WO2003102423A1 - Liquid ring compressor - Google Patents
Liquid ring compressor Download PDFInfo
- Publication number
- WO2003102423A1 WO2003102423A1 PCT/NO2003/000128 NO0300128W WO03102423A1 WO 2003102423 A1 WO2003102423 A1 WO 2003102423A1 NO 0300128 W NO0300128 W NO 0300128W WO 03102423 A1 WO03102423 A1 WO 03102423A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- bearing
- compressor
- compressor according
- liquid
- 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
- F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
- F04C19/005—Details concerning the admission or discharge
- F04C19/008—Port members in the form of conical or cylindrical pieces situated in the centre of the impeller
-
- 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
- F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
- F04C19/002—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids with rotating outer members
Definitions
- the present invention relates to a compressor, in particular a liquid ring compressor.
- Examples of these are water driven ejectors and liquid ring compressors, where both are frequently used with vacuum.
- a screw compressor with oil injection works polytropic, i.e. somewhere between adiabatic and isothermal.
- a liquid ring compressor consists mainly of an impeller which rotates eccentric in an outer enclosure together with a ring of water which the centrifugal force keeps in place against the periphery.
- the inlet is normally positioned as an opening in one or both of the end walls of the enclosure where the gas is drawn into the gaps of the impeller. Accordingly, it is arranged openings in the end walls on the pressure side, where the compressed gas is pushed out. All the types can have stationary commutators arranged centrally within the rotor where inlet and discharge happens radially.
- Liquid ring compressor does not transform the energy in the water in the same way as the ejector.
- the static pressure in the ring of water remains constant.
- the ring of water acts as a piston in every cell of the rotor.
- the principle for an ordinary liquid ring compressor is shown in figure 2, where a ring of liquid 23 rotates eccentric in a stationary enclosure 22, drive by a rotor 21 where the gap between the impeller will draw in gas on one side of a revolution and compress the gas on the other.
- the static pressure in the ring of water has to be the same as the compression pressure, otherwise the water will be pressed out of the cell, i.e. the water ring will be deformed.
- a liquid ring compressor usually has considerably higher pressure height and therefore requires higher speed of rotation than a vacuum pump.
- the highest loss of friction in a conventional water ring compressor arise when the rotor is touching the wall of the enclosure.
- the clearing must here be very small, something which involves the water against the enclosure's periphery to have the same speed as the impeller tips of the rotor.
- it must be very little clearance between the sides of the rotor and the enclosure. Also in these gaps there will be high frictions.
- liquid ring compressor has many advantages. It is very simple and can be one stage up to relatively high pressure ratios.
- US 5 251 593 discloses as the previous application that it is an intricate problem to get to, in relation to each other, eccentric bearings in combination with a stationary canals for the inlet and discharge of the gas.
- This publication indicates a bearing of the outer rotating cylinder on one side and the rotor on the opposite side, where a stationary plate close to the open end of the rotor has canals for inlet and discharge. It is mainly two decisive weaknesses with this design. The first is the one-sided bearing this solution gives, where the bearing load becomes uneven and too high. At the same time large axial thrust forces arise.
- the compressor according to the present invention has the objective to solve this problem which up to know has prevented a water ring compressor to exploit the above mentioned advantages with a co-rotor for the liquid ring. Another objective is to achieve almost isothermal compression with a new, very efficient direct injection of liquid into the gas during the whole compression stage.
- figure 1 shows a diagram with theoretical energy needs independence of pressure relation ship
- figure 2 shows schematic the principle for a liquid ring compressor
- figure 3 a liquid ring compressor according to the present invention in a divided longitudinal view
- figure 4 is a cross section of figure 4
- figure 5 shows the compressor as mounted
- figure 6 shows details of the rotor
- figures 7a and 7b shows details of the communicator
- figure 8 shows details of the bearing to the co-rotor, seals and the system for airing of the zones at the bearings.
- the main parts in figure 3 consists of two enclosures 1 and 2, two co-rotors 3 and 4, a rotor 6 and a rotor axle 5, a communicator 7, two bearings 1 1 for co-rotors 3 and 4 and two bearings 12 for the rotor axle 5 as well as the axles 8 and 9 for the outer and inner bearings 12.
- the sector II-III liquid is injected from the communicator directly into the rotor cells and the compression and cooling of the gas in the cells.
- a short rotor get little bending force from the gas pressure and is thereby allowed to be fixed to a flange on its axle only at one end wall and thereby being able to have a simple commutator in the entire width of the rotor. It is then only created two leakage gap between the commutator and the rotor. These gaps are the only place where leakage from the pressure side will find place. It can leak actually to both sides from the gap and along the periphery from the pressure discharge against the inlet, especially in the direction of rotation. Even in very small gaps, pure gas without liquid will with the present pressure be able to leak in considerable amounts, with smaller amounts deliver and lower efficiency as a result.
- the surface of the rotor 6 on the inside towards the commutator is at its ends 63 smooth, with interweaving canal openings 62 to each individual cell.
