EP0183813B1 - Flüssigkeitsring-verdichteraggregat - Google Patents

Flüssigkeitsring-verdichteraggregat Download PDF

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Publication number
EP0183813B1
EP0183813B1 EP85902989A EP85902989A EP0183813B1 EP 0183813 B1 EP0183813 B1 EP 0183813B1 EP 85902989 A EP85902989 A EP 85902989A EP 85902989 A EP85902989 A EP 85902989A EP 0183813 B1 EP0183813 B1 EP 0183813B1
Authority
EP
European Patent Office
Prior art keywords
liquid
pressure
pressure chamber
compressor
zone
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.)
Expired
Application number
EP85902989A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0183813A1 (de
Inventor
Udo Segebrecht
Siegfried Auschrat
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sihi GmbH and Co KG
Original Assignee
Sihi GmbH and Co KG
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 Sihi GmbH and Co KG filed Critical Sihi GmbH and Co KG
Priority to AT85902989T priority Critical patent/ATE40448T1/de
Publication of EP0183813A1 publication Critical patent/EP0183813A1/de
Application granted granted Critical
Publication of EP0183813B1 publication Critical patent/EP0183813B1/de
Expired legal-status Critical Current

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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
    • F04C19/004—Details concerning the operating liquid, e.g. nature, separation, cooling, cleaning, control of the supply

