US20150316071A1 - Centrifugal gas compressor or pump comprising a toothed ring and a cowl - Google Patents
Centrifugal gas compressor or pump comprising a toothed ring and a cowl Download PDFInfo
- Publication number
- US20150316071A1 US20150316071A1 US14/649,882 US201314649882A US2015316071A1 US 20150316071 A1 US20150316071 A1 US 20150316071A1 US 201314649882 A US201314649882 A US 201314649882A US 2015316071 A1 US2015316071 A1 US 2015316071A1
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- US
- United States
- Prior art keywords
- wheel
- compressor
- diffuser
- hub
- blades
- 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
- 239000012530 fluid Substances 0.000 claims abstract description 16
- 239000007789 gas Substances 0.000 description 18
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Images
Classifications
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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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/34—Rotor-blade aggregates of unitary construction, e.g. formed of sheet laminae
-
- 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
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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
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal 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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
-
- 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
Definitions
- FIGS. 6 and 7 show a centrifugal compressor 11 according to the prior art.
- the compressor 11 includes a compressor body 111 and a rotating part rotatively mounted in the compressor body 111 around a wheel axis A.
- the rotating part comprises a compressor wheel 112 mounted on a rotating shaft 114 in a bearing 113 of the compressor body 111 .
- the compressor wheel 112 comprises a hub 1120 and a set of blades 1121 attached to the hub.
- the compressor body 111 also comprises an axial opening placed opposite the hub 1120 and which comprises an intake 1110 .
- the compressor body 111 comprises a volute 1112 around the compressor wheel 112 .
- the volute 1112 comprises a peripheral opening placed on the periphery of the compressor wheel 112 and leads to an outlet 1113 which extends substantially in a direction tangent to the compressor wheel 112 .
- the peripheral opening is called a diffuser 1111 .
- the blades 1121 comprise a first edge 11211 , called a leading edge, opposite the axial opening 1110 and a second edge 11212 , called a trailing edge, opposite the diffuser 1111 so that the gases circulate from the axial opening 1110 to the diffuser 1111 being driven by the compressor wheel 112 .
- the shape of the blades 1121 is designed so that the gases receive mechanical energy by the compressor wheel 112 , that principally being accelerated, the kinetic energy thus obtained then being converted into pressure in the volute.
- Certain compressor wheel versions are cowled and comprise for this purpose a cowl attached to the blades, the section of which mates with that of the guide wall.
- Machines of the same type can be used for a fluid no longer gaseous, but liquid.
- the term pump is used instead of compressor.
- the speed of the fluid at the diffuser is high such that the friction losses along the diffuser wall related to the viscosity of the fluid are high.
- the tangential component of the speed of the fluid is very high and often predominant.
- the aim of the invention is to reduce these friction losses.
- the object of the invention is a centrifugal gas compressor or pump comprising a body, a wheel rotatively mounted in the body around a wheel axis, the wheel comprising a hub, a set of blades attached to the hub, the body comprising a diffuser placed on the periphery of the wheel and a fluid intake placed opposite the hub, the blades comprising a first edge opposite the axial opening and the second edge opposite the diffuser so that a fluid circulates from the intake to the diffuser, the second edges being located inside a blade-enveloping cylinder centered on the wheel axis, the wheel comprising at least one ring attached to the wheel and which extends radially beyond the blade-enveloping cylinder to form a diffuser wall.
- the diffuser zone comprises a wall which rotates at the same speed as that of the wheel.
- the difference between the average speed of the fluid and this wall is greatly reduced which allows the friction losses at this level to be greatly reduced.
- less losses on the kinetic energy of the fluid are obtained in the diffuser and, therefore, on the energy supplied in the form of pressure at the volute outlet.
- the wheel is submitted to pressure forces the resultant of which is an axial force.
- the pressure which is presented on the face of the wheel which carries the blades is in general very different to the one opposed to it.
