EP0050638B1 - Drehkolbenverdichter - Google Patents

Drehkolbenverdichter Download PDF

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Publication number
EP0050638B1
EP0050638B1 EP81901136A EP81901136A EP0050638B1 EP 0050638 B1 EP0050638 B1 EP 0050638B1 EP 81901136 A EP81901136 A EP 81901136A EP 81901136 A EP81901136 A EP 81901136A EP 0050638 B1 EP0050638 B1 EP 0050638B1
Authority
EP
European Patent Office
Prior art keywords
oil
compressor
manifold
air
housing
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
EP81901136A
Other languages
English (en)
French (fr)
Other versions
EP0050638A1 (de
Inventor
Edward Boller
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.)
Hydrovane Compressor Co Ltd
Original Assignee
Hydrovane Compressor Co Ltd
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 Hydrovane Compressor Co Ltd filed Critical Hydrovane Compressor Co Ltd
Publication of EP0050638A1 publication Critical patent/EP0050638A1/de
Application granted granted Critical
Publication of EP0050638B1 publication Critical patent/EP0050638B1/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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation

Definitions

  • the invention relates to rotary oil mist compressors and is concerned with that type of compressor having a housing within which there is a rotor stator unit in which, in use, air is compressed and oil is injected into the air and including a primary oil separation means for removing a proportion of the entrained oil from the air and a secondary oil separation means for removing substantially the remainder of the oil, the rotor stator unit and the primary separation means being situated in the compressor housing and the secondary separation means being situated in a separate housing detachably secured to the compressor housing, the primary and secondary oil separation means being connected by a pathway.
  • oil mist compressor is used herein to refer to those compressors, e.g. of eccentric rotor sliding vane type or of screw type, in which oil is injected into the air to be compressed and is subsequently separated from the compressed air, the separated oil being returned to the air inlet or sump of the compressor.
  • Eccentric rotor sliding vane compressors generally separate the entrained oil from the air in two stages.
  • the primary stage may consist of a tortuous passage or an impingement shield situated adjacent the outlets from the rotor stator unit, and a proportion of the oil droplets are induced to coalesce on the surface of the passage or the impingement shield and are then returned to the sump.
  • the secondary separation stage may consist of one or more felt pads or other filtering or coalescing media adapted to remove the majority of the remaining oil from the compressed air.
  • British Patent No. 783340 discloses a typical construction in which the primary separation stage is constituted by a tortuous pathway for the compressed air and the secondary stage comprises a tubular felt filler arranged with its axis vertical in a separate housing connected to the compressor casing.
  • the small quantity of oil which may coalesce in the substantially straight pathway between the primary and secondary separation stages is ultimately re-entrained by the compressed air and must thus be removed by the secondary separation stage. It is desirable that the separation of the oil from the compressed air be as efficient as possible, firstly because it is frequently inconvenient from the compressed air to have a significant amount of entrained oil in it, and secondly because oil that is not separated is lost and must subsequently be replaced.
  • a compressor of the type referred to above is characterised in that the pathway connecting the primary and secondary oil separation means includes a secondary separation manifold, in which, in use, oil droplets colesce and collect, there being an oil return passageway communicating with the manifold adapted to return the oil collected in the manifold back to the compressor housing for re-use, the compressor housing and the secondary separation housing communicating by means of a tube which has apertures in its side wall at its inlet end communicating with the interior of the compressor housing and apertures in its side wall at its outlet end which communicate with the secondary separation manifold.
  • the pathway is so constructed that, in use, the air is constrained to flow through a substantial angle when flowing out of the secondary separation manifold into the secondary oil separation means.
  • the acceleration and turbulence of the gas that is caused results in the coalescing and deposition of a proportion of the entrained oil thus reducing the separation load to which the secondary separation means is subjected and thus increasing the separation efficiency and service life of the secondary separation means.
  • the oil which is deposited in the secondary separation manifold is then returned to the compressor housing, e.g. to the sump of the housing, through the separate oil return passageway and this is pre- ferablyeffected under the action of the pressure of the compressed air itself.
  • the secondary separation means preferably comprises one or more tubular coalescing elements, of e.g. ceramic material communicating with the interior of the secondary separation manifold and these are preferably arranged with their axes vertical.
  • This latter feature is found to be preferable to arranging the tubular coalescing elements with their axes horizontal as is conventional since the oil trickles rapidly downwards and results in a greater proportion of the elements being unclogged with oil and thus available for separation.
  • the secondary separation manifold thus preferably extends horizontally, e.g. parallel to the rotor axis and the compressed airflows along it and then turns through substantially 90° to flow into the or each coalescing element.
  • the or each coalescing element has within it a tube into which the compressed air is constrained to flow, the or each tube being spaced from the interior of the or each coalescing element and having a plurality of spaced apertures in its wall.
  • the compressed air turns through 90° to enter the tube within the coalescing elements and is constrained to turn through a further bend of 90° when leaving the tube prior to actually passing through the wall of the coalescing element.
  • the apertures also distribute the air, and thus the oil separation load, over substantially the entire area of the or each coalescing element thus further increasing the oil separation efficiency.
  • the or each tube preferably projects into the secondary separation manifold so that separated oil present in the manifold is out of the main air flow and thus not prone to being re-entrained by the flow of the compressed air.
  • the removability of the secondary separation housing facilitates exchange and servicing of the coalescing elements.
  • the secondary separation housing has a compressed air outlet at its upper end.
  • the compressed air will therefore pass through the coalescing elements and then up to the outlet, while the coalesced oil will trickle downwards. This will mean that the oil will accumulate in a comparatively calm area of the secondary separation housing thus reducing the risk that it be re-entrained by the compressed air.
