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EP2574795B1 - Turbosoufflante de gaz d'échappement pour un moteur à combustion interne - Google Patents

Turbosoufflante de gaz d'échappement pour un moteur à combustion interne Download PDF

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Publication number
EP2574795B1
EP2574795B1 EP12179994.4A EP12179994A EP2574795B1 EP 2574795 B1 EP2574795 B1 EP 2574795B1 EP 12179994 A EP12179994 A EP 12179994A EP 2574795 B1 EP2574795 B1 EP 2574795B1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
bearing housing
combustion engine
gas turbocharger
coolant
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP12179994.4A
Other languages
German (de)
English (en)
Other versions
EP2574795A3 (fr
EP2574795A2 (fr
Inventor
Steffen Lippert
Martin Hopp
Helmut Blank
Dirk Schnelle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Inc
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 EP2574795A2 publication Critical patent/EP2574795A2/fr
Publication of EP2574795A3 publication Critical patent/EP2574795A3/fr
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Publication of EP2574795B1 publication Critical patent/EP2574795B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
    • 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
    • F01D25/12—Cooling
    • F01D25/125—Cooling of bearings
    • 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
    • F02B39/005—Cooling of pump drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • 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

Definitions

  • the invention relates to an exhaust-gas turbocharger for an internal combustion engine with a compressor which has a compressor wheel arranged in a compressor housing with a diffuser, a turbine which has a turbine wheel arranged in a turbine housing, a bearing housing in which a shaft connecting the compressor wheel to the turbine wheel is mounted is, with a bearing housing directed to the rear wall of the diffuser is cooled with coolant.
  • blow-by-gases crankcase breathers get low-pressure exhaust gas recirculation into the compressor housing of the turbocharger.
  • deposits of carbons from the exhaust gas and the oil of the blow-by gases in the compressor housing may result. These deposits occur mainly in the region of the diffuser, in which the temperatures rise particularly due to the low air flow cross section. This in turn leads to a narrowing of the flow-through cross section, whereby the power of the turbocharger drops at the same number of revolutions.
  • JP 2009-041443 A proposed a turbocharger in which the diffuser region of the compressor housing is cooled in order to avoid deposits in the compressor housing.
  • This turbocharger has a cooling water cooled bearing housing, the coolant jacket is guided from the back to the compressor housing by providing corresponding large-scale recesses on the rear wall of the compressor housing become.
  • such an embodiment is executable only in cooling water cooled turbochargers.
  • the distance to the flow-through channel remains relatively large, since the wall thickness of the casting compressor housing can not be made smaller due to the manufacturing process. This reduces the efficiency of cooling.
  • no coolant flow can be ensured at the compressor rear wall. Instead, flow dead spaces are to be expected in this area, which leads to a local heating of the coolant, which also significantly reduces the efficiency of cooling.
  • an exhaust gas turbocharger which has a compressor rear wall which forms with the bearing housing a coolant channel which is fluidically connected to the bearing housing cooling. This creates a cooling at the back of the compressor impeller.
  • This compressor rear wall is radially surrounded by a closed diffuser ring, which has no separate cooling, so that the cooling effect in the critical region of the diffuser is relatively low.
  • Other exhaust gas turbochargers with coolant devices are from the DE 103 25 980 A1 , of the US 4,815,184 A , of the EP 1 752 636 A2 and the WO 98/30791 A1 known.
  • an exhaust gas turbocharger with the features of the main claim. Characterized in that in the rear wall, a closed, annular coolant channel is formed, which extends around the entire circumference extends the diffuser and is closed by a wall of the bearing housing, an active and continuous flow through the coolant channel can be ensured because over the entire area flowed through uniform flow resistance and thus a constant pressure drop, which leads to dead water areas are avoided and thus the cooling efficiency is very high. Furthermore, such cooling can also be carried out on a bearing housing through which coolant does not otherwise flow.
  • the rear wall of the diffuser is at least partially formed by a separate annular component, which has an annular recess on its side facing the bearing housing, which serves as a coolant channel.
  • a separate annular component may be, for example, a rotating part, which is made of a different material than the compressor housing. This makes it possible to make the partition between the diffuser section and the coolant channel significantly thinner, whereby the heat transfer to the coolant and thus the heat dissipation is improved.
  • annular groove is formed on the recess bounding side walls of the annular member, in which a sealing ring is arranged, which rests against the bearing housing.
  • the annular member is bounded radially outwardly by the compressor housing and radially inwardly by the bearing housing.
