EP0401397B1 - Flüssigkeitsringverdichter - Google Patents

Flüssigkeitsringverdichter Download PDF

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Publication number
EP0401397B1
EP0401397B1 EP89110169A EP89110169A EP0401397B1 EP 0401397 B1 EP0401397 B1 EP 0401397B1 EP 89110169 A EP89110169 A EP 89110169A EP 89110169 A EP89110169 A EP 89110169A EP 0401397 B1 EP0401397 B1 EP 0401397B1
Authority
EP
European Patent Office
Prior art keywords
pressure
compressor
liquid ring
opening
additional openings
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 - Lifetime
Application number
EP89110169A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0401397A1 (de
Inventor
Peter Dipl.-Ing. Trimborn
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.)
Siemens AG
Original Assignee
Siemens AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8201464&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0401397(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP89110169A priority Critical patent/EP0401397B1/de
Priority to AT89110169T priority patent/ATE82620T1/de
Priority to DE8989110169T priority patent/DE58902779D1/de
Priority to FI902195A priority patent/FI902195A7/fi
Priority to US07/527,012 priority patent/US5073089A/en
Priority to CA002018032A priority patent/CA2018032A1/en
Priority to JP1990058402U priority patent/JPH035996U/ja
Publication of EP0401397A1 publication Critical patent/EP0401397A1/de
Publication of EP0401397B1 publication Critical patent/EP0401397B1/de
Application granted granted Critical
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C19/005—Details concerning the admission or discharge
    • F04C19/007—Port members in the form of side plates

