US20100143111A1 - Compressor stabilizer - Google Patents
Compressor stabilizer Download PDFInfo
- Publication number
- US20100143111A1 US20100143111A1 US12/630,530 US63053009A US2010143111A1 US 20100143111 A1 US20100143111 A1 US 20100143111A1 US 63053009 A US63053009 A US 63053009A US 2010143111 A1 US2010143111 A1 US 2010143111A1
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- US
- United States
- Prior art keywords
- compressor
- struts
- main flow
- flow duct
- circulation
- 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
- 239000003381 stabilizer Substances 0.000 title 1
- 238000011144 upstream manufacturing Methods 0.000 claims description 8
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 230000005284 excitation Effects 0.000 abstract description 10
- 238000009826 distribution Methods 0.000 abstract description 2
- 230000001788 irregular Effects 0.000 abstract 1
- 238000002485 combustion reaction Methods 0.000 description 11
- 239000007789 gas Substances 0.000 description 10
- 238000009828 non-uniform distribution Methods 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
Images
Classifications
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- 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
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- 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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
-
- 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
- F04D29/52—Casings; Connections of working fluid for axial 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
- F04D29/661—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
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- 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
- 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
Definitions
- the disclosure relates to the field of exhaust-gas-driven turbochargers, which, for example, include a compressor having a circulation chamber which is delimited from a main flow.
- exhaust-gas turbochargers having a turbine in the exhaust section of the internal combustion engine and having a compressor which is positioned upstream of the internal combustion engine.
- the exhaust gases of the internal combustion engine are expanded in the turbine.
- the work which is gained here is transmitted by a shaft to the compressor which compresses the air supplied to the internal combustion engine.
- DE 42 13 047 A1 discloses an exhaust-gas turbocharger, in the housing of which a compressor wheel rotates.
- the housing has an inlet duct into which is inserted an inner wall which firstly forms the main duct contour and secondly delimits an annular circulation chamber which surrounds the main duct.
- the interior space of the annular chamber is connected to the compressor inlet by an opening and, in the region of the compressor wheel, to the inlet duct by an annular slot in the contoured wall of the annular chamber.
- the contoured wall is held concentrically with respect to the housing by webs.
- the annular chamber which is provided in compressors of this type is a so-called characteristic-map-stabilizing measure.
- a recirculation of the flow from the compressor wheel back into the inlet duct upstream of the compressor wheel may take place, as a result of which the compressor wheel experiences an apparently higher throughput.
- the annular slot is utilized by the flow as an additional inlet. Recirculation therefore no longer takes place, which results in the desired displacement of the surge limit toward higher throughputs.
- EP0605184B1 discloses a compressor in which the generation of noise is supposed to be reduced by virtue of a multiplicity of ribs, which are offset relative to one another, being provided in the annular chamber or upstream of the annular chamber with respect to the flow direction of the air, which ribs deflect and partially reflect the sound, thereby reducing the noise.
- the attachment and arrangement of the ribs is however relatively complex and only partially successful, since the sound is nevertheless transmitted to the compressor housing and radiated into the environment.
- a compressor of an exhaust-gas turbocharger comprising: a rotatably mounted compressor wheel; a main flow duct for supplying a medium for compression to the compressor wheel; and a circulation chamber, arranged radially outside the main flow duct and delimited from the main flow duct by a contoured wall, which extends from an intake region of the main flow duct to a circulation opening formed into the contoured wall in a region of rotor blades of the compressor wheel, with the contoured wall being fastened to a housing of the compressor by struts in the circulation chamber, wherein a spacing between struts in at least one pair of struts arranged adjacent to one another in the circulation chamber is different in a circumferential direction than a spacing between struts arranged adjacent to one another in other pairs of struts.
- An exhaust-gas turbocharger having a compressor which comprises: a rotatably mounted compressor wheel; a main flow duct for supplying a medium for compression to the compressor wheel; and a circulation chamber, arranged radially outside the main flow duct and delimited from the main flow duct by a contoured wall, which extends from an intake region of the main flow duct to a circulation opening formed into the contoured wall in a region of rotor blades of the compressor wheel, with the contoured wall being fastened to a housing of the compressor by struts in the circulation chamber, wherein a spacing between struts in at least one pair of struts arranged adjacent to one another in the circulation chamber is different in a circumferential direction than a spacing between struts arranged adjacent to one another in other pairs of struts.
