WO1994027050A1 - Rotary screw compressor with seal means - Google Patents
Rotary screw compressor with seal means Download PDFInfo
- Publication number
- WO1994027050A1 WO1994027050A1 PCT/SE1994/000087 SE9400087W WO9427050A1 WO 1994027050 A1 WO1994027050 A1 WO 1994027050A1 SE 9400087 W SE9400087 W SE 9400087W WO 9427050 A1 WO9427050 A1 WO 9427050A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- compressor
- seal
- pressure
- cavity
- seal means
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C27/009—Shaft sealings specially adapted for pumps
Definitions
- the present invention relates to a rotary screw compressor of the kind specified in the preamble of claim 1.
- US-A 3 913 346 discloses a refrigeration compressor of the twin-screw type, in which the drive motor is internally cooled by liquid refrigerant of delivery pressure supplied from the condenser, and the liquid and evaporated gas is then drained to a closed working chamber in the compressor working space.
- the loss in compressor efficiency which is entailed with that system can be avoided by providing a pump for raising the pressure of the liquid before entering the motor space, so that the liquid-gas-mixture leaving the motor can be drained directly to the delivery line of the compressor.
- US-A 4 669 279 discloses such a system in connection with a centrifugal compressor.
- the object of the present invention is to attain a compressor with a seal between the low pressure end of the compressor working space and a high pressure cavity at the other side of the low pressure end wall, which seal should be effective as well as economical in operation.
- a compressor of the kind in question has the features specified in the characterizing portion of claim 1.
- Fig. 1 is a schematic illustration of a refrigeration system with a compressor according to the invention.
- Fig. 2 is a section through the seal means in the low pressure end section of the compressor in fig. 1.
- the refrigeration system in fig. 1 has a hermetic compressor-motor unit with a twin-screw rotary compressor 1, the low pressure end of which is connected to an electric motor 2. At the high pressure end of the compressor an oil separator 3 is provided for separating oil from the working fluid, which oil has been injected into the compressor working space for sealing, cooling and lubricating purposes.
- the refrigeration system is of conventional type including a condenser 4, an expansion valve 6 and an evaporator 5 connected by pipes, 8, 9, 10 to form a closed refrigeration circuit. Liquid refrigerant is supplied from the condenser 4 through a pipe 11 to the motor 2 for cooling the motor windings 18. In the pipe 11 a pump 7 is provided for raising the pressure to a level about 1 to 2 bars above delivery pressure.
- the liquid refrigerant When cooling the motor windings 18 the liquid refrigerant will partly be evaporated, and the gas-liquid mixture is drained to the discharge line of the compressor. In the illustrated embodiment the gas- liquid mixture is drained to the oil separator 3 where the remaining liquid is evaporated for cooling the oil.
- One of the rotors 13 of the compressor is directly driven by the motor 2 through a shaft 14 extending through the low pressure end section 15 of the compressor.
- roller bearings 16 and a seal arrangement 17 for sealing between the low pressure end of the compressor, where the pressure is about evaporating or suction pressure and the motor space where the pressure is 1 to 2 bars above condensing or delivery pressure.
- the seal arrangement is illustrated in fig. 2 in an enlarged section.
- the shaft 14, including a shaft sleeve 21, is extending through the low pressure end section 15 of the compressor and is at its left end connected to the motor 2 and at its right end to one of the compressor rotors 13.
- the seal arrangement 17 is on its left side exposed to a cavity communicating with the motor space and thus having a pressure above delivery pressure and on its right side to a cavity communicating with the low pressure end of the compressor working space and thus having a pressure corresponding to the compressor inlet pressure.
- a lip seal 20 Adjacent to the high pressure cavity a lip seal 20 is provided and adjacent to the low pressure cavity there is a non-contacting seal 24.
- An intermediate chamber 22 is formed between these two seals 20, 24, to which chamber oil of about delivery pressure is supplied through a nozzle 23, connected by a supply channel 28 to a source of oil under pressure, normally the oil separator of the compressor.
- the sealing is accomplished by a non-contacting seal 24, allowing the supplied oil to leak from the intermediate chamber 22 through the seal gap 27 to the compressor working space.
- the non-contacting seal can be of any kind, e.g. a labyrinth seal
- the preferred embodiment shown in the figure employs a so called floating seal of the type disclosed in US-A 5 009 583.
- the seal gap 27 can be as small as desired, since the seal body 24 is radially movable while being axially kept in a fixed position by the supports 25, 26 on either side.
- the seal body 24 is squeezed between these supports 25, 26 with a force large enough to prevent rotation but low enough to allow the seal body 24 to move radially.
- the seal body 24 thus is self-centering around the sleeve 21 of the shaft 14.
- the blocking oil leaking from the intermediate chamber 22 to the compressor working space passes the roller bearings 16 supporting the shaft and is used to lubricate these.
