US3771898A - Liquid ring compressor - Google Patents

Liquid ring compressor Download PDF

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Publication number
US3771898A
US3771898A US00164374A US3771898DA US3771898A US 3771898 A US3771898 A US 3771898A US 00164374 A US00164374 A US 00164374A US 3771898D A US3771898D A US 3771898DA US 3771898 A US3771898 A US 3771898A
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US
United States
Prior art keywords
pressure
wall
delivery pipe
compartment
pressure port
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
US00164374A
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English (en)
Inventor
U Segebrecht
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.)
Siemen and Hinsch GmbH
Original Assignee
Siemen and Hinsch GmbH
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 Siemen and Hinsch GmbH filed Critical Siemen and Hinsch GmbH
Application granted granted Critical
Publication of US3771898A publication Critical patent/US3771898A/en
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
    • F04C19/004—Details concerning the operating liquid, e.g. nature, separation, cooling, cleaning, control of the supply
    • 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 noise made by these machines can be extremely unpleasant, so that special measures are necessary for damping the noise, in particular when these machines operate in work rooms or in the vicinity of dwelling places.
  • the noise is particularly disturbing if, for example, a water seal compressor is running with a high vacuum on the suction side in the cavitation zone.
  • the noise can be very unpleasant if a liquid seal compressor delivers a relatively large quantity of gas at low compression ratio.
  • Vane-type pumps having-a rotary liquid seal in which a settling or separation chamber is arranged around the pump shaft, without special measures having been taken for effective sound damping.
  • a water ring air pump having a settling chamber in which the settling chamber is designed to also damp sound and comprises a vessel mounted on the overhead pressure delivery pipe of the pump and having a larger cross-section than that of the pressure delivery pipe..
  • This arrangement is expensive constructionally and the air pump must deliver against a relatively high liquid column on its pressure or delivery side.
  • a liquid seal gas pump is known furthermore in which the pressure port is subdivided, together with the pressure chamber, into two sectors, for the purpose of separate discharge of liquid and gas, the lower rim of the pressure delivery pipe lying above the start of the pressure port.
  • This arrangement has the purpose of reducing noise in the case of high vacuum on the suction side and is not suited therefore to all operating conditions of the machine.
  • the present invention has the object of damping with the simplest means those noises which occur on the delivery side of liquid seal compressors.
  • this object is achieved in that the part of the pressure chamber connected with the pressure delivery pipe is partially separated from the part connected with the pressure port by at least one wall descending into the zone of the pressure chamber filled with liquid.
  • the pressure port is in the upper region of the pressure chamber
  • the pressure delivery pipe is connected to the top of the chamber
  • a wall arranged in the pressure chamber extends from the'top downwards to below the pressure port, or, in the case of an approximately central pressure delivery pipe, the wall arranged in the .pressure chamber extends downwards to below the lower rim of the pressure delivery pipe.
  • two walls can be arranged such that a first wall extends from the top downwards to below the pressure port and a second wall, behind the first wall in terms of flow direction, rises from the bottom upwards to above the lower edge of the first wall.
  • a first wall can rise upwards to above the pressure port and a second wall, behind the first wall in terms of flow direction, can descend downwards to below-the upper edgeof the first wall.
  • a single wall extends downwards to below the lower rim of the pressure delivery pipe, whereas with the pressure delivery pipe connected to the bottom of the chamber a first wall extends upwards to above the pressure port and a second wall, in front of the first wall in terms of flow direction, extends downwards to below the upper edge of the first wall.
  • At least one of the walls forms a straight, curved or bent extension of the pressure delivery pipe.
  • the wall as an extension of the pressure delivery pipe does not cover the entire axial dimension of the pressure chamber. It consists advantageously of a length of pipe which leaves free a part of the axial dimension of the pressure chamber.
  • more than two walls can be arranged in the pressure chamber, which cover the axial dimension of the pressure chamber either wholly or in part and separate the space in connection with the pressure delivery pipe from the pressure port.