  • the compressor preferably includes a removable hollow oil return member, e.g. a bolt, which preferably extends into, and whose interior communicates with that of, the secondary separation manifold through which oil is returned for re-use. If the oil return member should become blocked it may be removed, cleared and replaced.
  • the compressor is of eccentric rotor sliding vane type having a compression section, seen in Figure 1, within a housing 2 removably connected to the side of which by bolts 3 is a separate secondary oil separation section within a housing 4.
  • the compression section of the compressor does not differ significantly from known constructions and will therefore only be described briefly.
  • the housing 2 is closed by two removable end plates 6 and 8 between which a stator 10 is secured. Eccentrically mounted within the stator is rotor 12 which may be rotated by a drive shaft 14 and which leaves a crescent shaped working space within the stator. A series of longitudinal slots are formed in the rotor each of which accommodates a sliding vane 16.
  • the lower portion of the housing 2 defines an oil sump.
  • oil is circulated by virtue of the compressor pressure through one or more oil coolers 7 in which the oil is cooled by virtue of an air flow caused by fan blades 9 on the drive shaft 14.
  • the rotor In use the rotor is rotated and the vanes are kept in contact with the interior of the stator by centrifugal force. Air is drawn into the stator through an inlet 18 which is controlled by an unloader valve 20 of known type. Oil is withdrawn from the sump and injected into the crescent shaped working space within the stator which ensures an adequate gas seal between the vanes and the stator and the end plates. The air within the crescent shaped working space is compressed as the rotor rotates, and the compressed air exits through a series of outlet ports 22 in the upper part of the stator.
  • an impingement shield 24 Surrounding the stator and coaxial with it is an impingement shield 24 which constitutes the primary separation section connected to the right hand end plate 8 and which extends down below the oil level in the sump as indicated by the dotted line marked 25 in Figure 2.
  • the air then passes towards and out through an outlet 26 into the secondary separation section.
  • the outlet 26 is a thermally actuated shut-off valve of the type described in British patent specification No. 1218769 and comprises a fixed tube 28 at the inlet end of which is a cap 30 having a closed end and apertures 32 formed in its side wall which fits inside the wall of the tube 28.
  • a spring 34 urges the cap into the closed position in which no gas can pass in through the apertures 32.
  • the cap 30 is secured in the open position by solder so that air can flow into it. If however the temperature of the compressed air should rise above a predetermined value the solder melts and the tube is closed by the cap 30 under the action of the spring 34.
  • the compressor pressure will then rise rapidly and the compressor will be throttled down by the unloader valve and then optionally turned off altogether by control means (not shown).
  • outlet apertures 36 which communicate with a secondary separation manifold 38.
  • a secondary separation manifold 38 Within the housing 4 there are two vertically arranged tubular ceramic secondary separation oil filters or coalescing elements 40 whose lower ends are closed and which are connected at their upper ends with opposite ends of the manifold 38.
  • a coaxially disposed metallic tube 42 Within each coalescing element there is a coaxially disposed metallic tube 42 whose lower end is closed, whose upper end communicates with the interior of the manifold 38 and is provided with a plurality of outlet apertures 44 spaced around its periphery and along its length. Compressed air in the manifold 38 therefore passes down into the tubes 42, through the outlet apertures 44 and thence through the walls of the ceramic tubes 40 along substantially their entire length. The air then passes upwardly in the housing 4 and out through an outlet 46.
  • an oil return bolt comprising a hollow tubular bolt 48, seen in Figure 4, in the wall of which a number of apertures 50 are formed. Entrained oil that is coalesced and separated from the air in the manifold flows through the apertures 50 and is then returned to the sump by the compressor pressure through a bore 52.
  • the two ceramic elements 40 are separated by a baffle 54 upstanding from the floor of the housing 4. Oil separated by the ceramic elements drips down on to the floor and then into a respective oil return aperture 56 whence it is returned to the sump by the compressor pressure through a common oil return bore 58.
  • the air is compressed as described above and a considerable proportion of the entrained oil is coalesced against the primary separation means constituted by the primary impingement shield 24 and drips down to the sump.
  • the air then passes round the end of the impingement shield 24 turning through 180°, as shown by the arrows in Figure 1, the acceleration and turbulence caused thereby resulting in further coalescing and deposition of oil.
  • the air then passes through one of the apertures 32 into the tube 28, thereby turning through a further 90°. Any oil that is coalesced during this turn will also drip down to the sump or will sink to the bottom of the tube 28.
  • the flow path of the air then turns through a further 90° when passing through one of the apertures 36 into the manifold 38.
  • Oil coalesced at this point will be deposited in the manifold 38, or in the tube 28 whence it will drip into the manifold.
  • the air in the manifold then passes into one or other of the tubes 42, thus turning through a further bend of about 90°.
  • the air then further passes through one of the apertures 44 in the tubes 42, turning through a further 90° bend and then through the material of the ceramic elements 40, where substantially all the remaining entrained oil is coalesced. Finally the air passes upwards and then out through the outlet 46.
  • Oil that is deposited within the manifold 38 is returned to the sump by the oil bolt 48 as described above, whilst oil coalesced by the ceramic elements 40 flows downwardly, drips onto the floor of the housing 4 and is returned to the sump via the bore 58.
  • the compressor in accordance with the invention provides compressed air that is substantially free of entrained oil because oil is separated from the air not only in the primary and secondary separation areas but also in the pathway between these two areas by virtue of the great number of bends in the pathway. Much of this oil is deposited or accumulated in the secondary separation manifold and it is then returned for re-use by a separate oil return passage and not re-entrained by the compressed air. If one or more of the ceramic elements should become clogged it may simply be replaced by removing the lower portion of the housing 4. The entire housing 4 is detachable from the remainder of the compressor which facilitates access and servicing. It will be appreciated that any desired number of ceramic elements may be used according to requirements and in addition these may be arranged in series rather than in parallel.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Claims (5)

