WO2013165840A1 - Roue de turbine de turbocompresseur à faible contrainte ayant un montage à trou traversant fileté - Google Patents

Roue de turbine de turbocompresseur à faible contrainte ayant un montage à trou traversant fileté Download PDF

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Publication number
WO2013165840A1
WO2013165840A1 PCT/US2013/038387 US2013038387W WO2013165840A1 WO 2013165840 A1 WO2013165840 A1 WO 2013165840A1 US 2013038387 W US2013038387 W US 2013038387W WO 2013165840 A1 WO2013165840 A1 WO 2013165840A1
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WO
WIPO (PCT)
Prior art keywords
turbine wheel
shaft
turbine
low stress
turbocharger
Prior art date
Application number
PCT/US2013/038387
Other languages
English (en)
Inventor
Brock Fraser
Paul Diemer
Original Assignee
Borgwarner Inc.
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 Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2013165840A1 publication Critical patent/WO2013165840A1/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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/025—Fixing blade carrying members on shafts
    • 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
    • F05D2240/20—Rotors
    • F05D2240/24—Rotors for turbines
    • 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
    • F05D2260/00—Function
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/31—Retaining bolts or nuts

Definitions

  • This invention relates to a turbocharger for an internal combustion engine. More particularly, this invention relates to turbocharger having a low stress turbine wheel which may be mounted to a turbine shaft via a through bore threaded mount.
  • a turbocharger is a type of forced induction system used with internal combustion engines. Turbochargers deliver compressed air to an engine intake, allowing more fuel to be combusted, thus boosting an engine's horsepower without significantly increasing engine weight. Thus, turbochargers permit the use of smaller engines that develop the same amount of horsepower as larger, normally aspirated engines. Using a smaller engine in a vehicle has the desired effect of decreasing the mass of the vehicle, increasing performance, and enhancing fuel economy. Moreover, the use of turbochargers permits more complete combustion of the fuel delivered to the engine, which contributes to the highly desirable goal of a cleaner environment.
  • Turbochargers typically include a turbine housing connected to the engine's exhaust manifold, a compressor housing connected to the engine's intake manifold, and a center bearing housing coupling the turbine and compressor housings together.
  • a turbine wheel in the turbine housing is rotatably driven by an inflow of exhaust gas supplied from the exhaust manifold.
  • a shaft rotatably supported in the center bearing housing connects the turbine wheel to a compressor impeller in the compressor housing so that rotation of the turbine wheel causes rotation of the compressor impeller.
  • the shaft connecting the turbine wheel and the compressor impeller defines an axis of rotation. As the compressor impeller rotates, it increases the air mass flow rate, airflow density and air pressure delivered to the engine's cylinders via the engine's intake manifold.
  • the turbine wheel operates in a high temperature environment and the turbine wheel may reach temperatures as high as 1922° F (1050° C).
  • the turbine wheel of a turbocharger rotates very fast.
  • the rotation speed of a turbine wheel is size dependent and smaller turbine wheels can rotate faster than larger wheels.
  • a turbocharger turbine wheel used in conjunction with an internal combustion engine may reach circumferential tip speeds of 530 meters per second.
  • the rapid rotation of the turbine wheel creates large centrifugal forces or centrifugal stress on the wheel.
  • the combination of the high temperature operating environment and the high centrifugal stress limit the materials which can be used in turbocharger turbine wheels.
  • One group of materials which has been used for turbocharger turbine wheels are the nickel-based super alloys.
  • the nickel-based super alloys generally contain nickel, chromium and iron, although, in certain alloys other metals may be included.
  • the Inconel ® alloys are examples of nickel-based super alloys.
  • the nickel-based super alloys have a density between 8 and 9 grams per cubic centimeter depending upon the alloy.
  • nickel-based super alloy turbine wheels may be heavy and this weight creates high centrifugal stress when the wheel is rotated at high speed.