  • FIGS. 1 to 18 nine different embodiments, each in two sections perpendicular to one another.
  • the suction chamber has been omitted from the right side of the Figure as it has no bearingon the present invention.
  • like components bear the same reference numerals, as follows: impeller 1, control disc 2, suction port 3 as shown in FIG. lib, pressure port 4, pressure reservoir chamber 5, pressure delivery pipe 6, wall 7 and wall 8.
  • the main liquid level in the pressure chamber is indicated in the Figures having even numbers by a horizontal, broken line, although because of mixing of the flowing media on the way from the pressure port to the delivery pipe this liquid level will be disturbed or agitated.
  • the advantage which can be obtained in accordance with the invention lies in that using the simplest of means, although the production of noise is not prevented, nevertheless its spread is substantially damped, since the direct air-borne sound, which normally originates at the pressure port where the discharge mixture enters into the gas compartment of the pressure chamber, is prevented by at least one wall arranged in the pressure chamber from entering into the delivery pipe directly from the gas compartment of the pressure chamber and reaching the human ear.
  • the wall or walls consisting for example of cast iron, must have satisfactory damping properties as must the housing wall of the pressure chamber itself.
  • one wall is sufficient, when two walls are not required for hydraulic reasons as for example in FIG. 6, to damp the direct air-borne sound; however, multiple partition walls arranged in the manner of a labyrinth in the pressure chamber bring about better sound damping.
  • noises emitted indirectly from the housing wall of the pressure chamber will be reduced only slightly and contribute their portion of total noise.
  • the dissipation of the remaining sound energy takes place in the discharge mixture which is located in front of and behind the wall or walls and in the delivery pipe.
  • the gas-liquid mixture is the most suitable chiefly because of its inhomogeneity, for the noises to be damped have extremely varied frequencies.
  • the operating wall extends down to below'the pressure port or to below the lower rim of the delivery pipe and descends into the zone of the pressure chamber filled with liquid, that is to say if necessary it descends sufficiently far to ensure a reliable exclusion of sound.
  • the type of structure shown in FIGS. ll 4, 9, 10, and 13-18 the operating wall extends down to below'the pressure port or to below the lower rim of the delivery pipe and descends into the zone of the pressure chamber filled with liquid, that is to say if necessary it descends sufficiently far to ensure a reliable exclusion of sound.
  • the first wall extending to below the pressure port can descend into the lower region of the pressure chamber, that is to say if necessary a considerable way down, while the other wall, which in terms of flow direction is behind the first wall, and which extends upwards to above the lower edge of the first wall, can be extended into the upper gas-filled zone of the pressure chamber and if necessary a considerable way upwards.
  • the first wall extending upwards to above the pressure port, as far as into the upper gas-filled part of the pressure chamber, and according to requirements possibly a considerable way upwards
  • the other wall which in terms of flow direction is in front of the first wall, and extends downwards to below the upper edge of the first wall, can also extend deep into the lower liquid-filled zone of the pressure chamber.
  • a liquid seal compressor having an impeller, a pressure chamber at the outlet of the impeller and at least one control disc having a pressure port disposed between the impeller and the pressure chamber, the pressure port providing communication therebetween and a pressure delivery pipe communicating with the pressure chamber for delivery of the pressurized fluid
  • the improvement for reducing noise emanating from the pressure port from being transmitted to the pressure delivery pipe comprising a wall means within the pressure chamber partially separating the chamber into a first compartment communicating with the pressure port and a second compartment communicating with the pressure delivery pipe, said wall extending into the liquid in the bottom of the pressure chamber, whereby the magnitude of the sound waves emanating from the pressure port are substantially reduced before reaching the pressure delivery pipe.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Jet Pumps And Other Pumps (AREA)
US00164374A 1970-07-22 1971-07-20 Liquid ring compressor Expired - Lifetime US3771898A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2036295A DE2036295C3 (de) 1970-07-22 1970-07-22 Flüssigkeitsringverdichter

