NL1040722B1 - Compressor housing. - Google Patents

Compressor housing. Download PDF

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Publication number
NL1040722B1
NL1040722B1 NL1040722A NL1040722A NL1040722B1 NL 1040722 B1 NL1040722 B1 NL 1040722B1 NL 1040722 A NL1040722 A NL 1040722A NL 1040722 A NL1040722 A NL 1040722A NL 1040722 B1 NL1040722 B1 NL 1040722B1
Authority
NL
Netherlands
Prior art keywords
compressor
housing
passage
spiral
diffuser
Prior art date
Application number
NL1040722A
Other languages
Dutch (nl)
Other versions
NL1040722A (en
Inventor
Rankenberg Mark
Kamphues Edwin
Schick Hedwig
Dehnen Ulrich
Original Assignee
Mitsubishi Turbocharger And Engine Europe B V
Mann & Hummel Gmbh
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 Mitsubishi Turbocharger And Engine Europe B V, Mann & Hummel Gmbh filed Critical Mitsubishi Turbocharger And Engine Europe B V
Priority to NL1040722A priority Critical patent/NL1040722B1/en
Publication of NL1040722A publication Critical patent/NL1040722A/en
Application granted granted Critical
Publication of NL1040722B1 publication Critical patent/NL1040722B1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/42Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226Fan casings
    • F04D29/4233Fan casings with volutes extending mainly in axial or radially inward direction
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01DNON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D9/00Stators
    • F01D9/02Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026Scrolls for radial machines or engines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00Pumping installations or systems
    • F04D25/02Units comprising pumps and their driving means
    • F04D25/024Units comprising pumps and their driving means the driving means being assisted by a power recovery turbine
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/42Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00Application
    • F05D2220/40Application in turbochargers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00Geometry
    • F05D2250/20Three-dimensional
    • F05D2250/24Three-dimensional ellipsoidal
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00Geometry
    • F05D2250/70Shape
    • F05D2250/71Shape curved
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00Materials; Properties thereof
    • F05D2300/40Organic materials
    • F05D2300/43Synthetic polymers, e.g. plastics; Rubber

Description

Title: Compressor housing
The invention relates to a compressor housing, a turbocharger comprising such a compressor housing, the use of such a turbocharger and a method of manufacturing such a compressor housing.
A turbocharger compressor and a plastic compressor housing are known from US2010/0232955. This compressor is a radial or centrifugal compressor. The plastic compressor housing defines at least a part of a compressor wheel compartment for a compressor wheel, a spiral shaped compressor passage, and a diffuser. With the rotational speed of the compressor wheel, fresh air is drawn in axially, wherein the fresh air is accelerated by means of the wheel to high velocity and then expelled in a radial direction. The diffuser's function is to slow down the high-velocity air, with minimal losses, so that both pressure and temperature rise. The spiral shaped compressor passage collects the air and slows it down further before it reaches the compressor passage outlet.
A turbocharger should be reliable and preferably lowers the overall emissions of the engine. With the mass production of turbochargers it is important that the turbocharger comprises of a minimum number of parts. Further, those parts should be easy to manufacture and easy to assemble, in order to provide a cost effective turbocharger.
It is an object of the present invention to provide a plastic compressor housing improving the performance of a compressor.
This object is achieved by a compressor housing according to claim 1.
An advantage of plastic compressor housings compared to conventional aluminum compressor housings is the greater freedom in design for cost efficiently manufacturing the compressor housing and improving the performance of the compressor as well. An additional advantage of plastic is that it is possible to manufacture a lightweight compressor housing. In the manufacturing process of a plastic compressor housing it is possible to reduce the material to be used by providing hollow spaces or thinner parts in less strength-critical areas of the compressor housing. In the strength critical areas of the plastic compressor housing, it is relatively simple to provide plastic supporting ribs or the like. Further, it is possible in a cost effective way to include in the manufacturing process different functions in the plastic compressor housing. In other words, it is relatively easy to provide openings for positioning reinforcing elements and/or a screw thread or other connecting shapes in the plastic design for connecting the compressor housing for example to a center hub rotating assembly of a turbocharger.