  • the weight of the turbine wheel also means that when there is a demand for a pressure boost by the turbocharger, the turbine can take some time to reach full speed. This can result in a lag between the initial demand for a turbocharger boost and the actual delivery of the pressure boost.
  • ⁇ (gamma) titanium aluminide has been introduced as a turbine wheel material
  • ⁇ (Gamma) titanium aluminide has a density of 4.0 grams per cubic centimeter and thus a ⁇ (gamma) titanium aluminide turbine wheel weighs half as much as an nickel-based super alloy turbine wheel of the same size.
  • the lower density of the gamma titanium aluminide allows the turbine wheel to have a lower weight, and thus, less stress.
  • the lower weight also allows the turbine to come up to speed faster so that there is less lag in pressure boost.
  • Borg Warner introduced EFR turbochargers to the market. These turbochargers have a ⁇ (gamma) titanium aluminide turbine wheel.
  • Turbocharger turbine wheels have had solid cores because a solid core helps the turbine wheel withstand the severe centrifugal stress created by the rapid rotation of the turbine wheel. Even with the advantage of lower weight provided by constructing the turbine wheel from ⁇ (gamma) titanium aluminide, the centrifugal forces remain high and ⁇ (gamma) titanium aluminide turbine wheels have solid cores.
  • the solid core turbines are either brazed or welded to the turbine shaft.
  • U.S. Patent publication 2007/0119908 relates to a titanium-aluminide turbine wheel which is joined to the end of a shaft by utilizing a titanium surface on the end of the shaft to be joined to the wheel, and electron-beam welding the wheel onto the titanium surface on the shaft.
  • Patent 6,007,301 relates to a turbine rotor consisting of a wheel made of a TiAl alloy of good heat resistance and a rotor shaft made of a structural steel or a martensitic heat resistant steel with good bonding strength.
  • the TiAl turbine wheel made by precision casting is butted to the shaft with insertion of a brazing filler in the butted interfaces and heated by high frequency induction heating in atmosphere of an inert gas or a reducing gas to a temperature higher than the liquidus temperature of the brazing metal but not exceeding 100° C above the liquidus temperature.
  • U.S. Patent 5,006,054 and U.S. Patent 4,891,184 disclose low density, high temperature and aluminum-rich intermetallic alloys displaying excellent elevated temperature properties, including oxidation resistance.
  • useful alloys are derived from changes in crystal structure and properties effected by selected-site substitution alloying with manganese and/or chromium, and, where used, vanadium, or equivalent site-substituting alloying elements.
  • the high temperature processing required for brazing or welding can cause problems.
  • the differential heating of the turbine wheel and shaft can induce stresses in the wheel and shaft. These stresses could cause failure if they are not relieved by heat treatment.
  • the brazing or welding process may deposit slightly more metal at one part of the wheel than the other. This can create an imbalance which must be corrected in order to allow the turbine wheel to rotate at high speeds.
  • the radial turbine wheel has the fluid flowing around the edge of the turbine wheel.
  • An example of such a wheel is a water wheel.
  • An axial turbine has the fluid flowing through the turbine blades.
  • a windmill is an example of an axial turbine.
  • the mixed flow turbine wheel combines the designs of both the axial flow and radial flow turbines. Mixed flow and axial flow turbine wheels tend to have lower stress than radial flow turbines.
  • a turbine wheel having a low stress geometry may be mounted on a shaft using an axial through bore threaded mounting. Wheels of low stress geometry which in addition are designed to run at lower speed are particularly suited for through bore mounting. Wheels of low stress geometry may be either axial flow or mixed flow wheels. A mixed flow wheel geometry is preferred. Low stress wheels may be made of heat resistant metals such as nickel-based super alloys. However, turbine wheels made from a high strength, low density, heat resistant material are easier to design and are thus preferred.
  • the first factor is the design of the turbine wheel itself. For a turbine wheel of a given size, axial and mixed flow turbine wheels tend to place less of the wheel mass at the edge of the wheel. Accordingly, axial and mixed flow turbine wheels have less centrifugal stress than radial turbine wheels.