Definitions

  • the invention relates to a liquid ring compressor according to the preamble of claim 1.
  • Such a liquid ring compressor is known from DE-C-32 10 161.
  • a plurality of additional openings of the same size designed as slots are provided in front of the pressure opening.
  • the invention is therefore based on the object of developing a liquid ring compressor according to the preamble of claim 1 in such a way that the pressure losses of the type mentioned above are further reduced.
  • the additional openings In the case of a liquid ring compressor with a flat control disk, it is particularly advantageous for the additional openings to extend in the radial direction up to the liquid ring extend that the envelope curve over the radially outer ends of the additional openings corresponds at least approximately to the course of the liquid ring which occurs at the nominal pressure ratio of the compressor. As a result, better compatibility of liquid-side liquid conveyance is also achieved. Excess liquid can be expelled through the additional openings reaching to the liquid ring even before the actual pressure opening, so that there are no longer any undesirable pressures causing loss of performance in the area of the apex of the compressor.
  • the desired dimensioning of the passage area of the additional openings is achieved in a liquid ring compressor with a conically shaped control element in that the additional openings are designed as straight-line slots, the length of which decreases towards the pressure opening.
  • the compressor housing which surrounds a blade wheel 5 which is offset eccentrically with respect to the housing axis 4 with its shaft axis 3.
  • the impeller 5 is mounted in bearing plates 6 attached to the compressor housing 2.
  • a suction and pressure port is arranged, of which only the suction port 7 is visible in the sectional view, for example.
  • a flat control disk 8 is inserted between the end shield 6 and the compressor housing 2.
  • This control disk 8 has at least one suction opening 9 and one pressure opening 10. Via these suction and pressure openings 9 and 10, the suction and pressure ports are connected to the respective vane chambers, which overlap with the suction and pressure openings 9 and 10.
  • gas can be sucked into the relevant blade chambers via the suction nozzle 7 and the suction opening 9 and gas can be expelled from the respective blade chambers via the pressure opening 10 and the pressure nozzle.
  • FIGS. 2 and 3 show several additional openings 12 are provided on the flat control disk 8 in relation to the compression direction (arrow 11) in front of the pressure opening 10. These additional openings 12 are covered on the side of the control disk 8 facing away from the impeller 5 by check valves. These check valves open the respective additional opening 12 as soon as there is a slightly higher pressure in the blade chamber passing by than at the pressure port. The gas compressed in the relevant vane chamber can thus flow out.
  • the additional openings 12 are formed in the radial direction with different lengths, the length of the additional openings 12 decreasing towards the pressure opening 10.
  • additional openings 12 thus have a passage area which decreases towards the pressure opening, since their width remains constant and is only slightly wider or equal to or smaller than the thickness of the blades of the impeller 5 is dimensioned.
  • the additional openings 12 are adapted in their radial course to the radial course of the blades, so that the respective additional opening 12 is completely covered when a blade passes by. In this way, backflows through the additional openings 12 between two different blade chambers can be avoided.
  • the additional openings 12 are dimensioned in their radial length such that they extend with their radially outer end 16 up to the course 13 or 14 or 15 of the liquid ring which is set in accordance with the nominal pressure ratio of the liquid ring compressor. This achieves a maximum passage area for each individual additional opening 12 as well as a maximum total passage area for the additional openings 12 released by the check valves at the respective pressure conditions.
  • the passage area available in each case is therefore in a first approximation proportional to the gas mass present in the blade chambers, so that the pressure losses are significantly reduced as a result of this adaptation.
  • a cone-like control element 17 is provided instead of a flat control disk 8.
  • This control element extends coaxially to the shaft 18 of the compressor and engages under the impeller 19 over an axial partial length.
  • a suction and a pressure opening 9 and 10 are again provided on the conical surface 20 of this control element 17, as shown in the development according to FIG. 5, a suction and a pressure opening 9 and 10 are again provided on the conical surface 20 of this control element 17, as shown in the development according to FIG. 5, a suction and a pressure opening 9 and 10 are again provided.
  • a plurality of additional openings 22 are connected upstream of the pressure opening.
  • the width 21 of these additional openings 22 is either slightly wider or the same or smaller than the thickness of the blades on the blade base, so that again a complete coverage of the individual additional openings 22 is achieved by the passing blades.
  • the individual additional openings 22 are shortened toward the pressure opening 10 in relation to the previous additional opening 22.
  • the necessary reduction in the passage area of the additional openings 22 closer to the pressure opening 10 is thus achieved.
  • the reduction from the additional opening to the additional opening is selected such that the total passage area of the additional openings 22, respectively opened by the check valves, is approximately proportional to the gas mass present in the respective vane chambers.
  • the degree of reduction from additional opening to additional opening is determined by the nominal pressure ratio of the compressor.
  • each additional opening 22 opens into a channel 24 formed in the cone body 23 of the cone-shaped control element 17.
  • the channels 24 are closed in themselves except for their outlet opening 26 lying on the end face 25 of the cone-like control element 17 and against each other delimited. A sufficient flow cross-section is available through these channels 24 for the gas mass to be discharged, so that no additional pressure losses occur.
  • this check valve consists of an elastic valve plate 27 resting on the outlet opening 26.
  • a catch plate 28 is arranged at a certain distance from the valve plate 27, against which the valve plate 27 comes to rest ( shown in dashed lines) when gas and / or liquid is expelled via the relevant additional opening 22 and the channel 24.
  • an arrangement is also possible in which the valve tongues protrude into the cone and directly cover the additional openings. This eliminates the gas-filled space between the additional openings and the valve tongues, in accordance with the arrangement shown in FIG.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Acyclic And Carbocyclic Compounds In Medicinal Compositions (AREA)
EP89110169A 1989-06-05 1989-06-05 Flüssigkeitsringverdichter Expired - Lifetime EP0401397B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP89110169A EP0401397B1 (de) 1989-06-05 1989-06-05 Flüssigkeitsringverdichter
AT89110169T ATE82620T1 (de) 1989-06-05 1989-06-05 Fluessigkeitsringverdichter.
DE8989110169T DE58902779D1 (de) 1989-06-05 1989-06-05 Fluessigkeitsringverdichter.
FI902195A FI902195A7 (fi) 1989-06-05 1990-05-02 Nesterengaskompressori
US07/527,012 US5073089A (en) 1989-06-05 1990-05-22 Liquid-ring compressor
CA002018032A CA2018032A1 (en) 1989-06-05 1990-06-01 Liquid-ring compressor
JP1990058402U JPH035996U (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1989-06-05 1990-06-01

