US20120263584A1 - Compressor Housing of a Radial Compressor - Google Patents

Compressor Housing of a Radial Compressor Download PDF

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Publication number
US20120263584A1
US20120263584A1 US13/446,684 US201213446684A US2012263584A1 US 20120263584 A1 US20120263584 A1 US 20120263584A1 US 201213446684 A US201213446684 A US 201213446684A US 2012263584 A1 US2012263584 A1 US 2012263584A1
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US
United States
Prior art keywords
burst
compressor
housing
protection ring
connection
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.)
Abandoned
Application number
US13/446,684
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English (en)
Inventor
Hedwig Schick
Bernhard Huurdeman
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
Original Assignee
Mann and Hummel GmbH
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 filed Critical Mann and Hummel GmbH
Assigned to MANN+HUMMEL GMBH reassignment MANN+HUMMEL GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SCHICK, HEDWIG, HUURDEMAN, BERNHARD, DR.
Publication of US20120263584A1 publication Critical patent/US20120263584A1/en
Abandoned 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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials 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
    • F05D2230/00—Manufacture
    • F05D2230/20—Manufacture essentially without removing material
    • F05D2230/23—Manufacture essentially without removing material by permanently joining parts together
    • 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
    • F05D2300/50—Intrinsic material properties or characteristics
    • F05D2300/518—Ductility