1. Rotierender Ölnebel-Kompressor mit einem Kompressorgehäuse (2), in dem sich eine Rotor-Stator-Einheit (10, 12) befindet, in der im Betrieb Luft verdichtet und Öl in die Luft eingespritzt wird, und mit einer Primär-Ölabscheideranordnung (24) zum Entfernen eines Teiles des mitgeführten Öls aus der verdichteten Luft sowie mit einer Sekundär-Ölabscheideranordnung (40) zum Entfernen im wesentlichen des Restes des mitgeführten Öls, wobei die Rotor-Stator-Einheit (10, 12) sowie die Primär-Abscheideranordnung (24) im Kompressorgehäuse (22) und die Sekundär-Abscheideranordnung (40) im einem getrennten Gehäuse (4), das lösbar am Kompressorgehäuse (2) befestigt ist, angeordnet sind und die Primär- und die Sekundär-Ölabscheideranordnung durch einen Strömungsweg verbinden sind, dadurch gekennzeichnet, daß der Strömungsweg einen Sekundärabscheidervertiler (38) enthält, in dem die Öltröpfchen im Betrieb koaleszieren und sich sammeln, daß ein Ölrückführungsweg (48, 52) vorgesehen ist,= der mit dem Verteiler in Verbindung steht und geeignet ist, das im Verteiler gesammelte Öl zur Wiederverwendung in das Kompressorgehäuse zurückzuleiten, und daß das Kompressorgehäuse (2) und das Sekundärabscheidergehäuse (4) durch eine Röhre (28) miteinander in Verbindung stehen, die Öffnungen (32) in ihrer Seitenwand an ihrem mit dem Inneren des Kompressorgehäuses (2) in Verbindung stehenden Einlaßende und Öffnungen (36) in ihrer Seitenwand an ihrem mit dem Sekundärabscheiderverteiler (38) in Verbindung stehenden Auslaßende aufweist.
2. Kompressor nach Anspruch 1, dadurch gekennzeichnet, daß der Strömungsweg so konstruiert ist, daß die Luft im Betrieb gezwungen wird, einen beträchtlichen Winkel zu durchströmen, wenn sie aus dem Sekundärabscheiderverteiler (38) in die Sekundär-Ölabscheideranordnung (40) strömt.
3. Kompressor nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Sekundär-Abscheideranordnung ein oder mehrere röhrenförmige Koaleszierungselemente (40), die mit ihrer Achse im wesentlichen vertikal angeordnet sind, und eine Röhre (42) innerhalb jedes Koaleszierungselements (40) enthält, in die die verdichtete Luft gezwungen wird, zu strömen, wobei die Röhre oder jede Röhre (42) im Abstand vom Inneren des zugehörigen Koaleszierungselementes (40) angeordnet ist und in ihrer Wand eine Mehrzahl von im Abstand voneinander angeordneten Öffnungen (44) aufweist.
4. Kompressor nach Anspruch 3, dadurch gekennzeichnet, daß die oder jede Röhre (40) in den Sekundärabscheiderverteiler (38) so vorspringt, daß das im Verteiler (38) vorhandene agbetrennte Öl im Betrieb sich außerhalb des Hauptluftstromes befindet.
5. Kompressor nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Röhre (28) zwischen dem Kompressorgehäuse (2) und dem Sekundärabscheidergehäuse (4) einen Teil eines thermisch gesteuerten Ventils bildet.
EP81901136A 1980-05-02 1981-05-01 Drehkolbenverdichter Expired EP0050638B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB8014662 1980-05-02
GB8014662A GB2075597B (en) 1980-05-02 1980-05-02 Rotary air compressors