  • the second factor is the density of the material from which the turbine wheel is made. A turbine wheel made from a strong low density material will weigh less, and thus have lower centrifugal stress.
  • Turbine wheels suitable for through bore mounting can be made by carefully designing a wheel with low stress geometry.
  • An axial flow wheel, or a mixed-flow wheel with very high axial content, having a very small-diameter hubline, would have a low level of centrifugal stress.
  • Such wheels can be made from a denser material such as a nickel-based superalloy and be through bore mounted.
  • a turbine wheel designed for lower rotation speed has less centrifugal stress and can be made from metals such as nickel-based superalloys and be through bore mounted.
  • greater freedom in design is possible with a turbine wheel of low stress geometry which is made from a high strength low density material.
  • low density heat resistant materials suitable for constructing the turbine wheels of the present invention include the intermetallic alloys of aluminum, titanium, and other metals such as those described in U.S. Patent 5,006,054 and U.S. Patent 4,891,184.
  • ⁇ (Gamma) titanium aluminide is a preferred material for the turbine wheel.
  • the through bore threaded mounting employs a female threaded component which is either female threads on the inside of the turbine wheel or the threads may be on the end of the turbine shaft with the wheel secured by a nut.
  • the turbine wheel may be mounted to the shaft in a cold operation thus avoiding all the problems caused by brazing or welding the shaft.
  • Figure 1 shows a low stress turbine wheel having an axial bore hole through the center of the hub and a threaded shaft extending through the hole;
  • Figure 2 shows a low stress turbine wheel having an axial bore hole through the center of the hub resting on a collar on the threaded shaft;
  • Figure 3 shows a low stress turbine wheel through bore mounted on a threaded shaft having a nut retaining the turbine wheel to the shaft;
  • Figure 4 shows a cut away view of a low stress turbine wheel having an axial bore hole in the hub and a cross section of a shaft suitable for mounting the turbine wheel;
  • Figure 5A shows a cut away view of a low stress turbine wheel, a bore hole in the hub, and female threads in the bore hole which allow the threads of the shaft to be screwed into the threads of the turbine wheel thereby securing the turbine wheel to the shaft;
  • Figure 5B shows a shaft suitable for mounting the turbine wheel illustrated in Figure
  • Figure 6A shows a cutaway view of a low stress turbine wheel having a conical bore hole
  • Figure 6B shows a shaft suitable for mounting the turbine wheel illustrated in Figure 6A wherein the turbine shaft has a conical taper suitable for attachment to a turbine wheel having threads at the end of the wheel hub;
  • Figure 7 shows a cutaway view of a turbine wheel having a conical bore hole and a cross-sectional view of a turbine shaft, having a conical taper, suitable for attachment to a low stress turbine wheel.
  • FIG. 1 shows a low stress turbine wheel being mounted on a threaded shaft.
  • the turbine wheel (1) has an axial bore hole, not shown in this view, in the hub (2) through which a shaft (3) extends.
  • the turbine wheel (1) has a slip fit on shaft (3), that is, when the shaft (3) is placed in the bore hole in the hub (2), the turbine wheel (1) moves down the shaft (3) with relatively little force until the turbine wheel (1) rests on collar (4) on shaft (3).
  • the collar (4) is an integral part of the shaft (3).
  • the turbine wheel (1) has blades (5) shaped to allow it to achieve a low stress geometry.
  • the shaft (3) is threaded on both ends (6) and (7). In use, the turbine rotates clockwise, as viewed facing the turbine.
  • the threads (6) are left hand threads.
  • the threads (7) are right hand threads.
  • the turbine wheel (1) is being moved down the threaded shaft (3)
  • FIG 2 shows a low stress geometry turbine wheel mounted on a threaded shaft.
  • the turbine wheel (1) has an axial bore hole, not shown in this view, in the hub (2) through which a shaft (3) extends.
  • the turbine wheel (1) has a slip fit on shaft (3), that is, when the shaft (3) is placed in the bore hole in the hub (2), the turbine wheel (1) moves down the shaft (3) with relatively little force until the turbine wheel (1) rests on collar (4) on shaft (3).
