EP3263911A1 - Kompressorgehäuse für einen turbolader und herstellungsverfahren dafür - Google Patents

Kompressorgehäuse für einen turbolader und herstellungsverfahren dafür Download PDF

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Publication number
EP3263911A1
EP3263911A1 EP16755427.8A EP16755427A EP3263911A1 EP 3263911 A1 EP3263911 A1 EP 3263911A1 EP 16755427 A EP16755427 A EP 16755427A EP 3263911 A1 EP3263911 A1 EP 3263911A1
Authority
EP
European Patent Office
Prior art keywords
raw material
abradable seal
press
ring member
inner circumferential
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Withdrawn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
EP16755427.8A
Other languages
English (en)
French (fr)
Other versions
EP3263911A4 (de
Inventor
Masahide Sakurai
Koichi Yonezawa
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.)
Toyota Motor Corp
Otics Corp
Original Assignee
Toyota Motor Corp
Otics Corp
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 Toyota Motor Corp, Otics Corp filed Critical Toyota Motor Corp
Publication of EP3263911A1 publication Critical patent/EP3263911A1/de
Publication of EP3263911A4 publication Critical patent/EP3263911A4/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Withdrawn legal-status Critical Current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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of 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

Definitions

  • the present invention relates to a compressor housing for a turbocharger and a method of manufacturing the same.
  • a compressor for use in a supercharger such as a turbocharger of an automobile includes a compressor housing that is configured to be able to house an impeller, and includes an intake port for sucking air toward the impeller, a scroll chamber for introducing air discharged by the impeller thereinto, the scroll chamber being formed in a circumferential direction at an outer circumferential side of the impeller, and a shroud surface opposed to the impeller.
  • compression efficiency of the compressor can be increased by minimizing a gap between blades of the impeller and the shroud surface of the compressor housing.
  • the gap is decreased, there is a risk that the impeller may be damaged, for example, when the impeller blades come into contact with the shroud surface of the compressor housing due to vibrations, a runout of an impeller rotation shaft, or the like.
  • an abradable seal made of a resin or the like that is softer than the impeller blades is attached to a portion of the compressor housing, which forms the shroud surface (Patent Document 1).
  • Patent Document 1 JP-A-09-170442
  • the abradable seal in order to fix the abradable seal to the shroud part, the abradable seal is expanded to a diffuser portion that is not opposed to the impeller, then, fastened and fixed thereto with a screw member through a screw hole provided in the diffuser portion. Further, a housing recess for housing a head of each screw member is provided on a diffuser surface of the abradable seal in order to avoid the head of the screw member from projecting into a fluid passage from the diffuser surface.
  • the housing recess that opens to the fluid passage affects intake air flowing through the fluid passage to thereby disturb a flow of airflow, which may reduce compression efficiency.
  • the housing recess has water or the like in, this may be a cause of corrosion.
  • such configuration has disadvantages such as increase of manufacturing processes and/or increase of material costs.
  • the abradable seal is expanded to the diffuser portion that is a region not opposed to the impeller, the abradable seal is relatively increased in size.
  • a material for forming the abradable seal is generally more costly than a material for forming the compressor housing. Therefore, upsizing of the abradable seal is disadvantageous in terms of cost.
  • the present invention has been made in view of the conventional problems as mentioned above, and it is intended to provide a compressor housing for a turbocharger which makes it possible to prevent reduction of compression efficiency and to maintain holdability for the abradable seal, and which is advantageous in terms of cost, and a method of manufacturing the same.
  • One aspect of the present invention provides a compressor housing for a turbocharger configured to house an impeller, the compressor housing including:
  • the inner circumferential recess includes a recess press-contact surface that is formed along the press-fitting direction of the ring member, and press-contacts the radial-direction outside surface of the ring member; and a recess opposing surface that opposes a press-fitting direction forward surface of the ring member
  • the abradable seal includes a flange that projects outwardly in the radial direction of the abradable seal, and the flange is held between the press-fitting direction forward surface and the recess opposing surface by press-fitting the ring member into the inner circumferential recess.
  • Another aspect of the present invention provides a method of manufacturing the compressor housing.
