WO2001029425A1 - Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines - Google Patents
Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines Download PDFInfo
- Publication number
- WO2001029425A1 WO2001029425A1 PCT/CH1999/000496 CH9900496W WO0129425A1 WO 2001029425 A1 WO2001029425 A1 WO 2001029425A1 CH 9900496 W CH9900496 W CH 9900496W WO 0129425 A1 WO0129425 A1 WO 0129425A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cooling fluid
- cooling
- stator part
- radial gap
- radial
- Prior art date
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
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
-
- 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
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
-
- 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
Definitions
- the invention relates to a method and a device for cooling the flow in radial gaps formed between rotors and stators of turbomachinery, according to the preamble of claim 1 and the preamble of claim 7, but in particular for cooling the flow in the radial gap between the compressor wheel and the housing of a radial compressor.
- non-contact seals especially labyrinth seals
- turbomachinery construction To seal rotating systems, non-contact seals, especially labyrinth seals, are widely used in turbomachinery construction.
- a high level of friction occurs as a result of the flow boundary layers that form. This leads to heating of the fluid in the separation gap and thus also to heating of the components surrounding the separation gap.
- the high material temperatures reduce the lifespan of the corresponding components.
- Air cooling for radial compressors with a sealing geometry on the rear side of the compressor wheel is known from EP 0 518 027 B1. This is between the individual sealing elements, an additional annular space is formed on the housing wall side of the radial compressor. A cold gas is introduced into this annular space, which has a higher pressure than the pressure prevailing at the outlet of the compressor wheel. The air supplied acts as impingement cooling. It divides in the sealing area and flows mainly radially inwards and outwards. This is also intended to achieve a blocking effect against the flow of hot compressor air from the outlet of the compressor wheel.
- the cooling effect that can be achieved in this way is limited due to several factors.
- the air injection leads to an increase in pressure and thrust, which increases the bearing load.
- the temperature of the available air is also a limiting element. Particularly in the case of high-speed compressor wheels and high pressure ratios, as are common in modern turbocharger construction, situations can arise in which this type of cooling is not sufficient.
- indirect cooling of the rear wall of the compressor wheel or of the medium flowing through the separation gap is also known from DE 196 52 754 A1.
- a supply and distribution device connected to the lubricating oil system of the turbocharger is arranged on or in the rear part of the housing part which forms the separating gap.
- the oil used for bearing lubrication serves as the cooling medium, for which purpose the lubricating oil circuit of the turbocharger is tapped.
- a disadvantage of this cooling is the relatively high oil requirement and the additional amount of heat to be dissipated by the oil cooler. This leads to an increased construction volume of the cooler.
- the cooling effect that can be achieved with indirect cooling is also limited, for which, in addition to the temperature of the cooling fluids that can be used in practice, the small construction volume available can be identified as the cause. Presentation of the invention
- the invention tries to avoid all these disadvantages. It is the object of the invention to provide a method for cooling the flow in radial gaps formed between rotors and stators of turbomachines which is improved with regard to its cooling effect. In addition, a simple, inexpensive and robust device for implementing the method is to be specified.
- both a stator part adjacent to the radial gap is acted on by a first cooling fluid and a second, gaseous cooling fluid is introduced into the radial gap.
- At least one recess is formed in the interior of the stator part adjacent to the radial gap or at least one cavity is arranged on the stator part.
- the recess or the cavity is connected both to a supply line and to a discharge line for the first cooling fluid.
- at least one feed channel and a discharge device for the second cooling fluid are arranged on the radial gap.
- Water is particularly advantageously used as the first cooling fluid and air as the second cooling fluid.
- Water has a slightly higher density than the known lubricating oils and an approximately twice as large specific heat capacity. Since it has a cooling medium to be dissipated heat flow is proportional to the product of density and specific heat capacity, there is a clear advantage when using water as the first cooling fluid compared to oil cooling. With the same mass flow and temperature of the water, a larger amount of heat can thus be extracted from the medium flowing through the radial gap via the stator part to be cooled. The cooling effect on the areas of the rotor adjacent to the radial gap is therefore also greater. Conversely, a smaller mass flow of cooling water is required to dissipate the same amount of heat compared to lubricating oil, as a result of which the supply and discharge device for the cooling fluid can be dimensioned correspondingly smaller.
- air as the second cooling fluid proves to be particularly advantageous because it is available in sufficient quantities, with sufficient pressure and at a suitably low temperature both in the environment and in the turbomachine itself.
- the first cooling fluid In a system consisting of an internal combustion engine, a charge air cooler and an exhaust gas turbocharger, either fresh water from outside the system or advantageously water present in the system is used as the first cooling fluid.
- the cooling water located in a cooling water circuit of the charge air cooler is used, which is branched off upstream of the charge air cooler.
