WO2013176853A1 - Enveloppe de stator refroidie par un fluide pour turbocompresseur à assistance électrique - Google Patents

Enveloppe de stator refroidie par un fluide pour turbocompresseur à assistance électrique Download PDF

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Publication number
WO2013176853A1
WO2013176853A1 PCT/US2013/038993 US2013038993W WO2013176853A1 WO 2013176853 A1 WO2013176853 A1 WO 2013176853A1 US 2013038993 W US2013038993 W US 2013038993W WO 2013176853 A1 WO2013176853 A1 WO 2013176853A1
Authority
WO
WIPO (PCT)
Prior art keywords
stator
surrounding wall
inlet
fluid cooled
housing
Prior art date
Application number
PCT/US2013/038993
Other languages
English (en)
Inventor
Michael Bucking
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 WO2013176853A1 publication Critical patent/WO2013176853A1/fr

Links

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
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/14—Casings modified therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
    • F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • a turbocharger uses exhaust gas energy, which would normally be wasted, to drive a turbine.
  • the turbine is mounted to a shaft that in turn drives a compressor.
  • the turbine converts the heat and kinetic energy of the exhaust into rotational power that drives the compressor.
  • the objective of a turbocharger is to improve the engine's volumetric efficiency by increasing the density of the air entering the engine.
  • the compressor draws in ambient air and compresses it into the intake manifold and ultimately the cylinders. Thus, a greater mass of air enters the cylinders on each intake stroke.
  • turbocharger When a turbocharger is sized to provide maximum power output for a particular engine, the turbocharger's low-load and transient response performance is generally less than optimal.
  • a turbocharger's compressor performance is dependent on the compressor speed. In order for the compressor to rotate fast enough to provide significant compression, or boost, to the engine, there must be a corresponding increase in exhaust gas flow. However, there is a time delay while the exhaust gases build up and the inertia of the turbine and compressor wheel assembly is overcome. This time delay between the engine's demand for boost and the actual increase in manifold pressure is often referred to as turbo lag.
  • Electrically-assisted turbochargers include an electric motor that is operative to supplement the rotational power derived from the exhaust during low- load and transient conditions.
  • the motor is connected to the same shaft that carries the turbine and compressor wheels.
  • the motor's rotor magnets are carried directly on the shaft, while the stator is contained within the turbocharger's center housing.
  • Electric motors are sensitive to heat and contamination. Accordingly, controlling heat and oil migration, which are common issues associated with turbochargers, becomes more problematic in electrically-assisted turbocharger applications. For example, excessive heat may overheat stator coils and may damage permanent magnets. Moreover, the additional heat from the electric motor (approx. 300° C) is, in some cases, sufficient to cause the turbocharger bearings to exceed permissible temperature limits. Accordingly, there is a need for an electrically-assisted turbocharger design that provides adequate cooling of the motor components.
  • the fluid cooled stator jacket for use with an electrically assisted turbocharger that has first and second housing segments and an electric motor stator disposed therein.
  • the fluid cooled stator jacket includes a housing adapted for insertion between the first and second housing segments.
  • the housing includes an inner surrounding wall and an outer surrounding wall defining an annular coolant chamber therebetween.
  • the housing may further include first and second end walls extending between the inner and outer surrounding walls.
  • the inner and outer surrounding walls may be cylindrical, for example.
  • the inner wall is sized and configured to receive the stator and the outer wall includes an inlet and an outlet each of which is in fluid communication with the coolant chamber.
  • the inlet may comprise an elongate cylindrical boss with an o-ring groove.
  • the inner surrounding wall includes a reduced diameter portion defining an abutment, and the stator abuts against the abutment.
  • the turbocharger includes a rotating assembly that includes a rotor mounted on a shaft, and a compressor wheel and a turbine wheel disposed on opposite ends of the shaft.
  • a bearing housing supports the rotating assembly and comprises upper and lower segments.
  • a stator is disposed around the rotor and the fluid cooled stator jacket is disposed in the bearing housing and around the stator.
  • the fluid cooled stator jacket includes a coolant housing having an inner surrounding wall and an outer surrounding wall defining an annular coolant chamber therebetween. The outer wall includes an inlet and an outlet in fluid communication with the coolant chamber.
  • the inlet comprises a cylindrical inlet boss and the outlet comprises a cylindrical outlet boss, wherein the lower segment includes an aperture adapted to receive the inlet boss and the upper segment includes an aperture adapted to receive the outlet boss.
  • the inner wall and the stator are configured to provide an annular clearance therebetween, and further comprising a thermal interface material disposed in the annular clearance.
  • the electrically assisted turbocharger includes a rotating assembly with a bearing housing configured to support the rotating assembly and comprising a first segment including an inlet aperture and a second segment including an outlet aperture.
  • a stator is disposed around the rotor and a fluid cooled stator jacket is disposed in the bearing housing and around the stator.
  • the fluid cooled stator jacket includes a coolant housing having an inner surrounding wall and an outer surrounding wall defining an annular coolant chamber therebetween.
  • the outer wall includes an inlet boss adapted for insertion into the inlet aperture and an outlet boss adapted for insertion into the outlet aperture.
  • the inner wall and the stator are configured to provide an annular clearance therebetween, and further comprising a thermal interface material disposed in the annular clearance.
  • a pair of seals are disposed on opposite ends of the stator, wherein each seal is operative to form a seal between the stator and the inner surrounding wall to contain the thermal interface material.