- FIG. 1 shows a sectional image of an exemplary exhaust-gas turbocharger having a compressor with a circulation chamber
- FIG. 2 shows a view of a section along the line II-II through the exemplary circulation chamber of the FIG. 1 compressor.
- Vibration-reducing measures are disclosed for a compressor having a circulation chamber which is delimited from the main flow.
- the struts which support a contoured wall are arranged spaced apart from one another to different extents in a circumferential direction.
- a uniform distribution of support ribs can lead to formation of exemplary excitation orders in the vibration excitation, with the excitation orders being directly dependent on the number of support ribs.
- the available excitation energy can be distributed between different excitation orders.
- the excitation per excitation order can therefore be reduced, and specific resonances can be targeted and avoided (e.g., suppressed).
- a non-uniform distribution of the support ribs can therefore lead to a reduced excitation of the rotor blade vibration.
- the non-uniform distribution of the support ribs can have an effect on distribution of the circumferential stiffness.
- the compressor housing which receives the flow of the radial compressor stage downstream of the diffuser and supplies the flow to the pipeline system can be configured as a spiral, and therefore need not be circumferentially symmetrical. This can lead to a non-uniform deformation in operation as a result of thermal loading of the housing.
- a non-uniform distribution of degrees of play between a rotating compressor and a stationary housing can be formed.
- the mean play can be increased, which can lead directly to efficiency losses.
- the inner housing which is close to the flow duct is also provided with a non-uniform stiffness over the circumference.
- a combination of the inner and outer housings can enable a reduction in play and provide an increase in efficiency.
- all of the pairs of struts arranged adjacent to one another can have a different spacing than the other pairs of struts arranged adjacent to one another.
- a circulation chamber which is configured according to the exemplary embodiments disclosed herein can be used in a compressor with a swirl-generating inlet guide wheel.
- the inlet guide wheel is arranged upstream of the intake region of the main flow duct with respect to the flow direction and, upstream of the compressor inlet, positively imparts a positive or negative flow component in the circumferential direction to the air which is supplied to the compressor.
- FIG. 1 An exemplary compressor of an exhaust-gas turbocharger is illustrated in FIG. 1 as including a compressor housing 10 and a compressor wheel 1 which is rotatably arranged in the housing on a shaft 3 .
- a turbine wheel 2 Connected to the shaft 3 is a turbine wheel 2 which is arranged in turbine housing 20 .
- the exhaust gases of the internal combustion engine are expanded in the turbine.
- the work gained is transmitted by means of the shaft to a compressor wheel which compresses the air supplied to the internal combustion engine.
- the compressor housing 10 surrounds an inflow duct 11 through which the air, as the medium for compression, is conducted to the compressor wheel.
- the arrows indicate air flows.
- An annular circulation chamber 13 is arranged in an interior of the compressor housing, which circulation chamber 13 radially surrounds the main flow duct and extends from the intake region 11 to an at least partially encircling circulation opening 12 in the region of the guide blades of the compressor wheel 1 .
- the circulation chamber 13 is open in the direction of the main flow duct via two openings.
- a radial inlet opening is arranged upstream of the compressor wheel, and a radial contoured groove, the circulation opening 12 , is arranged downstream of a leading edge of the compressor wheel and in a region of overlap with the inlet thereof.
- the circulation chamber 13 is delimited from the main flow duct by an annular contoured wall 15 .
- the contoured wall is connected to the inner compressor housing by means of a plurality of struts 14 .
- the struts which support the contoured wall can be spaced apart from one another to different extents in the circumferential direction, as illustrated in FIG. 2 .
- all of the pairs of struts arranged adjacent to one another have a different spacing than the other pairs of struts arranged adjacent to one another.
- the struts 14 which support the contoured wall may be configured with blade profiles or guide webs, of any desired shape, in order to impart a desired swirl to the flow in the circulation chamber.
- the struts 14 can all be aligned purely radially or can all be inclined to the same extent or different extents relative to the radial direction.
- the circulation opening 12 can be formed as an encircling annular gap or can be divided into a plurality of annular gap segments.
- the annular chamber can be divided into a plurality of segments in the circumferential direction.
- the segments can be of equal size or of different sizes.
Abstract
An annular circulation chamber is arranged in an interior of a compressor housing, which circulation chamber radially surrounds a main flow duct and extends from an intake region to an encircling circulation opening in a region of rotor blades of the compressor wheel. Between the circulation openings, the circulation chamber is delimited from the main flow duct by an annular contoured wall. The contoured wall is connected to the inner compressor housing by plural struts which are spaced apart from one another to different extents in the circumferential direction. As a result of the irregular distribution of the struts in the circumferential direction, generation of undesired vibration excitations can be reduced and/or eliminated.