Definitions

  • the invention relates to a liquid ring compressor unit with a horizontal shaft and a compressor housing, in which a pressure chamber is formed in connection with the possibly last compressor stage in connection with a pressure port, which by at least up to in the geodetically upper area of the pressure chamber Wave height and at least up to the height of the pressure opening of the compressor stage wall is divided into a first region, in which the pressure opening opens, and second region, which are connected to one another above the wall to form a path for the conveyed medium, and of which the second is connected to the pressure port.
  • liquid ring compressors require an operating liquid which is involved in the formation of the compressor cells, seals gaps within the delivery spaces and contributes to the dissipation of the heat generated during the compression. It is inevitable that a part of the operating liquid gets into the pumped gas and exits with it through the pressure opening from the delivery chamber of the compressor stage and is carried on by the pumped gas. Therefore, in general, a
  • Liquid separators are known which are assigned to the compressor as separate components. For example, designs are known in which the liquid separator is set up in an open or closed design next to the compressor, which means that considerable space is required. It is also known to
  • the separator is integrated in the base frame of the unit, but this is complicated and expensive to implement, and the return of operating fluid to the compressor after switching off the unit is also problematic. It is also known to arrange the compressor in a pot-shaped separating container, the separating space surrounding the compressor. This is only possible with small compressor types. In addition, this arrangement has structural disadvantages, because either suction and pressure ports must be arranged on an axial side of the compressor in a housing part or - if one of the ports is arranged on the separating tank - the tank must be correspondingly stable and therefore expensive (DE-C -1 293 942).
  • liquid separators are also known. These serve to extract the oil used to lubricate the compressor as far as it has got into the gas stream.
  • liquid ring compressors the liquid is directly involved in the formation of the compressor cells, with large amounts of the operating liquid being led out of the working space with the gas stream as a result of the large-area phase change.
  • the amounts of oil that get into the gas stream in a vane compressor are comparatively small, so that relatively small liquid separators can be used. It is therefore that there are proposals for connecting the liquid separator to the compressor in a common housing, although this leads to very complicated and therefore complex housing shapes (GB-A-393 977, DE-C-459 056, US-A- 2 057 381).
  • the pressure chamber contains a partition that rises from the bottom to the pressure opening of the pump stage and divides it into two areas. It serves to hold a liquid supply in the first area immediately following the pressure opening, which prevents gas from flowing back into the beginning of the pressure opening.
  • the second area of the pressure chamber behind the wall leads directly to the pressure port.
  • the entire amount of liquid contained in the conveyed gas stream is led out of the pressure chamber through the pressure port, so that it is necessary to connect a liquid separator downstream. That the pressure chamber can not be used as a liquid separator can be recognized from the fact that no precautions are taken Removal of the separated liquid is taken separately from the gas flow.
  • the pressure space is divided by walls into a first and a second area in such a way that in the first area a liquid level is maintained constantly well above the pressure opening becomes.
  • This is intended to effect noise reduction by preventing the direct sound connection between the pressure opening and the pressure port by the liquid-gas mixture filling the first pressure chamber area.
  • a separation effect cannot be achieved in the known pressure chamber; rather, the entire liquid obtained there must be removed with the gas stream to a separate liquid separator.
  • the invention has for its object to equip a liquid ring compressor of the type mentioned with less space and construction with a liquid separator.
  • the solution according to the invention is that the second area of the pressure chamber has a liquid overflow at medium height separate from the pressure port and that a plurality of deflections and / or baffles are formed in the path arranged in the upper area of the pressure chamber for the medium above the Shield the pressure spout from the pressure opening.
  • the wall separating the two areas of the pressure chamber serves to maintain a water supply in front of the pressure opening during the compressor operation in order to exclude the backflow of gas.
  • the overflow of the second pressure chamber area is advantageously approximately at wave height; however, it can also be located elsewhere within approximately the middle third of the pressure chamber height.
  • the feature that the pressure chamber is formed in the compressor housing following the compressor stage should generally mean that the pressure chamber and the working chamber of the compressor stage extend essentially over the same width and height within the same housing boundaries, with slight deviations of the upper and / or the lower limits are possible, provided this does not call into question the uniformity of the housing design.
  • the uniformity of the housing design is at least given when the walls of the pressure chamber can be viewed as a continuation of the walls of the working space, particularly in the axial direction.
  • the continuous cylindrical design of the housing walls of the pump stage and of the pressure chamber is particularly advantageous, the pressure port advantageously being connected to the pressure chamber at the top. Integrity of the housing parts enclosing the pressure chamber and the pump stage is not necessary.
  • At least part of the operating fluid contained in the pressure chamber can be returned from the second region of the pressure chamber to the working chamber of the compressor by a flow connection known in principle for such purposes.
  • a part of the necessary operating fluid can also be removed from the pressure chamber and a further part can be constantly supplied fresh from an external source, the latter being able to be kept at a cool enough temperature to keep the temperature of the operating fluid at the desired level.
  • a cooling device can also be arranged in a manner known per se in the liquid separator of the pressure chamber.