Definitions

  • the invention relates to a compressor housing of a radial compressor, in particular of a turbocharger of an internal combustion engine, in particular of a motor vehicle, with at least two housing components consisting at least partially of synthetic material, wherein a compressor impeller installation space and a spiral duct surrounding it radially on the outside with regard to a rotational axis of a compressor impeller are provided, and a securement structure enclosing the compressor impeller installation space at least partially in an annular manner is disposed in radial direction between the compressor impeller installation space and the spiral duct.
  • a radial compressor housing in particular for a turbocharger featuring at least two housing components is known from WO 2009/065881 A1.
  • a compressor impeller installation space and a spiral duct are provided.
  • the housing components are made of synthetic material.
  • the radial compressor housing can be made of synthetic material in an easy and cost-effective way.
  • the wall thicknesses can be optimized depending on the material used and the weight. Radial compressors have to guarantee an adequate operational safety. Due to the high impeller speeds of turbochargers there is a risk that, when the compressor impeller is damaged, metal shards penetrate the housing of the compressor and damage components in the engine compartment of the internal combustion engine. To avoid this, a securement structure encloses the compressor impeller installation space partially in a ring-shaped manner.
  • the securement structure is undetachably connected with one of the housing components.
  • the securement structure consists of a plurality of ribs which are integrally molded to an exterior side of an external wall surrounding the compressor impeller installation space. If parts break away from the compressor impeller, stiffening measures of the ribs shall prevent the housing from being penetrated.
  • An objective underlying the invention is to design a compressor housing as mentioned above that can be manufactured easily and which is robust. It should be optimized with regard to the material used and the weight. Furthermore, the operational safety shall be enhanced particularly in the case when parts break away from the compressor impeller.
  • the securement structure features a separate burst-protection ring with a tubular wall section enclosing the compressor impeller installation space circumferentially and which is disposed in the compressor housing and fixed in its position.
  • a burst-protection ring is therefore provided with a tubular wall section that encloses the compressor impeller installation space circumferentially in a closed manner.
  • the wall section forms circumferentially a preferably complete protection that prevents in particular parts breaking away from the compressor impeller from penetrating radially to the exterior.
  • the separate burst-protection ring can be in particular optimally adapted to the shape and/or size of the compressor housing.
  • the burst-protection ring can also be optimized for different requirements of the radial compressor with regard to its shape, size and/or material. For example, radial compressors can be designed for higher compressor impeller speeds than with known compressor housings made of synthetic material which are subjected to corresponding higher loads.
  • burst-protection ring As the burst-protection ring is disposed between the compressor impeller installation space and the spiral duct, it does not expand towards the exterior. In this way, the installation space needed for the compressor housing is smaller. Furthermore, the burst-protection ring cannot be seen from the outside which is optically appealing.
  • the separate burst-protection ring can be made of the same material as the compressor housing, or it can be made of other materials.
  • the tubular shape of the burst-protection ring stabilizes the compressor housing. It furthermore enhances the disruptive strength.
  • a burst-protection ring which is realized separately from the housing components simplifies the manufacture of the housing components unlike the compressor housings known from prior art where the housing components must be equipped with complex shapes that form the safety structure.
  • the burst-protection ring can simply be connected with one of the housing components before the housing is closed with the second housing component during assembly.
  • the separate burst-protection ring can influence positively the developing inherent vibrations.
  • the burst-protection ring dampens the inherent vibrations.
  • the burst-protection ring is fixed in the compressor housing in its position, this further enhances the stability of the compressor housing.
  • rattling of the burst-protection ring is prevented during operation of the radial compressor.
  • the burst-protection ring in conjunction with the circumferential wall section ensures an additional stability against a radial expansion of the wall surrounding the compressor impeller installation space.
  • the developing heat during the operation of the radial compressor can cause a stronger expansion of the synthetic material of the compressor housing than of the material of the compressor impeller. If the compressor impeller is in particular made of metal, its thermal expansion is lower than that of the compressor housing made of synthetic material. Due to the different expansion, the radial distance between a radial outer side of the compressor impeller and a radial inner side of the wall, which defines the compressor impeller installation space, can be enlarged. This may result in a reduced efficiency of the radial compressor.
  • the burst-protection ring can prevent the compressor housing from being radially expanded. In this way, the efficiency is less affected when the radial compressor is heated up.
  • the burst-protection ring is made of a material that can absorb the kinetic energy generated by fractions possibly thrown off the compressor impeller.
  • the compressor housing made of synthetic material in conjunction with the burst-protection ring can under severe stress pass a burst-protection test, also known as containment test, than conventional compressor housings made of synthetic material.
  • the burst-protection ring can also be called containment ring.
