SE542728C2 - Compressor Housing, Turbocharger, and Related Devices - Google Patents

Compressor Housing, Turbocharger, and Related Devices

Info

Publication number
SE542728C2
SE542728C2 SE1751495A SE1751495A SE542728C2 SE 542728 C2 SE542728 C2 SE 542728C2 SE 1751495 A SE1751495 A SE 1751495A SE 1751495 A SE1751495 A SE 1751495A SE 542728 C2 SE542728 C2 SE 542728C2
Authority
SE
Sweden
Prior art keywords
compressor
opening
compressor housing
turbocharger
intake passage
Prior art date
Application number
SE1751495A
Other versions
SE1751495A1 (en
Inventor
Joakim Kain
Original Assignee
Scania Cv Ab
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Scania Cv Ab filed Critical Scania Cv Ab
Priority to SE1751495A priority Critical patent/SE542728C2/en
Priority to PCT/SE2018/051246 priority patent/WO2019112510A1/en
Publication of SE1751495A1 publication Critical patent/SE1751495A1/en
Publication of SE542728C2 publication Critical patent/SE542728C2/en

Links

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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • 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
    • 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
    • F02B39/16—Other safety measures for, or other control of, 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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/04—Units comprising pumps and their driving means the pump being fluid-driven
    • 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
    • F04D29/68—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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B2037/125—Control for avoiding pump stall or surge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0215—Arrangements therefor, e.g. bleed or by-pass valves
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet
    • 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
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/10—Purpose of the control system to cope with, or avoid, compressor flow instabilities
    • F05D2270/101—Compressor surge or stall

Abstract

A compressor housing (1) for a turbocharger (3) is disclosed. The compressor housing (1) is configured to accommodate a compressor wheel (5) arranged to rotate in the compressor housing (1) around an axis (7). The compressor housing (1) comprises a compressor intake passage (9) with a first portion (9’) and a second portion (9”). The compressor housing (1) comprises a recirculation channel (13) with a first opening (15) at the first portion (9’) and a second opening (17) at the second portion (9”), wherein the first opening (15) is arranged at a greater radial distance (r1) from the axis (7) than the second opening (17). The present disclosure further relates to a compressor unit (21), a turbocharger (3), an engine (23) comprising a turbocharger (3), and a vehicle (29).