Publications (2)

Publication Number Publication Date
EP0050638A1 EP0050638A1 (de) 1982-05-05
EP0050638B1 true EP0050638B1 (de) 1984-02-22

Family

ID=10513176

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81901136A Expired EP0050638B1 (de) 1980-05-02 1981-05-01 Drehkolbenverdichter

Country Status (7)

Country Link
EP (1) EP0050638B1 (de)
DE (1) DE3162344D1 (de)
ES (1) ES501757A0 (de)
GB (1) GB2075597B (de)
HK (1) HK97384A (de)
IT (1) IT8148385A0 (de)
WO (1) WO1981003207A1 (de)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3149245A1 (de) * 1981-12-11 1983-06-16 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried "verdichteranlage"
GB2119443A (en) * 1982-04-24 1983-11-16 Gen Eng Radcliffe 1979 An oil sealed pump
DE3442626A1 (de) * 1984-11-22 1986-05-22 Rotorcomp Verdichter GmbH, 8000 München Fluidabscheider, insbesondere gas/fluessigkeit-abscheider
DE3521977A1 (de) * 1985-06-20 1987-01-02 Mahle Gmbh Kompakte luftverdichteranlage, insbesondere mit einem schraubenrotorenverdichter
GB2227057B (en) * 1988-12-22 1993-01-13 Multiphase Systems Plc Improvements in pumps
US5029448A (en) * 1990-01-23 1991-07-09 American Standard Inc. Oil separator for refrigeration systems
US5053126A (en) * 1990-02-28 1991-10-01 Ingersoll-Rand Company Apparatus for gas liquid separation
SE512435C2 (sv) * 1998-07-07 2000-03-20 Svenska Rotor Maskiner Ab Vätskeavskiljare för en vätskeinsprutad kompressor, särskilt en oljeavskiljare för en oljeinsprutad kylkompressor av skruvrotortyp

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2047728A (en) * 1933-06-22 1936-07-14 Laval Separator Co De Means for preventing oil fog from air pumps
GB783340A (en) * 1954-07-20 1957-09-25 Lead Wool Company Ltd Improvements in or relating to rotary air compressors
DE1293386B (de) * 1960-05-24 1969-04-24 Becker Gmbh Geb Drehkolbenverdichter oder -Vakuumpumpe
US3191854A (en) * 1960-06-02 1965-06-29 Atlas Copco Ab Compressor units
GB1486942A (en) * 1974-04-17 1977-09-28 Hydrovane Compressor Positive displacement compressors
IT7849496A0 (it) * 1977-05-25 1978-05-23 Hydrovane Compressor Perfezionamento nei compressori a capsulismo del tipo a tenuta di olio
GB2020750A (en) * 1978-03-13 1979-11-21 Imi Fluidair Ltd Rotary compressor

Also Published As

Publication number Publication date
ES8300954A1 (es) 1982-11-01
ES501757A0 (es) 1982-11-01
EP0050638A1 (de) 1982-05-05
GB2075597B (en) 1983-10-26
DE3162344D1 (en) 1984-03-29
GB2075597A (en) 1981-11-18
IT8148385A0 (it) 1981-04-30
WO1981003207A1 (en) 1981-11-12
HK97384A (en) 1984-12-21

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