  • the collar (4) is an integral part of the shaft (3).
  • the turbine wheel (1) has blades (5) shaped it to allow to achieve a low stress geometry.
  • the shaft (3) is threaded on both ends (6) and (7).
  • the threads (6) are left hand threads.
  • the threads (7) are right hand threads. In use, the turbine rotates clockwise, as viewed facing the turbine.
  • the turbine wheel (1) rests on collar (4).
  • FIG 3 shows a low stress turbine wheel mounted on a threaded shaft secured by a nut.
  • the turbine wheel (1) has an axial bore hole, not shown in this view, in the hub (2) through which a shaft (3) extends.
  • the turbine wheel (1) has a slip fit on shaft (3), that is, when the shaft (3) is placed in the bore hole in the hub (2), the turbine wheel (1) moves down the shaft (3) with relatively little force until the turbine wheel (1) rests on collar (4) on shaft (3).
  • the collar (4) is an integral part of the shaft (3).
  • the turbine wheel (1) has blades (5) shaped to achieve a low stress geometry.
  • the shaft (3) is threaded on both ends (6) and (7).
  • the threads (6) are left hand threads.
  • the threads (7) are right hand threads.
  • a nut (9) has been turned onto the threaded end (6) of the turbine shaft.
  • Figure 4 shows a cut away view of a low stress turbine wheel having a bore hole in the hub and a cross section of a shaft suitable for mounting the turbine wheel.
  • the turbine wheel (1) has an axial bore hole (10) in the hub (2) through which a shaft (3) may extend.
  • the turbine wheel (1) has blades (5) shaped to achieve a low stress geometry.
  • the turbine wheel (1) has a slip fit on shaft (3), that is, when the shaft (3) is placed in the bore hole in the hub (2), the turbine wheel (1) moves down the shaft (3) with relatively little force until the turbine wheel (1) rests on collar (4) on shaft (3).
  • the shaft (3) has a collar (4) which is an integral part of the shaft (3).
  • the shaft (3) is threaded on both ends (6) and (7).
  • the threads (6) are left hand threads.
  • the threads (7) are right hand threads.
  • Figure 5A shows a cut away view of a low stress turbine wheel having a bore hole in the hub, and threads in the bore hole which allow the threads of the shaft to be screwed into the threads of the turbine wheel thereby securing the turbine wheel to the shaft.
  • Figure 5B illustrates a shaft suitable for mounting the turbine wheel illustrated in Figure 5 A.
  • the turbine wheel (11) has an axial bore hole (13) in the hub (12) and threads (14) at the end of hub (12) to which shaft (3) can attach.
  • the turbine wheel (11) has a slip fit on shaft (3), that is, when the shaft (3) is placed in the bore hole (13) in the hub (12), the turbine wheel (11) moves down the shaft (3) with relatively little force until the threaded portions (6) and (14) engage.
  • the turbine wheel (11) has blades (15) shaped to achieve a low stress geometry.
  • the collar (4) is an integral part of the shaft (3).
  • the shaft (3) is threaded on both ends (6) and (7). In use, the turbine rotates clockwise, as viewed facing the turbine.
  • the threads (6) are left hand threads.
  • the threads (7) are right hand threads.
  • Figure 6A shows a cutaway view of a low stress turbine wheel having a conical bore hole and a cross-sectional view of a turbine shaft, having a conical taper, suitable for attachment to a low stress turbine wheel and suitable for securing to the turbine wheel using threads in the hub of the turbine wheel.
  • Figure 6B illustrates a shaft suitable for mounting the turbine wheel illustrated in Figure 6A
  • the turbine wheel (16) has an axial bore hole (19) in the hub (20) through which the shaft (3) extends.
  • the bore hole (19) has a conical section (20).
  • the turbine wheel (16) rotates clockwise, as viewed facing the turbine.