- the modification in the size of this face which results from adding the ring beyond the first edge of the blades also modifies this result.
- it is possible to adjust this result in particular in the case of a turbocompressor where the turbine wheel and the compressor wheel exert axial forces in opposite directions.
- the ring is inserted with play in a bore of the compressor body and is placed in such a way that its diffuser side face is in the same plane as the wall of the volute at this level.
- the gas flow which leaves the ring continues to be guided without discontinuity by the wall of the volute thus avoiding the creation of load losses.
- the body comprises a volute around the diffuser.
- the ring extends from the hub.
- the wheel comprises a cowl attached to the blades.
- the ring extends from the cowl.
- the diffuser zone comprises a wall possibly additional which rotates at the same speed as that of the wheel.
- This ring can be alone.
- the flow of the fluid is entirely channelled in this zone by the walls which substantially move at the same speed as the flow of the fluid, thus greatly reducing the friction losses.
- the balance of the pressure forces can be exerted in a direction opposite to that of the configuration with the ring in the extension of the hub.
- cowl and the blades are in one piece.
- the ring and the wheel in the extension of the hub are in one piece.
- the wheel is provided with high mechanical strength.
- Manufacture requires only a few modifications in the manufacturing technique.
- FIG. 1 is a longitudinal cross-sectional view of a machine fulfilling the function of compressor in accordance with a first embodiment of the invention
- FIG. 2 is a detailed view taken along the lines II of FIG. 1 ;
- FIG. 3 is a longitudinal cross-sectional view of a turbocompressor comprising a turbine and a compressor in accordance with the invention
- FIGS. 4 and 5 are views similar to FIG. 2 of a compressor wheel, but according to a third and a fourth embodiment of the invention.
- FIG. 6 is a longitudinal cross-sectional view through line VI-VI of FIG. 7 of a centrifugal compressor according to the prior art.
- FIG. 7 is a view of the compressor, the body being shown by a cross-sectional view through line VII-VII of FIG. 6 .
- the volute 2112 includes a peripheral opening forming a diffuser 2111 , placed on the periphery of the compressor wheel 212 and leading to an outlet 2113 which substantially extends in a direction tangential to the compressor wheel 212 .
- the blades 2121 include a first edge 21211 opposite the gas intake and a second edge 21212 opposite the diffuser 2111 .
- the gases circulate from the intake 2110 to the diffuser 2111 being driven by the compressor wheel 212 .
- the shape of the blades 2121 is designed so that the gases accelerate when passing through the compressor wheel 212 by means of the energy supplied by the wheel.
- the second edges 21212 extend substantially parallel to the wheel axis A and are contained in a virtual cylinder called blade-enveloping cylinder C.
- the hub 2120 extends beyond the fictive cylinder C in the form of a ring 21201 .
- the ring 21201 thus delimits the diffuser 2111 on one of its sides.
- the ring 21201 is inserted with play in a bore 2114 of the compressor body 211 and is placed in such a way that its diffuser 211 side face is in the same plane as the wall of the volute 2112 at this level.
- the shaft 214 is rotationally driven by drive means, not shown, at a speed which can be higher than 200,000 revolutions per minute.
- a gas flow is established between the gas inlet 2110 and the outlet 2113 .
- the speed of the gas at the outlet of the wheel, at the second edge of the blades, has a tangential component generally higher than the radial component.
- the relative speed between the ring and the gas flow is essentially the radial component and is therefore much lower than the speed of the gas flow against the fixed wall of the diffuser according to prior art. It can be seen that the losses related to the friction along the wall rendered rotative are substantially divided by two in relation to the fixed wall case, or even more in certain operating modes where the gas speed has a dominant tangential component.
- a turbocompressor comprises a turbine 30 and a compressor 31 in compliance with the invention.
- the wheels 302 , 312 of the turbine 30 and of the compressor 31 are mounted on the same shaft 32 , which is rotatively mounted by means of a bearing 33 placed between the body of the compressor 311 and the body of the turbine 301 .