Description
- This application claims priority under 35 U.S.C. §119 to European Patent Application No. 08170848.9 filed in Europe on Dec. 5, 2008, the entire content of which is hereby incorporated by reference in its entirety.
- The disclosure relates to the field of exhaust-gas-driven turbochargers, which, for example, include a compressor having a circulation chamber which is delimited from a main flow.
- To increase the power of an internal combustion engine, it is known to use exhaust-gas turbochargers having a turbine in the exhaust section of the internal combustion engine and having a compressor which is positioned upstream of the internal combustion engine. Here, the exhaust gases of the internal combustion engine are expanded in the turbine. The work which is gained here is transmitted by a shaft to the compressor which compresses the air supplied to the internal combustion engine. By using the energy of the exhaust gases to compress the air supplied to the combustion process in the internal combustion engine, it is possible to optimize the combustion process and the efficiency of the internal combustion engine.
- DE 42 13 047 A1 discloses an exhaust-gas turbocharger, in the housing of which a compressor wheel rotates. The housing has an inlet duct into which is inserted an inner wall which firstly forms the main duct contour and secondly delimits an annular circulation chamber which surrounds the main duct. The interior space of the annular chamber is connected to the compressor inlet by an opening and, in the region of the compressor wheel, to the inlet duct by an annular slot in the contoured wall of the annular chamber. The contoured wall is held concentrically with respect to the housing by webs.
- The annular chamber which is provided in compressors of this type is a so-called characteristic-map-stabilizing measure. Here, before the compressor surge limit is reached, a recirculation of the flow from the compressor wheel back into the inlet duct upstream of the compressor wheel may take place, as a result of which the compressor wheel experiences an apparently higher throughput. In the operating range close to the compressor choke limit, the annular slot is utilized by the flow as an additional inlet. Recirculation therefore no longer takes place, which results in the desired displacement of the surge limit toward higher throughputs.
- The desired expansion of the characteristic map of the compressor often comes at the expense not only of efficiency losses but also of the generation of inadmissible noise and vibrations. Such vibration excitations in the rotor blades may be attributed inter alia to the support ribs which serve to fasten the inner wall of the annular chamber to the housing.
- Various noise-reducing measures have been proposed. For example, EP0605184B1 discloses a compressor in which the generation of noise is supposed to be reduced by virtue of a multiplicity of ribs, which are offset relative to one another, being provided in the annular chamber or upstream of the annular chamber with respect to the flow direction of the air, which ribs deflect and partially reflect the sound, thereby reducing the noise. The attachment and arrangement of the ribs is however relatively complex and only partially successful, since the sound is nevertheless transmitted to the compressor housing and radiated into the environment.
- A compressor of an exhaust-gas turbocharger is disclosed, comprising: a rotatably mounted compressor wheel; a main flow duct for supplying a medium for compression to the compressor wheel; and a circulation chamber, arranged radially outside the main flow duct and delimited from the main flow duct by a contoured wall, which extends from an intake region of the main flow duct to a circulation opening formed into the contoured wall in a region of rotor blades of the compressor wheel, with the contoured wall being fastened to a housing of the compressor by struts in the circulation chamber, wherein a spacing between struts in at least one pair of struts arranged adjacent to one another in the circulation chamber is different in a circumferential direction than a spacing between struts arranged adjacent to one another in other pairs of struts.
- An exhaust-gas turbocharger is disclosed having a compressor which comprises: a rotatably mounted compressor wheel; a main flow duct for supplying a medium for compression to the compressor wheel; and a circulation chamber, arranged radially outside the main flow duct and delimited from the main flow duct by a contoured wall, which extends from an intake region of the main flow duct to a circulation opening formed into the contoured wall in a region of rotor blades of the compressor wheel, with the contoured wall being fastened to a housing of the compressor by struts in the circulation chamber, wherein a spacing between struts in at least one pair of struts arranged adjacent to one another in the circulation chamber is different in a circumferential direction than a spacing between struts arranged adjacent to one another in other pairs of struts.