An important feature of plastic is its relatively low thermal conductivity, i.e. plastic is a thermal insulator. The insulating plastic walls of the diffuser and the spiral shaped compressor passage provide a good insulating shield to protect the air being compressed inside the compressor against the external heat produced by external components such as for example the combustion engine. The shielding effect has the result that the air temperature inside the compressor is less heated by external influences such that in relative terms compared to aluminum more compression with the compressor can be achieved.
By using plastic it is further possible to design without complex manufacturing steps an arched or bent design of a diffuser channel for deflecting air tangentially and/or axially in the diffusor channel between the inlet and the outlet. The plastic inner walls of the diffuser channel are arch-shaped or bent between the inlet and the outlet. The arched diffuser optimizes flow patterns of the air to be compressed thereby increasing the performance of the compressor. The inner walls of the arched diffuser channel have a radius of curvature over more than 75% of the complete distance between diffuser inlet and diffuser outlet. In a diffuser channel having at least two radii of curvature, the centers of the at least two radii of curvature are located on one side of the diffuser only. In this way the diffuser defines a smooth arched flow path without any opposing bents, such as a first bend having a radius of curvature on a first side of. the diffuser and a second bend having a radius of curvature on a second opposing side of the diffuser. By providing the centers of the at least two radii of curvature on one side of the diffuser only an optimal air flow is provided through the diffuser to the spiral shaped compressor passage increasing the performance of the compressor.
In an embodiment, the compressor housing is made as one-piece plastic compressor housing. The one-piece plastic compressor housing does not require any joining steps in the manufacturing process. As a result, the inner walls of the diffuser and/or the spiral shaped compressor passage do not have any joining seams. A seam-free compressor housing optimizes air flow and further increases the performance of the compressor housing.
In another embodiment, the spiral shaped compressor passage comprises an outlet for supplying compressed air to at least one cylinder for combustion, wherein an end of the spiral shaped compressor passage opposing the outlet is closed. In other words this end is a dead end located at the start of the passage preventing air to enter directly in a wider diverged part of the passage located closer to the outlet of the passage near the cylinder. In this way the air collected in the passage near the closed end is forced to flow through the spiral shaped passage to the cylinder. By providing a closed end or a closed scroll, the airflow in the wider diverged part of the passage near the closed end is no longer disturbed, such that airflow and compression of the air are optimized in the compressor housing.
In a further embodiment, the housing comprises a hollow space between the compressor wheel compartment and the spiral shaped compressor passage. This hollow space or spaces reduce the weight and material to be used for manufacturing the compressor housing. The hollow space or spaces can be in fluid connection with the diffuser channel and the compressor compartment for recirculating air. It is also possible that the hollow space(s) is in fluid connection with different parts of the compressor compartment for recirculating air only in the compressor compartment. These fluid connections for recirculating air widen the compressor performance map by moving the surge line to the left in the compressor performance map by allowing a small amount of airflow to bleed off the low-velocity portion of the wheel and recirculate, to ward off blade stall. The main advantage of a compressor housing made from plastic is that these fluid connections can be established in an uncomplicated manner and in a cost-effective way.
In another embodiment the compressor housing comprises a center axis, which coincides in an assembled compressor with the axial axis of the compressor wheel, wherein the distance measured in a axial direction parallel to the axial axis of the compressor wheel between the center of the spiral shaped compressor passage and the center of the diffuser inlet is at least two times the distance measured in the axial direction between the center of the spiral shaped compressor passage and the inner wall of the spiral shaped compressor passage. This design of the arched diffusor in relation to the spiral passage provides a compressor housing improving the compression performance of the compressor.
To explain the invention in more detail, exemplary embodiments thereof will hereinafter be described with reference to the accompanying drawings, wherein:
Figure 1 shows a section of a turbocharger according to the present invention;
Figure 2 shows a section of a compressor having a compressor housing according to the present invention;
Figure 3 shows a schematic view of a part of a compressor housing according to the present invention;
Figure 4 shows a section of another embodiment of a compressor housing according to the present invention.
