EP2290205A1 - Boîtier de compresseur pour turbocompresseur - Google Patents

Boîtier de compresseur pour turbocompresseur Download PDF

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Publication number
EP2290205A1
EP2290205A1 EP08777250A EP08777250A EP2290205A1 EP 2290205 A1 EP2290205 A1 EP 2290205A1 EP 08777250 A EP08777250 A EP 08777250A EP 08777250 A EP08777250 A EP 08777250A EP 2290205 A1 EP2290205 A1 EP 2290205A1
Authority
EP
European Patent Office
Prior art keywords
compressor
compressor housing
annular groove
impeller
turbocharger
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Withdrawn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
EP08777250A
Other languages
German (de)
English (en)
Inventor
Atsushi Koike
Kiyokazu Iizuka
Fumie Matsuhashi
Takahiro Kobayashi
Nobuo Takei
Yukio Takahashi
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.)
IHI Corp
Original Assignee
IHI 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 IHI Corp filed Critical IHI Corp
Publication of EP2290205A1 publication Critical patent/EP2290205A1/fr
Withdrawn legal-status Critical Current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
    • F04D29/26—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
    • F04D29/26—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
    • F04D29/30—Vanes
    • 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
    • F04D29/40—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
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/40—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
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise
    • F05B2260/962—Preventing, counteracting or reducing vibration or noise by means creating "anti-noise"
    • 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
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise
    • F05D2260/963—Preventing, counteracting or reducing vibration or noise by Helmholtz resonators