- the fixed stator part is a housing part ei ⁇ nes radial compressor, which delimits the radial gap to the rotor, that is, to the rotating compressor wheel of a turbocharger.
- oil is used as the first cooling fluid, it can advantageously be branched off from the lubricating oil system, which is already present in the bearing housing of the turbomachine. In this way, a relatively simple and therefore inexpensive device can be created.
- the first cooling fluid is a gaseous medium, it can be used for both direct and indirect cooling.
- first and / or second cooling fluid When using helium or gases from low-temperature fluids, such as liquid nitrogen, carbon tetrachloride and benzin nitride, as the first and / or second cooling fluid, a particularly good cooling effect can be achieved.
- low-temperature fluids such as liquid nitrogen, carbon tetrachloride and benzin nitride
- Figure 1 is a schematic representation of the exhaust gas turbocharger connected to the internal combustion engine.
- FIG. 1 shows a schematic representation of an exhaust gas turbocharger 2 that interacts with an internal combustion engine 1 designed as a diesel engine.
- the latter consists of a radial compressor 3 and an exhaust gas turbine 4, which have a common shaft 5.
- the radial compressor 3 is connected to the combustion air via a charge air line 6 and the exhaust gas turbine 4 via an exhaust line 7 engine 1 connected.
- a charge air cooler 8 is arranged in the charge air line 6, ie between the radial compressor 3 and the internal combustion engine 1.
- the charge air cooler 8 has a cooling water circuit 9 with a supply or discharge, not shown.
- the radial compressor 3 is equipped with a compressor housing 10, in which a rotor 11 designed as a compressor wheel and connected to the shaft 5 is arranged.
- the compressor wheel 11 has a hub 13 with a plurality of rotor blades 12.
- a flow channel 14 is formed between the hub 13 and the compressor housing 10. Downstream of the blades 12, a radially arranged, bladed diffuser 15 adjoins the flow channel 14, which in turn opens into a spiral 16 of the radial compressor 3.
- the compressor housing 10 mainly consists of an air inlet housing 17, an air outlet housing 18, a diffuser plate 19 and a stator part 20 designed as an intermediate wall to a bearing housing 21 of the exhaust gas turbocharger 2 (FIG. 2).
- the hub 13 has a rear wall 22 on the turbine side and a fastening sleeve 23 for the shaft 5.
- the fastening sleeve 23 is received by the intermediate wall 20 of the compressor housing 10.
- another suitable compressor wheel / shaft connection can also be selected. It is also possible to use an unbladed diffuser.
- a circumferential recess 26 is formed in the intermediate wall 20 of the compressor housing 10 and is connected to both a supply line and a discharge line 27, 28 for a first cooling fluid 29.
- the intermediate wall 20 on the compressor wheel side of the recess 26 is made as thin as possible.
- a corresponding core is cast in during the manufacture of the intermediate wall 20, which must then be removed again.
- a thin-walled tube that is closed at both ends can also be cast into the intermediate wall 20, the interior of which then forms the recess 26 (not shown).
- the compressor wheel 11 When the exhaust gas turbocharger 2 is operating, the compressor wheel 11 sucks in ambient air as the working medium 31, which, as a main flow 32, enters the spiral 16 via the flow channel 14 and the diffuser 15, compresses there further and finally via the charge air line 6 for charging the exhaust gas turbocharger 2 connected internal combustion engine 1 is used.
- the working medium 31 heated during the compression process is cooled beforehand in the charge air cooler 8.
- the main flow 32 of the working medium 31 heated in the radial compressor 3 also acts on the radial gap 24 as a leakage flow 33, as a result of which the compressor wheel 11 is additionally heated.
- Cooling water which is branched off from the cooling water circuit 9 of the charge air cooler 8 is introduced as cooling fluid 29 into the recess 26 of the intermediate wall 20 which is arranged directly adjacent to this critical area. There is thus indirect cooling of the leakage flow 33 located in the radial gap 24 and thus also of the compressor wheel 11.
- the cooling fluid 29 is branched off upstream of the charge air cooler 8, so that effective cooling can be achieved with the relatively cold cooling water.
- the now heated Kuhlfluid is after the cooling ⁇ process stream 29 via the drain line 28 ⁇ fed back into the cooling water circuit 9 from the charge air cooler 8 (Fig. 1).
- Na ⁇ Moslich can take place in the system of the internal combustion engine 1, the charge air cooler 8 and Exhaust gas turbocharger 2 existing cooling water and fresh water from outside the system as cooling fluid 29 (not shown).
- direct cooling of the leakage flow 33 is provided.
- a plurality of feed channels 40 for a second cooling fluid 41 opening tangentially to the rear wall 22 of the compressor wheel 11 and arranged in the radial gap 24 are arranged so as to penetrate both the bearing housing 21 and the diffuser plate 19 (FIG. 2).