  • the method includes the steps of:
  • the flange of the abradable seal is held between the press-fitting direction forward surface of the ring member and the recess opposing surface of the inner circumferential recess by press-fitting the ring member into the inner circumferential recess of the housing body.
  • the diffuser surface has water or the like in, which may cause corrosion.
  • material cost does not increase.
  • the abradable seal can be downsized, which is advantageous in terms of cost.
  • an integral raw material constructed from a housing raw material to be a raw material for a housing body and a ring-shaped raw material to be a raw material for a ring member is formed in the step of forming an integral raw material, and in the step of machining and dividing the integral raw material, the integral raw material is machined, and then is divided to form the housing body and the ring member as separated bodies. That is, the ring-shaped raw material can be machined and divided simultaneously in the step of machining the housing body. In this way, the manufacturing processes can be simplified as compared to the case where both raw materials are separately prepared and machined independently.
  • the housing body and the ring member are formed from the housing raw material and the ring-shaped raw material respectively, both of which are cut out from the integral raw material, the housing body and the ring member are composed of the same forming material.
  • the housing body and the ring member have the same linear thermal expansion coefficients, accordingly, even if temperature change causes heat expansion or heat contraction in the housing body and/or the ring member, reduction of the press-contact force at a position where the radial-direction outside surface of the ring member and the recess press-contact surface of the inner circumferential recess come into press-contact with each other, can be prevented.
  • the press-fitted state of the ring member in relation to the inner circumferential recess of the housing body can be maintained.
  • reduction of the holdability for the abradable seal, of the inner circumferential recess of the housing body can be prevented even if any temperature change occurs.
  • a compressor housing for a turbocharger which makes it possible to prevent reduction of the compression efficiency and to maintain holdability for the abradable seal, and which is advantageous in terms of cost, and a method of manufacturing the same.
  • the compressor housing for a turbocharger according to the present invention can be used for a turbocharger for an automobile, and the like.
  • the ring member is preferably composed of the same forming material as the housing body.
  • both the housing body and the ring member have the same linear thermal expansion coefficients, accordingly, even if heat expansion or heat contraction occur in the housing body and/or the ring member, reduction of the press-contact force at a position where the radial-direction outside surface of the ring member and the recess press-contact surface of the inner circumferential recess come into press-contact with each other, can be prevented.
  • the press-fitted state of the ring member in relation to the inner circumferential recess of the housing body can be sufficiently maintained.
  • reduction of the holdability for the abradable seal, of the inner circumferential recess of the housing body can be sufficiently prevented even if any temperature change occurs.
  • the flange is formed on an entire circumference of the abradable seal.
  • the flange formed over the entire circumference of the abradable seal is held between the press-fitting direction forward surface of the ring member and the recess opposing surface of the inner circumferential recess in the housing body so as to fix the abradable seal, thereby reliably obtaining sufficient holdability for the abradable seal.
  • the abradable seal preferably includes the flange at a first end portion in the axial direction, and a second end portion of the abradable seal at the opposite side to the first end portion is preferably spatially apart from an opposing end surface that faces the second end portion in the inner circumferential recess.
  • the abradable seal is inserted into the inner circumferential recess with the second end portion being as a forward end, and the second end portion of the abradable seal is in contact with the opposing end surface of the inner circumferential recess, the abradable seal is prevented from expanding at the side of the second end portion and an amount of expansion at the side of the first end portion becomes large. As a result, a diffuser passage becomes narrow.
  • the flange is formed at the first end portion close to the diffuser passage, and the second end portion is made spatially apart from the opposing end surface of the inner circumferential recess. Consequently, the abradable seal is allowed to expand at the side of the second end portion, so that the amount of expansion at the side of the first end portion can be made small. As a result, the diffuser passage can be prevented from being narrowed.
  • an outer circumference surface of the abradable seal is preferably spatially apart from an outer circumference surface of the inner circumferential recess.
  • a space is formed between the abradable seal and the inner circumferential recess. Therefore, if the abradable seal expands, the outer circumference surface of the abradable seal expands inside of the space. Consequently, reduction of the diameter in the expanded abradable seal can be prevented.