In this description, identical or corresponding parts have identical of corresponding reference numerals.
Figure 1 shows a section of a turbocharger 10 according to the present invention. Turbochargers 10 have become more and more popular for use in connection with passenger car engines, because the use of a turbocharger 10 permits selection of a smaller engine that develops the same amount of horsepower. Using a smaller and a lower mass engine together with a turbocharger 10 has the desired effect of decreasing the overall weight of the car, decreasing fuel consumption and reducing the overall emissions of the engine, which contributes to a cleaner environment.
The turbocharger 10 includes a turbine 3 operatively-connected to the engine exhaust manifold (not shown), a centrifugal compressor 1 operatively connected to the engine air intake manifold (not shown), and a center hub rotating assembly 5 housing a shaft 7 that connects the compressor wheel 9 with the turbine wheel 11.
The turbine wheel 11 is driven to rotate by the exhaust gas flowing in the exhaust manifold. Rotation of the turbine wheel 11 causes by means of the shaft 7 rotation of the compressor wheel 9. As the compressor wheel 9 rotates in the compressor housing 15, it increases the air mass flow rate, airflow density and air pressure delivered to the engine cylinders (not shown).
The compressor housing 15 is shown in greater detail in figure 2. The compressor housing 15 is adapted to receive air from an air intake 17 and distribute the air to a compressor wheel 9 rotatable disposed around an axial axis 19 within the compressor housing 15 and coupled to an end of the shaft 7. The compressor housing 15 provides a compressor wheel compartment 21 for the compressor wheel 9, a spiral shaped compressor passage 23, and a diffuser 25 interposed between the compressor ' wheel 9 and the spiral shaped compressor passage 23. The spiral shaped compressor passage 23 is formed along an outer region and radially remote from the compressor wheel 9.
The diffuser 25 has inner walls 26, 28 defining a diffuser channel 30, an inlet 31 in fluid communication with the compressor wheel compartment 21 for radially receiving high-velocity fresh air axially drawn in by means of the compressor wheel 9 and an outlet 33 in fluid communication with the spiral shaped compressor passage 23. The distance between the inlet 31 of the diffuser channel 30 and the radially most remote compressor wheel tip 39 is smaller than 10 mm. In addition, the distance d between the opposing inner walls 26, 28 in the middle section of the diffuser is about 4 mm. As shown in figures 1 and 2 the distance between the opposing inner walls 26, 28 near the inlet 31 and/or near the outlet 33 may be somewhat larger than the distance d, but this distance is smaller than 2 times the distance d.
The plastic inner walls 26, 28 of the diffuser channel are curved providing an arched designed diffuser channel 30 between the inlet and the outlet for deflecting air tangentially and/or axially in the diffusor channel between the inlet and the outlet. Using the thermal insulating properties of plastic and the optimized airflow by means of the arched design of the diffuser channel 30 a significant increase of the compressor performance is achieved. By means of the arched design of the diffuser it is also possible without increasing the outer dimensions of the compressor housing to provide a longer diffuser channel. The longer diffuser channel improves the compressor performance further. It is also possible to provide a more compact compressor housing by means of an arched diffuser 25. With the arched diffuser 25 the passage 23 can be moved closer to the compressor wheel 9 thereby providing a reduction in the outer dimensions of the compressor housing 15.
The compressor housing 15 shown in figures 1 and 2 is made as one-piece plastic compressor housing 15. Such a one-piece plastic compressor housing 15 has no joining seams, which has a beneficial effect on the air flowing through the seam-free diffuser 25 and seam-free spiral shaped compressor passage 23. Compressor 15 can be manufactured by additive manufacturing such as laser sintering and/or by subtractive manufacturing. It is also possible to use lost core technology to manufacture the compressor housing 15.
The compressor housing 15 comprises a center axis 41, which as shown in figures 1 and 2 coincides in an assembled compressor 1 with the axial axis 19 of the compressor wheel 9.