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP89110169A EP0401397B1 (de) 1989-06-05 1989-06-05 Flüssigkeitsringverdichter

Publications (2)

Publication Number Publication Date
EP0401397A1 EP0401397A1 (de) 1990-12-12
EP0401397B1 true EP0401397B1 (de) 1992-11-19

Family

ID=8201464

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89110169A Expired - Lifetime EP0401397B1 (de) 1989-06-05 1989-06-05 Flüssigkeitsringverdichter

Country Status (7)

Country Link
US (1) US5073089A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
EP (1) EP0401397B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
JP (1) JPH035996U (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
AT (1) ATE82620T1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
CA (1) CA2018032A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
DE (1) DE58902779D1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
FI (1) FI902195A7 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4126322A1 (de) * 1991-08-08 1993-02-11 Siemens Ag Steuerkoerper fuer einen fluessigkeitsringverdichter
US5356268A (en) * 1993-09-29 1994-10-18 The Nash Engineering Company Check valve structures for liquid ring pumps
GB2303879B (en) * 1995-08-01 1999-09-15 Hick Hargreaves & Co Ltd Liquid ring pump
US6354808B1 (en) * 2000-03-01 2002-03-12 The Nash Engineering Company Modular liquid ring vacuum pumps and compressors
DE10121800C1 (de) * 2001-05-04 2002-08-22 Siemens Ag Flüssigkeitsringpumpe und Steuerscheibe für eine Flüssigkeitsringpumpe
JP5063010B2 (ja) * 2006-02-16 2012-10-31 東光東芝メーターシステムズ株式会社 ガス流量計およびガス流量計用回路ユニット
JP2008102811A (ja) * 2006-10-20 2008-05-01 Matsushita Electric Ind Co Ltd ガス制御システム
JP2008292115A (ja) * 2007-05-28 2008-12-04 Tokyo Gas Co Ltd ガス遮断システム、ガス遮断方法及びガス遮断プログラム
US20110243761A1 (en) * 2010-03-31 2011-10-06 Rusty Darsey Pulsation Dampener for Gas Compressors Having Selectable Size Choke Openings
US9689387B2 (en) * 2012-10-30 2017-06-27 Gardner Denver Nash, Llc Port plate of a flat sided liquid ring pump having a gas scavenge passage therein

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1180613A (en) * 1913-03-19 1916-04-25 Siemens Schuckertwerke Gmbh Rotary pump.
JPS555428A (en) * 1978-06-22 1980-01-16 Nakamura Suikan:Kk Water ring pump of side-air-port type
US4392783A (en) * 1980-12-12 1983-07-12 The Nash Engineering Company Liquid ring pump employing discharged pumping liquid for discharge port control
DE3210161C1 (de) * 1982-03-19 1983-10-06 Siemens Ag Fluessigkeitsringkompressor fuer Gase
US4498844A (en) * 1983-08-08 1985-02-12 The Nash Engineering Company Liquid ring pump with conical or cylindrical port member
US4521161A (en) * 1983-12-23 1985-06-04 The Nash Engineering Company Noise control for conically ported liquid ring pumps
US4551070A (en) * 1983-12-23 1985-11-05 The Nash Engineering Company Noise control for conically ported liquid ring pumps
US4850808A (en) * 1985-03-19 1989-07-25 The Nash Engineering Company Liquid ring pump having port member with internal passageways for handling carry-over gas

Also Published As

Publication number Publication date
ATE82620T1 (de) 1992-12-15
FI902195A7 (fi) 1990-12-06
FI902195A0 (fi) 1990-05-02
US5073089A (en) 1991-12-17
DE58902779D1 (de) 1992-12-24
EP0401397A1 (de) 1990-12-12
CA2018032A1 (en) 1990-12-05
JPH035996U (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1991-01-21

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