  • FIG. 1 is a side view in cross-section of a turbocharger incorporating a fluid cooled stator jacket according to an exemplary embodiment
  • FIG. 2 is an end view in cross-section of the turbocharger taken about lines 2-2 in FIG. 1 ;
  • FIG. 3 is an enlarged partial side view in cross-section of the fluid cooled stator jacket shown in FIGS. 1 and 2; and [0015] FIG. 4 is a perspective view of the fluid cooled stator jacket shown in FIGS. 1-3.
  • FIGS. 1 -3 illustrate an electrically assisted turbocharger with a bearing housing 85 comprised of first and second housing segments.
  • the housing segments are upper and lower halves 89 and 90, respectively, which are joined at flanges 91 , 92.
  • An electric motor is disposed in housing 85 and includes a stator 40 and a rotor 12 disposed on shaft 11.
  • the bearing housing 85 supports a rotating assembly 20 that includes shaft 1 1 , rotor 12, and a compressor wheel 22 and a turbine wheel 24 disposed on opposite ends of the shaft 11.
  • a cooling jacket 100 is fitted around the outside of the laminated stator pack 40 of the electric motor.
  • the cooling jacket 100 includes a housing 120 that has an inlet in the form of elongate cylindrical inlet boss 107 and an outlet in the form of elongate cylindrical outlet boss 109.
  • Coolant housing 120 includes an inner surrounding wall 106 and an outer surrounding wall 105 defining an annular coolant chamber 125 therebetween.
  • the housing includes first and second end walls 132, 134, respectively, that extend between the inner and outer surrounding walls 106, 105. It should be appreciated from the figures that the inlet and outlet are in fluid communication with coolant chamber 125 such that coolant 110 circulates through the cooling jacket 100.
  • the lower segment 90 includes an inlet aperture 127 adapted to receive the inlet boss 107.
  • the upper segment 89 includes an outlet aperture 129 adapted to receive the outlet boss 109.
  • Both the inlet boss and the outlet boss have o-ring grooves 108 as shown in FIG. 4.
  • an o-ring, or similar sealing device disposed in groove 108 mates with a complementary cylindrical surface of the corresponding inlet aperture 127 or outlet aperture 129.
  • An inlet fluid conducting fitting 101 can be fitted to the lower end of the inlet boss 107.
  • an outlet fluid conducting fitting 102 can be fitted to the outlet boss 109.
  • the cooling jacket is constructed of a material having good thermal conductivity characteristics and a coefficient of thermal expansion compatible with the coefficient of thermal expansion of the bearing housing in terms of dimensional compatibility.
  • the cooling jacket may be cast in aluminum, cast iron, or the like.
  • the inlet and outlet bosses (107, 109) are arranged perpendicular to the plane of a split line along the axis 1 of the bearing housing so that the cooling jacket 100 can be assembled into the lower half 90 of the bearing housing in a motion perpendicular to the plane of the split face of the bearing housing. And then the other part(s) of the split bearing housing 89 can be assembled in a like fashion.
  • the inner surrounding wall 106 of the cooling jacket 100 may be sized to provide an annular clearance 128 between the outer surface 43 of the stator 40 of the electric motor and inner surrounding wall 106. (This being the major thermal path in removing heat from the laminated stator pack.)
  • the annulus formed herein can be filled with a thermal interface material (TIM) to conduct heat away from the stator 40 of the electric motor to the inner wall of the cooling jacket and then to the cooling fluid 1 10.
  • TIM thermal interface material
  • a pair of seals 136 are disposed on opposite ends of the stator 40, wherein each seal is operative to form a seal between the stator
  • the outer surrounding wall 105 of the cooling jacket 100 may be sized to provide clearance 130 between the inner surface 65 of the bearing housing and the outer surrounding wall 105.
  • the annulus formed herein can be filled with a TIM to conduct heat away from the cooling fluid 1 10 to the bearing housing to provide some radiated heat rejection to the environment surrounding the bearing housing.
  • Thermal interface materials can be metal based, ceramic based, silicon based, carbon based, phase change materials, or other. Typically, they are delivered as greases, oils, or films. Examples are Thermigrease, Thermiflex, and Omegatherm.
  • the fluid cooled stator jacket extracts unwanted heat from the electric motor. This heat can be rejected via a vehicle cooling system, in which case the cooling fluid could be that of the vehicle (e.g. a water glycol mix), via a closed loop system, and thence to a vehicle cooling system, or via a separate cooling system just for the electric motor.
  • the coolant fluid 1 10 used in the water jacket 100 could be a direct tap off the vehicle cooling system, in which case the fluid could be water, ethylene glycol, propylene glycol, or a mix of the three.
  • the fluid may be in a closed loop system in which case it could be a refrigerant or a glycol-based fluid.
  • the assembly process for inserting the cooling jacket 100 into the bearing housing is as follows:
  • the outside surface 43 of the laminated stator pack 40 of the electric motor/generator can be coated with a TIM.
  • the electric motor is slid into the inner surrounding sidewall 106 until it abuts against the abutment 111 between the reduced diameter portion 103 and the larger inside diameter of the remainder of inner surrounding sidewall 106.
  • a constraint device such as a snap ring (not shown) may be inserted into the cooling jacket on the turbine end of the stator to axially constrain the stator in a direction opposite to that of the abutment 111.
  • the outer surrounding wall 105 of the cooling jacket, and the abutment 1 1 1 can also be coated with a TIM.
  • turbocharger rotating assembly should be mounted to the electric motor by this stage.
  • This assembly of turbocharger rotating assembly, electric motor, and cooling jacket can now be placed into the lower part of the bearing housing.
  • the inlet boss 107 With an o-ring located in the o-ring groove 108, must be slid into its complementary inlet aperture 127 in the bearing housing. If a sealing medium between the parts of the split bearing housing is required, it should now be applied.
  • the other part(s) of the bearing housing can now be fitted over the outlet boss 109, and a sealing o-ring. Mechanical fasters are used to exert the appropriate clamping load between the upper and lower flanges (91,92) of the bearing housing.