  • the tip clearance can be set to be small from the beginning.
  • the abradable seal having the ring member attached thereto when installed on the housing body, the abradable seal can be inserted into the inner circumferential recess such that the outer circumference surface of the abradable seal is in no contact with the outer circumference surface of the inner circumferential recess, which improves assemble workability.
  • the ring-shaped raw material can be formed as a single body with the housing raw material along a place for press-fitting the ring member in the step of forming an integral raw material.
  • the ring-shaped raw material is formed in the step of forming an integral raw material as a single body with the housing raw material along an end portion of an intake port that is formed at an opposite side to a side on which the ring member is to be press-fitted. Also in this case, the molding cost and the casting cost can be reduced, to thereby totally reduce the manufacturing costs.
  • a compressor housing for a turbocharger according to the present embodiment will be described with reference to Figures 1 to 9 .
  • a compressor housing 1 for a turbocharger according to the present embodiment (hereinafter also referred to as the "compressor housing 1") is equipped with a housing body 20, an abradable seal 30, and a ring member 40 as shown in Figure 1 .
  • the housing body 20 is configured to be able to house an impeller 10, and includes an inner circumferential recess 21 recessively formed on an annular inner circumference surface along an outer circumference 10a of the impeller 10.
  • the abradable seal 30 is annularly formed and disposed in the inner circumferential recess 21, and the inner circumference surface of the abradable seal 30 forms a shroud surface 31 that opposes the impeller 10.
  • the ring member 40 is formed in a ring shape along the inner circumferential recess 21 of the housing body 20, and is press-fitted into the inner circumferential recess 21 in the axial direction of the impeller.
  • the inner circumferential recess 21 includes a recess press-contact surface 212 that is formed along the press-fitting direction (i.e. the axial direction X) of the ring member 40, and press-contacts a radial-direction outside surface 42 of the ring member 40; and a recess opposing surface 213 that opposes a press-fitting direction forward surface 41 of the ring member 40.
  • the abradable seal 30 includes a flange 32 that projects outwardly in a radial direction of the abradable seal 30, and the flange 32 is held between the press-fitting direction forward surface 41 and the recess opposing surface 213 by press-fitting the ring member 40 into the inner circumferential recess 21.
  • the compressor housing 1 forms an outer shell of a compressor (compression machine) for use in a turbocharger of an automobile.
  • the compressor housing 1 according to the present embodiment will be described in detail below.
  • the housing body 20 is made of an aluminum cast product obtained by gravity casting, and is equipped with an intake port 11, an intake passage 12, and a scroll chamber 13, as shown in Figures 1 and 2 .
  • the intake port 11 and the intake passage 12 are defined by a cylindrical portion 23.
  • the scroll chamber 13 is formed on the outer circumference side of the impeller 10 in the circumferential direction to introduce air discharged from the impeller 10 thereinto.
  • the inner circumferential recess 21 is formed on the inner circumference surface of the housing body 20 along the outer circumference of the abradable seal 30. And, the inner circumferential recess 21 includes a first cylindrical recessed portion 210 that is recessively formed along a cylindrical abradable seal body part 310 that will be mentioned below, of the abradable seal 30, and a second cylindrical recessed portion 220 that is formed recessively further than the first recessed portion 210 along an enlarged diameter part 311. Thus, the inner circumferential recess 21 is configured to be able to have the abradable seal 30 disposed therein.
  • the second cylindrical recessed portion 220 of the inner circumferential recess 21 includes the recess press-contact surface 212 that is formed along the press-fitting direction of the ring member 40 that will be mentioned below, and press-contacts the radial-direction outside surface 42 of the ring member 40; and the recess opposing surface 213 that extends in the radial direction in such a manner to oppose the press-fitting direction forward surface 41 that defines a press-fitting direction X forward side of the ring member 40.
  • the abradable seal 30 is formed of an elastically deformable material.
  • the abradable seal 30 is made of a polyimide resin.
  • the material for forming the abradable seal 30 is not limited to this, and available materials include Teflon (registered trademark), PPS (polyphenylene sulfide) resin, and PEEK (polyetheretherketone) resin, and the like.