- the bearing 33 is formed, in this example, by two ball bearings.
- the turbine 30 includes a turbine body 301 and a rotating part rotatively mounted on the turbine body 301 around the wheel axis A.
- the rotating part includes a turbine wheel 302 which comprises a hub 3020 and a set of blades 3021 attached to the hub 3020 .
- the turbine body 301 includes a turbine volute 3012 around the turbine wheel 302 .
- the volute 3012 comprises an intake 3013 which extends substantially in a tangential direction and leads to a nozzle 3011 placed on the periphery of the turbine wheel 302 .
- the turbine body 301 also comprises an axial opening placed opposite the hub 3020 and which acts as an outlet 3010 for the gases.
- the turbine body 301 comprises a guide wall 3014 opposite the blades 3021 of the turbine wheel 302 in such a way as to leave only a small space between the blades 3021 and the turbine body 301 .
- the purpose of the nozzle 3011 is to channel the gases which enter by the intake 3013 into the turbine volute 3012 to be directed to the blades 3021 of the turbine wheel 302 with an appropriate direction and speed.
- the shape of the blades 3021 is designed so that the gases are decompressed by passing through the turbine wheel 302 and restore energy to it.
- the turbine wheel 302 includes a ring 30201 extending from the hub 3020 beyond the blade-enveloping cylinder C′.
- the ring 30201 forms one of the walls of the nozzle 3011 .
- the wheel 402 of a compressor also comprises a cowl 4022 attached to the blades 4021 and channelling the gases between the cowl and the hub 4020 .
- the cowl 4022 forms one piece with the blades 4021 but can be attached by other means.
- the cowl is extended by a second ring 40220 opposite the ring 40201 which extends the hub.
- the diffuser 4011 comprises two walls which delimit it and are rotative to limit the friction losses.
- the invention is not limited to the embodiments described above which are provided only as an example.
- the ring could equip only the cowl, the machines can circulate a liquid instead of a gaseous fluid.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Ceramic Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Supercharger (AREA)
Abstract
Description
- This application is a National Phase entry of PCT Application No. PCT/FR2013/052934, filed Dec. 4, 2013, which claims priority from FR Application No. 1261612, filed Dec. 4, 2012, the disclosures of which are hereby incorporated by referenced herein in their entirety.
- The invention relates to a rotating machine such as a compressor of a centrifugal type for a gaseous fluid or a pump for a liquid. In particular, it concerns the diffusion system of such a machine.
- Rotating machines such as a compressor of a centrifugal type or a pump are widely used in industry, in particular in the field of combustion engines. In particular, a turbine coupled on the same shaft to a compressor is used to form a turbocompressor. The turbine is supplied by the exhaust gases of an engine and drives the compressor which compresses the fresh air to supercharge the engine. Certain compressors are driven by an electric motor.
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FIGS. 6 and 7 show acentrifugal compressor 11 according to the prior art. Thecompressor 11 includes acompressor body 111 and a rotating part rotatively mounted in thecompressor body 111 around a wheel axis A. The rotating part comprises acompressor wheel 112 mounted on a rotatingshaft 114 in abearing 113 of thecompressor body 111. Thecompressor wheel 112 comprises ahub 1120 and a set ofblades 1121 attached to the hub. Thecompressor body 111 also comprises an axial opening placed opposite thehub 1120 and which comprises anintake 1110. Thecompressor body 111 comprises avolute 1112 around thecompressor wheel 112. Thevolute 1112 comprises a peripheral opening placed on the periphery of thecompressor wheel 112 and leads to anoutlet 1113 which extends substantially in a direction tangent to thecompressor wheel 112. The peripheral opening is called adiffuser 1111. Theblades 1121 comprise afirst edge 11211, called a leading edge, opposite theaxial opening 1110 and asecond edge 11212, called a trailing edge, opposite thediffuser 1111 so that the gases circulate from theaxial opening 1110 to thediffuser 1111 being driven by thecompressor wheel 112. The shape of theblades 1121 is designed so that the gases receive mechanical energy by thecompressor wheel 112, that principally being accelerated, the kinetic energy thus obtained then being converted into pressure in the volute. - Certain compressor wheel versions are cowled and comprise for this purpose a cowl attached to the blades, the section of which mates with that of the guide wall.