Description

Compressor Housing, Turbocharger, and Related Devices TECHNICAL FIELD The present disclosure relates to a compressor housing for a turbocharger. The present disclosure further relates to a compressor unit for a turbocharger, a turbocharger for an engine, an engine comprising a turbocharger, and a vehicle.
BACKGROUND A turbocharger is a device used to compress air to an inlet of a combustion engine. A turbocharger comprises a compressor unit a turbine unit. The compressor unit comprises a compressor housing and a compressor wheel rotatably arranged in the compressor housing. The turbine unit comprises a turbine housing and a turbine wheel rotatably arranged in the turbine housing. Exhaust gases from the engine are ducted through the turbine housing to spin the turbine wheel. The turbine wheel is connected to the compressor wheel, usually via a shaft. The compressor wheel is arranged to compress air to an inlet of the engine. Some engines comprise a charge air cooler between the compressor unit and the inlet of the engine.
Since the turbocharger utilizes energy of the exhaust gases to compress the air to the inlet of the engine, the turbocharger is an efficient means for compressing the air to the inlet. By using a turbocharger on an engine, the performance of the engine can be increased, and the fuel efficiency of the engine can be increased.
Turbochargers are associated with some problems and drawbacks. One problem is commonly known as surge. Surge appears when a pressure ratio over the compressor wheel is high and the air flow over the compressor wheel is low. If so, a flow instability is induced in the compressor housing and the air tends to go backward over the compressor wheel. This may for example occur when a driver backs off the throttle too fast, for example when changing gears, and can be heard as a fluttering noise. Surge can damage components of the turbocharger, such as bearings of the turbocharger and the compressor wheel. Surge is not desired since it generates noise, limits the life span of the turbocharger and risks breakdown of the turbocharger. Further, since the turbocharger should not operate in a surge range of the turbo map where surge is likely to occur, it narrows the field of operation, limits the performance, limits gear shifting speed and development of the turbocharger.
Attempts have been made to reduce the occurrence of surge by arranging a channel in the compressor housing through which air can flow when a pressure ratio over the compressor wheel is high and the airflow over the compressor wheel is low. Such a channel can reduce the occurrence of surge to some extent.
A further problem associated with turbochargers is that a turbocharger requires space in an engine compartment of a vehicle. The engine compartment of a vehicle is a confined space where a lot of components are to be fitted. Further, vehicles can be sold with different types and sizes of engines which may pose a problem for bigger engines comprising a turbocharger. In addition, engines comprising cylinders in a v-configuration, such as V6-engines, and V8-engines usually comprises two turbochargers, one turbocharger per cylinder bank. Further, a turbocharger, and especially the turbine unit of the turbocharger, is getting hot during operation. Therefore, additional space is required between the turbocharger and other components in an engine compartment.
SUMMARY It is an object of the present invention to overcome, or at least alleviate, at least some of the above-mentioned problems and drawbacks.
According to a first aspect of the invention, the object is achieved by a compressor housing for a turbocharger, wherein the compressor housing is configured to accommodate a compressor wheel arranged to rotate in the compressor housing around an axis. The compressor housing comprises a compressor intake passage with a first portion and a second portion. The first portion is arranged upstream of the second portion in an intended flow direction in the compressor intake passage, and the second portion is configured to enclose a portion of the compressor wheel. The compressor housing comprises a recirculation channel with a first opening at the first portion and a second opening at the second portion, wherein the first opening is arranged at a greater radial distance from the axis than the second opening.
Since the first opening is arranged at a greater radial distance from the axis than the second opening, a compressor housing is provided with improved ability to withstand surge. This because in a situation where a pressure ratio over a compressor wheel in the compressor housing is high and the air flow over the compressor wheel is low, the air may flow into the second opening of the recirculation channel and out into the compressor intake passage through the first opening. Since the first opening is arranged at a greater radial distance from the axis than the second opening, the air flowing out from the first opening will have a low impact on the flow in the compressor intake passage. That is, the air flowing out from the first opening will have a lower impact on the flow in the compressor intake passage as compared to a compressor housing comprising a channel having openings at the same radial distance from a rotational axis of a compressor wheel. Thereby, the risk of flow instability in the compressor intake passage is reduced in situations where the pressure ratio over a compressor wheel in the compressor housing is high and the air flow over the compressor wheel is low. As a result, a compressor housing is provided improving the transient surge performance of a turbocharger. Further, a compressor housing is provided that allows for faster reduction of fuel injection without risking surge. As a further result thereof, the compressor housing provided allows for shorter gear changing times without risking damage of components of a turbocharger.