Definitions

  • the present invention relates to a compressor housing for a turbocharger capable of reducing abnormal noise (high-frequency noise).
  • a supercharging operation means that air or air-fuel mixture supplied to a cylinder of an internal combustion engine is compressed in advance, and a compressor used for the supercharging operation is called a supercharger.
  • a supercharger for performing the supercharging operation using exhaust gas of the internal combustion engine is simply called an exhaust turbine supercharger or a turbocharger.
  • Fig. 1 is an overall configuration diagram showing an example of a conventional turbocharger.
  • the turbocharger includes a turbine rotor shaft 51, a compressor impeller 52, a bearing housing 53, a turbine housing 54, a compressor housing 55a, and a seal plate 55b.
  • the bearing housing 53, the turbine housing 54, the compressor housing 55a, and the seal plate 55b are connected to each other in an order shown in the drawing.
  • the turbine rotor shaft 51 is configured by integrally forming a turbine impeller 51a with a rotor shaft 51b by welding, and is rotationally supported by the bearing housing 53 so as to be coaxially connected to the compressor impeller 52.
  • the turbine impeller 51a is rotationally driven using the exhaust gas of the internal combustion engine, and the rotation force is transmitted to the compressor impeller 52 via the rotor shaft 51b to be rotationally driven so that air (or air-fuel mixture) is compressed and supplied to the internal combustion engine. Accordingly, it is possible to remarkably improve performance of the internal combustion engine.
  • Fig. 2 is a performance characteristic diagram showing an example of a compressor constituting the turbocharger.
  • a general compressor As the rpm N becomes high, a pressure ratio becomes high and a flow rate becomes large.
  • the one-point dashed line indicates a surge line.
  • the flow rate arrives at the surge line at the same rpm, a surge is generated in a blade surface of the compressor impeller.
  • the compressor hardly performs a compression operation and violent surge noise (intermittence noise) is observed.
  • an operation line of the engine having the turbocharger is set so as to be sufficiently away from the surge line.
  • the turbocharger provided with the sliding member includes a new air passage 63 which guides fresh air to a compressor impeller in a compressor housing; a first air intake and exhaust port 68 which is formed on a part of a compressor housing wall facing to the compressor impeller; a second air intake and exhaust port 69 which faces the more upstream fresh air passage than the compressor impeller; and a bypass passage 60 which communicates the first and second air intake and exhaust ports with each other, wherein a sliding member 65 is attached to at least a part of the compressor housing wall facing the blade edge of the compressor impeller.
  • a centrifugal compressor 71 includes a compressor housing 73 and a compressor wheel 74 mounted in the housing and having a compressor blade 75.
  • the compressor housing 73 includes a cover plate 76 and a diffuser flange 79 fixed to both the cover plate 76 and a bearing housing.
  • the diffuser flange 79 includes an outer edge portion attached to a cover member and a radial inside portion attached to the bearing housing.
  • a brittle groove portion is defined at a position halfway between the outer edge portion and the radial inside portion and thereby the expected breaking of the diffuser flange is made possible when the compressor wheel is broken.
  • the dashed line indicates a pre-surge line
  • the abnormal noise (high-frequency noise) may be generated.
  • the high-frequency noise may arrive at a sound pressure level of 90 dB or more, but does not deteriorate performance of the compressor.
  • the abnormal noise contributes to one of noise sources in an automobile requiring a silent state, it is necessary to prepare a countermeasure for the abnormal noise.
  • the abnormal noise is continuously generated up to the surge point.
  • the abnormal noise is not generated in a surge state, but instead surge noise (intermittence noise) is observed.
  • the abnormal noise can be reduced or removed by shifting the surge line to the side of the small flow rate by using the compressor housing provided with the above-described circulation passage, but in the compressor housing provided with the circulation passage, a problem arises in that a structure is complex and a manufacture cost is more expensive than that of the compressor housing without the circulation passage.
  • an object of the invention is to provide a compressor housing for a turbocharger capable of remarkably reducing or removing abnormal noise (high-frequency noise) generated from a pre-surge line to a surge line without a sound isolator or a circulation passage.
  • a compressor housing for a turbocharger for rotationally driving a turbine impeller using exhaust gas of an internal combustion engine and transmitting the rotation force to a compressor impeller to be rotationally driven so that air or air-fuel mixture is compressed and supplied to the internal combustion engine
  • the compressor impeller has a plurality of long blades and short blades alternately arranged in a circumferential direction
  • an inner surface of the compressor housing is provided with an annular groove which surrounds vicinities of leading edge tip portions of the short blades in a circumferential direction and is concave outward so as not to communicate with a suction port of a compressor.
  • an axial center of the annular groove is located within 5 mm from the leading edge tip portions of the short blades in an axial direction on an upstream or downstream side thereof, an axial groove width is no less than 2.5 mm and no more than 10 mm, and a maximum diameter of the annular groove is less than 1.2 times a diameter of each leading edge tip portion of the short blades.
  • the annular groove extends outward from the inner surface of the compressor housing so as to be perpendicular or inclined with respect to a rotary shaft of a compressor.
  • the inventors of the invention have independently examined and found out that the abnormal noise is generated by a rotating stall of the impeller and peeling becomes large to thereby contact with the short blade.
  • the invention is based on the above-described new viewpoints.
  • the inner surface of the compressor housing is provided with the annular groove which surrounds vicinities of the leading edge tip portions of the short blades in a circumferential direction and is concave outward so as not to communicate with the suction port of the compressor, a sectional area of a flow passage in the annular groove is suddenly enlarged. Accordingly, it is possible to silence the noise.
  • the silencing advantage is shown in the embodiments described below.
  • Fig. 5 is an overall configuration diagram showing a turbocharger having a compressor housing according to the invention.
  • the turbocharger rotationally drives a turbine impeller 1 by use of exhaust gas of an internal combustion engine, and a rotation force thereof is transmitted to a compressor impeller 2 to rotationally drive the compressor impeller 2 so that air or air-fuel mixture is compressed and supplied to the internal combustion engine.
  • Fig. 6 is an enlarged sectional diagram showing the compressor housing in Fig. 5
  • Fig. 7 is a perspective diagram showing the compressor impeller 2.
  • the compressor impeller 2 includes a plurality of long blades 2a and short blades 2b alternately arranged in a circumferential direction.
  • a compressor housing 10 according to the invention has an inner surface in which an annular groove 12 is formed. The annular groove 12 surrounds vicinities of the leading edge tip portions of the short blades 2b of the compressor impeller 2 and is concave outward so as not to communicate with a suction port of the compressor.