- Exemplary embodiments of a compressor according to the disclosure are schematically illustrated and explained in more detail below on the basis of the figures. In all the figures, equivalent elements are provided with the same reference numerals. In the figures:
-
FIG. 1 shows a sectional image of an exemplary exhaust-gas turbocharger having a compressor with a circulation chamber; and -
FIG. 2 shows a view of a section along the line II-II through the exemplary circulation chamber of theFIG. 1 compressor. - Vibration-reducing measures are disclosed for a compressor having a circulation chamber which is delimited from the main flow.
- According to the exemplary embodiments, the struts which support a contoured wall are arranged spaced apart from one another to different extents in a circumferential direction.
- A uniform distribution of support ribs can lead to formation of exemplary excitation orders in the vibration excitation, with the excitation orders being directly dependent on the number of support ribs. With a non-uniform distribution, the available excitation energy can be distributed between different excitation orders. The excitation per excitation order can therefore be reduced, and specific resonances can be targeted and avoided (e.g., suppressed). A non-uniform distribution of the support ribs can therefore lead to a reduced excitation of the rotor blade vibration.
- The non-uniform distribution of the support ribs can have an effect on distribution of the circumferential stiffness. In general, the compressor housing which receives the flow of the radial compressor stage downstream of the diffuser and supplies the flow to the pipeline system can be configured as a spiral, and therefore need not be circumferentially symmetrical. This can lead to a non-uniform deformation in operation as a result of thermal loading of the housing. As a result, a non-uniform distribution of degrees of play between a rotating compressor and a stationary housing can be formed. To prevent the rotor blades of the compressor wheel from grinding against the housing parts, the mean play can be increased, which can lead directly to efficiency losses. With non-uniform distribution of the support ribs, the inner housing which is close to the flow duct is also provided with a non-uniform stiffness over the circumference. A combination of the inner and outer housings can enable a reduction in play and provide an increase in efficiency.
- Optionally, all of the pairs of struts arranged adjacent to one another can have a different spacing than the other pairs of struts arranged adjacent to one another.
- A circulation chamber which is configured according to the exemplary embodiments disclosed herein can be used in a compressor with a swirl-generating inlet guide wheel. Here, the inlet guide wheel is arranged upstream of the intake region of the main flow duct with respect to the flow direction and, upstream of the compressor inlet, positively imparts a positive or negative flow component in the circumferential direction to the air which is supplied to the compressor.
- An exemplary compressor of an exhaust-gas turbocharger is illustrated in
FIG. 1 as including acompressor housing 10 and acompressor wheel 1 which is rotatably arranged in the housing on ashaft 3. Connected to theshaft 3 is aturbine wheel 2 which is arranged inturbine housing 20. The exhaust gases of the internal combustion engine are expanded in the turbine. The work gained is transmitted by means of the shaft to a compressor wheel which compresses the air supplied to the internal combustion engine. Thecompressor housing 10 surrounds aninflow duct 11 through which the air, as the medium for compression, is conducted to the compressor wheel. The arrows indicate air flows. - An
annular circulation chamber 13 is arranged in an interior of the compressor housing, whichcirculation chamber 13 radially surrounds the main flow duct and extends from theintake region 11 to an at least partially encircling circulation opening 12 in the region of the guide blades of thecompressor wheel 1. Thecirculation chamber 13 is open in the direction of the main flow duct via two openings. A radial inlet opening is arranged upstream of the compressor wheel, and a radial contoured groove, the circulation opening 12, is arranged downstream of a leading edge of the compressor wheel and in a region of overlap with the inlet thereof. Between the encircling circulation openings, thecirculation chamber 13 is delimited from the main flow duct by an annular contouredwall 15. The contoured wall is connected to the inner compressor housing by means of a plurality ofstruts 14. - According to the disclosure, the struts which support the contoured wall can be spaced apart from one another to different extents in the circumferential direction, as illustrated in
FIG. 2 . - In one exemplary embodiment, all of the pairs of struts arranged adjacent to one another have a different spacing than the other pairs of struts arranged adjacent to one another.
- The
struts 14 which support the contoured wall may be configured with blade profiles or guide webs, of any desired shape, in order to impart a desired swirl to the flow in the circulation chamber. - The
struts 14 can all be aligned purely radially or can all be inclined to the same extent or different extents relative to the radial direction. - The circulation opening 12 can be formed as an encircling annular gap or can be divided into a plurality of annular gap segments. Likewise, the annular chamber can be divided into a plurality of segments in the circumferential direction. Here, the segments can be of equal size or of different sizes.