Accordingly, a compressor housing for a turbocharger is provided overcoming, or at least alleviating, at least some of the above-mentioned problems and drawbacks. As a result, the above-mentioned object is achieved.
The first opening is arranged at a first radial distance from the axis, and the second opening is arranged at a second radial distance from the axis, and wherein the first radial distance is 63% - 77% greater than the second radial distance. Thereby, the risk of flow instability in the compressor intake passage is reduced, and a compressor housing is provided improving the transient surge performance of a turbocharger, and improving the ability to withstand surge.
Optionally, the area of the first opening is greater than the area of the second opening. Thereby, when air is flowing through the recirculation channel, the air will have a lower velocity at the first opening, than at the second opening of the recirculation channel. As a result, a compressor housing is provided with further improved flow characteristics and a further improved ability to withstand surge.
Optionally, the area of the first opening is at least 3 times greater than the area of the second opening. As a result, a compressor housing is provided with further improved flow characteristics a further improved ability to withstand surge.
Optionally, the area of the first opening is at least 6 times greater than the area of the second opening. As a result, a compressor housing is provided with further improved flow characteristics a further improved ability to withstand surge.
Optionally, the second opening extends along more than 15% of a total circumference of the second portion of the compressor intake passage. Thereby, a compressor housing is provided with further improved flow characteristics and a further improved ability to withstand surge. This because a sufficient flow of air is ensured through the second opening of the recirculation channel.
Optionally, the first opening extends along more than 15% of a total circumference of the first portion of the compressor intake passage. Thereby, a compressor housing is provided with further improved flow characteristics and a further improved ability to withstand surge. This because a sufficient flow of air is ensured through the first opening of the recirculation channel.
Optionally, a cross-sectional area of the recirculation channel increases along substantially the entire extension of the recirculation channel from the second opening towards the first opening. Thereby, when air is flowing in the recirculation channel from the second opening towards the first opening, the velocity of the air decreases along substantially the entire extension of the recirculation channel. Further, the air will have a lower velocity at the first opening, than at the second opening of the recirculation channel. As a result, a compressor housing is provided with further improved flow characteristics and a further improved ability to withstand surge.
Optionally, the compressor intake passage is funnel-shaped. Thereby, a compressor housing is provided with further improved flow characteristics and a further improved ability to withstand surge. In addition, a more compact compressor housing can be provided.
The compressor housing comprises an inflow portion configured to duct air to the compressor intake passage, and wherein the inflow portion is configured to duct the air substantially radially in relation to the axis. Thereby, a compact compressor housing is provided. In addition, since the inflow portion is configured to duct the air substantially radially in relation to the axis, and since the first opening is arranged at a greater radial distance from the axis than the second opening, a compressor housing is provided with a further improved ability to withstand surge.
According to a second aspect of the invention, the object is achieved by a compressor unit for a turbocharger, wherein the compressor unit comprises a compressor housing according to some embodiments, and a compressor wheel rotatably arranged in the compressor housing, wherein the second portion of the compressor intake passage of the compressor housing is arranged radially outwardly of a portion of the compressor wheel.
Since the compressor unit comprises a compressor housing with improved ability to withstand surge, a compressor unit is provided reducing the risk of flow instability in the compressor intake passage, and having an improved ability to withstand surge. Thus, a compressor unit is provided improving the transient surge performance of a turbocharger. Further, a compressor unit is provided that allows for faster reduction of fuel injection without risking surge. As a further result thereof, the compressor unit provided allows for shorter gear changing times without risking damage of components of the turbocharger.
Accordingly, a compressor unit for a turbocharger is provided overcoming, or at least alleviating, at least some of the above-mentioned problems and drawbacks. As a result, the above-mentioned object is achieved.
According to a third aspect of the invention, the object is achieved by a turbocharger for an engine, wherein the turbocharger comprises a turbine unit and a compressor unit according to some embodiments, wherein the turbine unit comprises a turbine connected to the compressor wheel of the compressor unit.
Since the turbocharger comprises a compressor unit with an improved ability to withstand surge, a turbocharger is provided reducing the risk of flow instability in the compressor intake passage, and having an improved ability to withstand surge. Thus, a turbocharger is provided with improved transient surge performance. Further, a turbocharger is provided that allows for faster reduction of fuel injection without risking surge. As a further result thereof, the turbocharger provided allows for shorter gear changing times without risking damage of components of the turbocharger.