.The distance A1 measured only in a axial direction parallel to the axial axis 19 between the center 45 of the spiral shaped compressor passage 23 and the center 47 of the diffuser inlet 31 is about two times the distance A2 measured in the axial direction only between the center 4 5 of the spiral shaped compressor passage 23 and the inner wall 49 of the spiral shaped compressor passage 23. The position to measure these distances is preferably where the diameter of the passage reaches or has reached its maximum diameter. A preferred area is about 270°-360° measured from the start of the passage. In this preferred area of the spiral shaped compressor passage 23 the maximum distance Al is preferably sixth times the distance A2. By means of such a design it is possible to achieve more performance within a restricted radial volume .
Figure 3 shows a schematic view of a spiral shaped compressor passage 23 of a compressor housing 15 according to the present invention. The spiral shaped compressor passage 23 comprises a passage outlet 51 for supplying compressed air to at least one cylinder (not shown) for combustion. The passage 23 diverges in the direction of the outlet 51, such that the cross sectional area of the passage 23 smoothly increases. An end 53 of the spiral shaped compressor passage 23 opposing the outlet 51 is closed. By providing a closed end 53 in the passage 23, the airflow in the wider diverged part Z of the passage 23 near the closed end 53 is no longer disturbed, such that airflow and compression of the air in the passage 23 are further optimized. The closed end is located at a distance smaller than 3 cm of the outer wall of the spiral shaped compressor passage.
In figure 4 a section of another embodiment of a compressor housing 115 according to the present invention is shown. The compressor housing 115 is made of four plastic components 2, 4, 6, 8 defining the compressor wheel compartment 121, the passage 123, the diffuser 125, and the air intake 117. These plastic components 2, 4, 6, 8 can be joined together by means of hot gas welding. The advantage of hot gas welding two plastic components is high-quality seams. Such high-quality seams reduce the impact of a seam to the air flow. Other joining techniques like ultrasonic welding or adhering can also be used to join the components. The position of a seam can be chosen such that the influence of the seam of the air flow is negligible. By using plastic it also possible in an uncomplicated manner to shape each component to integrate various functions therein such as complementary shapes of the component parts to be connected together for providing a stronger connection. It is also possible to use different types of plastic for each component. For example, component 8 can be manufactured from a plastic type having a lower quality than the plastic type of the other components 2, 4, 6 .
Though not shown, it is preferred to provide a housing 115 in which the components 2, 4, 6, 8 are joined such that the passage 23 is seam-free. It is also possible to reduce the number of plastic components 2, 4, 6, 8, if desired.
The compressor housing 115 comprises a hollow space 122 between the compressor wheel compartment 121 and the spiral shaped compressor passage 123. The dimensions of the spiralshaped hollow space 122 change over 360 degrees and preferably these dimensions change inversely proportional with the dimensions of the spiral shaped compressor passage 123. The hollow space may comprise various compartments or multiple spaces separated by reinforcing ribs or the like. This hollow space 122 reduces the weight and material to be used for manufacturing the compressor housing 115.
The hollow space 122 can be in fluid connection (not shown) with the diffuser channel 125 and the compressor compartment 121 for recirculating air. It is also possible that the hollow space 122 is in fluid connection (not shown) with different parts of the compressor compartment 121 only for recirculating air.
The turbocharger 10 shown in the figures comprising a plastic compressor housing 15 preferably manufactured of polyphenylene sulfide.
The compressor housing according to the present invention can be made from any suitable thermosetting polymers such as for example phenol formaldehyde resin or any suitable high temperature thermoplastic polymers such as for example polyphenylene sulfide.
It is possible that the closed end 53 is located against the outer wall of the spiral shaped compressor passage 23.
The plastic turbocharger compressor housing 115 can be manufactured by injection molding and assembling e.g. welding and/or screwing.
The compressor housing according to the present invention can also be used in an electrically driven or supported flow compressor or a secondary air charger.
It is also possible to provide a turbocharger compressor housing manufactured of plastic material, wherein the housing comprises at least a part of a compressor wheel compartment for a compressor wheel, and a spiral shaped compressor passage the spiral passage comprises an outlet for supplying compressed air to at least one cylinder for combustion, wherein an end opposing the outlet is closed. Such a compressor housing can be combined with any of the above features and it is further possible to use this housing having a closed end without an arched diffuser.