- Thus, it will be appreciated by those skilled in the art that the present invention can be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The presently disclosed embodiments are therefore considered in all respects to be illustrative and not restricted. The scope of the invention is indicated by the appended claims rather than the foregoing description and all changes that come within the meaning and range and equivalence thereof are intended to be embraced therein.
-
- A Axis
- 1 Compressor wheel
- 10 Compressor housing
- 11 Intake duct
- 12 Circulation openings
- 13 Circulation chamber
- 14 Struts
- 15 Contoured wall
- 2 Turbine wheel
- 20 Turbine housing
- 3 Turbine shaft
- 30 Bearing housing
Claims (11)
1. A compressor of an exhaust-gas turbocharger, comprising:
a rotatably mounted compressor wheel;
a main flow duct for supplying a medium for compression to the compressor wheel; and
a circulation chamber, arranged radially outside the main flow duct and delimited from the main flow duct by a contoured wall, which extends from an intake region of the main flow duct to a circulation opening formed into the contoured wall in a region of rotor blades of the compressor wheel, with the contoured wall being fastened to a housing of the compressor by struts in the circulation chamber, wherein a spacing between struts in at least one pair of struts arranged adjacent to one another in the circulation chamber is different in a circumferential direction than a spacing between struts arranged adjacent to one another in other pairs of struts.
2. The compressor as claimed in claim 1 , wherein struts arranged adjacent to one another in all of the pairs of struts have a different spacing in the circumferential direction than struts arranged adjacent to one another in the other pairs of struts.
3. The compressor as claimed in claim 1 , comprising:
two or more circulation openings, formed into the contoured wall which are spaced apart from one another in a direction of flow in the main flow duct.
4. The compressor as claimed in claim 1 , wherein the struts are blade profiles or guide webs for imparting a swirl to a flow in the circulation chamber.
5. The compressor as claimed in claim 1 , wherein the struts are all aligned radially, or are all inclined to a same extent relative to a radial direction of the compressor.
6. The compressor as claimed in claim 1 , comprising:
an inlet guide wheel for generating a swirl in a flow, the inlet guide wheel being arranged upstream of the intake region of the main flow duct.
7. The compressor as claimed in claim 2 , comprising:
two or more circulation openings, formed into the contoured wall which are spaced apart from one another in a direction of flow in the main flow duct.
8. The compressor as claimed in claim 7 , wherein the struts are blade profiles or guide webs imparting a swirl to a flow in the circulation chamber.
9. The compressor as claimed in claim 8 , wherein the struts are all aligned radially, or are all inclined to a same extent relative to a radial direction of the compressor.
10. The compressor as claimed in claim 9 , comprising:
an inlet guide wheel for generating a swirl in a flow, the inlet guide wheel being arranged upstream of the intake region of the main flow duct.
11. An exhaust-gas turbocharger having a compressor which comprises:
a rotatably mounted compressor wheel;
a main flow duct for supplying a medium for compression to the compressor wheel; and
a circulation chamber, arranged radially outside the main flow duct and delimited from the main flow duct by a contoured wall, which extends from an intake region of the main flow duct to a circulation opening formed into the contoured wall in a region of rotor blades of the compressor wheel, with the contoured wall being fastened to a housing of the compressor by struts in the circulation chamber, wherein a spacing between struts in at least one pair of struts arranged adjacent to one another in the circulation chamber is different in a circumferential direction than a spacing between struts arranged adjacent to one another in other pairs of struts.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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EP08170848.9 | 2008-12-05 | ||
EP08170848A EP2194277A1 (en) | 2008-12-05 | 2008-12-05 | Compressor stabiliser |
Publications (1)
Publication Number | Publication Date |
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US20100143111A1 true US20100143111A1 (en) | 2010-06-10 |
