US20110091323A1 - Compressor housing for turbocharger - Google Patents
Compressor housing for turbocharger Download PDFInfo
- Publication number
- US20110091323A1 US20110091323A1 US12/999,931 US99993108A US2011091323A1 US 20110091323 A1 US20110091323 A1 US 20110091323A1 US 99993108 A US99993108 A US 99993108A US 2011091323 A1 US2011091323 A1 US 2011091323A1
- Authority
- US
- United States
- Prior art keywords
- compressor
- compressor housing
- annular groove
- turbocharger
- impeller
- 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
Links
- 238000002485 combustion reaction Methods 0.000 claims description 11
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- 239000000446 fuel Substances 0.000 claims description 5
- 239000000203 mixture Substances 0.000 claims description 5
- 230000002159 abnormal effect Effects 0.000 description 31
- 238000010586 diagram Methods 0.000 description 25
- 238000005259 measurement Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000011056 performance test Methods 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 2
- 239000012634 fragment Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000002542 deteriorative effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000003252 repetitive effect Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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 55 a , and a seal plate 55 b.
- the bearing housing 53 , the turbine housing 54 , the compressor housing 55 a , and the seal plate 55 b 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 51 a with a rotor shaft 51 b 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 51 a 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 51 b 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 compressor constituting the turbocharger.
- 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 compressor housing provided with the circulation passage is disclosed in, for example, Patent Documents 1 and 2.
- 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.
- an object is to retain breakage fragments of a compressor wheel (impeller) inside a diffuser flange by expectedly destructing the diffuser flange when the wheel is broken, to prevent serious accidents caused by the breakage fragments.
- 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.
- Patent Document 1
- Patent Document 2
- 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 (high-frequency 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.
- 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.
- FIG. 1 is an overall configuration diagram showing an example of a conventional turbocharger.
- FIG. 3 is a schematic diagram showing ‘Turbocharger Provided With Sliding Member’ disclosed in Japanese published unexamined application No.11-173153.
- FIG. 4 is a schematic diagram showing an apparatus disclosed in Japanese published unexamined application No.11-190297.
- FIG. 5 is an overall configuration diagram showing a turbocharger having a compressor housing according to the invention.
- FIG. 6 is a sectional diagram showing the compressor housing in FIG. 5 .
- FIG. 9B is a test result of the conventional compressor housing, where a turbo rpm is 160,000 rpm and a flow rate is 5 m 3 /min.
- FIG. 9C is a test result of the conventional compressor housing, where a turbo rpm is 160,000 rpm and a flow rate is 4.3 m 3 /min.
- FIG. 10B is a test result of the compressor housing according to the invention, where a turbo rpm is 160,000 rpm and a flow rate is 5 m 3 /min.
- FIG. 10C is a test result of the compressor housing according to the invention, where a turbo rpm is 160,000 rpm and a flow rate is 4.3 m3/min.
- FIG. 11A is a diagram showing an original compressor housing.
- FIG. 11B is a diagram showing a second compressor housing according to a second embodiment of the invention.
- FIG. 11C is a diagram showing a third compressor housing according to the second embodiment of the invention.
- 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 2 a and short blades 2 b alternately arranged in a circumferential direction.
- a compressor housing 10 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 2 b 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 2 b 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 2 b.
- 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. 7 in which a flow state of a compressed fluid is schematically illustrated, peeling which is generated in the vicinity of an inlet or a tip of the long blade becomes large to thereby contact with the short blade at a position indicated by a dashed line in the drawing.
- an abnormal noise frequency does not depend on a first rotation
- an abnormal noise start point is identical with a pre-surge point (a pressure variation start point of the inlet)
- the abnormal noise is continuously generated in an unstable region of the compressor (a pressure characteristic in which a pressure increases rightward)
- the compressor housing is vibrated.
- 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 and
- FIG. 8B shows the conventional compressor housing provided with a circulation passage.
- the compressor housing 10 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.
- annular groove 12 In this example, 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 2 b in an axial direction on the upstream side thereof, an axial groove width b of the annular groove 12 is 2.5 mm, and 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 , 9 B, and 9 C are test results of the conventional compressor housing.