  • the flow connection can be formed by a separate line which leads from the second region of the pressure chamber to a part of the lower pressure of the working chamber. It can also be formed by an opening in the wall dividing the pressure chamber, through which liquid flows into the first area of the pressure chamber and from there through the pressure slot or separate flow connections into the working chamber of the compressor. Regardless of a possible flow connection for returning operating fluid into the working chamber of the compressor, at least one level compensation opening of small cross-section can be provided in the wall, which, if the machine is switched off, allows a Excess liquid, which would be difficult in the work area when restarting, flows out over the first area of the pressure chamber. Conversely, this opening can also be used to return to the work space the liquid supply that has accumulated in the second area of the pressure chamber and is required to restart the pump.
  • a level controller can be provided in the liquid separator of the pressure chamber.
  • the housing of the compressor is formed by the suction cover 1, the suction-side control disk 2, the housing 3 of the compressor stage, the pressure-side control disk 4 and the pressure chamber housing 5. These housing parts have an approximately circular cross-sectional shape in cross section to the plane of the drawing.
  • the suction cover 1 contains the suction space 6, to which the gas to be conveyed is fed via the suction nozzle 7 arranged at the top. It also contains a hub with a shaft bore, which includes a seal 8 for sealing the rotor shaft 9.
  • the suction cover 1 is tightly connected to the suction-side control disk 2, which contains the suction opening 10 at a suitable, known location, which does not have to match the location shown.
  • the housing 3 of the compressor stage is tightly connected to the suction-side control disk 2.
  • This forms an annular housing wall, the inner surface 11 of which is eccentric to the shaft 9 and, with the vane rotor 12 seated on the shaft, encloses the working space 13, in which the dotted liquid ring, which closes the vane cells between the vanes on the outside, rotates radially on the outside.
  • the pressure-side control disk 4 which contains the pressure opening 15 at a known, suitable location, is closely connected to the compressor stage. It is always close to the inner boundary 16 of the vane cells in the circumferential direction just before the apex of the work area. In the case shown, you have to imagine them above the wave height.
  • the pressure chamber housing 5 which is formed, for example, by a cylindrical wall part 17 and a flat, front wall part 18 and to which the pressure connection 39 is connected at the top.
  • a wall 19 projects vertically from below up to the height of the pressure opening 15 and separates the first pressure chamber region 20 from the second pressure chamber region 21, the axial dimension of the first region 20 being approximately 1/3 to 1/2 of the axial width of the working chamber 13 is, while the axial dimension of the second region 21 is about 2 to 3 times as large.
  • the second pressure chamber region 21 has a drain or overflow opening 22, the lower edge of which determines the mirror 23 in the second pressure chamber region 21, which is considerably exceeded by the wall 19.
  • An approximately horizontal rib 24 lies above the first pressure chamber region 20 and the wall 19 and thereby forces the medium flow emerging from the pressure opening 15 and bouncing against the wall 19 to be deflected further in the horizontal direction.
  • It contains one or more openings 27 for the passage of the separated liquid downwards.
  • a portion of the medium flow deflected upward by the rib 26 strikes the horizontal rib 28, which represents a continuation of the rib 24, in order to then be deflected horizontally by the upper part of the housing wall 17 to the pressure port 39.
  • the ribs 24, 28 form one effective shielding of the pressure port 39 from the pressure opening 15 and those areas of the medium flow in which even larger proportions of entrained liquid are suspected.
  • the shaft 9 can be mounted within the housing at a location not shown, for example in the control disks 2, 4.
  • the suction cover 1 contains a chamber 30 which is partitioned off by a wall 29 and which is connected via a bore 31 to a fresh liquid source, not shown.
  • the chamber 30 is connected to the working space 13 through a bore 32. Via the path 31, 30, 32, the desired amount of fresh liquid can therefore be supplied to the working area of the pump stage.
  • the pressure-side control disc 4 contains. geodetically low-lying point, a small bore 33 through which operating fluid can flow back into the working space 13 during operation from the first area 20 of the pressure chamber and which enables a level compensation even when the compressor is at a standstill.
  • the wall 19 contains geodetic a small hole 34 located at a low point, which is used for level compensation during the compressor standstill.
  • the compressor sucks gas from the suction nozzle 7 via the suction chamber 6 and the suction opening 10, which gas is compressed in the working chamber 13 in order to be expelled through the pressure opening 15 into the first region 20 of the pressure chamber.
  • Liquid collects there, which is retained by the wall 19 in front of the pressure opening in order to form a liquid barrier against the backflow of gas into the pressure opening.
  • the outflowing gas / liquid mixture impinges against the upper part of the wall 19, whereby a separation is promoted, then passes through the curved channel formed by the wall 19, the rib 24 and the rib 25, in which a coarse separation takes place, after further separation in the area of the ribs 26 and 28 to reach the pressure port 39, in which way the ribs and the pressure chamber walls form deflections and baffles on which liquid separates.
  • the compressor can be designed in several stages, the last compressor stage taking the place of the compressor stage shown in the drawing.
  • the invention is also applicable to those types of compressors in which suction and pressure ports are arranged on the same axial side of the pump stage, in that suction and pressure spaces are formed separately from one another in the same housing part.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP85902989A 1984-06-13 1985-06-10 Flüssigkeitsring-verdichteraggregat Expired EP0183813B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85902989T ATE40448T1 (de) 1984-06-13 1985-06-10 Fluessigkeitsring-verdichteraggregat.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843421866 DE3421866A1 (de) 1984-06-13 1984-06-13 Fluessigkeitsring-verdichteraggregat
DE3421866 1984-06-13