  • the abradable seal 30 has an annular shape, and the entire inner circumference surface forms the shroud surface 31, opposing the impeller 10 ( Figure 1 ).
  • the abradable seal 30 includes the cylindrical abradable seal body part 310, and the enlarged diameter part 311 that is formed on the opposite side to the intake port 11 (i.e.
  • the enlarged diameter part 311 is formed in the circumference direction of the abradable seal 30.
  • the enlarged diameter part 311 includes the flange 32 that projects outwardly in the radial direction. In the present embodiment, the flange 32 is formed on the entire circumference of the enlarged diameter part 311.
  • the abradable seal 30, as shown in Figures 1 and 2 is disposed in the inner circumferential recess 21 such that the abradable seal body part 310 is positioned in the first recessed portion 210 of the inner circumferential recess 21 and the enlarged diameter part 311 is positioned in the second recessed portion 220.
  • the ring member 40 is formed in a ring shape along the recess press-contact surface 212 of the inner circumferential recess 21, and has a substantially rectangular cross section as shown in Figures 1 and 2 .
  • the radial-direction outside surface 42 that oppose the recess press-contact surface 212 is formed over the entire outer periphery of the ring member 40 along the press-fitting direction X.
  • the outer diameter of the ring member 40 is slightly larger than the inner diameter of the second recessed portion 220 of the inner circumferential recess 21.
  • the radial-direction outside surface 42 press-contacts the recess press-contact surface 212 by press-fitting the ring member 40 into the second recessed portion 220.
  • a space 50 that is surrounded by the press-fitting direction forward surface 41, the recess opposing surface 213 and the outer circumference surface 32a is formed. Furthermore, in the first recessed portion 210, because the outer diameter of the abradable seal body part 310 is smaller than the inner diameter of the first recessed portion 210, the outer circumference surface 310a of the abradable seal body part 310 is spatially apart from the outer circumference surface 210a of the first recessed portion 210. Thus, a space 51 is formed between the outer circumference surface 310a of the abradable seal body part 310 and the outer circumference surface 210a of the first recessed portion 210.
  • the abradable seal 30 has the flange 32 formed at a first end portion 34 thereof in the axial direction X. And, a second end portion 35 at an opposite side to the first end portion 34 is spatially apart from an opposing end surface 210b that faces the second end portion 35 in the inner circumferential recess 21. Thus, a space 52 is formed between the second end portion 35 and the opposing end surface 210b.
  • a bearing housing or an end surface 70 of a backplate is located on the opposite side to the intake port 11 of the housing body 20.
  • a diffuser portion 14 that serves as a fluid passage that connects the impeller 10 side to a scroll chamber 12 is formed between the end surface 70 and the housing body 20.
  • a surface that opposes the end surface 70 forms a diffuser surface 24.
  • the impeller 10 is arranged on the side of the inner circumference surface (the shroud surface 31) of the abradable seal 30 in the housing body 20 in a rotatable manner around a rotation shaft 15.
  • the impeller 10 has a hub 16 and a plurality of blades 17 that are arranged in the circumferential direction of the hub 16 and project from the outer circumference surface thereof. The plurality of blades 17 are arranged facing the shroud surface 31 of the abradable seal 30.
  • an integral raw material 60 constructed from a housing raw material 20a which will be a raw material for the housing body 20, and a ring-shaped raw material 40a which will be a raw material for the ring member 40, is firstly formed (a step S1 of forming an integral raw material).
  • the integral raw material 60 was formed from an aluminum alloy by a gravity casting method. As shown in Figure 4 , the intake port 11 and the intake passage 12 were formed in the integral raw material 60, and the ring-shaped raw material 40a was formed in a ring shape protrudingly toward the opposite side to the intake port 11 along a place 40b (the second recessed portion 220 in Figure 2 ) at which the ring member 40 would be press-fitted in the housing raw material 20a. Moreover, the scroll chamber 13 was formed in the integral raw material 60 using a core.
  • the integral raw material 60 ( Figure 4 ) was machined and divided to form the housing body 20 and the ring member 40 as shown in Figure 5 (a step S2 of machining and dividing the integral raw material).