- Machines of the same type can be used for a fluid no longer gaseous, but liquid. In this case, the term pump is used instead of compressor.
- The speed of the fluid at the diffuser is high such that the friction losses along the diffuser wall related to the viscosity of the fluid are high. At this level, the tangential component of the speed of the fluid is very high and often predominant. The aim of the invention is to reduce these friction losses.
- With these targets in mind, the object of the invention is a centrifugal gas compressor or pump comprising a body, a wheel rotatively mounted in the body around a wheel axis, the wheel comprising a hub, a set of blades attached to the hub, the body comprising a diffuser placed on the periphery of the wheel and a fluid intake placed opposite the hub, the blades comprising a first edge opposite the axial opening and the second edge opposite the diffuser so that a fluid circulates from the intake to the diffuser, the second edges being located inside a blade-enveloping cylinder centered on the wheel axis, the wheel comprising at least one ring attached to the wheel and which extends radially beyond the blade-enveloping cylinder to form a diffuser wall.
- A result of the ring is that the diffuser zone comprises a wall which rotates at the same speed as that of the wheel. The difference between the average speed of the fluid and this wall is greatly reduced which allows the friction losses at this level to be greatly reduced. Thus, less losses on the kinetic energy of the fluid are obtained in the diffuser and, therefore, on the energy supplied in the form of pressure at the volute outlet. It can also be seen that the wheel is submitted to pressure forces the resultant of which is an axial force. In particular, the pressure which is presented on the face of the wheel which carries the blades is in general very different to the one opposed to it. The modification in the size of this face which results from adding the ring beyond the first edge of the blades also modifies this result. Thus, it is possible to adjust this result, in particular in the case of a turbocompressor where the turbine wheel and the compressor wheel exert axial forces in opposite directions.
- In a particular manner, the ring is inserted with play in a bore of the compressor body and is placed in such a way that its diffuser side face is in the same plane as the wall of the volute at this level. The gas flow which leaves the ring continues to be guided without discontinuity by the wall of the volute thus avoiding the creation of load losses.
- According to an additional characteristic, the body comprises a volute around the diffuser.
- According to an embodiment, the ring extends from the hub.
- In a particular embodiment, the wheel comprises a cowl attached to the blades. According to an improvement, the ring extends from the cowl. Thus, the diffuser zone comprises a wall possibly additional which rotates at the same speed as that of the wheel. This ring can be alone. In combination with the ring in the extension of the hub, the flow of the fluid is entirely channelled in this zone by the walls which substantially move at the same speed as the flow of the fluid, thus greatly reducing the friction losses. The balance of the pressure forces can be exerted in a direction opposite to that of the configuration with the ring in the extension of the hub.
- In a particular embodiment, the cowl and the blades are in one piece.
- According to another arrangement, the ring and the wheel in the extension of the hub are in one piece. Thus the wheel is provided with high mechanical strength. Manufacture requires only a few modifications in the manufacturing technique.