- FIGS. 9A , 9 B, and 9 C 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.
- FIGS. 10A , 10 B, and 10 C are test results of the compressor housing according to the invention.
- FIGS. 10A , 10 B, and 10 C 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 d 1 and d 2 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 2 b , an axial groove width b 1 of the annular groove 12 is 3.5 mm, and an outer diameter d 3 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.
- the third compressor housing shown in FIG. 11C is configured in such a manner that an annular cavity having an inner diameter (d 4 ) of 75 mm, an outer diameter (d 5 ) of 90 mm, and a length (b 2 ) 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 .
- 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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Supercharger (AREA)
Abstract
A compressor impeller 2 has a plurality of long blades 2 a and short blades 2 b alternately arranged in a circumferential direction, and an inner surface of a compressor housing 10 is provided with an annular groove 12 which surrounds vicinities of leading edge tip portions of the short blades 2 b in a circumferential direction and is concave outward so as not to communicate with a suction port of a compressor.
Description
- 1. Field of the Invention
- The present invention relates to a compressor housing for a turbocharger capable of reducing abnormal noise (high-frequency noise).
- 2. Description of the Related Art
- 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. In addition, 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. In the drawing, the turbocharger includes aturbine rotor shaft 51, acompressor impeller 52, abearing housing 53, aturbine housing 54, acompressor housing 55 a, and aseal plate 55 b. - The
bearing housing 53, the turbine housing 54, the compressor housing 55 a, and theseal plate 55 b are connected to each other in an order shown in the drawing. In addition, theturbine rotor shaft 51 is configured by integrally forming aturbine impeller 51 a with arotor shaft 51 b by welding, and is rotationally supported by thebearing housing 53 so as to be coaxially connected to thecompressor impeller 52. - With such a configuration, the
turbine impeller 51 a is rotationally driven using the exhaust gas of the internal combustion engine, and the rotation force is transmitted to thecompressor impeller 52 via therotor shaft 51 b 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. As shown in the drawing, in a general compressor, as the rpm N becomes high, a pressure ratio becomes high and a flow rate becomes large. In the drawing, the one-point dashed line indicates a surge line. When the flow rate arrives at the surge line at the same rpm, a surge is generated in a blade surface of the compressor impeller. As a result, the compressor hardly performs a compression operation and violent surge noise (intermittence noise) is observed. - Accordingly, as shown in the drawing, an operation line of the engine having the turbocharger is set so as to be sufficiently away from the surge line.
- In addition, in the past, as means for shifting the surge line to a side of a small flow rate, there is a conventional compressor housing provided with a circulation passage for increasing an intake air amount in appearance, the circulation passage being used to communicate a suction port of the compressor with a part in the course of a compression passage of the compressor.
- The compressor housing provided with the circulation passage is disclosed in, for example,
Patent Documents - In ‘Turbocharger Provided With Sliding Member’ disclosed in
Patent Document 1, an object is to obtain high compression efficiency without deteriorating durability in a turbocharger configured to prevent surging, choking, etc. - As shown in
FIG. 3 , the turbocharger provided with the sliding member includes anew air passage 63 which guides fresh air to a compressor impeller in a compressor housing; a first air intake andexhaust port 68 which is formed on a part of a compressor housing wall facing to the compressor impeller; a second air intake andexhaust port 69 which faces the more upstream fresh air passage than the compressor impeller; and abypass passage 60 which communicates the first and second air intake and exhaust ports with each other, wherein a slidingmember 65 is attached to at least a part of the compressor housing wall facing the blade edge of the compressor impeller. - In ‘Inside of Compressor and Turbine and Related Improvement’ disclosed in
Patent Document 2, an object is to retain breakage fragments of a compressor wheel (impeller) inside a diffuser flange by expectedly destructing the diffuser flange when the wheel is broken, to prevent serious accidents caused by the breakage fragments. - As shown in
FIG. 4 , acentrifugal compressor 71 includes acompressor housing 73 and acompressor wheel 74 mounted in the housing and having a compressor blade 75. Thecompressor housing 73 includes acover plate 76 and adiffuser flange 79 fixed to both thecover plate 76 and a bearing housing. Thediffuser flange 79 includes an outer edge portion attached to a cover member and a radial inside portion attached to the bearing housing. In the diffuser, 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. -
Patent Document 1 - Japanese published unexamined application No.11-173153, ‘Turbocharger Provided With Sliding Member’
-
Patent Document 2 - Japanese published unexamined application No.11-190297, ‘Inside of Compressor and Turbine and Related Improvement’
- In the above-described performance characteristic diagram, the dashed line indicates a pre-surge line, and when a flow rate becomes smaller than the pre-surge line at the same rpm, 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. However, since 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.