  • the annular member on its radially outwardly bounding side wall on a shoulder which rests against a shoulder on the compressor housing.
  • a coolant inlet opening and a coolant outlet opening are arranged on the coolant channel closing wall of the bearing housing, via which the coolant can be supplied to the channel from the outside and discharged from the channel again. Over this, the cooling can be connected to the coolant circuit of the internal combustion engine.
  • a separating wall closing the cross section of the coolant channel is arranged in the recess between the coolant inlet opening and the coolant outlet opening. This provides forced flow along the annulus from the coolant inlet port to the outlet port, preventing short circuit flow.
  • the compressor housing is secured to the cooling passage closing wall of the bearing housing with the interposition of the shoulder of the annular member. Again, the cost of assembly is minimized by the positions of the components are determined by the shape.
  • the annular component is made of a good heat-conducting metal, in particular copper. This again increases the cooling efficiency, so that deposits are reliably avoided.
  • an exhaust-gas turbocharger is created whose efficiency is consistently high even with prolonged use by reliably avoiding deposits in the area of the diffuser, since the heat flow is reliably limited even at full load. This leads to improved engine filling and thus lower fuel consumption.
  • the figure shows a side view of an exhaust gas turbocharger according to the invention in a partially sectioned illustration.
  • the exhaust gas turbocharger consists of a turbine 10 and a compressor 12, the compressor wheel 14 and the turbine wheel are coupled to each other via a non-visible shaft in a known manner.
  • the turbine wheel runs in a turbine housing 18, which is spirally formed and has a tangential exhaust gas inlet 20 and an axial exhaust gas outlet 22.
  • the turbine housing 18 is secured to a bearing housing 24 via a tension band 26 in which the shaft is supported and oil spaces are provided to ensure lubrication of the shaft bearings.
  • a compressor housing 30 is attached via a clamping band 32 to a wall 28 of the bearing housing 24, in which the compressor wheel 14 rotates.
  • This is supplied via an axial air inlet 34 with a mixture of air and possibly exhaust gases and blow-by gases, compresses them and leads them into a diffuser 36 having spiral annular channel 38 and an invisible air outlet, from where the gas with increased pressure the cylinders of an internal combustion engine is supplied.
  • the spiral annular channel 38 is bounded in the region of the diffuser 36 on its side facing the bearing housing by a rear wall 42 which is formed on a separate annular member 44 which has an annular recess 46 with an open side. This is limited by radially inwardly and outwardly by side walls 48, 50 annular recess 46 is closed by the wall 28 of the bearing housing 24, wherein the wall 28 abuts against the ends of the two side walls 48, 50. At these ends of the side walls 48, 50 each have a groove 52, 54 is formed, in each of which a sealing ring 56, 58th is arranged, wherein the sealing rings 56, 58 bear against the wall 28 of the bearing housing 24 for sealing the recess 46.
  • the fastening of the compressor housing 30 on the bearing housing 24 with the clamping band 32 takes place with the interposition of a further sealing ring 60 in a groove 62 which is formed on the wall 28 of the bearing housing 24.
  • This groove 62 is located radially outwardly immediately behind a shoulder 64 which is formed on the bearing housing 24, wherein the compressor housing 30 has an axially extending annular projection 66, with which pushed the compressor housing against the shoulder 64 on the wall 28 for prefixing becomes.
  • the annular member 44 is fastened to the wall 28 of the bearing housing 24 by means of invisible screws.
  • the annular member 44 also has on its outer periphery a shoulder 68 which corresponds to a shoulder 70 on the rear wall 42 of the compressor housing 30, from which the projection 66 extends, so that the annular member 44 in its position to the compressor housing 30 is positioned.
  • the inner circumference of the annular member 44 abuts radially against a shoulder 72 of the wall 28 of the bearing housing 24.
  • the wall 28 closed by the annular recess 46 a closed channel, which serves as a coolant channel.
  • a coolant inlet opening and adeffenauslassö réelle and which are guided through pipe sockets to the outside, formed, via which the coolant channel is supplied with coolant.
  • the annular member between the coolant inlet port and the coolant outlet port has an invisible cross-sectional closing wall which prevents coolant from flowing directly from the coolant inlet port to the coolant outlet port without flowing around the shaft.
  • a heating of the compressor air by passing heat flows from the turbine side to the compressor side is just as reliably prevented, as a further heating of the air through the compression process itself. This results in a higher degree of compaction, which in turn leads to improved engine filling. Deposits in the region of the diffuser are reliably prevented by exhaust gases and blow-by gases, which in turn would lead to a reduced performance of the compressor. This ensures a continuous flow with high throughput and good heat transfer.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)

Claims (9)

  1. Turbocompresseur de gaz d'échappement pour une machine à combustion interne comprenant
    un compresseur (12), lequel possède une roue de compresseur (14) disposée dans un carter de compresseur (30) avec un diffuseur (36),
    une turbine (10), qui possède une roue de turbine disposée dans un carter de turbine (18),
    un logement de palier (24), dans lequel est logé un arbre qui relie la roue de compresseur (14) à la roue de turbine, une paroi arrière (42) du diffuseur (36) orientée vers le logement de palier (24) étant refroidie avec un réfrigérant,
    un canal à réfrigérant (74) fermé de forme annulaire étant formé au niveau de la paroi arrière (42), lequel s'étend autour de la totalité du pourtour du diffuseur (36) et est fermé par une paroi (28) du logement de palier (24),
    caractérisé en ce
    que la paroi arrière (42) du diffuseur (36) est au moins partiellement formée par un élément structural (44) de forme annulaire séparé, lequel possède, au niveau de son côté orienté vers le logement de palier (24), un évidement (46) de forme annulaire qui sert de canal à réfrigérant (74).
  2. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon la revendication 1, caractérisé en ce qu'une rainure (52, 54) de forme annulaire est respectivement formée au niveau des parois latérales (48, 50) de l'élément structural (44) de forme annulaire qui délimitent l'évidement (46), dans laquelle est respectivement disposée une bague d'étanchéité (56, 58) qui repose contre le logement de palier (24).
  3. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon la revendication 1 ou 2, caractérisé en ce que l'élément structural (44) de forme annulaire est délimité dans le sens radial vers l'extérieur par le carter de compresseur (30) et délimité dans le sens radial vers l'intérieur par le logement de palier (24).
  4. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon l'une des revendications 1 à 3, caractérisé en ce que l'élément structural (44) de forme annulaire possède, au niveau de sa paroi latérale (50) de délimitation dans le sens radial vers l'extérieur, un talon (68) qui repose contre un talon (70) au niveau du carter de compresseur (30).
  5. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon l'une des revendications précédentes, caractérisé en ce qu'une ouverture d'entrée de réfrigérant et une ouverture de sortie de réfrigérant sont disposées au niveau de la paroi (28) du logement de palier (24) qui ferme le canal à réfrigérant.
  6. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon la revendication 5, caractérisé en ce qu'une paroi de séparation qui ferme la section transversale du canal à réfrigérant est disposée dans l'évidement (46) entre l'ouverture d'entrée de réfrigérant et l'ouverture de sortie de réfrigérant.
  7. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon l'une des revendications 1 à 6, caractérisé en ce que l'élément structural (44) de forme annulaire est fixé par des vis au logement de palier (24).
  8. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon la revendication 4 ou l'une des revendications 5 à 7, lorsqu'elle est dépendante de la revendication 4, caractérisé en ce que le carter de compresseur (30) est fixé à la paroi (28) du logement de palier (24) qui ferme le canal à réfrigérant en intercalant le talon (68) de l'élément structural (44) de forme annulaire.
  9. Turbocompresseur de gaz d'échappement pour une machine à combustion interne selon l'une des revendications précédentes, caractérisé en ce que l'élément structural (44) de forme annulaire est fabriqué en un métal conduisant bien la chaleur, notamment en cuivre.
EP12179994.4A 2011-09-27 2012-08-10 Turbosoufflante de gaz d'échappement pour un moteur à combustion interne Active EP2574795B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011053954.9A DE102011053954B4 (de) 2011-09-27 2011-09-27 Abgasturbolader für eine Verbrennungskraftmaschine

Publications (3)

Publication Number Publication Date
EP2574795A2 EP2574795A2 (fr) 2013-04-03
EP2574795A3 EP2574795A3 (fr) 2018-05-02
EP2574795B1 true EP2574795B1 (fr) 2019-11-27

Family

ID=47002574

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12179994.4A Active EP2574795B1 (fr) 2011-09-27 2012-08-10 Turbosoufflante de gaz d'échappement pour un moteur à combustion interne

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EP (1) EP2574795B1 (fr)
DE (1) DE102011053954B4 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6215248B2 (ja) * 2015-03-18 2017-10-18 株式会社豊田自動織機 ターボチャージャ
CN109236745B (zh) * 2018-11-16 2023-10-20 四川聚亿重工有限公司 透平压缩机的定子结构
CN110578562B (zh) * 2019-08-30 2023-08-29 上海齐耀动力技术有限公司 一种冷却结构及其连接结构
DE102022118713A1 (de) 2022-07-26 2024-02-01 Rolls-Royce Solutions GmbH Verdichteranordnung, Turbolader und Brennkraftmaschine
DE102024106746A1 (de) * 2024-03-08 2025-09-11 Borgwarner Inc. Turbineneinheit für eine aufladevorrichtung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4704075A (en) * 1986-01-24 1987-11-03 Johnston Andrew E Turbocharger water-cooled bearing housing
US6032466A (en) * 1996-07-16 2000-03-07 Turbodyne Systems, Inc. Motor-assisted turbochargers for internal combustion engines
DE19652754A1 (de) * 1996-12-18 1998-06-25 Asea Brown Boveri Abgasturbolader
DE10325980A1 (de) * 2003-06-07 2004-12-23 Daimlerchrysler Ag Abgasturbolader
US7469689B1 (en) * 2004-09-09 2008-12-30 Jones Daniel W Fluid cooled supercharger
JP4692820B2 (ja) * 2005-08-11 2011-06-01 株式会社Ihi 電動機付過給機
JP4821734B2 (ja) 2007-08-08 2011-11-24 トヨタ自動車株式会社 ターボチャージャの冷却装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2574795A3 (fr) 2018-05-02
DE102011053954A1 (de) 2013-03-28
EP2574795A2 (fr) 2013-04-03
DE102011053954B4 (de) 2016-11-03

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