  • the burst-protection ring may be disposed in an annular space surrounding the compressor impeller installation space radially outside and which is defined by at least two of the housing components.
  • the annular space may preferably be accessible from the outside prior to the assembly of the housing components. This makes it easy to introduce the burst-protection ring into the annular space during the assembly of the compressor housing. It can also be secured against loss at one of the housing components.
  • the annular space may be closed. This makes it easy to fix the burst-protection ring in the annular space. Additional fasteners are not required.
  • the separate burst-protection ring may be disposed advantageously in an annular space which already exists in the compressor housing.
  • the burst-protection ring may be fixed in the compressor housing by means of a form-fit connection, in particular by clamping ribs and/or snap-in hooks and/or beads, and/or by means of a force-fit connection, in particular by pressing on or by pressing in the burst-protection ring, and/or by means of a cohesive connection, in particular by a glued connection, an injection connection or a welded connection.
  • Such connections make it possible to fix the burst-protection ring easily, reliably and in a stable manner in the compressor housing.
  • the burst-protection ring Before assembly of the housing, the burst-protection ring can be easily fixed by means of the connection at one of the housing components. Thus, it is easy to realize a loss prevention device.
  • Both housing components can then be connected with each other.
  • Form-fit connections can be easily realized in particular by connecting bars and grooves which can cooperate in a form-fit manner when inserting or placing the burst-protection ring on a corresponding housing part.
  • clamping ribs and/or snap-in hooks and/or beads that already exist in the compressor housing can be used.
  • Form-fit connections can be easily realized in a stable manner. If required, they can be loosened again easily.
  • the advantage of force-fit connections is that they can be realized easily and in a stable manner. Additional connection components such as, in particular, ribs, snap-in hooks or beads at the burst-protection ring and at the corresponding housing component are not required.
  • Cohesive connections allow to realize easily an additional sealing function. Cohesive connections enable in particular to seal easily gaps between the burst-protection ring and the corresponding housing component.
  • the burst-protection ring can advantageously be made at least in the wall section of a ductile material, in particular metal, synthetic material, carbon fibers, ceramics, aramid fibers or a material mix.
  • Ductile material can feature a high impact strength, a high elongation at break and/or a high vibration damping.
  • Ductile material can give the burst-protection ring, in particular the wall section, optimal characteristics with regard to elasticity, ductility, and deformability. In this way, the burst-protection ring can easily and reliably absorb the energy of thrown-off fractions. It can thus prevent fractions from penetrating.
  • the burst-protection ring can at least participate in forming a wall section of the spiral duct.
  • the burst-protection ring can participate in designing one part of the flow contour in the spiral duct.
  • the housing components and the burst-protection ring can be assembled in a modular way to form the spiral duct.
  • the flow contour in the spiral duct can be optimized by the shape and/or size of the burst-protection ring.
  • the burst-protection ring can enhance the stability of the walls of the spiral duct.
  • FIG. 1 is a schematic axial cross section of a compressor housing of a radial compressor according to a first example of an embodiment, wherein a burst-protection ring is disposed in an annular space which surrounds a compressor impeller installation space; and
  • FIG. 2 is a schematic axial cross section of a compressor housing according to a second example of an embodiment which resembles the compressor housing in FIG. 1 , wherein the burst-protection ring here forms part of a wall of a spiral duct.
  • FIG. 1 shows a housing 16 made of three housing components, that is an upper section 10 , a bottom section 12 , and a middle section 14 , for a radial compressor of an exhaust gas turbocharger of an internal combustion engine
  • the exhaust gases of the internal combustion engine drive a turbine impeller which is connected to a compressor impeller not shown in FIG. 1 for co-rotation.
  • the compressor impeller pivots in the housing 16 around a rotational axis 18 indicated in FIG. 1 .
  • the rotation of the compressor impeller aspirates combustion air in an intake tract of the internal combustion engine and compresses it to a higher turbo pressure under which the combustion air is supplied to cylinders of the internal combustion engine
  • a middle section 14 is disposed between the upper section 10 and the bottom section 12 .
  • the upper section 10 , the bottom section 12 , and the middle section 14 are made of thermoplastics.
  • Two annular joining areas 20 and 22 are formed at the upper section 10 .
  • a corresponding end face 24 of the middle section 14 abuts on the joining area 20 .
  • An end face 26 of the bottom section 12 abuts on the joining area 22 .
  • the joining area 20 and the end face 24 as well as the joining area 22 and the end face 26 each form weld zones.
  • a curvature 28 extending in an annular manner and enlarging in circumferential direction is formed at the upper section 10 in FIG. 1 and is open at the bottom. At the radially inside placed end of the curvature 28 abuts a curved section 32 on a contact area 30 .
  • the curved section 32 is adapted to the enlarged shape of the curvature 28 . It is integrally molded to the middle section 14 .
  • the middle section 14 comprises furthermore an axial section 34 with a curve 36 towards a radial section 38 .
  • the curved section 32 is integrally molded to the section 38 .
  • the bottom section 12 is designed substantially as an annular curvature 40 that enlarges in circumferential direction.
  • a bushing 42 extending axially towards the upper section 10 is attached to the radial exterior side.
  • the end face 26 is located at the free end of the bushing 42 .