Publications (1)

Publication Number Publication Date
US3771898A true US3771898A (en) 1973-11-13

Family

ID=5777487

Family Applications (1)

Application Number Title Priority Date Filing Date
US00164374A Expired - Lifetime US3771898A (en) 1970-07-22 1971-07-20 Liquid ring compressor

Country Status (16)

Country Link
US (1) US3771898A (enrdf_load_stackoverflow)
JP (1) JPS5145082B1 (enrdf_load_stackoverflow)
AT (1) AT306221B (enrdf_load_stackoverflow)
BE (1) BE770188A (enrdf_load_stackoverflow)
CA (1) CA939309A (enrdf_load_stackoverflow)
CH (1) CH529296A (enrdf_load_stackoverflow)
DE (1) DE2036295C3 (enrdf_load_stackoverflow)
DK (1) DK131054B (enrdf_load_stackoverflow)
ES (1) ES393545A1 (enrdf_load_stackoverflow)
FI (1) FI52621C (enrdf_load_stackoverflow)
FR (1) FR2103218A5 (enrdf_load_stackoverflow)
GB (1) GB1355116A (enrdf_load_stackoverflow)
IT (1) IT943524B (enrdf_load_stackoverflow)
NL (1) NL167225C (enrdf_load_stackoverflow)
SE (1) SE375134B (enrdf_load_stackoverflow)
ZA (1) ZA714902B (enrdf_load_stackoverflow)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392783A (en) * 1980-12-12 1983-07-12 The Nash Engineering Company Liquid ring pump employing discharged pumping liquid for discharge port control
US4449891A (en) * 1981-06-13 1984-05-22 Robert Bosch Gmbh Aggregate for supplying fuel from supply container to internal combustion engine
US4710105A (en) * 1984-06-13 1987-12-01 Sihi Gmbh & Co. Kg Liquid-ring compressor unit
US5096386A (en) * 1989-11-17 1992-03-17 Sundstrand Corporation Integral liquid ring and regenerative pump
US5639221A (en) * 1995-08-21 1997-06-17 Siemens Aktiengesellschaft Liquid ring compressor with side shield located inlet separator
AU693307B2 (en) * 1994-12-23 1998-06-25 Sterling Fluid Systems (Germany) Gmbh Liquid ring gas pump with a silencer in the pressure chamber
WO2011128502A3 (en) * 2010-04-14 2012-05-31 Evac International Oy Liquid ring pump and method for operating a liquid ring pump

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3230069C2 (de) * 1982-08-12 1987-05-07 Wacker-Chemie GmbH, 8000 München Verfahren und Vorrichtung zur Abtrennung und Reinigung von Vinylchlorid aus Abgasen, die aus Vinylchlorid-Polymerisationen stammen
DE3337837A1 (de) * 1983-10-18 1985-04-25 Siemens AG, 1000 Berlin und 8000 München Fluessigkeitsringpumpe
EP0547436B1 (de) * 1991-12-17 1995-03-08 Siemens Aktiengesellschaft Flüssigkeitsringpumpe
DE9314146U1 (de) * 1993-09-18 1995-01-26 Sihi GmbH & Co KG, 25524 Itzehoe Flüssigkeitsringgaspumpe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1529815A (en) * 1923-10-06 1925-03-17 Siemen Otto Rotary pump
GB468590A (en) * 1936-09-29 1937-07-08 Fabig Georg Improvements relating to rotary pumps
US2101389A (en) * 1936-10-16 1937-12-07 Robert L Miller Muffler
US2808780A (en) * 1952-10-07 1957-10-08 Philips Corp Rotary pump
US2860722A (en) * 1954-08-23 1958-11-18 Gen Motors Corp Silencer
US3228587A (en) * 1962-10-17 1966-01-11 Siemen & Hinsch Gmbh Liquid-ring gas pumps