- When the flow rate becomes small at the same rpm, the abnormal noise (high-frequency 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.
- In the past, since a generation cause of the abnormal noise (high-frequency noise) is not clear, in general, a sound isolator has been used in order to isolate the noise generated from the turbocharger, but a problem arises in that it takes a cost to perform the sound isolation.
- The abnormal noise (high-frequency 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.
- The present invention is contrived to solve the above-described problems. That is, 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.
- According to an aspect of the invention, there is provided 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, wherein the compressor impeller has a plurality of long blades and short blades alternately arranged in a circumferential direction, and wherein 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.
- According to a preferred embodiment of the invention, 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.
- That is, according to the above-described configuration of the invention, since 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.
- In addition, the silencing advantage is shown in the embodiments described below.
-
FIG. 1 is an overall configuration diagram showing an example of a conventional turbocharger. -
FIG. 2 is a performance characteristic diagram of a compressor constituting the turbocharger. -
FIG. 3 is a schematic diagram showing ‘Turbocharger Provided With Sliding Member’ disclosed in Japanese published unexamined application No.11-173153. -
FIG. 4 is a schematic diagram showing an apparatus disclosed in Japanese published unexamined application No.11-190297. -
FIG. 5 is an overall configuration diagram showing a turbocharger having a compressor housing according to the invention. -
FIG. 6 is a sectional diagram showing the compressor housing inFIG. 5 . -
FIG. 7 is a perspective diagram showing a compressor impeller. -
FIG. 8A is a diagram showing the compressor housing according to a first embodiment of the invention. -
FIG. 8B is a diagram showing the conventional compressor housing provided with a circulation passage. -
FIG. 9A is a test result of the conventional compressor housing, where a turbo rpm is 160,000 rpm and a flow rate is 6 m3/min. -
FIG. 9B is a test result of the conventional compressor housing, where a turbo rpm is 160,000 rpm and a flow rate is 5 m3/min. -
FIG. 9C is a test result of the conventional compressor housing, where a turbo rpm is 160,000 rpm and a flow rate is 4.3 m3/min. -
FIG. 10A is a test result of the compressor housing according to the invention, where a turbo rpm is 160,000 rpm and a flow rate is 6 m3/min. -
FIG. 10B is a test result of the compressor housing according to the invention, where a turbo rpm is 160,000 rpm and a flow rate is 5 m3/min. -
FIG. 10C is a test result of the compressor housing according to the invention, where a turbo rpm is 160,000 rpm and a flow rate is 4.3 m3/min. -
FIG. 11A is a diagram showing an original compressor housing. -
FIG. 11B is a diagram showing a second compressor housing according to a second embodiment of the invention. -
FIG. 11C is a diagram showing a third compressor housing according to the second embodiment of the invention. - Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. In the respective drawings, the same reference numerals are given to the same components, and the repetitive description will be omitted.