  • the integral raw material 60 in the state shown in Figure 4 is machined cutting an inner circumferential portion 20b of a part that will be the housing raw material 20a to form the inner circumferential recess 21 ( Figure 5 ) including the first recessed portion 210 and the second recessed portion 220, thereby forming a portion that will be the housing body 20.
  • a portion that will be the ring member 40 is formed by grinding a part that will be the ring-shaped raw material 40a.
  • the integral raw material 60 thus machined was divided into two components so as to prepare the housing body 20 and the ring member 40.
  • the ring member 40 is press-fitted into the abradable seal 30 that has been prepared in advance, and is assembled thereto. Then, the resulting assembly is press-fitted into the inner circumferential recess 21 of the housing body 20 (a step S3 of press-fitting). As shown in Figure 7 , the flange 32 was held between the press-fitting direction forward surface 41 of the ring member 40 and the recess opposing surface 213 of the inner circumferential recess 21 by press-fitting the ring member 40 into the second recessed portion 220 in the inner circumferential recess 21.
  • the outer diameter of the radial-direction outside surface 42 of the ring member 40 was slightly larger than the inner diameter of the recess press-contact surface 212 of the second recessed portion 220.
  • the radial-direction outside surface 42 of the ring member 40 was made press-contacted with the recess press-contact surface 212 of the second recessed portion 220 by press-fitting the ring member 40 into the second recessed portion 220. It is noted that the radial-direction inside surface 43 of the ring member 40 press-contacts the outer circumference surface 311 of the enlarged part 313 of the abradable seal 30.
  • an inner circumferential portion 30b ( Figure 7 ) of the abradable seal 30 was cut along with the ring member 40 and the inner circumference surface of the housing body 20 to form the shroud surface 31 as shown in Figure 8 (a step S4 of forming a shroud surface).
  • a continuously smooth surface that continues from the intake port 11 to the diffuser surface 24 through the intake passage 12 and the shroud surface 31 was formed. In this way, the compressor housing 1 was completed.
  • the flange 32 of the abradable seal 30 is held between the press-fitting direction forward surface 41 of the ring member 40 and the recess opposing surface 213 of the inner circumferential recess 21 by press-fitting the ring member 40 into the inner circumferential recess 21 of the housing body 20.
  • the abradable seal 30 is fixed to the inner circumferential recess 21 of the housing body 20.
  • the diffuser surface 24 has water or the like, which may cause corrosion.
  • material cost does not increase.
  • the abradable seal 30 can be downsized, which is advantageous in terms of cost.
  • the ring member 40 is composed of the same forming material as the housing member 20.
  • both the housing body 20 and the ring member 40 have the same linear thermal expansion coefficients, accordingly, even if heat expansion or heat contraction occur in the housing body 20 and/or the ring member 40, reduction of the press-contact force at a position where the radial-direction outside surface 42 of the ring member 40 and the recess press-contact surface 212 of the inner circumferential recess 21 come into press-contact with each other, can be prevented.
  • the press-fitted state of the ring member 40 in relation to the inner circumferential recess 21 of the housing body 20 can be maintained.
  • reduction of the holdability for the abradable seal 30, of the inner circumferential recess 21 of the housing body 20 can be sufficiently prevented even if any temperature change occurs.
  • the flange 32 is formed on an entire circumference of the abradable seal 30.
  • the flange 32 formed over the entire circumference of the abradable seal 30 is held between the press-fitting direction forward surface 41 of the ring member 40 and the recess opposing surface 213 of the inner circumferential recess 21 so as to fix the abradable seal, thereby reliably obtaining sufficient holdability for the abradable seal 30.
  • the ring member 40 is formed along the recess press-contact surface 212 of the second recessed portion 220 in the inner circumferential recess 21, the radial-direction outside surface 42 of the ring member 40 is formed on the entire circumference of the ring member 40. Consequently, a position where the recess press-contact surface 212 and the radial-direction outside surface 42 come into press-contact with each other can be obtained widely, so that the ring member 40 can be reliably fixed to the housing body 20.