Publications (2)

Publication Number Publication Date
EP0183813A1 EP0183813A1 (de) 1986-06-11
EP0183813B1 true EP0183813B1 (de) 1989-01-25

Family

ID=6238222

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85902989A Expired EP0183813B1 (de) 1984-06-13 1985-06-10 Flüssigkeitsring-verdichteraggregat

Country Status (12)

Country Link
US (1) US4710105A (xx)
EP (1) EP0183813B1 (xx)
JP (1) JPH0643838B2 (xx)
AU (1) AU577390B2 (xx)
CA (1) CA1329185C (xx)
DE (2) DE3421866A1 (xx)
DK (1) DK152858C (xx)
ES (1) ES287425Y (xx)
FI (1) FI83905C (xx)
SG (1) SG44789G (xx)
WO (1) WO1986000117A1 (xx)
ZA (1) ZA854150B (xx)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20015709U1 (de) * 2000-09-11 2002-01-31 Speck Pumpenfabrik Walter Spec Flüssigkeitsringpumpe mit Nabensteuerung

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0279292B1 (de) * 1987-02-17 1991-04-17 Siemens Aktiengesellschaft Flüssigkeitsabschneider
GB2217392B (en) * 1988-04-19 1991-05-01 Plessey Co Plc Improvements relating to gas and/or vapour compressors
DE3867068D1 (de) * 1988-11-07 1992-01-30 Siemens Ag Fluessigkeitsringpumpe.
CN1071004C (zh) * 1995-08-21 2001-09-12 西门子公司 环形液体压缩机
EP0766988A1 (de) * 1995-10-06 1997-04-09 Siemens Aktiengesellschaft Abscheidevorrichtung zum Abscheiden der in einem Gas-Flüssigkeits-Gemisch enthaltenen Flüssigkeit
US6976833B2 (en) * 2003-11-17 2005-12-20 Carrier Corporation Compressor discharge chamber with baffle plate
DE102007001770A1 (de) * 2007-01-05 2008-07-10 Gardner Denver Deutschland Gmbh Saugrohr
FI126831B (fi) 2010-04-14 2017-06-15 Evac Oy Nesterengaspumppu ja menetelmä nesterengaspumpun käyttämiseksi
RU171811U1 (ru) * 2016-06-15 2017-06-16 Общество с ограниченной ответственностью "Компания "КОРД" Жидкостно-кольцевая машина
JP6992778B2 (ja) * 2019-02-28 2022-01-13 株式会社デンソー 圧縮機
CN114810597B (zh) * 2022-05-11 2023-02-03 广东锦坤实业有限公司 一种脂肪酸加工的高效冰冻真空系统

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191006938A (en) * 1910-03-19 1910-11-03 Aublet Harry & Co Ltd A Rotary Gas or Air Compressor.
US1530973A (en) * 1923-12-22 1925-03-24 American Mach & Foundry Vacuum pump
DE459056C (de) * 1925-11-01 1928-04-26 Becker Maschinenfabrik Geb Geblaese mit umlaufenden Kolbenschiebern und einem den Arbeitszylinder umschliessenden, als OElbehaelter und OElabscheider dienenden Gehaeuse
US1702939A (en) * 1926-02-25 1929-02-19 Combustion Utilities Corp Lubricating system for air blowers
US1626768A (en) * 1926-03-08 1927-05-03 Carl W Vollmann Rotary compressor
GB377476A (en) * 1931-09-01 1932-07-28 Drysdale & Co Ltd Improvements in air-pumps
GB393977A (en) * 1931-12-16 1933-06-16 Thomas Winter Nichols Improvements in rotary air pumps or compressors
US2057381A (en) * 1933-01-06 1936-10-13 Gen Household Utilities Compan Pump for refrigerating means
US2070151A (en) * 1934-05-10 1937-02-09 Stokes Machine Co Vacuum pump
US2227441A (en) * 1934-08-07 1941-01-07 Stokes Machine Co Vacuum pump
GB858422A (en) * 1956-05-02 1961-01-11 Otto Siemen Multi-stage liquid-ring gas-pump
DE2036295C3 (de) * 1970-07-22 1975-09-18 Siemen & Hinsch Gmbh Flüssigkeitsringverdichter
DE2318538B2 (de) * 1973-04-12 1975-12-04 Siemens Ag, 1000 Berlin Und 8000 Muenchen Verteiler für einen Flüssigkeitsringgasverdichter
JPS57148097A (en) * 1981-03-09 1982-09-13 Mitsubishi Heavy Ind Ltd Rotary compressor
JPS5929791A (ja) * 1982-08-13 1984-02-17 Mitsubishi Electric Corp スクロ−ル圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20015709U1 (de) * 2000-09-11 2002-01-31 Speck Pumpenfabrik Walter Spec Flüssigkeitsringpumpe mit Nabensteuerung

Also Published As

Publication number Publication date
AU577390B2 (en) 1988-09-22
EP0183813A1 (de) 1986-06-11
FI860563A (fi) 1986-02-07
FI83905C (fi) 1991-09-10
JPH0643838B2 (ja) 1994-06-08
DE3567941D1 (en) 1989-03-02
FI860563A0 (fi) 1986-02-07
DK67586A (da) 1986-02-12
JPS61502407A (ja) 1986-10-23
DE3421866A1 (de) 1985-12-19
AU4432185A (en) 1986-01-10
WO1986000117A1 (en) 1986-01-03
DK152858B (da) 1988-05-24
DK152858C (da) 1988-10-24
ES287425Y (es) 1986-07-16
SG44789G (en) 1990-03-09
US4710105A (en) 1987-12-01
CA1329185C (en) 1994-05-03
ES287425U (es) 1985-12-16
ZA854150B (en) 1986-02-26
FI83905B (fi) 1991-05-31
DK67586D0 (da) 1986-02-12

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