-
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 acompressor impeller 2 to rotationally drive thecompressor 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 inFIG. 5 , andFIG. 7 is a perspective diagram showing thecompressor impeller 2. - As shown in
FIG. 7 , in this invention, thecompressor impeller 2 includes a plurality oflong blades 2 a andshort blades 2 b alternately arranged in a circumferential direction. - As shown in
FIG. 6 , acompressor housing 10 according to the invention has an inner surface in which anannular groove 12 is formed. Theannular groove 12 surrounds vicinities of the leading edge tip portions of theshort blades 2 b of thecompressor 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 theshort blades 2 b in an axial direction on an upstream or downstream side thereof. An axial groove width b of theannular groove 12 is no less than 2.5 mm and no more than 10 mm. A maximum diameter d of theannular groove 12 is desirably less than 1.2 times a diameter of each leading edge tip portion of theshort blades 2 b. - In this example, the
annular groove 12 extends outward from the inner surface of thecompressor 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. - In the turbocharger mounted to an engine for an automobile, 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. 7 in which a flow state of a compressed fluid is schematically illustrated, peeling which is generated in the vicinity of an inlet or a tip of the long blade becomes large to thereby contact with the short blade at a position indicated by a dashed line in the drawing. - The reason is because an abnormal noise frequency does not depend on a first rotation, an abnormal noise start point is identical with a pre-surge point (a pressure variation start point of the inlet), the abnormal noise is continuously generated in an unstable region of the compressor (a pressure characteristic in which a pressure increases rightward), and the compressor housing is vibrated.
- In addition, 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.
- On the basis of the above-described new viewpoints, 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 andFIG. 8B shows the conventional compressor housing provided with a circulation passage. - The
compressor housing 10 according to the invention is configured by additionally forming theannular groove 12 in an inner surface of the compressor housing of the turbocharger in which the abnormal noise (high-frequency noise) was observed. - In this example, an axial center of the
annular groove 12 is located at a position shifted by 4 mm from the leading edge tip portions of theshort blades 2 b in an axial direction on the upstream side thereof, an axial groove width b of theannular groove 12 is 2.5 mm, and a depth c of theannular groove 12 is 4 mm. In addition, in this example, theannular groove 12 extends outward from the inner surface of thecompressor housing 10 so as to be perpendicular with respect to the rotary shaft of the compressor. - Meanwhile, 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 m3/min in order of the diagrams. In each ofFIGS. 9A , 9B, and 9C, the left side indicates a noise measurement value and the right side indicates a pressure variation measurement value. - In these diagrams, at positions when a turbo rpm is 160,000 rpm, a flow rate is about 6 m3/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 m3/min in order of the diagrams. In each ofFIGS. 10A , 10B, and 10C the left side indicates a noise measurement value and the right side indicates a pressure variation measurement value. - In these diagrams, at positions when a turbo rpm is 160,000 rpm, a flow rate is about 6 m3/min, and a frequency is about 2.3 kHz, peaks are hardly generated in the noise and the pressure variation, which shows that the above-described abnormal noise (high-frequency noise) is hardly generated.
- Table 1 shows a measurement result of an abnormal noise output at an abnormal noise start point in this embodiment.
- In this Table, 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’, and a reference comparative example corresponds to ‘With Circulation Passage’ as another countermeasure for abnormal noise.
-
TABLE 1 ABNORMAL NOISE START POINT IN CASE OF NOISE COUNTERMEASURE NOISE REVOLUTION Nt FLOW RATE Q PRESSURE ABNORMAL NOISE MEASURE TYPE (rpm) (m3/min) RATIO π OUTPUT (V) FREQUENCY (kHz) WITH ANNULAR 160,000 (2.67 kHz) (6.015) (2.627) (0.0153) (2.21) GROOVE 180,000 (3.00 kHz) 7.526 3.190 0.1856 2.39 WITH 160,000 (2.67 kHz) — — — — CIRCULATION 180,000 (3.00 kHz) — — — — PASSAGE ORIGINAL 160,000 (2.67 kHz) 6.177 2.597 0.3706 2.15 (NO MEASURE) 180,000 (3.00 kHz) 7.503 3.099 0.5468 2.26 WITH ANNULAR GROOVE: NO ABNORMAL NOISE IS OBSERVED AT 160,000 rpm. VALUES IN PARENTHESES ARE REFERENCE VALES OF PRE-SURGE POINT - In this Table, at both turbo rpm of 160,000 rpm and 180,000 rpm, it is observed that an abnormal noise output is more reduced than that of ‘Original’.
- In addition, in ‘With Circulation Passage’ as a reference comparative example, it is possible to obtain the same advantage, but the compressor housing provided with the circulation passage has a problem that a structure is complex and a manufacture cost is more expensive than that of the compressor housing without the circulation passage. Accordingly, it is not possible to obtain the object of the invention.