- the seal gap 27 therefore must be dimensioned so that the leakage is sufficient for that lubrication requirement.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE69406134T DE69406134T2 (de) | 1993-05-14 | 1994-02-04 | Rotierender schraubenverdichter und dichtung |
EP94910075A EP0698185B1 (en) | 1993-05-14 | 1994-02-04 | Rotary screw compressor with seal means |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE9301662A SE9301662L (sv) | 1993-05-14 | 1993-05-14 | Skruvkompressor med tätningsorgan |
SE9301662-4 | 1993-05-14 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1994027050A1 true WO1994027050A1 (en) | 1994-11-24 |
Family
ID=20389942
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/SE1994/000087 WO1994027050A1 (en) | 1993-05-14 | 1994-02-04 | Rotary screw compressor with seal means |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0698185B1 (sv) |
DE (1) | DE69406134T2 (sv) |
DK (1) | DK0698185T3 (sv) |
SE (1) | SE9301662L (sv) |
WO (1) | WO1994027050A1 (sv) |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0775812A1 (en) * | 1995-11-22 | 1997-05-28 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Seal arrangement for engine-driven supercharger |
DE29807796U1 (de) * | 1998-04-30 | 1999-09-09 | Ghh Rand Schraubenkompressoren | Dichtungsanordnung für einen Wellenzapfen eines trockenlaufenden Rotationsschraubenverdichters |
US6283739B1 (en) * | 1997-03-26 | 2001-09-04 | Iec L.L.C. | Steam-driven propeller engine |
DE19882900B4 (de) * | 1998-03-24 | 2004-04-15 | Taiko Kikai Industries Co., Ltd. | Schraubenrotor-Nassvakuumpumpe |
FR2853699A1 (fr) * | 2003-04-08 | 2004-10-15 | Cyclam Sas | Compresseur rotatif a gaz |
WO2013067099A1 (en) * | 2011-11-02 | 2013-05-10 | Trane International Inc. | High pressure seal vent |
EP2642125A4 (en) * | 2010-11-16 | 2016-11-16 | Shanghai Power Tech Screw Machinery Co Ltd | LIQUID PUMP WITH TWIN SCREW |
WO2019201884A1 (de) * | 2018-04-18 | 2019-10-24 | Henkel Ag & Co. Kgaa | Pumpe mit einer produktkammer |
CN111670306A (zh) * | 2016-12-22 | 2020-09-15 | 株式会社日立产机系统 | 螺旋式压缩机 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3913346A (en) * | 1974-05-30 | 1975-10-21 | Dunham Bush Inc | Liquid refrigerant injection system for hermetic electric motor driven helical screw compressor |
DE3503039A1 (de) * | 1985-01-30 | 1986-07-31 | Wankel Gmbh, 1000 Berlin | Wellendichtung zwischen kaeltekompressor und antriebsmotor |
US4669279A (en) * | 1985-03-19 | 1987-06-02 | Ebara Corporation | Motor cooling apparatus for refrigerator |
-
1993
- 1993-05-14 SE SE9301662A patent/SE9301662L/sv unknown
-
1994
- 1994-02-04 WO PCT/SE1994/000087 patent/WO1994027050A1/en active IP Right Grant
- 1994-02-04 DK DK94910075T patent/DK0698185T3/da active
- 1994-02-04 EP EP94910075A patent/EP0698185B1/en not_active Expired - Lifetime
- 1994-02-04 DE DE69406134T patent/DE69406134T2/de not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3913346A (en) * | 1974-05-30 | 1975-10-21 | Dunham Bush Inc | Liquid refrigerant injection system for hermetic electric motor driven helical screw compressor |
DE3503039A1 (de) * | 1985-01-30 | 1986-07-31 | Wankel Gmbh, 1000 Berlin | Wellendichtung zwischen kaeltekompressor und antriebsmotor |
US4669279A (en) * | 1985-03-19 | 1987-06-02 | Ebara Corporation | Motor cooling apparatus for refrigerator |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0775812A1 (en) * | 1995-11-22 | 1997-05-28 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Seal arrangement for engine-driven supercharger |
US6283739B1 (en) * | 1997-03-26 | 2001-09-04 | Iec L.L.C. | Steam-driven propeller engine |
DE19882900B4 (de) * | 1998-03-24 | 2004-04-15 | Taiko Kikai Industries Co., Ltd. | Schraubenrotor-Nassvakuumpumpe |
DE29807796U1 (de) * | 1998-04-30 | 1999-09-09 | Ghh Rand Schraubenkompressoren | Dichtungsanordnung für einen Wellenzapfen eines trockenlaufenden Rotationsschraubenverdichters |
FR2853699A1 (fr) * | 2003-04-08 | 2004-10-15 | Cyclam Sas | Compresseur rotatif a gaz |
EP2642125A4 (en) * | 2010-11-16 | 2016-11-16 | Shanghai Power Tech Screw Machinery Co Ltd | LIQUID PUMP WITH TWIN SCREW |
WO2013067099A1 (en) * | 2011-11-02 | 2013-05-10 | Trane International Inc. | High pressure seal vent |
CN104126072A (zh) * | 2011-11-02 | 2014-10-29 | 特灵国际有限公司 | 高压密封通气孔 |
US9022760B2 (en) | 2011-11-02 | 2015-05-05 | Trane International Inc. | High pressure seal vent |
CN111670306A (zh) * | 2016-12-22 | 2020-09-15 | 株式会社日立产机系统 | 螺旋式压缩机 |
WO2019201884A1 (de) * | 2018-04-18 | 2019-10-24 | Henkel Ag & Co. Kgaa | Pumpe mit einer produktkammer |
Also Published As
Publication number | Publication date |
---|---|
EP0698185A1 (en) | 1996-02-28 |
SE9301662D0 (sv) | 1993-05-14 |
SE500488C2 (sv) | 1994-07-04 |
SE9301662L (sv) | 1994-07-04 |
DK0698185T3 (da) | 1998-05-18 |
EP0698185B1 (en) | 1997-10-08 |
DE69406134T2 (de) | 1998-04-09 |
DE69406134D1 (de) | 1997-11-13 |
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