  • An axial center a of the annular groove 12 is located within 5 mm from the leading edge tip portions of the short blades 2b in an axial direction on an upstream or downstream side thereof.
  • An axial groove width b of the annular groove 12 is no less than 2.5 mm and no more than 10 mm.
  • a maximum diameter d of the annular groove 12 is desirably less than 1.2 times a diameter of each leading edge tip portion of the short blades 2b.
  • the annular groove 12 extends outward from the inner surface of the compressor housing 10 so as to be perpendicular with respect to a rotary shaft of the compressor, but may extend so as to be inclined thereto.
  • the above-described abnormal noise (high-frequency noise) was observed during an engine test. For this reason, a component performance test of a turbo unit was carried out. Even in this component performance test, the abnormal noise was observed at a turbo rpm of 160,000 rpm and 180,000 rpm, and the generation frequency was about 2.3 kHz equivalent to an engine.
  • the inventors of the invention have independently examined and found out that the abnormal noise is generated by a rotating stall of the impeller. That is, as shown in Fig.
  • the inventors of the invention have considered that a high abnormal noise generation frequency of 2.3 kHZ is generated by a characteristic of the impeller, that is, generated by the fact that the number of stall cells (the number of stall blades) is large.
  • the inventors of the invention have prepared two types of compressor housings for delaying a stall and have carried out the component performance test of the turbo unit.
  • Fig. 8A is a diagram showing the compressor housing according to a first embodiment of the invention.
  • Fig. 8A shows the compressor housing according to the invention
  • Fig. 8B shows the conventional compressor housing provided with a circulation passage.
  • the compressor housing 10 according to the invention is configured by additionally forming the annular groove 12 in an inner surface of the compressor housing of the turbocharger in which the abnormal noise (high-frequency noise) was observed.
  • an axial center of the annular groove 12 is located at a position shifted by 4 mm from the leading edge tip portions of the short blades 2b in an axial direction on the upstream side thereof
  • an axial groove width b of the annular groove 12 is 2.5 mm
  • a depth c of the annular groove 12 is 4 mm.
  • the annular groove 12 extends outward from the inner surface of the compressor housing 10 so as to be perpendicular with respect to the rotary shaft of the compressor.
  • a shape of the inner surface of the conventional compressor housing provided with the circulation passage is identical with that of the compressor housing of the turbocharger in which the abnormal noise (high-frequency noise) was observed, but its molding is newly manufactured.
  • the circulation passage of the compressor housing communicates a suction port of the compressor with the same position as the position of the compressor housing 10 of the present invention.
  • a groove width b' of the circulation passage is 2.5 mm and a groove width e of an outlet port is 6 mm.
  • Figs. 9A, 9B, and 9C are test results of the conventional compressor housing.
  • Figs. 9A, 9B, and 9C show cases where a turbo rpm is 160,000 rpm, and flow rates are about 6, 5, and 4.3 m 3 /min in order of the diagrams.
  • the left side indicates a noise measurement value and the right side indicates a pressure variation measurement value.
  • a flow rate is about 6 m 3 /min, and a frequency is about 2.3 kHz, large peaks are generated in the noise and the pressure variation, which corresponds to the above-described abnormal noise (high-frequency noise).
  • Figs. 10A, 10B, and 10C are test results of the compressor housing according to the invention.
  • Figs. 10A, 10B, and 10C show cases where a turbo rpm is 160,000 rpm, and flow rates are about 6, 5, and 4.3 m 3 /min in order of the diagrams.
  • the left side indicates a noise measurement value and the right side indicates a pressure variation measurement value.
  • Table 1 shows a measurement result of an abnormal noise output at an abnormal noise start point in this embodiment.
  • the conventional compressor housing without a countermeasure for abnormal noise corresponds to 'Original'
  • the compressor housing according to the invention corresponds to 'With Annular Groove'
  • a reference comparative example corresponds to 'With Circulation Passage' as another countermeasure for abnormal noise.
  • Figs. 11B and 11C are diagrams showing the compressor housing according to a second embodiment of the invention.
  • Fig. 11A shows an original compressor housing
  • Fig. 11B shows a second compressor housing according to the invention
  • Fig. 11C shows a third compressor housing according to the invention.
  • An original turbocharger is different from that of the first embodiment, and in these diagrams, diameters d1 and d2 are 62 mm and 82 mm, respectively.
  • the second compressor housing shown in Fig. 11B is configured in such a manner that the annular groove 12 is additionally formed in the inner surface of the original compressor housing shown in Fig. 11A .
  • annular groove 12 is identical with that of each leading edge tip portion of the short blades 2b, an axial groove width b1 of the annular groove 12 is 3.5 mm, and an outer diameter d3 of the annular groove 12 is 80 mm.
  • the annular groove 12 extends outward upstream from the inner surface of the compressor housing 10 so as to be inclined at 60 degree with respect to the rotary shaft of the compressor.
  • 11C is configured in such a manner that an annular cavity having an inner diameter (d4) of 75 mm, an outer diameter (d5) of 90 mm, and a length (b2) of 22.5 mm is formed in an outer side of the annular groove 12 of the second compressor housing shown in Fig. 11B .
  • a surge flow rate can be reduced from about 8.4 m 3 /min of the original compressor housing shown in Fig. 11A to about 7.7 m 3 /min in the case of Fig. 11B and about 7.6 m 3 /min in the case of Fig. 11C . Accordingly, as obviously shown in the results, it is possible to reduce a surge line by using the compressor housing according to the invention including those shown in Figs. 11B and 11C , and thus to reduce an abnormal noise output.
  • the inner surface of the compressor housing 10 is provided with the annular groove 12 which surrounds vicinities of the leading edge tip portions of the short blades in a circumferential direction and is concave outward so as not to communicate with the suction port of the compressor, a sectional area of the flow passage is suddenly enlarged by the annular groove 12.
  • the annular groove 12 As a result, it is possible to silence noise and to remarkably reduce or remove the abnormal noise (high-frequency noise) generated from a pre-surge line to a surge line without a sound isolator or a circulation passage.

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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)
EP08777250A 2008-06-17 2008-06-17 Boîtier de compresseur pour turbocompresseur Withdrawn EP2290205A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2008/061012 WO2009153854A1 (fr) 2008-06-17 2008-06-17 Boîtier de compresseur pour turbocompresseur

Publications (1)

Publication Number Publication Date
EP2290205A1 true EP2290205A1 (fr) 2011-03-02

Family

ID=41433785

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08777250A Withdrawn EP2290205A1 (fr) 2008-06-17 2008-06-17 Boîtier de compresseur pour turbocompresseur

Country Status (5)

Country Link
US (1) US20110091323A1 (fr)
EP (1) EP2290205A1 (fr)
KR (1) KR20100119565A (fr)
CN (1) CN102066717A (fr)
WO (1) WO2009153854A1 (fr)

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Also Published As

Publication number Publication date
KR20100119565A (ko) 2010-11-09
CN102066717A (zh) 2011-05-18
WO2009153854A1 (fr) 2009-12-23
US20110091323A1 (en) 2011-04-21

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