphery of the outer races 13, 137 in communication.
  • the oil is additionally distributed via injection oil bores 165, 166 into the bearings and can thus be lubricated be used.
  • an outlet bore 167 is further included.
  • the difference between the turbocharger 121 and the turbochargers 1, 61 already shown is the nature of the shaft 129.
  • the shaft 129 is composed of various shaft sections 171, 173, 175.
  • the rolling element raceways 145, 147 are correspondingly introduced only in a shaft section 173.
  • the shaft portion 173 assumes the function of the otherwise required inner bearing rings accordingly.
  • the shaft portion 173 is made of temperature-resistant steel, whereas the two axially adjacent shaft portions 171, 175 are made requirement-specific from a cheaper metallic material.
  • the shaft portions 171, 173, 175 have axially inwardly extending recesses 176, 177, 178, 179.
  • the inner recesses 176, 177, 178, 179 are formed as cavities, which provide an additional volume of air available. Due to this, they cause a reduction of the heat conduction from the turbine wheel 127 to the bearings.
  • the turbine wheel 127 also has a recess 180, which additionally increases the volume of air and thus reduces the heat conduction.
  • the shaft sections 171, 173, 175 are welded together in the present case. After welding the shaft sections 171, 173, 175, finally, the shaft section 175 is welded to the turbine wheel 127.
  • a friction welding is used for this purpose.
  • the welded shaft portions 171, 173, 175 and the shaft 129 is finally welded to the side of the shaft portion 175 by a Reibsch consult- method with the turbine wheel 127.
  • the turbine wheel 127 also has an inner recess 180, which further reduces the volume of air for reducing the heat conduction from the turbine wheel 127 to the rolling bearing 133 during operation of the turbocharger 121.
  • the compressor wheel 125 For fastening the compressor wheel 125 to the shaft 129, the latter is pushed onto the side of the shaft 129 opposite the turbine wheel 127 and fastened there by means of a nut 153.
  • an oil separator 169 which operates by means of the centrifugal force principle, is attached to the shaft 129.
  • FIG. 4 shows a further turbocharger 181 with a bearing arrangement 183.
  • the turbocharger 181 includes a compressor wheel 185 and a turbine wheel 187 disposed at opposite ends of an axially extending shaft 189.
  • the shaft 189 is rotatably mounted within a likewise axially extending bearing housing 191.
  • the bearing assembly 183 further comprises a rolling bearing 193 disposed within the bearing housing 191 with two axially adjacent outer bearing rings 195, 197 which, as in the previous figures, are spaced apart by means of a prestressed spring element 199 disposed between them.
  • the rolling bearing 193 further comprises rolling elements 201 formed as balls, which are held in rows in cages 203, respectively.
  • the rolling elements 201 are guided in WälzEffbahnen 205, 207.
  • the shaft 189 is made of three separate shaft sections 237, 239, 241.
  • the shaft portions 237, 239, 241 are made of different materials, the shaft portion 239 is made of temperature-resistant steel.
  • the other two shaft sections 237, 241 are made of a less expensive metallic material.
  • the WälzEffegabahnen 205, 207 are introduced accordingly only in the shaft portion 239, which consists of the steel.
  • the shaft portion 239 takes over the function of the inner bearing rings, so that both the cost and the assembly costs are reduced and increases the accuracy.
  • the shaft portion 239 is each frontally formed with two axially extending shaft journals 243, 245. These shaft journals 243, 245 engage a built state in the bores 247, 249 which are respectively formed at the axial abutment points of the shaft sections 237, 241.
  • the shaft journals 243, 245 are correspondingly pressed into the holes 247, 249 during assembly.
  • the shaft portion 241 on the opposite side of the bore 249 a shaft journal 255 which is pressed into the bore 257 of the turbine wheel 187.
  • the two components or the shaft 189 and the turbine wheel 187 are welded to the contact points 259.
  • a laser beam welding is used, whereby components with high welding speed, narrow and slim weld form and connect with low thermal distortion. The laser beam welding is performed without feeding a filler material.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention porte sur un ensemble palier (3, 63, 123, 183) pour un turbocompresseur (1, 61, 121, 181), comprenant un logement de palier (11, 71, 131, 191) qui s'étend dans une direction axiale, un palier à roulement (13, 73, 133, 193) disposé à l'intérieur du logement de palier (11, 71, 131, 191) et comportant une bague extérieure de palier (15, 17, 75, 77, 135, 137, 195, 197) et un certain nombre de corps roulants (21, 81, 101, 161), ainsi qu'un arbre (9, 69, 129, 189) monté de façon rotative à l'intérieur du logement de palier (11, 71, 131, 191) et s'étendant axialement. L'arbre (9, 69, 129, 189) entoure une piste de roulement de corps roulants (25, 27, 85, 87, 145, 147, 205, 207) pour le guidage des corps roulants (21, 81, 101, 161). L'invention porte aussi sur un turbocompresseur (1, 61, 121, 181) comportant un tel ensemble palier (3, 63, 123, 183). Un tel ensemble palier (3, 63, 123, 183) permet d'obtenir, avec un montage simple et des coûts réduits, le montage fiable d'un arbre (9, 69, 129, 189) dans un turbocompresseur (1, 61, 121, 181).
PCT/EP2011/070048 2010-12-17 2011-11-14 Ensemble palier pour un turbocompresseur et turbocompresseur WO2012079881A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201180060643XA CN103261716A (zh) 2010-12-17 2011-11-14 用于涡轮增压机的轴承装置和涡轮增压机
US13/994,260 US20130272854A1 (en) 2010-12-17 2011-11-14 Bearing arrangement for a turbocharger, and turbocharger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010054939.8 2010-12-17
DE102010054939A DE102010054939A1 (de) 2010-12-17 2010-12-17 Lageranordnung für einen Turbolader und Turbolader

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WO2012079881A1 true WO2012079881A1 (fr) 2012-06-21

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CN (1) CN103261716A (fr)
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WO (1) WO2012079881A1 (fr)

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WO2015197304A1 (fr) * 2014-06-25 2015-12-30 Continental Automotive Gmbh Dispositif de palier pour arbre, notamment d'un dispositif turbocompresseur
DE102014220618B3 (de) * 2014-10-10 2016-03-10 Continental Automotive Gmbh Lagereinheit für das Laufzeug eines Abgasturboladers
DE102015215750A1 (de) 2015-08-18 2017-02-23 Continental Automotive Gmbh Verfahren zur Montage einer Wälzlagereinheit auf den Rotor eines Turboladers
DE102015218399A1 (de) 2015-09-24 2017-03-30 Continental Automotive Gmbh Verfahren zur Montage einer Wälzlagerung auf einen Rotor eines Abgasturboladers
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DE102014220618B3 (de) * 2014-10-10 2016-03-10 Continental Automotive Gmbh Lagereinheit für das Laufzeug eines Abgasturboladers
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DE102010054939A1 (de) 2012-06-21
US20130272854A1 (en) 2013-10-17

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