Landscapes

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

Abstract

L'invention concerne une enveloppe (100) de stator refroidie par un fluide (100) destinée à être utilisée avec un turbocompresseur à assistance électrique et qui comporte des premier et second segments de logement (89, 90) dans lesquels est disposé un stator (40) de moteur électrique. L'enveloppe (100) de stator refroidie par un fluide comprend un logement (120) pour liquide de refroidissement conçu pour être inséré entre les premier et second segments (89, 90). Le logement (120) pour liquide de refroidissement comprend une paroi périphérique interne (106) et une paroi périphérique externe (105) formant une chambre annulaire (125) pour le liquide de refroidissement. Le logement comprend également des première et seconde parois terminales (132, 134) s'étendant entre les parois périphériques interne et externe (106, 105). La paroi périphérique interne (106) est dimensionnée et configurée pour accueillir le stator (40) et la paroi périphérique externe (105) comprend un orifice d'admission (107) et un orifice d'évacuation (109), chacun étant en communication fluidique avec la chambre (125) de liquide de refroidissement. L'orifice d'admission (107) comprend une protubérance cylindrique allongée pourvue d'une gorge (108) pour joint torique.
PCT/US2013/038993 2012-05-23 2013-05-01 Enveloppe de stator refroidie par un fluide pour turbocompresseur à assistance électrique WO2013176853A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201261650642P 2012-05-23 2012-05-23
US61/650,642 2012-05-23

Publications (1)

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WO2013176853A1 true WO2013176853A1 (fr) 2013-11-28

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114215637A (zh) * 2021-12-30 2022-03-22 康跃科技(山东)有限公司 一种电辅助增压器低温冷却结构

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000130176A (ja) * 1998-10-30 2000-05-09 Isuzu Motors Ltd 発電・電動機を備えたターボチャージャ
US7469689B1 (en) * 2004-09-09 2008-12-30 Jones Daniel W Fluid cooled supercharger
US20100175377A1 (en) * 2009-01-12 2010-07-15 Will Hippen Cooling an electrically controlled turbocharger
US20100247343A1 (en) * 2006-08-18 2010-09-30 Ihi Corporation Motor-driven supercharger
US20100284824A1 (en) * 2009-04-02 2010-11-11 Ecomotors International, Inc. Cooling an Electrically Controlled Turbocharger

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000130176A (ja) * 1998-10-30 2000-05-09 Isuzu Motors Ltd 発電・電動機を備えたターボチャージャ
US7469689B1 (en) * 2004-09-09 2008-12-30 Jones Daniel W Fluid cooled supercharger
US20100247343A1 (en) * 2006-08-18 2010-09-30 Ihi Corporation Motor-driven supercharger
US20100175377A1 (en) * 2009-01-12 2010-07-15 Will Hippen Cooling an electrically controlled turbocharger
US20100284824A1 (en) * 2009-04-02 2010-11-11 Ecomotors International, Inc. Cooling an Electrically Controlled Turbocharger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114215637A (zh) * 2021-12-30 2022-03-22 康跃科技(山东)有限公司 一种电辅助增压器低温冷却结构

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