- the supply channels 40 are connected downstream of the charge air cooler 8 to the charge air line 6, so that cooled charge air is used as the second cooling fluid 41 (FIG. 1).
- the second cooling fluid 41 can also be introduced into the radial gap at a different point (not shown).
- a pure film cooling of the entire rear wall 22 of the compressor wheel 11 is achieved by the tangential introduction of the second cooling fluid 41.
- the second cooling fluid 41 replaces the hot leakage flow 33, so that the boundary layer which forms on the rear wall 22 of the compressor wheel 11 is formed from the start, above all, by the cooled charge air.
- the subsequent discharge of the second cooling fluid 41 takes place via a discharge device 42 which engages in the intermediate wall 20 of the compressor housing 10.
- cooling media such as helium or gases from low-temperature fluids (e.g. liquid nitrogen, carbon tetrachloride, benzene nitride, etc.) can also be used as the first and second cooling fluids 29, 41.
- low-temperature fluids e.g. liquid nitrogen, carbon tetrachloride, benzene nitride, etc.
- oil is used as the first cooling fluid 29, it can be supplied externally or advantageously branched off from the lubricating oil system which is already present in the bearing housing 21 of the exhaust gas turbocharger 2 (not shown). To this A relatively simple and therefore inexpensive supply of this likewise suitable cooling fluid is possible.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Supercharger (AREA)
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020027003417A KR100637643B1 (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
AU60757/99A AU6075799A (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
JP2001531986A JP2003515690A (en) | 1999-10-20 | 1999-10-20 | Method and apparatus for cooling flow in a radial gap formed between a rotor and a stator of a turbine machine |
EP99947180A EP1222399B1 (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
PCT/CH1999/000496 WO2001029425A1 (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
CNB998169617A CN1258648C (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling in the radial gaps formed between the rotors and stators of turbomachines |
DE59906615T DE59906615D1 (en) | 1999-10-20 | 1999-10-20 | METHOD AND DEVICE FOR COOLING THE FLOW IN THE RADIAL COLUMNS DESIGNED BETWEEN ROTORS AND STATORS OF TURBO MACHINES |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CH1999/000496 WO2001029425A1 (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001029425A1 true WO2001029425A1 (en) | 2001-04-26 |
Family
ID=4551726
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CH1999/000496 WO2001029425A1 (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
Country Status (7)
Country | Link |
---|---|
EP (1) | EP1222399B1 (en) |
JP (1) | JP2003515690A (en) |
KR (1) | KR100637643B1 (en) |
CN (1) | CN1258648C (en) |
AU (1) | AU6075799A (en) |
DE (1) | DE59906615D1 (en) |
WO (1) | WO2001029425A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2067999A1 (en) | 2007-12-06 | 2009-06-10 | Napier Turbochargers Limited | Liquid cooled turbocharger impeller and method for cooling an impeller |
EP2090788A1 (en) | 2008-02-14 | 2009-08-19 | Napier Turbochargers Limited | Impeller and turbocharger |
DE102007001487B4 (en) * | 2007-01-10 | 2015-07-16 | Caterpillar Energy Solutions Gmbh | Method and device for compressor wheel cooling of a compressor |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005018771B4 (en) * | 2005-04-22 | 2015-06-18 | Man Diesel & Turbo Se | Internal combustion engine |
JP6015843B2 (en) * | 2013-02-21 | 2016-10-26 | トヨタ自動車株式会社 | Cooling device for a supercharger of an internal combustion engine equipped with a blow-by gas recirculation device |
CN104595247A (en) * | 2015-01-05 | 2015-05-06 | 珠海格力电器股份有限公司 | Centrifugal compressor with recooling structure |
CN104595246A (en) * | 2015-01-05 | 2015-05-06 | 珠海格力电器股份有限公司 | Centrifugal compressor with recooling structure |
CN106286338A (en) * | 2015-06-02 | 2017-01-04 | 上海优耐特斯压缩机有限公司 | The structure that the centrifugal compressor leakage air using high-speed electric expreess locomotive is cooled down |