-
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, andFIG. 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 theannular groove 12 is additionally formed in the inner surface of the original compressor housing shown inFIG. 11A . - In this example, an axial center of the
annular groove 12 is identical with that of each leading edge tip portion of theshort blades 2 b, an axial groove width b1 of theannular groove 12 is 3.5 mm, and an outer diameter d3 of theannular groove 12 is 80 mm. In addition, in this example, theannular groove 12 extends outward upstream from the inner surface of thecompressor housing 10 so as to be inclined at 60 degree with respect to the rotary shaft of the compressor. - The third compressor housing shown in
FIG. 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 theannular groove 12 of the second compressor housing shown inFIG. 11B . - As a test result of the turbocharger having the compressor housings shown in
FIGS. 11A , 11B, and 11C, at a pressure ratio of 2.4, a surge flow rate can be reduced from about 8.4 m3/min of the original compressor housing shown inFIG. 11A to about 7.7 m3/min in the case ofFIG. 11B and about 7.6 m3/min in the case ofFIG. 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. - As described above, according to the configuration of the invention, since the inner surface of the
compressor housing 10 is provided with theannular 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 theannular 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. - The invention is not limited to the preferred embodiments, but may be, of course, modified into various forms without departing from the spirit and the scope of the invention.
Claims (3)
1. 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,
wherein the compressor impeller has a plurality of long blades and short blades alternately arranged in a circumferential direction, and
wherein 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.
2. The compressor housing for the turbocharger according to claim 1 ,
wherein 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.
3. The compressor housing for the turbocharger according to claim 1 ,
wherein 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.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2008/061012 WO2009153854A1 (en) | 2008-06-17 | 2008-06-17 | Compressor housing for turbo charger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110091323A1 true US20110091323A1 (en) | 2011-04-21 |
Family
ID=41433785
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/999,931 Abandoned US20110091323A1 (en) | 2008-06-17 | 2008-06-17 | Compressor housing for turbocharger |
Country Status (5)
Country | Link |
---|---|
US (1) | US20110091323A1 (en) |
EP (1) | EP2290205A1 (en) |
KR (1) | KR20100119565A (en) |
CN (1) | CN102066717A (en) |
WO (1) | WO2009153854A1 (en) |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100232959A1 (en) * | 2006-06-21 | 2010-09-16 | Nobuo Takei | Bearing structure of rotating machine, rotating machine, method of manufacturing bearing structure, and method of manufacturing rotating machine |
WO2013162896A1 (en) * | 2012-04-23 | 2013-10-31 | Borgwarner Inc. | Turbocharger shroud with cross-wise grooves and turbocharger incorporating the same |
WO2013162874A1 (en) * | 2012-04-23 | 2013-10-31 | Borgwarner Inc. | Turbocharger blade with contour edge relief and turbocharger incorporating the same |
WO2014004238A1 (en) * | 2012-06-25 | 2014-01-03 | Borgwarner Inc. | Exhaust-gas turbocharger |
WO2014018270A1 (en) * | 2012-07-26 | 2014-01-30 | Borgwarner Inc. | Compressor cover with circumferential groove |
CN104040185A (en) * | 2012-01-23 | 2014-09-10 | 株式会社Ihi | Centrifugal compressor |