- The invention will be better understood and other features and advantages of the invention will become apparent on reading the following description, the description making reference to the appended drawings:
-
FIG. 1 is a longitudinal cross-sectional view of a machine fulfilling the function of compressor in accordance with a first embodiment of the invention; -
FIG. 2 is a detailed view taken along the lines II ofFIG. 1 ; -
FIG. 3 is a longitudinal cross-sectional view of a turbocompressor comprising a turbine and a compressor in accordance with the invention; -
FIGS. 4 and 5 are views similar toFIG. 2 of a compressor wheel, but according to a third and a fourth embodiment of the invention; -
FIG. 6 is a longitudinal cross-sectional view through line VI-VI ofFIG. 7 of a centrifugal compressor according to the prior art; and -
FIG. 7 is a view of the compressor, the body being shown by a cross-sectional view through line VII-VII ofFIG. 6 . - A
compressor 21 in accordance with a first embodiment of the invention, such as shown onFIGS. 1 and 2 , includes acompressor body 211 and a rotating part rotatively mounted in thecompressor body 211 around a wheel axis A. The rotating part includes acompressor wheel 212 mounted on a rotatingshaft 214 on a bearing of thecompressor body 211. Thecompressor wheel 212 comprises ahub 2120 and a set ofblades 2121 attached to thehub 2120. Thecompressor body 211 also includes an axial opening placed opposite thehub 2120 and which comprises anintake 2110. Thecompressor body 211 includes avolute 2112 around thecompressor wheel 212. Thevolute 2112 includes a peripheral opening forming a diffuser 2111, placed on the periphery of thecompressor wheel 212 and leading to anoutlet 2113 which substantially extends in a direction tangential to thecompressor wheel 212. Theblades 2121 include afirst edge 21211 opposite the gas intake and asecond edge 21212 opposite the diffuser 2111. The gases circulate from theintake 2110 to the diffuser 2111 being driven by thecompressor wheel 212. The shape of theblades 2121 is designed so that the gases accelerate when passing through thecompressor wheel 212 by means of the energy supplied by the wheel. The second edges 21212 extend substantially parallel to the wheel axis A and are contained in a virtual cylinder called blade-enveloping cylinder C. - In compliance with the invention, the
hub 2120 extends beyond the fictive cylinder C in the form of aring 21201. Thering 21201 thus delimits the diffuser 2111 on one of its sides. Thering 21201 is inserted with play in abore 2114 of thecompressor body 211 and is placed in such a way that itsdiffuser 211 side face is in the same plane as the wall of thevolute 2112 at this level. - In operation, the
shaft 214 is rotationally driven by drive means, not shown, at a speed which can be higher than 200,000 revolutions per minute. A gas flow is established between thegas inlet 2110 and theoutlet 2113. The speed of the gas at the outlet of the wheel, at the second edge of the blades, has a tangential component generally higher than the radial component. The relative speed between the ring and the gas flow is essentially the radial component and is therefore much lower than the speed of the gas flow against the fixed wall of the diffuser according to prior art. It can be seen that the losses related to the friction along the wall rendered rotative are substantially divided by two in relation to the fixed wall case, or even more in certain operating modes where the gas speed has a dominant tangential component. - In the embodiment shown on
FIG. 3 , a turbocompressor comprises a turbine 30 and acompressor 31 in compliance with the invention. Thewheels compressor 31 are mounted on thesame shaft 32, which is rotatively mounted by means of abearing 33 placed between the body of thecompressor 311 and the body of theturbine 301. Thebearing 33 is formed, in this example, by two ball bearings. - The turbine 30 includes a