Accordingly, a turbocharger is provided overcoming, or at least alleviating, at least some of the above-mentioned problems and drawbacks. As a result, the above-mentioned object is achieved.
According to a fourth aspect of the invention, the object is achieved by an engine comprising a turbocharger according to some embodiments, wherein the turbocharger is configured to compress air to an inlet of the engine.
Since the engine comprises a turbocharger having an improved ability to withstand surge, an engine is provided capable of operating in a wider operational range without risking surge and without risking damage of components of the turbocharger. Thus, an engine is provided with improved transient surge performance. Further, an engine is provided that allows for faster reduction of fuel injection without risking surge. As a further result thereof, the engine provided allows for shorter gear changing times without risking damage of components of the turbocharger of the engine.
Accordingly, an engine is provided overcoming, or at least alleviating, at least some of the above-mentioned problems and drawbacks. As a result, the above-mentioned object is achieved.
According to a fifth aspect of the invention, the object is achieved by a vehicle comprising an engine according to some embodiments.
Since the vehicle comprises an engine according to some embodiments, a vehicle is provided overcoming, or at least alleviating, at least some of the above-mentioned problems and drawbacks.
Further features of, and advantages with, the present invention will become apparent when studying the appended claims and the following detailed description.
BRIEF DESCRIPTION OF THE DRAWINGS Various aspects of the invention, including its particular features and advantages, will be readily understood from the example embodiments discussed in the following detailed description and the accompanying drawings, in which: Fig. 1 illustrates a cross section of a compressor housing for a turbocharger, according to some embodiments, Fig. 2 illustrates a second cross section of the compressor housing, illustrated in Fig. 1, Fig. 3 illustrates a turbocharger, according to some embodiments, Fig. 4 illustrates an engine, according to some embodiments, and Fig. 5 illustrates a vehicle, according to some embodiments.
DETAILED DESCRIPTION Aspects of the present invention will now be described more fully. Like numbers refer to like elements throughout. Well-known functions or constructions will not necessarily be described in detail for brevity and/or clarity.
Fig. 1 illustrates a cross section of a compressor housing 1 for a turbocharger, according to some embodiments. The compressor housing 1 is configured to accommodate a compressor wheel 5 arranged to rotate in the compressor housing 1 around an axis 7. The compressor housing 1 comprises a compressor intake passage 9 and an inflow portion 19 configured to duct air to the compressor intake passage 9. The compressor intake passage 9 is configured to duct air to the compressor wheel 5, and is arranged in close proximity to the compressor wheel 5 in the compressor housing 1. The compressor intake passage 9 comprises a first portion 9’ and a second portion 9”. The first portion 9’ is arranged upstream of the second portion 9” in an intended flow direction 11 in the compressor intake passage 9. The second portion 9” is configured to enclose a portion 5’ of the compressor wheel 5. That is, when the compressor wheel 5 is arranged in the compressor housing 1, the second portion 9” of the compressor intake passage 9 is arranged radially outwardly of the portion 5’ of the compressor wheel 5.
The compressor housing 1 comprises a recirculation channel 13 with a first opening 15 at the first portion 9’ and a second opening 17 at the second portion 9”. The first opening 15 is arranged at a first radial distance r1 from the axis 7 and the second opening 17 is arranged at a second radial distance r2 from the axis 7. As indicated in Fig. 1, the first radial distance r1 is greater than the second radial distance r2. Accordingly, the first opening 15 is arranged at a greater radial distance r1 from the axis 7 than the second opening 17. According to the illustrated embodiments, the first radial distance r1 is approximately 68% greater than the second radial distance r2. According to further embodiments, the first radial distance r1 is 63 % - 77 % greater than the second radial distance r2.
Since the first radial distance r1 is greater than the second radial distance r2, a compressor housing is provided with improved ability to withstand surge. This because when a pressure ratio over the compressor wheel 5 is high and the air flow over the compressor wheel 5 is low, air may flow into the second opening 17, through the recirculation channel 13, and out into the compressor intake passage 9 through the first opening 15. Since the first opening 15 is arranged at a greater radial distance from the axis 7 than the second opening 17, the air flowing out from the first opening 15 will have a low impact on the flow in the compressor intake passage 9. Accordingly, when a turbocharger comprising the compressor housing 1 is operating in a surge range, air may flow into the second opening 17, through the recirculation channel 13, and out into the compressor intake passage 9, via the first opening 15, and since the first opening 15 is arranged at a greater radial distance from the axis 7 than the second opening 17, the air flowing out from the first opening 15 will have a low impact on the flow in the compressor intake passage 9. Thereby, the risk of flow instability in the compressor intake passage 9 is reduced, which improves the ability to withstand surge.