- the commutator has a row of grooves 71 in the opposite side sections. The grooves are under liquid pressure from the liquid canal 74 which thereby is blocking for gas leakages in the actual direction.
- the liquid ring compressor according to the present invention could be designed with hydro dynamic bearing for the co-rotor. These could then be lubricated and cooled with the same liquid which was used for injection. But with the starting point with necessary axle diameter and speed, research shows however that the friction losses in such bearings then will be very high and some of the advantages with a co-rotor are lost. With higher pressure the bearing size increases further and the losses in them become unacceptable. On the other hand the same relationship seems to be acceptable for relatively large ball or roller bearings, but at the same time this leads to new problems around the bearing sealing. Bearings with integrated seals can not operate close to the necessary speeds and there do not exist any static seals which allows this, or that will achieve acceptable lifetime. Labyrinth seals however are touch-free and can operate with high speeds, but do not give any static sealing. These seals assume there are no differential pressures across the seal.
- a co-rotor is aired to the compressor enclosure through the holes 81 as shown in figure 8.
- the enclosure is in turn aired to atmosphere or is by compression of other gases to prevent discharge, aired to the inlet, and thereby it will not be a differential pressure across the bearing of the co-rotor.
- Blocking liquid which leaks from the gap between the commutator and the rotor will during operation be projected out into the liquid ring and will not be able to reach the bearings for the co-rotor.
- the design only needs a static bearing seal during the stopping phase, where the danger for splashing water against the seals is apparent when the water ring collapses due to lack of centrifugal force.
- the seal is in other words static at low speeds and seems dynamic at higher speeds, where its purpose is only to prevent bearing grease to be projected out.
- Bearing of the co-rotor will with this system get about the same surrounding relationship and security as if they operated in air. It is the diameter on the bearing of the rotor and the eccentricity between the rotors which decide the diameter on the bearing axles of the co-rotor because the bearing of the rotor as shown is inserted in these.
- the load on the bearing of the rotor becomes the same as for the co-rotor. To withstand this load, at the same time as giving smallest possible dimensions for the axle to the co-rotor, so-called needle bearings are used for the rotor.
- the commutator is fixed to the one, stationary axle 8 for the co-rotor.
- the axle connects the canals of the commutator with the respective inlet and discharge for gas and injection liquid.
- the compressor according to the present invention When the compressor according to the present invention is used for other gases than air, e.g. cooling system or in a petrochemical plant, it can be useful to use the actual gas in the liquid phase for injection and as liquid ring.
- other gases e.g. cooling system or in a petrochemical plant
- the compressor will according to the present invention be very suitable as compressor in a gas turbine plant which operates with relatively high pressure relationship.
- the air from this will indeed in contrast to the turbo compressor, be cold, but it is necessary to note that the heat which the turbo compressor delivers is taken out of the axle of the turbine and reduces the output effect accordingly at the same time as the warm air to do not make it possible for heat recovery from the turbine exhaust.
- the air from the compressor can be heat exchanged with the exhaust gas and almost reach the same temperatures as after a turbine compressor.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03756128A EP1502028B1 (en) | 2002-04-19 | 2003-04-16 | Liquid ring compressor |
JP2004509281A JP2005534843A (en) | 2002-04-19 | 2003-04-16 | Liquid ring compressor |
AU2003263670A AU2003263670A1 (en) | 2002-04-19 | 2003-04-16 | Liquid ring compressor |
US10/511,753 US20050271520A1 (en) | 2002-04-19 | 2003-04-16 | Liquid ring compressor |
DE60318841T DE60318841T2 (en) | 2002-04-19 | 2003-04-16 | LIQUID RING COMPRESSORS |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
NO20021844A NO316638B1 (en) | 2002-04-19 | 2002-04-19 | Vaeskeringkompressor |
NO20021844 | 2002-04-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003102423A1 true WO2003102423A1 (en) | 2003-12-11 |
Family
ID=19913538
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/NO2003/000128 WO2003102423A1 (en) | 2002-04-19 | 2003-04-16 | Liquid ring compressor |
Country Status (11)
Country | Link |
---|---|
US (2) | US20050271520A1 (en) |