  • An axial section 44 of the upper section 10 abuts on the internal wall of the bushing 42 .
  • the housing 16 is in this area double-walled.
  • the bottom section 12 is—at its bottom side facing away from the upper section 10 —designed to receive a housing bottom not shown in the drawing.
  • the curvature 28 at the upper section 10 , the curved section 32 at the middle section 14 , and the curvature 40 at the bottom section 12 form a spiral duct 46 .
  • a burst-protection ring 50 which forms a compressor impeller installation space 48 is inserted in a force-fit manner to the radial outer wall of the axial section 34 .
  • the burst-protection ring 50 is made of aluminum.
  • the housing 16 is stiffened thanks to the burst-protection ring 50 . If parts break away from the compressor impeller, precautions have been taken by the burst-protection ring 50 which shall prevent the housing 16 from being penetrated.
  • the burst-protection ring 50 is located in a circumferential annular space 52 .
  • the annular space 52 is formed between the upper section 10 and the middle section 14 .
  • the annular space 52 encloses the axial section 34 radially outside. It is separated from the axial section 34 via the wall of the middle section 14 with respect to fluid mechanics.
  • the burst-protection ring 50 is disposed between the compressor impeller installation space 48 and the spiral duct 46 .
  • the burst-protection ring 50 features a tubular wall section 54 that is coaxial to the compressor impeller installation space 48 .
  • the wall section 54 encloses the compressor impeller installation space 48 circumferentially in a closed manner.
  • the burst-protection ring 50 is fixed in its position by means of a force-fit connector assembly on the axial section 34 of the middle section 14 in the housing 16 .
  • the housing 16 For manufacturing the housing 16 , the upper section 10 , the bottom section 12 , and the middle section 14 are made of synthetic material in separate processes.
  • the burst-protection ring 50 is made of aluminum as a separate component.
  • the burst-protection ring 50 is placed in a force-fit manner in axial direction on the axial section 34 of the middle section 14 . In this way, it is secured against loss at the middle section 14 .
  • the middle section 14 together with the burst-protection ring 50 is inserted in axial direction into the upper section 10 so that the joining area 20 of the upper section 10 and the joining area 22 of the middle section 14 abut each other and the contact area 30 of the curved section 32 abuts against the end of the curvature 28 .
  • the bottom section 12 is then placed in axial direction on the upper section 10 so that the end face 26 of the bottom section 12 abuts against the end face 22 of the upper section 10 .
  • the joining area 20 and the end face 24 as well as the joining area 24 and the end face 26 are then welded with each other by means of ultrasonic welding. During the welding process, the burst-protection ring 50 acts as vibration damping.
  • the compressor impeller is now disposed in the compressor impeller installation space 48 in a manner that is of no interest here.
  • FIG. 2 shows a second example of an embodiment of a housing 116 .
  • Those elements that are similar to those in the first example of an embodiment in FIG. 1 have the same reference numerals with the difference that the value 100 is added.
  • the second example of an embodiment differs from the first example of an embodiment in that the curved section 132 that defines also the spiral duct 146 , and the radial section 138 are parts of the burst-protection ring 150 instead of being integrally molded to the middle section 114 , as is the case in the first example of an embodiment.
  • the curved section 132 and the radial section 138 are integrally molded to the side of the coaxial wall section 154 of the burst-protection ring 150 that faces the bottom section 112 .
  • the burst-protection ring 150 also forms the radial wall section 138 of the spiral duct 146 .
  • the curve 136 of the middle section 114 ends in radial direction approximately at the height of the radial outer interior side of the annular space 152 . That end of the curve 136 supports the radial section 138 of the burst-protection ring 150 at its backside in radial direction that faces away from the spiral duct 146 .
  • the burst-protection ring 150 features between the coaxial wall section 154 and the radial section 138 a curve 158 that fits closely to the radial outer surface of the curve 136 of the middle section 114 .
  • a plurality of ribs 156 is integrally molded to the radial outer circumferential side of the coaxial wall section 154 and the curve 158 of the burst-protection ring 150 .
  • the ribs 156 achieve a further stiffening of the burst-protection ring 150 and therefore of the housing 116 .
  • the invention is not limited to housing 16 ; 116 of a radial compressor of a turbocharger of a motor vehicle. Rather, it can also be used with different radial compressors, for example with industrial engines.
  • upper section 10 ; 110 and bottom section 12 ; 112 refer only to the exemplary orientation of the housing 16 ; 116 in FIGS. 1 and 2 .
  • the housings 16 ; 116 can also be oriented differently in the space, for example such that the upper section 10 ; 110 is located spatially at the bottom and the bottom section 12 ; 112 spatially at the top.
  • the burst-protection rings 50 ; 150 can also be made of a different, preferably ductile material, in particular of a metal, synthetic material, carbon fiber, ceramics, aramid fibers or a material mix.
  • the burst-protection rings 50 ; 150 may also be fixed in the housing 16 ; 116 in a different way instead of pressing them on the axial section 34 ; 134 .
  • the burst-protection rings 50 ; 150 may be fixed in the housing 16 ; 116 by means of another force-fit connection, a form-fit connection, for example by means of clamping ribs and/or snap-in hooks and/or beads and/or by means of a cohesive connection, for example by means of a glued connection, an injection connection or a welded connection.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US13/446,684 2011-04-14 2012-04-13 Compressor Housing of a Radial Compressor Abandoned US20120263584A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011017052A DE102011017052A1 (de) 2011-04-14 2011-04-14 Verdichtergehäuse eines Radialverdichters
DE102011017052.9-15 2011-04-14