CN111720331B (en) * | 2020-05-22 | 2022-08-09 | 洛阳瑞华新能源技术发展有限公司 | Single-stage centrifugal pump with liquid collecting and draining flow channel and flow dividing partition plate having at least 2 liquid draining ports |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB191114702A (en) * | 1910-06-22 | 1912-07-22 | Hugo Junkers | Improvements in or relating to Centrifugal or Turbo-compressors. |
US2384251A (en) * | 1943-01-14 | 1945-09-04 | Wright Aeronautical Corp | Liquid cooled supercharger |
DE968742C (en) * | 1944-09-22 | 1958-03-27 | Daimler Benz Ag | Multi-stage radial blower, preferably loading blower for aircraft engines |
US3966351A (en) * | 1974-05-15 | 1976-06-29 | Robert Stanley Sproule | Drag reduction system in shrouded turbo machine |
EP0518027A1 (en) * | 1991-06-14 | 1992-12-16 | Mitsubishi Jukogyo Kabushiki Kaisha | Centrifugal compressor |
DE19548852A1 (en) | 1995-12-27 | 1997-07-03 | Asea Brown Boveri | Radial compressor for exhaust gas turbo-supercharger |
DE19652754A1 (en) | 1996-12-18 | 1998-06-25 | Asea Brown Boveri | Exhaust gas supercharger |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61112737A (en) * | 1984-11-08 | 1986-05-30 | Mitsubishi Heavy Ind Ltd | Supercharger |
JPS6434435A (en) * | 1987-07-06 | 1989-02-03 | Agency Ind Science Techn | Temperature sensitive gel and manufacture thereof |
JPH0333431A (en) * | 1989-06-30 | 1991-02-13 | Hitachi Ltd | Supercharger for internal combustion engine |
JP2924363B2 (en) * | 1991-09-18 | 1999-07-26 | 石川島播磨重工業株式会社 | Water-cooled bearing housing structure for turbocharger |
JP2918773B2 (en) * | 1993-11-08 | 1999-07-12 | 株式会社日立製作所 | Centrifugal compressor |
JPH07208189A (en) * | 1994-01-10 | 1995-08-08 | Hino Motors Ltd | Supercharger cooling device of engine |
JP3606293B2 (en) * | 1996-02-14 | 2005-01-05 | 石川島播磨重工業株式会社 | Exhaust turbine turbocharger |
-
1999
- 1999-10-20 DE DE59906615T patent/DE59906615D1/en not_active Expired - Fee Related
- 1999-10-20 EP EP99947180A patent/EP1222399B1/en not_active Expired - Lifetime
- 1999-10-20 AU AU60757/99A patent/AU6075799A/en not_active Abandoned
- 1999-10-20 CN CNB998169617A patent/CN1258648C/en not_active Expired - Fee Related
- 1999-10-20 KR KR1020027003417A patent/KR100637643B1/en not_active IP Right Cessation
- 1999-10-20 JP JP2001531986A patent/JP2003515690A/en active Pending
- 1999-10-20 WO PCT/CH1999/000496 patent/WO2001029425A1/en active IP Right Grant
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB191114702A (en) * | 1910-06-22 | 1912-07-22 | Hugo Junkers | Improvements in or relating to Centrifugal or Turbo-compressors. |
US2384251A (en) * | 1943-01-14 | 1945-09-04 | Wright Aeronautical Corp | Liquid cooled supercharger |
DE968742C (en) * | 1944-09-22 | 1958-03-27 | Daimler Benz Ag | Multi-stage radial blower, preferably loading blower for aircraft engines |
US3966351A (en) * | 1974-05-15 | 1976-06-29 | Robert Stanley Sproule | Drag reduction system in shrouded turbo machine |
EP0518027A1 (en) * | 1991-06-14 | 1992-12-16 | Mitsubishi Jukogyo Kabushiki Kaisha | Centrifugal compressor |
EP0518027B1 (en) | 1991-06-14 | 1995-07-05 | Mitsubishi Jukogyo Kabushiki Kaisha | Centrifugal compressor |
DE19548852A1 (en) | 1995-12-27 | 1997-07-03 | Asea Brown Boveri | Radial compressor for exhaust gas turbo-supercharger |
DE19652754A1 (en) | 1996-12-18 | 1998-06-25 | Asea Brown Boveri | Exhaust gas supercharger |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007001487B4 (en) * | 2007-01-10 | 2015-07-16 | Caterpillar Energy Solutions Gmbh | Method and device for compressor wheel cooling of a compressor |
EP2067999A1 (en) | 2007-12-06 | 2009-06-10 | Napier Turbochargers Limited | Liquid cooled turbocharger impeller and method for cooling an impeller |
WO2009071910A1 (en) * | 2007-12-06 | 2009-06-11 | Napier Turbochargers Limited | Liquid cooled turbocharger impeller and method for cooling an impeller |
EP2090788A1 (en) | 2008-02-14 | 2009-08-19 | Napier Turbochargers Limited | Impeller and turbocharger |
Also Published As
Publication number | Publication date |
---|---|
DE59906615D1 (en) | 2003-09-18 |
CN1375041A (en) | 2002-10-16 |
EP1222399B1 (en) | 2003-08-13 |
CN1258648C (en) | 2006-06-07 |
KR100637643B1 (en) | 2006-10-23 |
AU6075799A (en) | 2001-04-30 |
EP1222399A1 (en) | 2002-07-17 |
JP2003515690A (en) | 2003-05-07 |
KR20020041437A (en) | 2002-06-01 |
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