turbine body 301 and a rotating part rotatively mounted on theturbine body 301 around the wheel axis A. The rotating part includes aturbine wheel 302 which comprises ahub 3020 and a set ofblades 3021 attached to thehub 3020. Theturbine body 301 includes aturbine volute 3012 around theturbine wheel 302. Thevolute 3012 comprises anintake 3013 which extends substantially in a tangential direction and leads to anozzle 3011 placed on the periphery of theturbine wheel 302. Theturbine body 301 also comprises an axial opening placed opposite thehub 3020 and which acts as anoutlet 3010 for the gases. Theturbine body 301 comprises a guide wall 3014 opposite theblades 3021 of theturbine wheel 302 in such a way as to leave only a small space between theblades 3021 and theturbine body 301. The purpose of thenozzle 3011 is to channel the gases which enter by theintake 3013 into theturbine volute 3012 to be directed to theblades 3021 of theturbine wheel 302 with an appropriate direction and speed. The shape of theblades 3021 is designed so that the gases are decompressed by passing through theturbine wheel 302 and restore energy to it. - In the same way as for
compressor 31, theturbine wheel 302 includes aring 30201 extending from thehub 3020 beyond the blade-enveloping cylinder C′. Thering 30201 forms one of the walls of thenozzle 3011. - According to a third embodiment, shown on
FIG. 4 , thewheel 402 of a compressor also comprises acowl 4022 attached to theblades 4021 and channelling the gases between the cowl and thehub 4020. Thecowl 4022 forms one piece with theblades 4021 but can be attached by other means. In compliance with the invention, the cowl is extended by asecond ring 40220 opposite thering 40201 which extends the hub. Thus, thediffuser 4011 comprises two walls which delimit it and are rotative to limit the friction losses. - According to a fourth embodiment, shown on
FIG. 5 , thewheel 502 of a compressor also includes a fixedcowl 5022 on theblades 5021, but only in the most peripheral part of thewheel 502. Thecowl 5022 forms one piece with theblades 5021, but can be attached by other means. In compliance with the invention, the cowl is extended by asecond ring 50220, substantially parallel to thering 50201 which extends the hub. Thus, thediffuser 5011 comprises two walls which delimit it and which are rotative to limit the friction losses. - The invention is not limited to the embodiments described above which are provided only as an example. For instead, the ring could equip only the cowl, the machines can circulate a liquid instead of a gaseous fluid.
Claims (8)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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FR1261612 | 2012-12-04 | ||
FR1261612A FR2998920B1 (en) | 2012-12-04 | 2012-12-04 | ROTATING MACHINE SUCH AS A TURBINE OR A COMPRESSOR. |
PCT/FR2013/052934 WO2014096604A1 (en) | 2012-12-04 | 2013-12-04 | Centrifugal gas compressor or pump comprising a toothed ring and a cowl |
Publications (1)
Publication Number | Publication Date |
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US20150316071A1 true US20150316071A1 (en) | 2015-11-05 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US14/649,882 Abandoned US20150316071A1 (en) | 2012-12-04 | 2013-12-04 | Centrifugal gas compressor or pump comprising a toothed ring and a cowl |
Country Status (6)
Country | Link |
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US (1) | US20150316071A1 (en) |
EP (1) | EP2929161B1 (en) |
JP (1) | JP2015537156A (en) |
ES (1) | ES2763546T3 (en) |
FR (1) | FR2998920B1 (en) |
WO (1) | WO2014096604A1 (en) |
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ITUB20150308A1 (en) * | 2015-05-04 | 2016-11-04 | Ebara Corp | IMPELLER STRUCTURE, ESPECIALLY FOR CENTRIFUGAL PUMPS |
FR3060672A1 (en) * | 2016-12-21 | 2018-06-22 | Valeo Systemes De Controle Moteur | ELECTRICAL COMPRESSOR WITH IMPROVED WHEEL |