When a turbocharger comprising the compressor housing 1 is operating outside of the surge range, and when the pressure at the first opening 15 is higher than the pressure at the second opening 17, the air may flow through the recirculation channel 13 in the opposite direction, i.e. from the first opening 15 towards the second opening 17. That is, during operation of a turbocharger comprising the compressor housing 1, air is flowing through the inflow portion 19 to the compressor intake passage 9. Most of the air will flow along the compressor intake passage 9 to the compressor wheel 5. However, some air may also flow to the compressor wheel 5 via the recirculation duct 13.
According to the illustrated embodiments, the first radial distance r1 is defined as the shortest distance between the axis 7 and a portion of the first opening 15 and the second radial distance r2 is defined as the shortest distance between the axis 7 and a portion of the second opening 15. Thus, in embodiments where an opening comprises two delimiting surfaces arranged at different radial distances from the axis 7, such as the first opening 15 according to the illustrated embodiments, the radial distance r1 corresponds to a distance between the axis 7 and the delimiting surface being closest to the axis 7.
According to the illustrated embodiments, the first opening 15 is arranged a first axial distance d1 from the second opening 17 measured along the axis 7. According to the illustrated embodiments, the first axial distance d1 is 82.6 % of the second radial distance r2. According to further embodiments, the first axial distance d1 is 70 % - 90 % of the second radial distance r2. In embodiments where the first opening 15 is arranged a first axial distance d1 from the second opening 17, the air flowing out from the first opening 15 will have a low impact on the flow in the compressor intake passage 9. As a result, a compressor housing 1 is provided with further improved ability to withstand surge. According to the illustrated embodiments, the first axial distance d1 between the first and second openings 15, 17 is defined as the shortest distance between a portion of the first opening 15 and a portion of the second opening 17 in the direction of the axis 7.
According to the illustrated embodiments, a cross-sectional area cA of the recirculation channel 13 increases along substantially the entire extension of the recirculation channel 13 from the second opening 17 towards the first opening 15. Thereby, when air is flowing in the recirculation channel 13 from the second opening 17 towards the first opening 15, the velocity of the air decreases along substantially the entire extension of the recirculation channel 13. Further, the air will have a lower velocity at the first opening 15, than at the second opening 17 of the recirculation channel 13. As a result, a compressor housing 1 is provided with improved flow characteristics and a further improved ability to withstand surge.
Further, according to the illustrated embodiments, the recirculation channel 13 is an annular recirculation channel extending around the axis 7 and having an extension in the radial direction of the axis 7. Thus, due to these features, the cross-sectional area cA of the recirculation channel 13 increases significantly along substantially the entire extension of the recirculation channel 13 from the second opening 17 towards the first opening 15.
Further, according to the illustrated embodiments, the compressor intake passage 9 is funnel-shaped, and the recirculation channel 13 is funnel-shaped. Thereby, a compressor housing 1 is provided with further improved flow characteristics and a further improved ability to withstand surge. This because when a turbocharger, comprising the compressor housing 1, is operating in a surge range, air may flow into the second opening 17, through the funnelshaped recirculation channel 13, and out into the compressor intake passage 9 via the first opening 15, and from the first opening 15 to the compressor wheel 5, via the funnel-shaped compressor intake passage 9. In addition, since the compressor intake passage 9 and the recirculation channel 13 are funnel-shaped, a more compact compressor housing 1 can be provided, especially in an axial direction of the compressor housing 1, i.e. in a direction coinciding with the axis 7 of rotation of the compressor wheel 5.
According to the embodiments illustrated in Fig. 1, the inflow portion 19 is configured to duct the air substantially radially in relation to the axis 7. The feature that the inflow portion 19 is configured to duct the air substantially radially in relation to the axis 7, may encompass that the inflow portion 19 is configured to duct the air in an average direction having an angle relative the axis 7 within the range of 30 degrees - 0 degrees, or 25 degrees - 0 degrees, or 20 degrees - 0 degrees. According to the illustrated embodiments, the inflow portion 19 is configured to duct the air in an average direction having an angle of 15 degrees relative the axis 7. Since the inflow portion 19 is configured to duct the air substantially radially in relation to the axis 7, and since the first opening 15 is arranged at a greater radial distance r1 from the axis 7 than the second opening 17, a compressor housing 1 is provided with a further improved ability to withstand surge. This because the air will flow from the inflow portion 19 to the compressor intake passage 9 substantially radially in relation to the axis 7, and the air will, at least to some extent, keep moving in radial directions towards the axis 7 when flowing in the compressor intake passage 9, and since the first opening 15 is arranged at a greater radial distance r1 from the axis 7 than the second opening 17, the air flowing out from the first opening 15 will have a low impact on the flow of air in the in the compressor intake passage 9.