EP (1) | EP1502028B1 (en) |
JP (1) | JP2005534843A (en) |
CN (1) | CN1656317A (en) |
AT (1) | ATE384877T1 (en) |
AU (1) | AU2003263670A1 (en) |
DE (1) | DE60318841T2 (en) |
ES (1) | ES2300607T3 (en) |
NO (1) | NO316638B1 (en) |
PT (1) | PT1502028E (en) |
WO (1) | WO2003102423A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019043044A1 (en) * | 2017-08-29 | 2019-03-07 | Friedrich-Alexander-Universität Erlangen-Nürnberg | Liquid ring pump |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10669850B2 (en) | 2016-12-22 | 2020-06-02 | Brian Blackwell | Impeller-type liquid ring compressor |
GB2565579B (en) | 2017-08-17 | 2020-03-04 | Edwards Ltd | A pump and method of pumping a fluid |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4747752A (en) * | 1987-04-20 | 1988-05-31 | Somarakis, Inc. | Sealing and dynamic operation of a liquid ring pump |
US5100300A (en) * | 1990-12-28 | 1992-03-31 | The Nash Engineering Company | Liquid ring pumps having rotating lobe liners with end walls |
US5251593A (en) * | 1989-05-31 | 1993-10-12 | Pedersen John R | Thermodynamic liquid ring machine |
US5370502A (en) * | 1993-01-14 | 1994-12-06 | The Nash Engineering Company | Liquid ring pumps with pressurized gas supported rotating liners |
US5395215A (en) * | 1994-07-26 | 1995-03-07 | The Nash Engineering Company | Supports for rotatable housing of liquid ring pumps |
WO1995017605A1 (en) * | 1993-12-20 | 1995-06-29 | Siemens Aktiengesellschaft | Liquid ring vacuum pump |
US5653582A (en) * | 1995-09-26 | 1997-08-05 | The Nash Engineering Company | Fluid bearing pad arrangement for liquid ring pump systems |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1668532A (en) * | 1924-09-08 | 1928-05-01 | W L Stewart | Rotary machine |
US2771860A (en) * | 1950-08-22 | 1956-11-27 | Werner P Falk | Hydraulic machine |
IN166621B (en) * | 1986-01-09 | 1990-06-23 | Warman Int Ltd | |
US5197863A (en) * | 1990-12-28 | 1993-03-30 | The Nash Engineering Company | Bearing fluid distribution systems for liquid ring pumps with rotating lobe liners |
CN1079503C (en) * | 1995-08-16 | 2002-02-20 | 西门子公司 | Ring liquid compression engine |
DE19758340A1 (en) * | 1997-12-22 | 1999-07-08 | Gardner Denver Wittig Gmbh | Multi-flow liquid ring pump |
-
2002
- 2002-04-19 NO NO20021844A patent/NO316638B1/en unknown
-
2003
- 2003-04-16 PT PT03756128T patent/PT1502028E/en unknown
- 2003-04-16 EP EP03756128A patent/EP1502028B1/en not_active Expired - Lifetime
- 2003-04-16 JP JP2004509281A patent/JP2005534843A/en active Pending
- 2003-04-16 AU AU2003263670A patent/AU2003263670A1/en not_active Abandoned
- 2003-04-16 CN CN03812088.7A patent/CN1656317A/en active Pending
- 2003-04-16 AT AT03756128T patent/ATE384877T1/en not_active IP Right Cessation
- 2003-04-16 WO PCT/NO2003/000128 patent/WO2003102423A1/en active IP Right Grant
- 2003-04-16 US US10/511,753 patent/US20050271520A1/en not_active Abandoned
- 2003-04-16 DE DE60318841T patent/DE60318841T2/en not_active Expired - Fee Related
- 2003-04-16 ES ES03756128T patent/ES2300607T3/en not_active Expired - Lifetime
-
2008
- 2008-06-30 US US12/164,908 patent/US20080260543A1/en not_active Abandoned
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4747752A (en) * | 1987-04-20 | 1988-05-31 | Somarakis, Inc. | Sealing and dynamic operation of a liquid ring pump |
US5251593A (en) * | 1989-05-31 | 1993-10-12 | Pedersen John R | Thermodynamic liquid ring machine |
US5100300A (en) * | 1990-12-28 | 1992-03-31 | The Nash Engineering Company | Liquid ring pumps having rotating lobe liners with end walls |
US5370502A (en) * | 1993-01-14 | 1994-12-06 | The Nash Engineering Company | Liquid ring pumps with pressurized gas supported rotating liners |
WO1995017605A1 (en) * | 1993-12-20 | 1995-06-29 | Siemens Aktiengesellschaft | Liquid ring vacuum pump |
US5395215A (en) * | 1994-07-26 | 1995-03-07 | The Nash Engineering Company | Supports for rotatable housing of liquid ring pumps |
US5653582A (en) * | 1995-09-26 | 1997-08-05 | The Nash Engineering Company | Fluid bearing pad arrangement for liquid ring pump systems |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019043044A1 (en) * | 2017-08-29 | 2019-03-07 | Friedrich-Alexander-Universität Erlangen-Nürnberg | Liquid ring pump |
Also Published As
Publication number | Publication date |
---|---|
NO20021844D0 (en) | 2002-04-19 |
ES2300607T3 (en) | 2008-06-16 |
NO20021844L (en) | 2003-10-20 |
DE60318841D1 (en) | 2008-03-13 |
PT1502028E (en) | 2008-05-06 |
AU2003263670A1 (en) | 2003-12-19 |
US20050271520A1 (en) | 2005-12-08 |
ATE384877T1 (en) | 2008-02-15 |
JP2005534843A (en) | 2005-11-17 |
DE60318841T2 (en) | 2009-01-22 |
EP1502028A1 (en) | 2005-02-02 |
EP1502028B1 (en) | 2008-01-23 |
US20080260543A1 (en) | 2008-10-23 |
CN1656317A (en) | 2005-08-17 |
NO316638B1 (en) | 2004-03-15 |
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