US20150118061A1 (en) * | 2013-10-31 | 2015-04-30 | André Hildebrandt | Radial Compressor |
US20160138608A1 (en) * | 2013-08-06 | 2016-05-19 | Ihi Corporation | Centrifugal compressor and turbocharger |
US20170198713A1 (en) * | 2015-02-18 | 2017-07-13 | Ihi Corporation | Centrifugal compressor and turbocharger |
US20180010464A1 (en) * | 2015-03-26 | 2018-01-11 | Mitsubishi Heavy Industries, Ltd. | Turbine impeller and variable geometry turbine |
US9896937B2 (en) | 2012-04-23 | 2018-02-20 | Borgwarner Inc. | Turbine hub with surface discontinuity and turbocharger incorporating the same |
US10132331B2 (en) | 2013-12-17 | 2018-11-20 | Man Energy Solutions Se | Radial compressor stage |
US20190055953A1 (en) * | 2016-03-03 | 2019-02-21 | Ihi Corporation | Rotary machine |
US11193494B2 (en) * | 2019-04-23 | 2021-12-07 | Hyundai Motor Company | Compressor wheel for turbocharger |
US11555507B2 (en) * | 2018-12-19 | 2023-01-17 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Turbocompressor with adapted meridian contour of the blades and compressor wall |
US12000410B2 (en) * | 2022-05-27 | 2024-06-04 | Toyota Motor Engineering & Manufacturing North America, Inc. | Shroud for an air moving device |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011153021A2 (en) * | 2010-06-04 | 2011-12-08 | Borgwarner Inc. | Compressor of an exhaust-gas turbocharger |
KR20150114384A (en) * | 2014-04-01 | 2015-10-12 | (주)계양정밀 | Turbocharger with device reducing nvh |
KR20190075514A (en) | 2017-12-21 | 2019-07-01 | 주식회사 포스코 | Apparatus for front-end bending control of rolling plate and control method using the same |
JP7047468B2 (en) * | 2018-03-05 | 2022-04-05 | いすゞ自動車株式会社 | Turbo turbocharger, turbocharger system and turbocharger system supercharging method |
US20210062823A1 (en) * | 2019-09-03 | 2021-03-04 | Garrett Transportation I Inc. | Compressor with ported shroud for flow recirculation and with noise attenuator for blade passing frequency noise attenuation, and turbocharger incorporating same |
KR20210056086A (en) | 2019-11-08 | 2021-05-18 | 현대위아 주식회사 | Turbo charger for vehicle |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4212585A (en) * | 1978-01-20 | 1980-07-15 | Northern Research And Engineering Corporation | Centrifugal compressor |
US4930978A (en) * | 1988-07-01 | 1990-06-05 | Household Manufacturing, Inc. | Compressor stage with multiple vented inducer shroud |
US5466118A (en) * | 1993-03-04 | 1995-11-14 | Abb Management Ltd. | Centrifugal compressor with a flow-stabilizing casing |
US20020164245A1 (en) * | 2001-04-05 | 2002-11-07 | Tomoyoshi Okamura | Pump |
US6619909B2 (en) * | 1998-12-10 | 2003-09-16 | United Technologies Corporation | Casing treatment for a fluid compressor |
US20070269308A1 (en) * | 2006-05-22 | 2007-11-22 | Wood Terry G | Engine intake air compressor having multiple inlets and method |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB9721434D0 (en) | 1997-10-10 | 1997-12-10 | Holset Engineering Co | Improvements in or relating to compressors and turbines |
JP4028923B2 (en) | 1997-12-10 | 2008-01-09 | 株式会社協立 | Turbocharger with sliding member |
JP2000064848A (en) * | 1998-08-21 | 2000-02-29 | Ishikawajima Harima Heavy Ind Co Ltd | Turbo-charger |
JP2003343486A (en) * | 2002-05-28 | 2003-12-03 | Ishikawajima Harima Heavy Ind Co Ltd | Centrifugal compressor equipped with long-and-short impeller |
JP4321037B2 (en) * | 2002-10-25 | 2009-08-26 | 株式会社豊田中央研究所 | Centrifugal compressor for turbocharger |
-
2008
- 2008-06-17 EP EP08777250A patent/EP2290205A1/en not_active Withdrawn
- 2008-06-17 KR KR1020107020044A patent/KR20100119565A/en not_active Application Discontinuation