Fig. 2 illustrates a second cross section of the compressor housing 1, illustrated in Fig. 1. As best seen in Fig. 2, the area of the first opening 15 in the compressor intake passage 9 is much greater than the area of the second opening 17 in the intake passage 9. According to the illustrated embodiments, the area of the first opening 15 is approximately 8 times greater than the area of the second opening 17. According to further embodiments, the area of the first opening 15 may be 1.2 - 30, 1.5 - 28, 2 - 25, 3 - 20, 4 - 15, 5 - 11, 6 - 10, or 7 - 9 times greater than the area of the second opening 17.
Since the area of the first opening 15 in the compressor intake passage 9 is greater than the area of the second opening 17 in the intake passage 9, the air will have a lower velocity at the first opening 15 than at the second opening 17 when flowing in the recirculation channel 13 from the second opening 17 towards the first opening 15. As a result, air flowing out from the first opening 15 will have a low impact on the flow in the in the compressor intake passage 9. Thereby, a compressor housing 1 is provided with further improved flow characteristics and a further improved ability to withstand surge.
According to the illustrated embodiments, the second opening 17 extends along substantially the entire circumference C1 of the second portion 9” of the compressor intake passage 9. According to further embodiments, the second opening 17 may extend along more than 10%, 15%, 25%, 40%, 60%, 80%, or 90% of a total circumference C1 of the second portion 9” of the compressor intake passage 9. Since the second opening 17 extends along a great proportion of circumference C1 of the second portion 9” of the compressor intake passage 9, a compressor housing 1 is provided with improved flow characteristics and a further improved ability to withstand surge. This because air may flow from a compressor wheel in radial directions thereof into the second opening 17 in an efficient and essentially uniform manner.
Further, according to the illustrated embodiments, the first opening 15 extends along substantially the entire circumference C2 of the first portion 9’ of the compressor intake passage 9. According to further embodiments, the first opening 15 may extend along more than 10%, 15%, 25%, 40%, 60%, 80%, or 90% of a total circumference C2 of the first portion 9’ of the compressor intake passage 9. Since the first opening 15 extends along a great proportion of circumference C2 of the first portion 9’ of the compressor intake passage 9, a compressor housing 1 is provided with improved flow characteristics and a further improved ability to withstand surge. This because air may flow out from the first opening 15 in an efficient and essentially uniform manner, causing a low impact on the flow in the compressor intake passage 9. Accordingly, since the first opening 15 extends along a great proportion of circumference C2 of the first portion 9’, the air will flow out from the first opening 15 along a great proportion of the circumference C2 of the first portion 9’, which ensures that the air can flow from a great proportion of the circumference C2 of the first portion 9’ towards a compressor wheel, which causes a low impact on the flow in the compressor intake passage 9, and provides further improved flow characteristics in the compressor intake passage 9.
Fig. 3 illustrates a turbocharger 3, according to some embodiments. The turbocharger 3 comprises a turbine unit 25 and a compressor unit 21. The compressor unit 21 comprises a compressor wheel 5 and a compressor housing 1 according to the embodiments illustrated in Fig. 1 and Fig. 2. The compressor wheel 5 is rotatably arranged in the compressor housing 1. The turbine unit 25 comprises a turbine housing 28 and a turbine wheel 26 rotatably arranged in the turbine housing 28. The turbine wheel 26 is connected to the compressor wheel 5 of the compressor unit 21, via a shaft 30.
Fig. 4 illustrates an engine 23 according to some embodiments. The engine 23 comprises a turbocharger 3 according to the embodiments illustrated in Fig. 3. The turbocharger 3 is configured to compress air to an inlet 27 of the engine 23. The engine 23 may be an internal combustion engine, for example a compression ignition engine, such as a diesel engine, or an Otto engine with a spark-ignition device, wherein the Otto engine may be configured to run on gas, petrol, alcohol or similar volatile fuels or combinations thereof.
Fig. 5 illustrates a vehicle 29, according to some embodiments. The vehicle 29 comprises wheels 31 and an engine 23 according to the embodiments illustrated in Fig. 4. The engine 23 is configured to provide motive power to the vehicle 29 via one or more of the wheels 31 of the vehicle 29. The vehicle 29 illustrated in Fig. 5 is a truck. However, the engine 23, as referred to herein, may be comprised in another type of manned or unmanned vehicle for land or water based propulsion such as a lorry, a bus, a construction vehicle, a tractor, a car, a boat, a ship, or the like. Further, the engine 23, as referred to herein, may be a stationary internal combustion engine, for example an internal combustion engine of an engine driven generator.
It is to be understood that the foregoing is illustrative of various example embodiments and that the invention is defined only by the appended claims. A person skilled in the art will realize that the example embodiments may be modified, and that different features of the example embodiments may be combined to create embodiments other than those described herein, without departing from the scope of the present invention, as defined by the appended claims.
As used herein, the term "comprising" or "comprises" is open-ended, and includes one or more stated features, elements, steps, components or functions but does not preclude the presence or addition of one or more other features, elements, steps, components, functions or groups thereof.