Family
ID=40445382
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US12/630,530 Abandoned US20100143111A1 (en) | 2008-12-05 | 2009-12-03 | Compressor stabilizer |
Country Status (5)
Country | Link |
---|---|
US (1) | US20100143111A1 (en) |
EP (1) | EP2194277A1 (en) |
JP (1) | JP2010151128A (en) |
KR (1) | KR20100065101A (en) |
CN (1) | CN101749283A (en) |
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US20120260652A1 (en) * | 2009-11-06 | 2012-10-18 | Johannes Hiry | Compressor comprising an insert in the inlet region |
WO2013133979A1 (en) * | 2012-03-06 | 2013-09-12 | Borgwarner Inc. | Exhaust-gas turbocharger |
US20130255253A1 (en) * | 2012-03-28 | 2013-10-03 | GM Global Technology Operations LLC | Fluid drive mechanism for turbocharger |
US9157446B2 (en) | 2013-01-31 | 2015-10-13 | Danfoss A/S | Centrifugal compressor with extended operating range |
US20160131145A1 (en) * | 2014-11-10 | 2016-05-12 | Honeywell International Inc. | Adjustable-trim centrifugal compressor with ported shroud, and turbocharger having same |
US10267214B2 (en) | 2014-09-29 | 2019-04-23 | Progress Rail Locomotive Inc. | Compressor inlet recirculation system for a turbocharger |
SE1751495A1 (en) * | 2017-12-05 | 2019-06-06 | Scania Cv Ab | Compressor Housing, Turbocharger, and Related Devices |
US20190242402A1 (en) * | 2018-02-07 | 2019-08-08 | Man Energy Solutions Se | Radial Compressor |
US10630144B2 (en) | 2015-12-03 | 2020-04-21 | Mitsubishi Heavy Industries, Ltd. | Electric motor support mechanism, compressor, and turbocharger |
US10954960B2 (en) | 2016-02-12 | 2021-03-23 | Ihi Corporation | Centrifugal compressor |
US10962016B2 (en) | 2016-02-04 | 2021-03-30 | Danfoss A/S | Active surge control in centrifugal compressors using microjet injection |
DE112011102931B4 (en) | 2010-09-02 | 2022-06-15 | Borgwarner Inc. | Compressor recirculation in annular volume |
US11519423B1 (en) | 2021-11-11 | 2022-12-06 | Progress Rail Locomotive Inc. | Compressor joint |
US11614001B1 (en) | 2021-11-11 | 2023-03-28 | Progress Rail Locomotive Inc. | Turbine containment |
US11719129B2 (en) | 2021-11-11 | 2023-08-08 | Progress Rail Locomotive Inc. | Compressor housing |
US11739763B2 (en) | 2021-11-11 | 2023-08-29 | Progress Rail Locomotive Inc. | Impeller attach mechanism |
US11781489B2 (en) | 2021-11-11 | 2023-10-10 | Progress Rail Locomotive Inc. | Gear train joint |
US11879348B2 (en) | 2021-11-11 | 2024-01-23 | Progress Rail Locomotive Inc. | Bearing carrier |
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US20120260652A1 (en) * | 2009-11-06 | 2012-10-18 | Johannes Hiry | Compressor comprising an insert in the inlet region |
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US10184481B2 (en) | 2013-01-31 | 2019-01-22 | Danfoss A/S | Centrifugal compressor with extended operating range |
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US10962016B2 (en) | 2016-02-04 | 2021-03-30 | Danfoss A/S | Active surge control in centrifugal compressors using microjet injection |
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DE112016006410B4 (en) | 2016-02-12 | 2023-06-07 | Ihi Corporation | CENTRIFUGAL COMPRESSOR |
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US20190242402A1 (en) * | 2018-02-07 | 2019-08-08 | Man Energy Solutions Se | Radial Compressor |
US10968922B2 (en) * | 2018-02-07 | 2021-04-06 | Man Energy Solutions Se | Radial compressor |
US11519423B1 (en) | 2021-11-11 | 2022-12-06 | Progress Rail Locomotive Inc. | Compressor joint |
US11614001B1 (en) | 2021-11-11 | 2023-03-28 | Progress Rail Locomotive Inc. | Turbine containment |
US11719129B2 (en) | 2021-11-11 | 2023-08-08 | Progress Rail Locomotive Inc. | Compressor housing |
US11739763B2 (en) | 2021-11-11 | 2023-08-29 | Progress Rail Locomotive Inc. | Impeller attach mechanism |
US11781489B2 (en) | 2021-11-11 | 2023-10-10 | Progress Rail Locomotive Inc. | Gear train joint |
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Also Published As
Publication number | Publication date |
---|---|
JP2010151128A (en) | 2010-07-08 |
EP2194277A1 (en) | 2010-06-09 |
CN101749283A (en) | 2010-06-23 |
KR20100065101A (en) | 2010-06-15 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: ABB TURBO SYSTEMS AG,SWITZERLAND Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:KUEHNEL, JANPETER;REEL/FRAME:023601/0821 Effective date: 20091202 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- AFTER EXAMINER'S ANSWER OR BOARD OF APPEALS DECISION |