  • the turbine wheel (16) when placed on the shaft, moves down the shaft easily until the threaded sections, (22) and (6) meet.
  • the turbine wheel (16) has blades (18) shaped to achieve a low stress geometry.
  • the shaft (3) is threaded on both ends (6) and (7).
  • the shaft has a conical section (21).
  • the threads (6) are left hand threads.
  • the threads (7) are right hand threads.
  • Figure 7 shows a cutaway view of a low stress turbine wheel having a conical bore hole, and a cross-sectional view of a turbine shaft having a conical taper.
  • the turbine wheel (23) has an axial bore hole (27) in the hub (24).
  • the bore hole (27) has a conical section (29).
  • the shaft has a conical section (28).
  • the turbine wheel (23) has blades (25) shaped to achieve a low stress geometry.
  • the turbine wheel of the present invention has a bore hole through the center of the hub of the wheel along an axis defined by the axis of the turbocharger shaft connecting the turbine wheel to the compressor portion of the turbocharger.
  • the turbocharger shaft is threaded and the turbine wheel is retained on the shaft by a female threaded component which is either female threads in the hub of the turbine wheel or by a nut which is screwed down onto the threads.
  • This mounting of the turbine wheel has many advantages.
  • the turbine wheel may be attached to the shaft in a low temperature process which avoids the high temperatures required for brazing or welding. In particular, the low temperature attachment process avoids differential heating of the turbine wheel and shaft which can induce stresses in the wheel and shaft.
  • the low temperature attachment process removes the extra step of heat treatment to relieve stress.
  • the brazing or welding process may deposit slightly more metal at one part of the wheel than the other. This can create an imbalance which must be corrected in order to allow the turbine wheel to rotate at high speeds.
  • the through bore mounting also lowers capital equipment costs because it does not require welding or heat treatment equipment.
  • the turbine wheel In order to achieve through bore mounting of the turbine wheel to the turbine shaft the turbine wheel has to have a low stress design. Radial flow turbine wheels tend to have higher centrifugal stress than axial or mixed flow design turbine wheels. For a turbine wheel of a given size, axial and mixed flow turbine wheels tend to place less of the wheel mass at the edge of the wheel. Accordingly, axial and mixed flow turbine wheels have less centrifugal stress than radial turbine wheels. With careful design it is possible to make a turbine wheel of low stress design suitable for through bore mounting from a denser material such as nickel based superalloy. For example, a carefully designed axial, or mixed flow turbine wheel prepared from a nickel-based superalloy, such as an Inconel ® alloy, may be through bore mounted.
  • Such mounting is of a turbine wheel made from a nickel -based superalloy, such as an Inconel ® alloy is particularly feasible when the wheel is also designed to run at lower speeds.
  • a turbine wheel of low stress geometry which is made from a high strength low density material.
  • a turbine wheel made from a strong low density material will weigh less, and thus have lower centrifugal stress. Accordingly, it is easier to design a low stress turbine if a high strength low density material is used to make it.
  • Examples of the low density heat resistant materials having sufficient strength to be used as turbine wheels of the present invention include the intermetallic alloys of aluminum, titanium, and other metals such as those described in U.S. Patent 5,006,054 and U.S. Patent 4,891 , 184.
  • ⁇ (Gamma) titanium aluminide is a preferred material for the turbine wheel.
  • the through bore threaded mounting employs a female threaded component which is either female threads on the inside of the turbine wheel or the threads on the end of the turbine shaft.
  • the turbine wheel is secured to the shaft either by a nut turned onto the threads or by turning the threads in the wheel hub onto the threads of the shaft.
  • the turbine wheel (1) has a slip fit on the threaded shaft (3).
  • a collar (4) on the shaft prevents the turbine wheel from moving.
  • the turbine wheel (1) is slipped down the threaded shaft (3) until it rests on the collar (4).
  • a nut (9) is placed on the end of the threaded shaft (6) and is turned to place pressure on turbine wheel (1) thereby securing it to the threaded shaft (3).
  • This embodiment is illustrated in Figures 1-4.
  • the threaded end (6) of threaded rod (3) has left handed threads. Accordingly, the rotation of the turbine wheel does not cause the nut to loosen during use.
  • the low density heat resistant materials having sufficient strength to be used as turbine wheels including intermetallic aluminum alloys, such those disclosed in U.S. Patent 5,006,054, U.S. Patent 4,891,184, and ⁇ (gamma) titanium aluminide, tend to be brittle. Accordingly, care must be taken to control the pressure on the turbine wheel (1) exerted by the nut (9). The pressure must be sufficient to secure the turbine wheel (1) to the shaft but not so large as to cause the turbine wheel (1) to crack.
  • the turbine wheel (1) does not have a slip fit on the shaft (3).
  • the axial bore hole (10) in the turbine wheel (1) is slightly smaller than the shaft (3) and must be expanded by heating before it is put on the shaft (3).
  • This particular embodiment is represented by Figures 1-4.
  • the only difference between the slip fit embodiment and the embodiment in which the turbine wheel (1) must be heated is that in the heated embodiment the axial bore hole (10) in the hub is made slightly smaller relative to the shaft (3) than in the slip fit embodiment.
  • the turbine wheel is further secured to the shaft by a nut (9). The left hand threads of the shaft and of the nut securing the turbine wheel to the shaft will assure that the turbine wheel will not loosen from the shaft in use.
  • the difference in size between the axial bore hole (10) and the shaft (3) is not large and thus the temperature to which the wheel must be heated is much lower than the temperature required to braze or weld a steel shaft to a turbine wheel having a solid hub. Accordingly, the mild heating required to expand the axial bore hole (10) does not cause the stresses which brazing or welding would cause.
  • a low stress turbine wheel having a conical axial bore hole and threads in the hub is placed on a turbine shaft, having a conical taper, suitable for attachment to a low stress geometry turbine wheel.
  • the turbine wheel (16) has an axial bore hole (19) in the hub (17) through which the shaft (3) extends and blades (18) are shaped to achieve a low stress geometry.
  • the bore hole (19) has a conical section (20) and a threaded section (22). This is illustrated in Figure 6A.
  • the shaft has a conical section (21).
  • the shaft (3) is threaded on both ends (6) and (7). In use, the turbine rotates clockwise, as viewed facing the turbine.
  • the threads (6) are left hand threads.
  • the threads (7) are right hand threads.
  • the turbine wheel (6) when placed on the shaft, moves down the shaft easily until the threaded sections, (20) and (6), meet.
  • the threads (22) in the turbine wheel (16) are turned onto the threaded section (6) of shaft (3), conical tapered sections (20) and (21) are forced together securing the turbine wheel (16) to the shaft (3). This is illustrated in Figure 6B. Because the turbine wheel is secured to the shaft by left hand threads it will not loosen from the shaft in use.
  • a low stress turbine wheel having a conical bore hole
  • the turbine wheel (23) has an axial bore hole (27) in the hub (24).
  • the bore hole (27) has a conical section (29).
  • the turbine wheel (23) has blades (25) shaped to provide low stress geometry.
  • the shaft has a conical section (28).
  • the turbine wheel (23) when placed on the shaft, moves down the shaft easily until the conical sections, (28) and (29), meet.
  • the turbine wheel is secured to the shaft by left hand threads it will not loosen from the shaft in use.
  • the type of female threaded component it may be either threads cut in the hub of the turbine wheel or a nut on the turbine shaft to retain the turbine wheel.
  • the turbine wheel is made from a low density, high strength, heat resistant material, the embodiments in which a nut is used to secure the turbine wheel to the shaft are preferred.
  • the low density heat resistant materials having sufficient strength to be used as turbine wheels tend to be hard materials in which it is difficult to cut threads.
  • the coefficient of thermal expansion of the steel turbine shaft becomes important.
  • the low density heat resistant materials having sufficient strength to be usable as turbine wheels in the present invention, have rather low coefficients of thermal expansion.
  • ⁇ (gamma) titanium aluminide has a coefficient of linear thermal expansion of 12.2 ( ⁇ / ⁇ per Kelvin degree). If the coefficient of thermal expansion of the turbine wheel is much less than that of the shaft, tension will be created as the turbine is used in its working environment where temperatures may reach as high as 1922° F (1050° C). If the coefficient of thermal expansion of the shaft is much less than that of the turbine wheel, the turbine wheel could become loose during use as the temperature increases. An exact match of coefficients is not required.
  • High temperature steels having a coefficient of thermal expansion within approximately 2 ⁇ /m per Kelvin degree of the coefficient of thermal expansion of the turbine wheel material may be used easily.
  • the closeness of fit of the shaft to the turbine wheel axial bore hole can influence the type of steel chosen. For example, if the steel has a lower coefficient of thermal expansion than the turbine wheel, the turbine wheel can be heated before being placed on the shaft. This would allow the shaft turbine wheel fit to tightly at lower temperatures and more normally at higher temperatures. Similarly, if the steel used in the shaft has a higher coefficient of thermal expansion than that of the turbine wheel, a slightly looser slip fit could be used. This would allow the shaft to expand at working temperature without becoming too tight.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Supercharger (AREA)

Abstract

L'invention porte sur une roue de turbine à faible contrainte pour turbocompresseur (1) destinée à un moteur à combustion interne. La roue de turbine (1) est montée sur l'arbre (3) de la turbine au moyen d'un montage fileté à trou traversant (10, 13, 19, 27).
PCT/US2013/038387 2012-05-02 2013-04-26 Roue de turbine de turbocompresseur à faible contrainte ayant un montage à trou traversant fileté WO2013165840A1 (fr)

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US61/641,457 2012-05-02

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016198629A1 (fr) * 2015-06-12 2016-12-15 Areva Np Pompe avec organe d'imperdabilité
US11525394B2 (en) * 2018-08-07 2022-12-13 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine shaft, turbocharger, and manufacturing method of turbocharger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6052897A (en) * 1996-10-02 2000-04-25 Asea Brown Boveri Ag Compressor-wheel arrangement for turbochargers
US20040202556A1 (en) * 2003-04-08 2004-10-14 Svihla Gary R. Turbocharger rotor
US20050175465A1 (en) * 2004-02-10 2005-08-11 Toshihiko Nishiyama Structure for connecting compressor wheel and shaft
US20100054944A1 (en) * 2007-03-16 2010-03-04 Peter Fledersbacher Rotor assembly for an exhaust gas turbocharger
JP2011137379A (ja) * 2009-12-25 2011-07-14 Ihi Corp インペラ取付構造及び過給機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6052897A (en) * 1996-10-02 2000-04-25 Asea Brown Boveri Ag Compressor-wheel arrangement for turbochargers
US20040202556A1 (en) * 2003-04-08 2004-10-14 Svihla Gary R. Turbocharger rotor
US20050175465A1 (en) * 2004-02-10 2005-08-11 Toshihiko Nishiyama Structure for connecting compressor wheel and shaft
US20100054944A1 (en) * 2007-03-16 2010-03-04 Peter Fledersbacher Rotor assembly for an exhaust gas turbocharger
JP2011137379A (ja) * 2009-12-25 2011-07-14 Ihi Corp インペラ取付構造及び過給機

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016198629A1 (fr) * 2015-06-12 2016-12-15 Areva Np Pompe avec organe d'imperdabilité
FR3037365A1 (fr) * 2015-06-12 2016-12-16 Areva Pompe avec organe d'imperdabilite
CN107743551A (zh) * 2015-06-12 2018-02-27 阿海珐核能公司 具有防损构件的泵
CN107743551B (zh) * 2015-06-12 2019-07-16 阿海珐核能公司 具有防损构件的泵
US11525394B2 (en) * 2018-08-07 2022-12-13 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbine shaft, turbocharger, and manufacturing method of turbocharger

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