  • the sectional shape of the ring member 40 is designed to be substantially rectangular.
  • the sectional shape is not limited to this, and can be determined as appropriate in view of formability of the ring member 40, easiness of press-fitting into the inner circumferential recess 21, required holdability for the abradable seal 30, manufacturing cost, and so on.
  • the flange 32 is protrudingly formed outward in the radial direction on the entire circumference of the abradable seal 30.
  • the flange 32 is not limited to this configuration.
  • the flange 32 may be formed on part of the outer circumference of the abradable seal 30.
  • a position to form the flange 32 can be determined as appropriate in view of formability of the abradable seal 30, manufacturing costs, required holdability for the abradable seal 30, and so on.
  • the abradable seal 30 includes the flange 32 at the first end portion 34 in the axial direction, and the second end portion 35 of the abradable seal 30 at the opposite side to the first end portion 34 is spatially apart from the opposing end surface 210b that faces the second end portion 35 in the inner circumferential recess 21.
  • the abradable seal 30 is inserted into the inner circumferential recess 21 with the second end portion 35 being as a forward end, and the second end portion 35 of the abradable seal 30 is in contact with the opposing end surface 210b of the inner circumferential recess 21, the abradable seal 30 is prevented from expanding at the side of the second end portion 35. Consequently, the diffuser passage 14 becomes narrow.
  • the flange 32 is formed at the first end portion 34 close to the diffuser passage 14, and the second end portion 35 is made spatially apart from the opposing end surface 210b of the inner circumferential recess 21.
  • the abradable seal 30 is allowed to expand at the side of the second end portion 35, so that the amount of expansion at the side of the first end portion 34 can be made small.
  • the diffuser passage 14 can be prevented from being narrowed.
  • the outer circumference surface 310a of the abradable seal 30 is spatially apart from the outer circumference surface 210a.
  • the space 51 is formed between the abradable seal 30 and the inner circumferential recess 21.
  • the outer circumference surface 310a of the abradable seal 30 expands inside of the space 51. Consequently, reduction of diameter in the expanded abradable seal 30 can be prevented.
  • the tip clearance can be set to be small from the beginning.
  • the abradable seal 30 having the ring member 40 attached thereto is installed on the housing body 20, it is possible to insert the abradable seal 30 into the inner circumferential recess 21 such that the outer circumference surface 310a of the abradable seal 30 is in no contact with the outer circumference surface 210a of the inner circumferential recess 21, which improves assemble workability.
  • the compressor housing 1 for a turbocharger in the present embodiment, it is possible to manufacture the compressor housing 1 that exhibits the above-mentioned operational effects.
  • the integral raw material 60 constructed from the housing raw material 20a which will be a raw material for the housing body 20, and the ring-shaped raw material 40a which will be a raw material for the ring member 40, is formed, and in the step S2 of machining and dividing the integral raw material, the integral raw material 60 is machined and divided to form the housing body 20 and the ring member 40.
  • the ring member 40 is formed by machining and dividing in the step to process the housing body 20 by machining (the step S2 of machining and dividing the integral raw material). In this way, the manufacturing processes can be simplified as compared to the case where both raw materials 20a and 40b are separately prepared and machined independently.
  • the housing body 20 and the ring member 40 are formed from the housing raw material 20a and the ring-shaped raw material 40a respectively, both of which are cut out from the integral raw material 60, the housing body 20 and the ring member 40 are composed of the same forming material.
  • the housing body 20 and the ring member 40 have the same linear thermal expansion coefficients, accordingly, even if temperature change causes heat expansion or heat contraction in the housing body 20 and/or the ring member 40, reduction of the press-contact force at a position where the radial-direction outside surface 42 of the ring member 40 and the recess press-contact surface 212 of the inner circumferential recess 21 come into press-contact with each other, can be prevented.
  • the press-fitted state of the ring member 40 in relation to the inner circumferential recess 21 of the housing body 20 can be maintained.
  • reduction of the holdability for the abradable seal 30, of the inner circumferential recess 21 of the housing body 20 can be prevented even if any temperature change occurs.
  • the ring-shaped raw material 40a is formed in the step S1 of forming an integral raw material, as a single body with the housing raw material 20a along a place in which the ring member 40 is to be press-fitted.
  • the molding cost can be reduced.
  • the casting cost can be reduced in the case of casting a single body compared to the case of casting both raw materials separately. Consequently, the manufacturing cost can be reduced.
  • the ring-shaped raw material 40a was formed in the housing raw material 20a at the opposite side to the intake port 11 along a place 40b in which the ring member 40 is to be press-fitted.
  • the following configuration can also be adopted.
  • the ring-shaped raw material 40a may be formed in the housing raw material 20a along an end portion 11a of the intake port 11 so as to protrude toward the opposite side to the side on which the ring member is to be press-fitted, as a single body with the housing raw material 20a.
  • the molding cost and the casting cost can be reduced, thereby exhibiting the operational effects of reducing the manufacturing cost.
  • the integral raw material 60 is formed by gravity casting in the step S1 of forming an integral raw material.
  • the forming method is not limited to this.
  • the integral raw material 60 may be formed by a die-casting method or other conventional methods. When the die-casting method is adopted, the integral raw material 60 is divided into plural pieces as appropriate to eliminate any undercut.
  • the compressor housing 1 for a turbocharger which makes it possible to prevent reduction of the compression efficiency and to maintain holdability for the abradable seal, and which is advantageous in terms of cost, and the method of manufacturing the same.
EP16755427.8A 2015-02-25 2016-02-22 Kompressorgehäuse für einen turbolader und herstellungsverfahren dafür Withdrawn EP3263911A4 (de)

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JP2015034671 2015-02-25
PCT/JP2016/055111 WO2016136681A1 (ja) 2015-02-25 2016-02-22 過給機用のコンプレッサハウジング及びその製造方法

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WO2020001752A1 (en) * 2018-06-26 2020-01-02 Volvo Truck Corporation A compressor device for an internal combustion engine

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WO2016151747A1 (ja) * 2015-03-24 2016-09-29 三菱重工業株式会社 インペラカバー、回転機械、及びインペラカバーの製造方法
JP6589217B2 (ja) * 2015-04-17 2019-10-16 三菱重工コンプレッサ株式会社 回転機械、回転機械の製造方法
DE102017127628A1 (de) * 2017-11-22 2019-05-23 Man Energy Solutions Se Turbine und Turbolader

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JP3294491B2 (ja) * 1995-12-20 2002-06-24 株式会社日立製作所 内燃機関の過給機
JP3639846B2 (ja) * 1997-04-22 2005-04-20 株式会社協立 滑り部材付きターボチャージャ
JP3858347B2 (ja) * 1997-05-30 2006-12-13 石川島播磨重工業株式会社 ターボチャージャ
JP2011052558A (ja) * 2009-08-31 2011-03-17 Toyota Motor Corp 過給機
JP5471650B2 (ja) * 2009-11-05 2014-04-16 トヨタ自動車株式会社 過給機のコンプレッサハウジング
JP2011153570A (ja) * 2010-01-27 2011-08-11 Toyota Motor Corp 過給機のアブレーダブルシール固定構造
JP5402682B2 (ja) * 2010-01-29 2014-01-29 株式会社Ｉｈｉ ターボチャージャのシール装置
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JP2013124564A (ja) * 2011-12-13 2013-06-24 Otics Corp 過給機用のコンプレッサハウジング
JP5905736B2 (ja) * 2012-02-22 2016-04-20 トヨタ自動車株式会社 排気タービン過給機の製造方法及び排気タービン過給機
JP2014088785A (ja) * 2012-10-29 2014-05-15 Otics Corp 過給機用のコンプレッサハウジング

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020001752A1 (en) * 2018-06-26 2020-01-02 Volvo Truck Corporation A compressor device for an internal combustion engine

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JPWO2016136681A1 (ja) 2017-11-30
EP3263911A4 (de) 2018-02-21
CN107208657A (zh) 2017-09-26
US20170350408A1 (en) 2017-12-07
WO2016136681A1 (ja) 2016-09-01

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