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL289207A (enrdf_load_stackoverflow) * 1900-01-01
GB121518A (en) * 1917-12-19 1918-12-19 Ransomes & Rapier Ltd Improvements in or relating to Rotary Pumps.
DE350594C (de) * 1920-09-30 1922-03-23 Carlo Bonzanigo Fluegelradgeblaese mit umlaufendem abdichtenden Fluessigkeitsring
US1768279A (en) * 1927-09-26 1930-06-24 Auto Prime Pump Company Air pump
GB377476A (en) * 1931-09-01 1932-07-28 Drysdale & Co Ltd Improvements in air-pumps

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1529815A (en) * 1923-10-06 1925-03-17 Siemen Otto Rotary pump
GB468590A (en) * 1936-09-29 1937-07-08 Fabig Georg Improvements relating to rotary pumps
US2101389A (en) * 1936-10-16 1937-12-07 Robert L Miller Muffler
US2808780A (en) * 1952-10-07 1957-10-08 Philips Corp Rotary pump
US2860722A (en) * 1954-08-23 1958-11-18 Gen Motors Corp Silencer
US3228587A (en) * 1962-10-17 1966-01-11 Siemen & Hinsch Gmbh Liquid-ring gas pumps

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392783A (en) * 1980-12-12 1983-07-12 The Nash Engineering Company Liquid ring pump employing discharged pumping liquid for discharge port control
US4449891A (en) * 1981-06-13 1984-05-22 Robert Bosch Gmbh Aggregate for supplying fuel from supply container to internal combustion engine
US4710105A (en) * 1984-06-13 1987-12-01 Sihi Gmbh & Co. Kg Liquid-ring compressor unit
AU577390B2 (en) * 1984-06-13 1988-09-22 Sihi Gmbh & Co Kg Liquid ring compressor
US5096386A (en) * 1989-11-17 1992-03-17 Sundstrand Corporation Integral liquid ring and regenerative pump
AU693307B2 (en) * 1994-12-23 1998-06-25 Sterling Fluid Systems (Germany) Gmbh Liquid ring gas pump with a silencer in the pressure chamber
US5639221A (en) * 1995-08-21 1997-06-17 Siemens Aktiengesellschaft Liquid ring compressor with side shield located inlet separator
WO2011128502A3 (en) * 2010-04-14 2012-05-31 Evac International Oy Liquid ring pump and method for operating a liquid ring pump
US8944778B2 (en) 2010-04-14 2015-02-03 Evac International Oy Liquid ring pump and method for operating a liquid ring pump
RU2569988C2 (ru) * 2010-04-14 2015-12-10 Евак Ой Жидкостный кольцевой насос и способ приведения в действие жидкостного кольцевого насоса

Also Published As

Publication number Publication date
ZA714902B (en) 1972-04-26
NL7110025A (enrdf_load_stackoverflow) 1972-01-25
GB1355116A (en) 1974-06-05
FR2103218A5 (enrdf_load_stackoverflow) 1972-04-07
AT306221B (de) 1973-03-26
NL167225C (nl) 1981-11-16
JPS5145082B1 (enrdf_load_stackoverflow) 1976-12-02
DK131054C (enrdf_load_stackoverflow) 1975-10-20
IT943524B (it) 1973-04-10
CA939309A (en) 1974-01-01
CH529296A (de) 1972-10-15
BE770188A (fr) 1971-12-01
FI52621B (enrdf_load_stackoverflow) 1977-06-30
DK131054B (da) 1975-05-20
DE2036295B2 (de) 1973-09-20
SE375134B (enrdf_load_stackoverflow) 1975-04-07
FI52621C (fi) 1977-10-10
ES393545A1 (es) 1974-08-01
NL167225B (nl) 1981-06-16
DE2036295A1 (de) 1972-01-27
DE2036295C3 (de) 1975-09-18

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