Claims (15)

1. Compressorbehuizing die is vervaardigd van kunststoffen materiaal, waarbij de behuizing is voorzien van: - ten minste een deel van een compressorwielcompartiment voor een compressorwiel, - een spiraalgevormde compressor-doorgang, en - een diffusor die binnenwanden heeft die een diffusor-kanaal, een ingang alsmede een uitgang definiëren, waarbij de ingang in fluïdum verbinding staat met het compressorwielcompartiment voor het ontvangen van verse lucht met een hoge snelheid die axiaal naar binnen wordt getrokken door middel van het compressorwiel en de uitgang staat in fluïdum verbinding met de spiraalgevormde compressor-doorgang, waarbij de kunststofbinnenwanden van het diffusor-kanaal een gewelfd ontwerp hebben tussen de ingang en de uitgang voor het tangentieel en/of axiaal afbuigen van lucht in het diffusor-kanaal tussen de ingang en de uitgang.Compressor housing made of plastic material, the housing comprising: - at least a part of a compressor wheel compartment for a compressor wheel, - a spiral-shaped compressor passage, and - a diffuser that has inner walls that have a diffuser channel, a define an input as well as an output, wherein the input is in fluid communication with the compressor wheel compartment for receiving fresh air at a high speed which is drawn axially inwards by means of the compressor wheel and the output is in fluid communication with the spiral-shaped compressor passage wherein the plastic inner walls of the diffuser channel have a curved design between the entrance and the exit for tangentially and / or axially deflecting air in the diffuser channel between the entrance and the exit.
2. Compressorbehuizing volgens conclusie 1, waarbij de compressorbehuizing is vervaardigd als een eendelige kunststoffen compressorbehuizing. The compressor housing of claim 1, wherein the compressor housing is made as a one-piece plastic compressor housing.
3. Compressorbehuizing volgens conclusie 1 of 2, waarbij de afstand tussen de tegenover elkaar gelegen binnenwanden constant is over meer dan 25% van de lengte van het diffusor-kanaal. Compressor housing according to claim 1 or 2, wherein the distance between the opposite inner walls is constant over more than 25% of the length of the diffuser channel.
4. Compressorbehuizing volgens ten minste één der voorgaande conclusies, waarbij het gewelfde ontwerp van het diffusor-kanaal wordt gedefinieerd door een krommingsradius of door ten minste twee krommingsradii, waarbij in het gewelfde ontwerp met ten minste twee krommingsradii de middelpunten van de krommingsradii zijn gelegen op één zijde van de diffusor.Compressor housing according to at least one of the preceding claims, wherein the diffused channel's curved design is defined by a curvature radius or by at least two curvature radii, wherein in the curved design with at least two curvature radii the centers of curvature radii are located at one side of the diffuser.
5. Compressorbehuizing volgens ten minste één der voorgaande conclusies, waarbij de spiraalgevormde compressor-doorgang is voorzien van een uitgang voor het toevoeren van samengedrukte lucht naar ten minste één cilinder voor verbranding, waarbij een tegenover de uitgang gelegen uiteinde van de spiraalgevormde compressor-doorgang gesloten is.Compressor housing according to at least one of the preceding claims, wherein the spiral-shaped compressor passage is provided with an outlet for supplying compressed air to at least one cylinder for combustion, wherein an end of the spiral-shaped compressor passage opposite the outlet is closed. is.
6. Compressorbehuizing volgens conclusie 5, waarbij het gesloten uiteinde is gelegen tegen de buitenwand van de spiraalgevormde compressor-doorgang. Compressor housing according to claim 5, wherein the closed end is located against the outer wall of the spiral-shaped compressor passage.
7. Compressorbehuizing volgens conclusie 5, waarbij het gesloten uiteinde is gelegen op een afstand die kleiner is dan drie centimeter van de buitenwand van de spiraalgevormde compressor-doorgang. The compressor housing of claim 5, wherein the closed end is located at a distance that is less than three centimeters from the outer wall of the spiral-shaped compressor passageway.