CN113775533B (en) * | 2021-09-15 | 2024-02-20 | 浙江理工大学 | Turbopump device for rocket engine |
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US20100196163A1 (en) * | 2009-02-03 | 2010-08-05 | Yagi Nobuyori | Method of manufacturing impeller, impeller, and compressor having impeller |
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JPS5155816A (en) * | 1974-11-13 | 1976-05-17 | Komatsu Mfg Co Ltd | KAKYUKI |
JPH1068398A (en) * | 1996-08-28 | 1998-03-10 | Maruyama Mfg Co Ltd | Centrifugal blower |
DE10226696A1 (en) * | 2002-06-15 | 2003-12-24 | Daimler Chrysler Ag | Exhaust gas turbocharger for internal combustion engine has turbine wheel of exhaust gas turbine provided with shroud ring radially encompassing turbine blades, and tunnel-form flow path is formed between adjacent turbine blades |
DE102009004881A1 (en) * | 2009-01-16 | 2010-07-29 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Exhaust gas turbocharger for a motor vehicle, comprises shaft bearing turbine wheel and compressor impeller, where the turbine wheel, the compressor impeller and the shaft are formed as single-piece metallic powder injection molded part |
DE102009060056A1 (en) * | 2009-12-22 | 2011-06-30 | BorgWarner Inc., Mich. | Wave bond of an exhaust gas turbocharger |
DE102010026909A1 (en) * | 2010-03-19 | 2011-09-22 | Daimler Ag | Charging device for a fuel cell |
JP2011208558A (en) * | 2010-03-29 | 2011-10-20 | Mitsubishi Heavy Ind Ltd | Centrifugal fluid machine |
DE102010040823A1 (en) * | 2010-09-15 | 2012-03-15 | Robert Bosch Gmbh | Turbo supercharger for use in e.g. internal combustion engine, of motor car, has turbine wheel spine whose outer diameter is greater than outer diameter of turbine blade ring to partially compensate occurrence of axial forces |
WO2012061545A2 (en) * | 2010-11-05 | 2012-05-10 | Borgwarner Inc. | Simplified variable geometry turbocharger with increased flow range |
US8764376B2 (en) * | 2011-05-16 | 2014-07-01 | Honeywell International Inc. | Diffuser divider |
DE202012004682U1 (en) * | 2012-05-04 | 2012-05-24 | Borg Warner Inc. | turbocharger |
-
2012
- 2012-12-04 FR FR1261612A patent/FR2998920B1/en active Active
-
2013
- 2013-12-04 ES ES13815041T patent/ES2763546T3/en active Active
- 2013-12-04 JP JP2015546079A patent/JP2015537156A/en active Pending
- 2013-12-04 EP EP13815041.2A patent/EP2929161B1/en active Active
- 2013-12-04 US US14/649,882 patent/US20150316071A1/en not_active Abandoned
- 2013-12-04 WO PCT/FR2013/052934 patent/WO2014096604A1/en active Application Filing
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US4257744A (en) * | 1979-03-21 | 1981-03-24 | Westinghouse Electric Corp. | Impeller and shaft assembly for high speed gas compressor |
US5984629A (en) * | 1993-09-25 | 1999-11-16 | Ksb Aktiengesellscaft | Turbo-machine with reduced abrasive wear |
US5902546A (en) * | 1996-07-10 | 1999-05-11 | Mitsubishi Heavy Industries, Ltd. | Aluminum alloy impeller and manufacturing method of the same |
US20070059179A1 (en) * | 2005-09-13 | 2007-03-15 | Ingersoll-Rand Company | Impeller for a centrifugal compressor |
US20080118341A1 (en) * | 2006-11-16 | 2008-05-22 | Honeywell International Inc. | Wide flow compressor with diffuser bypass |
US20110200439A1 (en) * | 2008-10-23 | 2011-08-18 | Akihiro Nakaniwa | Impeller, compressor, and method for producing impeller |
US20100196163A1 (en) * | 2009-02-03 | 2010-08-05 | Yagi Nobuyori | Method of manufacturing impeller, impeller, and compressor having impeller |
US20120051885A1 (en) * | 2009-05-11 | 2012-03-01 | Francois Danguy | Double exhaust centrifugal pump |
Also Published As
Publication number | Publication date |
---|---|
EP2929161B1 (en) | 2019-10-02 |
FR2998920B1 (en) | 2018-07-27 |
JP2015537156A (en) | 2015-12-24 |
EP2929161A1 (en) | 2015-10-14 |
FR2998920A1 (en) | 2014-06-06 |
WO2014096604A1 (en) | 2014-06-26 |
ES2763546T3 (en) | 2020-05-29 |
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