- 2008-06-17 WO PCT/JP2008/061012 patent/WO2009153854A1/en active Application Filing
- 2008-06-17 CN CN2008801299776A patent/CN102066717A/en active Pending
- 2008-06-17 US US12/999,931 patent/US20110091323A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4212585A (en) * | 1978-01-20 | 1980-07-15 | Northern Research And Engineering Corporation | Centrifugal compressor |
US4930978A (en) * | 1988-07-01 | 1990-06-05 | Household Manufacturing, Inc. | Compressor stage with multiple vented inducer shroud |
US5466118A (en) * | 1993-03-04 | 1995-11-14 | Abb Management Ltd. | Centrifugal compressor with a flow-stabilizing casing |
US6619909B2 (en) * | 1998-12-10 | 2003-09-16 | United Technologies Corporation | Casing treatment for a fluid compressor |
US20020164245A1 (en) * | 2001-04-05 | 2002-11-07 | Tomoyoshi Okamura | Pump |
US20070269308A1 (en) * | 2006-05-22 | 2007-11-22 | Wood Terry G | Engine intake air compressor having multiple inlets and method |
Non-Patent Citations (1)
Title |
---|
Translation of JP 2003-343486 provided by Patent Utility Model & Gazette * |
Cited By (34)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8535022B2 (en) * | 2006-06-21 | 2013-09-17 | Ihi Corporation | Bearing structure of rotating machine, rotating machine, method of manufacturing bearing structure, and method of manufacturing rotating machine |
US20100232959A1 (en) * | 2006-06-21 | 2010-09-16 | Nobuo Takei | Bearing structure of rotating machine, rotating machine, method of manufacturing bearing structure, and method of manufacturing rotating machine |
EP2808555A1 (en) * | 2012-01-23 | 2014-12-03 | IHI Corporation | Centrifugal compressor |
US9897110B2 (en) * | 2012-01-23 | 2018-02-20 | Ihi Corporation | Centrifugal compressor |
EP2808555A4 (en) * | 2012-01-23 | 2015-09-02 | Ihi Corp | Centrifugal compressor |
US20140377053A1 (en) * | 2012-01-23 | 2014-12-25 | Ihi Corporation | Centrifugal compressor |
CN104040185A (en) * | 2012-01-23 | 2014-09-10 | 株式会社Ihi | Centrifugal compressor |
WO2013162874A1 (en) * | 2012-04-23 | 2013-10-31 | Borgwarner Inc. | Turbocharger blade with contour edge relief and turbocharger incorporating the same |
CN104204444A (en) * | 2012-04-23 | 2014-12-10 | 博格华纳公司 | Turbocharger blade with contour edge relief and turbocharger incorporating the same |
CN104204453A (en) * | 2012-04-23 | 2014-12-10 | 博格华纳公司 | Turbocharger shroud with cross-wise grooves and turbocharger incorporating the same |
US9896937B2 (en) | 2012-04-23 | 2018-02-20 | Borgwarner Inc. | Turbine hub with surface discontinuity and turbocharger incorporating the same |
WO2013162896A1 (en) * | 2012-04-23 | 2013-10-31 | Borgwarner Inc. | Turbocharger shroud with cross-wise grooves and turbocharger incorporating the same |
US20150086395A1 (en) * | 2012-04-23 | 2015-03-26 | Borgwarner Inc. | Turbocharger blade with contour edge relief and turbocharger incorporating the same |
US9683442B2 (en) | 2012-04-23 | 2017-06-20 | Borgwarner Inc. | Turbocharger shroud with cross-wise grooves and turbocharger incorporating the same |
US10119411B2 (en) | 2012-06-25 | 2018-11-06 | Borgwarner Inc. | Exhaust-gas turbocharger |
WO2014004238A1 (en) * | 2012-06-25 | 2014-01-03 | Borgwarner Inc. | Exhaust-gas turbocharger |
US20150240834A1 (en) * | 2012-07-26 | 2015-08-27 | Borgwarner Inc. | Compressor cover with circumferential groove |
CN104395582A (en) * | 2012-07-26 | 2015-03-04 | 博格华纳公司 | Compressor cover with circumferential groove |
WO2014018270A1 (en) * | 2012-07-26 | 2014-01-30 | Borgwarner Inc. | Compressor cover with circumferential groove |
US9982685B2 (en) * | 2012-07-26 | 2018-05-29 | Borgwarner Inc. | Compressor cover with circumferential groove |