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DE (1) DE102011017052A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105531461A (zh) * 2013-09-25 2016-04-27 三菱重工业株式会社 压缩机及增压器
CN105814319A (zh) * 2013-12-24 2016-07-27 三菱重工业株式会社 压缩机及增压器
FR3075890A1 (fr) * 2017-12-22 2019-06-28 Valeo Systemes De Controle Moteur Volute et procede de fabrication d'une volute
CN110056399A (zh) * 2018-01-18 2019-07-26 曼恩能源方案有限公司 用于燃气涡轮发动机的防爆装置
US20190284956A1 (en) * 2018-03-14 2019-09-19 Man Energy Solutions Se Casing Of A Turbocharger And Turbocharger

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013011458A1 (de) 2013-07-10 2015-01-15 Mann+Hummel Gmbh Verdichtergehäuse eines Radialverdichters
DE102014009504A1 (de) * 2014-06-26 2015-12-31 Mtu Friedrichshafen Gmbh Verdichtergehäuse für eine Turbine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4818176A (en) * 1987-04-15 1989-04-04 Mtu Motoren-Und Turbinen-Union Muenchen Gmbh Burst guard ring for turbo-engine housings
EP0834646A1 (de) * 1996-10-02 1998-04-08 Asea Brown Boveri AG Berstschutzvorrichtung für Radialturbinen von Turboladern
US20090290979A1 (en) * 2008-05-23 2009-11-26 Mitsubishi Heavy Industries, Ltd. Compressor housing

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2706110C3 (de) * 1977-02-14 1981-07-09 Aktiengesellschaft Kühnle, Kopp & Kausch, 6710 Frankenthal Verdichtergehäuse vorzugsweise für Abgasturbolader
WO2009065881A1 (de) 2007-11-20 2009-05-28 Mann+Hummel Gmbh Gehäuse für einen radialverdichter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4818176A (en) * 1987-04-15 1989-04-04 Mtu Motoren-Und Turbinen-Union Muenchen Gmbh Burst guard ring for turbo-engine housings
EP0834646A1 (de) * 1996-10-02 1998-04-08 Asea Brown Boveri AG Berstschutzvorrichtung für Radialturbinen von Turboladern
US20090290979A1 (en) * 2008-05-23 2009-11-26 Mitsubishi Heavy Industries, Ltd. Compressor housing
US8251650B2 (en) * 2008-05-23 2012-08-28 Mitsubishi Heavy Industries, Ltd. Compressor housing

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105531461A (zh) * 2013-09-25 2016-04-27 三菱重工业株式会社 压缩机及增压器
EP3009634A4 (de) * 2013-09-25 2016-09-14 Mitsubishi Heavy Ind Ltd Verdichter und auflader
CN105814319A (zh) * 2013-12-24 2016-07-27 三菱重工业株式会社 压缩机及增压器
EP3051144A4 (de) * 2013-12-24 2016-11-16 Mitsubishi Heavy Ind Ltd Verdichter und auflader
KR101844166B1 (ko) * 2013-12-24 2018-03-30 미츠비시 쥬고교 가부시키가이샤 압축기 및 과급기
FR3075890A1 (fr) * 2017-12-22 2019-06-28 Valeo Systemes De Controle Moteur Volute et procede de fabrication d'une volute
CN110056399A (zh) * 2018-01-18 2019-07-26 曼恩能源方案有限公司 用于燃气涡轮发动机的防爆装置
US20190284956A1 (en) * 2018-03-14 2019-09-19 Man Energy Solutions Se Casing Of A Turbocharger And Turbocharger

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Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SCHICK, HEDWIG;HUURDEMAN, BERNHARD, DR.;SIGNING DATES FROM 20120613 TO 20120618;REEL/FRAME:028432/0143

STCB Information on status: application discontinuation

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