Claims (12)

1. A compressor housing (1) for a turbocharger (3), wherein the compressor housing (1) is configured to accommodate a compressor wheel (5) arranged to rotate in the compressor housing (1) around an axis (7), wherein the compressor housing (1) comprises a compressor intake passage (9) with a first portion (9’) and a second portion (9”), wherein the first portion (9’) is arranged upstream of the second portion (9”) in an intended flow direction (11) in the compressor intake passage (9), and wherein the second portion (9”) is configured to enclose a portion (5’) of the compressor wheel (5), wherein the compressor housing (1) comprises an inflow portion (19) configured to duct air to the compressor intake passage (9), and wherein the inflow portion (19) is configured to duct the air substantially radially in relation to the axis (7), characterized in that the compressor housing (1) comprises a recirculation channel (13) with a first opening (15) at the first portion (9’) and a second opening (17) at the second portion (9”), wherein the first opening (15) is arranged at a greater radial distance (r1) from the axis (7) than the second opening (17) and wherein the first opening (15) is arranged a first axial distance (d1) from the second opening (17) measured along the axis (7), and wherein the first axial distance (d1) is between 70 % and 90 % of a radial distance (r2) between the axis and the second opening (17) and wherein the first radial distance (r1) is between 63 % and 77 % greater than the second radial distance (r2).
2. The compressor housing (1) according to any one of the preceding claims, wherein the area of the first opening (15) is greater than the area of the second opening (17).
3. The compressor housing (1) according to claim 2, wherein the area of the first opening (15) is at least 3 times greater than the area of the second opening (17).
4. The compressor housing (1) according to claim 2, wherein the area of the first opening (15) is at least 6 times greater than the area of the second opening (17).
5. The compressor housing (1) according any one of the preceding claims, wherein the second opening (17) extends along more than 15% of a total circumference (C1) of the second portion (9”) of the compressor intake passage (9).
6. The compressor housing (1) according any one of the preceding claims, wherein the first opening (15) extends along more than 15% of a total circumference (C2) of the first portion (9’) of the compressor intake passage (9).
7. The compressor housing (1) according any one of the preceding claims, wherein a cross-sectional area (cA) of the recirculation channel (13) increases along substantially the entire extension of the recirculation channel (13) from the second opening (17) towards the first opening (15).
8. The compressor housing (1) according any one of the preceding claims, wherein the compressor intake passage (9) is funnel-shaped.
9. A compressor unit (21) for a turbocharger (3), wherein the compressor unit (21) comprises a compressor housing (1) according to any one of the preceding claims, and a compressor wheel (5) rotatably arranged in the compressor housing (1), wherein the second portion (9”) of the compressor intake passage (9) of the compressor housing (1) is arranged radially outwardly of a portion (5’) of the compressor wheel (5).
10. A turbocharger (3) for an engine (23), wherein the turbocharger (3) comprises a turbine unit (25) and a compressor unit (21) according to claim 9, wherein the turbine unit (25) comprises a turbine (26) connected to the compressor wheel (5) of the compressor unit (21).
11. An engine (23) comprising a turbocharger (3) according to claim 10, wherein the turbocharger (3) is configured to compress air to an inlet (27) of the engine (23).
12. A vehicle (29) comprising an engine (23) according to claim 11.
SE1751495A 2017-12-05 2017-12-05 Compressor Housing, Turbocharger, and Related Devices SE542728C2 (en)

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EP0229519B2 (en) * 1985-12-24 1996-11-13 Holset Engineering Company Limited Improvements in and relating to compressors
US5246335A (en) * 1991-05-01 1993-09-21 Ishikawajima-Harimas Jukogyo Kabushiki Kaisha Compressor casing for turbocharger and assembly thereof
US7575411B2 (en) * 2006-05-22 2009-08-18 International Engine Intellectual Property Company Llc Engine intake air compressor having multiple inlets and method
JP2009068372A (en) * 2007-09-11 2009-04-02 Ihi Corp Centrifugal compressor
EP2194277A1 (en) * 2008-12-05 2010-06-09 ABB Turbo Systems AG Compressor stabiliser
JP5444836B2 (en) * 2009-05-20 2014-03-19 株式会社Ｉｈｉ Centrifugal compressor
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WO2016151689A1 (en) * 2015-03-20 2016-09-29 三菱重工業株式会社 Centrifugal compressor and supercharger comprising same

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