8. Compressorbehuizing volgens ten minste één der voorgaande conclusies, waarbij de behuizing is voorzien van een holle ruimte tussen het compressorwielcompartiment en de spiraalgevormde compressor-doorgang. Compressor housing according to at least one of the preceding claims, wherein the housing is provided with a hollow space between the compressor wheel compartment and the spiral-shaped compressor passage.
9. Compressorbehuizing volgens conclusie 8, waarbij de holle ruimte in fluïdum verbinding staat met de diffusor en het compressorwielcompartiment voor het her-circuleren van lucht. The compressor housing of claim 8, wherein the cavity is in fluid communication with the diffuser and the compressor wheel compartment for recirculating air.
10. Compressorbehuizing volgens conclusie 8 of 9, waarbij de holle ruimte in fluïdum verbinding staat met een eerste en een tweede deel van het compressorwielcompartiment voor het her-circuleren van lucht in het compressorwielcompartiment.A compressor housing as claimed in claim 8 or 9, wherein the cavity is in fluid communication with a first and a second part of the compressor wheel compartment for recirculating air in the compressor wheel compartment.
11. Compressorbehuizing volgens ten minste één der voorgaande conclusies, waarbij de afstand gemeten in een axiale richting parallel aan de axiale as van het compressorwiel tussen het midden van de spiraalgevormde compressor-doorgang en het midden van de diffusoringang ten minste anderhalf keer, bij voorkeur ten minste twee keer de afstand is gemeten in de axiale richting tussen het midden van de spiraalgevormde compressor-doorgang en de binnenwand van de spiraalgevormde compressor-doorgang.Compressor housing according to at least one of the preceding claims, wherein the distance measured in an axial direction parallel to the axial axis of the compressor wheel between the center of the spiral-shaped compressor passage and the center of the diffuser input is at least one and a half times, preferably at least one and a half times has been measured at least twice the distance in the axial direction between the center of the spiral-shaped compressor passage and the inner wall of the spiral-shaped compressor passage.
12. Compressorbehuizing volgens ten minste één der voorgaande conclusies, waarbij de kortste afstand tussen de diffusoruitgang en de hartlijn van de compressorwielbehuizing gelijk of groter is dan de kortste afstand tussen het midden van de spiraalgevormde compressordoorgang en de hartlijn van de compressorwielbehuizing.A compressor housing according to at least one of the preceding claims, wherein the shortest distance between the diffuser output and the axis of the compressor wheel housing is equal to or greater than the shortest distance between the center of the spiral-shaped compressor passage and the axis of the compressor wheel housing.
13. Turbolader omvattende een radiale compressor met een compressorbehuizing volgens ten minste één van de voorgaande conclusies. A turbocharger comprising a radial compressor with a compressor housing according to at least one of the preceding claims.
14. Gebruik van een turbolader volgens conclusie 13 in een motor. Use of a turbo charger according to claim 13 in an engine.
15. Werkwijze voor het vervaardigen van een kunststoffen compressorbehuizing volgens één der voorgaande conclusies 1-12 door spuitgieten en/of samenstellen door bijvoorbeeld lassen en/of schroeven.Method for manufacturing a plastic compressor housing according to any one of the preceding claims 1-12 by injection molding and / or assembly by, for example, welding and / or screwing.
NL1040722A 2014-03-12 2014-03-12 Compressor housing. NL1040722B1 (en)

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NL1040722A NL1040722B1 (en) 2014-03-12 2014-03-12 Compressor housing.
EP15158599.9A EP2918790A1 (en) 2014-03-12 2015-03-11 Compressor housing
EP15158597.3A EP2918789A1 (en) 2014-03-12 2015-03-11 Compressor housing

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NL1040722B1 true NL1040722B1 (en) 2015-11-19

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EP2918790A1 (en) 2015-09-16
EP2918789A1 (en) 2015-09-16
NL1040722A (en) 2015-11-05
NL1040722A1 (en)

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