US20160138608A1 (en) * | 2013-08-06 | 2016-05-19 | Ihi Corporation | Centrifugal compressor and turbocharger |
US10138898B2 (en) * | 2013-08-06 | 2018-11-27 | Ihi Corporation | Centrifugal compressor and turbocharger |
US20150118061A1 (en) * | 2013-10-31 | 2015-04-30 | André Hildebrandt | Radial Compressor |
US9976566B2 (en) * | 2013-10-31 | 2018-05-22 | Man Diesel & Turbo Se | Radial compressor |
US10132331B2 (en) | 2013-12-17 | 2018-11-20 | Man Energy Solutions Se | Radial compressor stage |
US10364825B2 (en) * | 2015-02-18 | 2019-07-30 | Ihi Corporation | Centrifugal compressor and turbocharger |
US20170198713A1 (en) * | 2015-02-18 | 2017-07-13 | Ihi Corporation | Centrifugal compressor and turbocharger |
US20180010464A1 (en) * | 2015-03-26 | 2018-01-11 | Mitsubishi Heavy Industries, Ltd. | Turbine impeller and variable geometry turbine |
US10563515B2 (en) * | 2015-03-26 | 2020-02-18 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Turbine impeller and variable geometry turbine |
US20190055953A1 (en) * | 2016-03-03 | 2019-02-21 | Ihi Corporation | Rotary machine |
US10975878B2 (en) * | 2016-03-03 | 2021-04-13 | Ihi Corporation | Rotary machine |
US11555507B2 (en) * | 2018-12-19 | 2023-01-17 | Ebm-Papst Mulfingen Gmbh & Co. Kg | Turbocompressor with adapted meridian contour of the blades and compressor wall |
US11193494B2 (en) * | 2019-04-23 | 2021-12-07 | Hyundai Motor Company | Compressor wheel for turbocharger |
US12000410B2 (en) * | 2022-05-27 | 2024-06-04 | Toyota Motor Engineering & Manufacturing North America, Inc. | Shroud for an air moving device |
Also Published As
Publication number | Publication date |
---|---|
EP2290205A1 (en) | 2011-03-02 |
KR20100119565A (en) | 2010-11-09 |
CN102066717A (en) | 2011-05-18 |
WO2009153854A1 (en) | 2009-12-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20110091323A1 (en) | Compressor housing for turbocharger | |
JP5351401B2 (en) | Compressor | |
US6540480B2 (en) | Compressor | |
US10669889B2 (en) | Heat shield for mixed flow turbine wheel turbochargers | |
US9816523B2 (en) | Centrifugal compressor | |
US10280836B2 (en) | Variable nozzle unit and variable geometry system turbocharger | |
CN108779708B (en) | Rotating mechanical blade, supercharger, and method for forming flow field of rotating mechanical blade and supercharger | |
US8388312B2 (en) | Compressor for an exhaust gas turbocharger | |
JP2017519154A (en) | Diffuser for centrifugal compressor | |
JPH10176699A (en) | Centrifugal compressor | |
JP2004027931A (en) | Centrifugal compressor | |
US6932563B2 (en) | Apparatus, system and method for minimizing resonant forces in a compressor | |
JP2012002140A (en) | Turbine and supercharger | |
JP2004143995A (en) | Centrifugal multi-vane blower | |
JP2008240713A (en) | Compressor housing for turbocharger | |
JP2014234803A (en) | Variable displacement turbine and variable displacement supercharger | |
JP2014240612A (en) | Centrifugal compressor and supercharger | |
JP6947304B2 (en) | Turbines and turbochargers | |
JP5830991B2 (en) | Centrifugal compressor | |
JP2012087709A (en) | Turbocompressor | |
WO2019107488A1 (en) | Multi-stage centrifugal compressor, casing, and return vane | |
GB2074244A (en) | Air intake structure for a compressor | |
JP2004353607A (en) | Centrifugal compressor | |
KR20190074405A (en) | Apparatus for air intake duct of vehicle | |
KR20200124375A (en) | Compressor wheel for turbo chagrger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: IHI CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KOIKE, ATSUSHI;IIZUKA, KIYOKAZU;MATSUHASHI, FUMIE;AND OTHERS;REEL/FRAME:025520/0361 Effective date: 20100818 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |