EP2918790A1 - Verdichtergehäuse - Google Patents

Verdichtergehäuse Download PDF

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Publication number
EP2918790A1
EP2918790A1 EP15158599.9A EP15158599A EP2918790A1 EP 2918790 A1 EP2918790 A1 EP 2918790A1 EP 15158599 A EP15158599 A EP 15158599A EP 2918790 A1 EP2918790 A1 EP 2918790A1
Authority
EP
European Patent Office
Prior art keywords
compressor
passage
spiral shaped
diffuser
compressor housing
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.)
Withdrawn
Application number
EP15158599.9A
Other languages
English (en)
French (fr)
Inventor
Mark Rankenberg
Edwin Kamphues
Hedwig Schick
Ulrich Dehnen
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.)
Mann and Hummel GmbH
Mitsubishi Turbocharger and Engine Europe BV
Original Assignee
Mann and Hummel GmbH
Mitsubishi Turbocharger and Engine Europe BV
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 Mann and Hummel GmbH, Mitsubishi Turbocharger and Engine Europe BV filed Critical Mann and Hummel GmbH
Publication of EP2918790A1 publication Critical patent/EP2918790A1/de
Withdrawn legal-status Critical Current

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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/024—Units comprising pumps and their driving means the driving means being assisted by a power recovery turbine
    • 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • 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
    • F05D2250/00—Geometry
    • F05D2250/20—Three-dimensional
    • F05D2250/24—Three-dimensional ellipsoidal
    • 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
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved
    • 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the invention relates to a compressor housing, a turbocharger comprising such a compressor housing, the use of such a turbocharger and a method of manufacturing such a compressor housing.
  • a turbocharger compressor comprising a plastic compressor housing is known from US2010/0232955 .
  • This compressor is a radial or centrifugal compressor.
  • the plastic compressor housing forms at least a part of a compressor wheel compartment for a compressor wheel, a spiral shaped compressor passage, and a diffuser.
  • the diffuser's function is to slow down the high-velocity air, with minimal losses, so that both pressure and temperature rise.
  • the spiral shaped compressor passage collects the air and slows it down further before it reaches the compressor passage outlet.
  • the start of a loop of the spiral shaped compressor passage does not provide an endless fluid communication path with an end of the loop.
  • the closed end of the spiral shaped compressor passage is a dead end which provides a one-way air flow between the closed end and the outlet.
  • the dead end located at the start of the passage prevents air to enter directly in a wider diverged part of the passage located close to the outlet of the passage. In this way the air collected in the passage near the closed end is forced to flow towards the outlet through the loop defined by the spiral shaped passage.
  • the compressor housing is preferably manufactured from plastic or aluminum.
  • An advantage of plastic is that the plastic compressor passage with the closed end can be manufactured cost efficiently. Further, it is possible in a cost effective way to include in the manufacturing process different functions in the plastic compressor housing. In other words, it is relatively easy to provide openings for positioning reinforcing elements and/or a screw thread or other connecting shapes in the plastic design for connecting the compressor housing for example to a center hub rotating assembly of a turbocharger. Further, it is possible to reduce the amount of plastic material to be used by providing hollow spaces or thinner parts in less strength-critical areas of the compressor housing. In the strength critical areas of the plastic compressor housing, plastic supporting ribs or the like can be provided.
  • plastic has a relatively low thermal conductivity, i.e. plastic is a thermal insulator.
  • the insulating plastic walls of a diffuser and the spiral shaped compressor passage provide a good insulating shield to protect the air being compressed inside the compressor against the external heat produced by external components such as for example the combustion engine.
  • the shielding effect has the result that the air temperature inside the compressor is less heated by external influences such that in relative terms compared to aluminum more compression with the compressor can be achieved.
  • the compressor housing is made as one-piece compressor housing.
  • the one-piece compressor housing is made without joining steps, such that the inner walls of the diffuser and/or the spiral shaped compressor passage do not have any joining seams.
  • a seam-free compressor housing optimizes air flow and further increases the performance of the compressor housing.
  • the housing comprises a hollow space between the compressor wheel compartment and the spiral shaped compressor passage.
  • This hollow space or spaces reduce the weight and material to be used for manufacturing the compressor housing.
  • the hollow space or spaces can be in fluid connection with the diffuser channel and the compressor compartment for recirculating air. It is also possible that the hollow space(s) is in fluid connection with different parts of the compressor compartment for recirculating air only in the compressor compartment.
  • These fluid connections for recirculating air widen the compressor performance map by moving the surge line to the left in the compressor performance map by allowing a small amount of airflow to bleed off the low-velocity portion of the wheel and recirculate, to ward off blade stall.
  • An advantage of a compressor housing made from plastic is that these fluid connections can be established in an uncomplicated manner and in a cost-effective way.
  • FIG. 1 shows a section of a turbocharger 10 according to the present invention.
  • Turbochargers 10 have become more and more popular for use in connection with passenger car engines, because the use of a turbocharger 10 permits selection of a smaller engine that develops the same amount of horsepower.
  • Using a smaller and a lower mass engine together with a turbocharger 10 has the desired effect of decreasing the overall weight of the car, decreasing fuel consumption and reducing the overall emissions of the engine, which contributes to a cleaner environment.
  • the turbocharger 10 includes a turbine 3 operatively connected to the engine exhaust manifold (not shown), a centrifugal compressor 1 operatively connected to the engine air intake manifold (not shown), and a center hub rotating assembly 5 housing a shaft 7 that connects the compressor wheel 9 with the turbine wheel 11.
  • the turbine wheel 11 is driven to rotate by the exhaust gas flowing in the exhaust manifold. Rotation of the turbine wheel 11 causes by means of the shaft 7 rotation of the compressor wheel 9. As the compressor wheel 9 rotates in the compressor housing 15, it increases the air mass flow rate, airflow density and air pressure delivered to the engine cylinders (not shown).
  • the compressor housing 15 is shown in greater detail in figure 2 .
  • the compressor housing 15 is adapted to receive air from an air intake 17 and distribute the air to a compressor wheel 9 rotatable disposed around an axial axis 19 within the compressor housing 15 and coupled to an end of the shaft 7.
  • the compressor housing 15 provides a compressor wheel compartment 21 for the compressor wheel 9, a spiral shaped compressor passage 23, and a diffuser 25 interposed between the compressor wheel 9 and the spiral shaped compressor passage 23.
  • the spiral shaped compressor passage 23 is formed along an outer region and radially remote from the compressor wheel 9.
  • the diffuser 25 has inner walls 26, 28 defining a diffuser channel 30, an inlet 31 in fluid communication with the compressor wheel compartment 21 for radially receiving high-velocity fresh air axially drawn in by means of the compressor wheel 9 and an outlet 33 in fluid communication with the spiral shaped compressor passage 23.
  • the distance between the inlet 31 of the diffuser channel 30 and the radially most remote compressor wheel tip 39 is smaller than 10 mm.
  • the distance d between the opposing inner walls 26, 28 in the middle section of the diffuser is about 4 mm. As shown in figures 1 and 2 the distance between the opposing inner walls 26, 28 near the inlet 31 and/or near the outlet 33 may be somewhat larger than the distance d. The maximum distance is smaller than 2 times the distance d.
  • the inner walls 26, 28 of the diffuser channel are curved providing an arched designed diffuser channel 30 between the inlet and the outlet for deflecting air tangentially and/or axially in the diffusor channel between the inlet and the outlet.
  • the compressor housing 15 shown in figures 1 and 2 is made as one-piece compressor housing 15. Such a one-piece compressor housing 15 has no joining seams, which has a beneficial effect on the air flowing through the seam-free diffuser 25 and seam-free spiral shaped compressor passage 23.
  • Compressor 15 can be manufactured by additive manufacturing such as laser sintering and/or by subtractive manufacturing. It is also possible to use lost core technology to manufacture the compressor housing 15.
  • the compressor housing 15 comprises a center axis 41, which as shown in figures 1 and 2 coincides in an assembled compressor 1 with the axial axis 19 of the compressor wheel 9.
  • the distance A1 measured only in a axial direction parallel to the axial axis 19 between the center 45 of the spiral shaped compressor passage 23 and the center 47 of the diffuser inlet 31 is about two times the distance A2 measured in the axial direction only between the center 45 of the spiral shaped compressor passage 23 and the inner wall 49 of the spiral shaped compressor passage 23.
  • the position to measure these distances is preferably where the diameter of the passage reaches or has reached its maximum diameter.
  • a preferred area is about 270°-360° measured from the start of the passage.
  • the maximum distance A1 is preferably sixth times the distance A2.
  • FIG. 3 shows a schematic view of a loop of a spiral shaped compressor passage 23 of a compressor housing 15 according to the present invention.
  • the spiral shaped compressor passage 23 comprises a passage outlet 51 for supplying compressed air to at least one cylinder (not shown) for combustion.
  • the passage 23 diverges in the direction of the outlet 51, such that the cross sectional area of the passage 23 smoothly increases between the start 52 of the loop of the spiral shaped compressor passage 23 and the outlet 51.
  • An end 53 of the spiral shaped compressor passage 23 opposing the outlet 51 is closed. This end 53 also defines the start 52 of the loop of the spiral shaped compressor passage 23.
  • FIG. 5 shows a schematic view of a spiral shaped compressor passage 223 of a conventional compressor housing.
  • the spiral shaped compressor passage 223 comprises a joint 260 where the loop start 252 of the spiral shaped compressor passage 223 meets the loop end 263 of the spiral shaped compressor passage 223.
  • the loop start 252 and the loop end 263 are in direct fluid communication with each other such that the air collected in the passage 223 near the loop start 252 may flow directly into the loop end 263 or vice versa.
  • Figure 5 shows the direct air flow from the loop start 252 towards the loop end 263 as indicated by the arrows B without flowing through the loop.
  • the main air flow is indicated by arrows A in figure 5 .
  • the spiral shaped compressor passage 23 ( figure 3 ) does not provide an endless fluid communication path (such as in figure 5 ) between the start 52 of the loop and the wider diverged part Z of the spiral shaped compressor passage located closer to the outlet 51.
  • the closed end 53 of the spiral shaped compressor passage is a dead end which provides a one-way air flow indicated in figure 3 by the arrows inside the spiral shaped compressor passage 23 between the closed end 53 and the outlet 51.
  • FIG 4 a section of another embodiment of a compressor housing 115 according to the present invention is shown.
  • the compressor housing 115 is made of four components 2, 4, 6, 8 defining the compressor wheel compartment 121, the passage 123, the diffuser 125, and the air intake 117.
  • the components 2, 4, 6, 8 are made from plastic.
  • the plastic components 2, 4, 6, 8 can be joined together by means of hot gas welding.
  • the advantage of hot gas welding two plastic components is high-quality seams. Such high-quality seams reduce the impact of a seam to the air flow.
  • Other joining techniques like ultrasonic welding or adhering can also be used to join the components.
  • the position of a seam can be chosen such that the influence of the seam of the air flow is negligible.
  • component 8 can be manufactured from a plastic type having a lower quality than the plastic type of the other components 2, 4, 6.
  • the compressor housing 115 comprises a hollow space 122 between the compressor wheel compartment 121 and the spiral shaped compressor passage 123.
  • the dimensions of the spiral-shaped hollow space 122 change over 360 degrees and preferably these dimensions change inversely proportional with the dimensions of the spiral shaped compressor passage 123.
  • the hollow space may comprise various compartments or multiple spaces separated by reinforcing ribs or the like. This hollow space 122 reduces the weight and material to be used for manufacturing the compressor housing 115.
  • the hollow space 122 can be in fluid connection (not shown) with the diffuser channel 125 and the compressor compartment 121 for recirculating air. It is also possible that the hollow space 122 is in fluid connection (not shown) with different parts of the compressor compartment 121 only for recirculating air.
  • the plastic compressor housing 15 is preferably manufactured of polyphenylene sulfide.
  • the compressor housing according to the present invention can also be made from suitable thermosetting polymers such as for example phenol formaldehyde resin or suitable high temperature thermoplastic polymers such as for example polyphenylene sulfide.
  • suitable thermosetting polymers such as for example phenol formaldehyde resin or suitable high temperature thermoplastic polymers such as for example polyphenylene sulfide.
  • closed end 53 is located against the outer wall of the spiral shaped compressor passage 23.
  • the plastic turbocharger compressor housing 115 can be manufactured by injection molding and assembling e.g. welding and/or screwing.
  • the compressor housing according to the present invention can also be used in an electrically driven or supported flow compressor or a secondary air charger.
  • the inner walls of the arched diffuser channel have a radius of curvature over more than 75% of the complete distance between diffuser inlet and diffuser outlet.
  • the centers of the at least two radii of curvature are located on one side of the diffuser only.
  • the diffuser defines a smooth arched flow path without any opposing bents, such as a first bend having a radius of curvature on a first side of the diffuser and a second bend having a radius of curvature on a second opposing side of the diffuser.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
EP15158599.9A 2014-03-12 2015-03-11 Verdichtergehäuse Withdrawn EP2918790A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL1040722A NL1040722B1 (en) 2014-03-12 2014-03-12 Compressor housing.

Publications (1)

Publication Number Publication Date
EP2918790A1 true EP2918790A1 (de) 2015-09-16

Family

ID=50555170

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EP15158597.3A Withdrawn EP2918789A1 (de) 2014-03-12 2015-03-11 Verdichtergehäuse
EP15158599.9A Withdrawn EP2918790A1 (de) 2014-03-12 2015-03-11 Verdichtergehäuse

Family Applications Before (1)

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EP15158597.3A Withdrawn EP2918789A1 (de) 2014-03-12 2015-03-11 Verdichtergehäuse

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EP (2) EP2918789A1 (de)
NL (1) NL1040722B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109871653A (zh) * 2019-03-15 2019-06-11 南京航空航天大学 航空发动机数学模型部件特性修正方法
CN114837759A (zh) * 2017-07-28 2022-08-02 康明斯有限公司 用于涡轮机的涡轮的扩散器空间

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016213296A1 (de) * 2016-07-20 2018-01-25 Man Diesel & Turbo Se Strömungsmaschine und Verfahren zum Herstellen desselben
JP6756563B2 (ja) * 2016-09-30 2020-09-16 ダイハツ工業株式会社 排気ターボ過給機
DE102018200287A1 (de) 2018-01-10 2019-07-11 Siemens Aktiengesellschaft Turbomaschineninnengehäuse
US20220196031A1 (en) * 2019-05-24 2022-06-23 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Centrifugal compressor and turbocharger

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2916198A (en) * 1956-06-18 1959-12-08 Zenas V Weisel Turbo-compressor apparatus
EP0138480A2 (de) * 1983-10-03 1985-04-24 The Garrett Corporation Zentrifugalkompressor
EP1061265A1 (de) * 1999-06-14 2000-12-20 Wärtsilä NSD Schweiz AG Aufladegruppe für einen Grossdieselmotor
US6210109B1 (en) * 1998-12-18 2001-04-03 Echo Incorporated Portable fluid blower
DE102008043461A1 (de) * 2008-11-04 2010-05-06 Robert Bosch Gmbh Verfahren und Vorrichtung zur Diagnose eines Turboladers eines Verbrennungsmotors
US20100202877A1 (en) * 2007-06-26 2010-08-12 Borgwarner Inc. Turbocharger diffuser
US20100232955A1 (en) 2007-11-20 2010-09-16 Hedwig Schick Housing for a radical compressor
US20120180476A1 (en) * 2011-01-17 2012-07-19 Ford Global Technologies, Llc Internal combustion engine with exhaust-gas turbocharging

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009055614B4 (de) * 2009-01-15 2017-03-23 Mann + Hummel Gmbh Turbolader mit einem Verdichtergehäuse aus Kunststoff

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2916198A (en) * 1956-06-18 1959-12-08 Zenas V Weisel Turbo-compressor apparatus
EP0138480A2 (de) * 1983-10-03 1985-04-24 The Garrett Corporation Zentrifugalkompressor
US6210109B1 (en) * 1998-12-18 2001-04-03 Echo Incorporated Portable fluid blower
EP1061265A1 (de) * 1999-06-14 2000-12-20 Wärtsilä NSD Schweiz AG Aufladegruppe für einen Grossdieselmotor
US20100202877A1 (en) * 2007-06-26 2010-08-12 Borgwarner Inc. Turbocharger diffuser
US20100232955A1 (en) 2007-11-20 2010-09-16 Hedwig Schick Housing for a radical compressor
DE102008043461A1 (de) * 2008-11-04 2010-05-06 Robert Bosch Gmbh Verfahren und Vorrichtung zur Diagnose eines Turboladers eines Verbrennungsmotors
US20120180476A1 (en) * 2011-01-17 2012-07-19 Ford Global Technologies, Llc Internal combustion engine with exhaust-gas turbocharging

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114837759A (zh) * 2017-07-28 2022-08-02 康明斯有限公司 用于涡轮机的涡轮的扩散器空间
CN114837759B (zh) * 2017-07-28 2023-07-18 康明斯有限公司 用于涡轮机的涡轮的扩散器空间
CN109871653A (zh) * 2019-03-15 2019-06-11 南京航空航天大学 航空发动机数学模型部件特性修正方法

Also Published As

Publication number Publication date
NL1040722B1 (en) 2015-11-19
NL1040722A (en) 2015-11-05
EP2918789A1 (de) 2015-09-16

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