EP0030619B1 - Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers - Google Patents

Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers Download PDF

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Publication number
EP0030619B1
EP0030619B1 EP80106829A EP80106829A EP0030619B1 EP 0030619 B1 EP0030619 B1 EP 0030619B1 EP 80106829 A EP80106829 A EP 80106829A EP 80106829 A EP80106829 A EP 80106829A EP 0030619 B1 EP0030619 B1 EP 0030619B1
Authority
EP
European Patent Office
Prior art keywords
compressor
oil
lubricating
bearing
drainage
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
EP80106829A
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German (de)
English (en)
Other versions
EP0030619A1 (fr
Inventor
Karl Prof. Dr.-Ing. Bammert
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.)
CESSIONE;MAN GUTEHOFFNUNGSHUTTE GMBH
Original Assignee
Karl Prof. Dr.-Ing. Bammert
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 Karl Prof. Dr.-Ing. Bammert filed Critical Karl Prof. Dr.-Ing. Bammert
Publication of EP0030619A1 publication Critical patent/EP0030619A1/fr
Application granted granted Critical
Publication of EP0030619B1 publication Critical patent/EP0030619B1/fr
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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for pumps
    • 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

Definitions

  • the invention relates to a rotary compressor, in particular a screw rotor compressor, in which each end of the shaft of the or each rotor is mounted in the housing by means of a radial sliding bearing and is surrounded by a shaft seal between the latter and the working space of the compressor, and a lubricating oil circuit is provided for bearing lubrication, with a lubricating oil container from which from which the lubricating oil is fed to the bearings via an oil pump and lines and into which the lubricating oil that flows from each bearing into a storage space on the side of the bearing facing away from the working space flows back via oil return channels.
  • a compressor of this type is known from DE-OS 2 441 520, in which the annular drainage space is part of an elaborate sealing arrangement of great length, which has the purpose of sucking unfiltered outside air into the working space of the compressor and the leakage of lubricant. and to avoid coolant from the compressor working space along the shaft.
  • the sealing arrangement has, in addition to the drainage space, further annular spaces, one of which is acted upon as a barrier pressure space by a compressed gas source, in particular by the compressor outlet.
  • the annular drainage space opens up to the outside, and this means that the quantities of gas entering the drainage space from the barrier pressure space are lost.
  • a length-increasing seal with sealing oil supply is arranged between the outer chamber and the bearing. Part of the sealing oil gets into the outer chamber, is drawn off together with the leak gas and must be separated from the leak gas by a cyclone separator. If a refrigerant is compressed, parts of it will dissolve in the sealing oil so that it is lost for reuse.
  • the invention has for its object to provide a rotary compressor of the type mentioned, in particular for refrigerant compression, in which a very simple, cheap and space-saving seal arrangement between the work space and the bearing can be used and still both a leakage gas loss and an impairment of the lubricating oil circuit by under Pressure dissolving gas is avoided.
  • a pressure compensation connection is provided between the lubricating oil circuit and the suction side of the compressor, through which the entire lubricating oil circuit on the suction side of the oil pump is essentially under the suction pressure of the compressor, and that between the The shaft seal and the bearing are arranged in a drainage space surrounding the shaft in a ring shape to collect lubricating oil escaping from the bearing on this side and any leakage gas that passes through the shaft seal, which is connected to the associated storage space via a drainage channel and thereby also under the suction pressure of the compressor stands.
  • a second circuit for a coolant and sealant can be provided, which is fed to the working space of the compressor and is separated from the compressed gas stream by a separator connected to the pressure side of the compressor.
  • a connecting line with a valve can be provided between the separator and the separating container of the lubricant circuit, which valve can be controlled by a level switch on the separating container.
  • the compressor has a housing 10, in the working space 12 of which two rotors 14 are mounted next to one another, which engage in one another with helically arranged ribs and grooves. Only one of these rotors 14 is visible in the drawing.
  • the shaft 16 of the rotor is supported at both ends by means of radial sliding bearings 18 and also at the end on the pressure side by means of an axial roller bearing 20.
  • the shaft of one rotor, the main rotor is driven by a drive (not shown), and the main rotor drives the secondary rotor by direct meshing engagement or also by means of a synchronous gear (not shown).
  • the gas to be compressed in particular a refrigerant such as difluoromonochloromethane, which in this case is under the evaporator pressure, is sucked in via the suction line 22 and the suction nozzle 24, compressed in the working chamber 12 by the rotors 14 and via the pressure nozzle 26 and the pressure line 28 as
  • the separator and storage container serving pressure container 30 is supplied, from where it passes through the separating filter 32 and the pipeline 34 to the consumer and, in the case of refrigerants, to the condenser.
  • oil or another liquid suitable as a coolant, sealant and lubricant which is supplied to the working space 12 by means of the line 36 via a cooler 38, a throttle element 40 and the housing bore 42 in order to close the rotors cool, seal against each other and against the housing and lubricate on their meshing flanks.
  • This oil is discharged together with the compressed gas stream via the pressure port 26 and the pressure line 28 and separated from the gas stream in the container 30 and returned to the sump 44.
  • oil is removed from a closed reservoir 46 via a pump 48 and a cooler 50 and fed to the lubricant bores of the bearings 18 via the line 52 and the housing channels 54. From these lubricant holes, the oil enters the bearing gap in both axial directions. A portion of the oil passes directly from the bearing gap into the oil collecting spaces 56, 58, which are connected to one another by a longitudinal channel 60 in the housing 10. The portion of the oil which occurs in the direction of the working space passes from the respective bearing 18 into an annular oil collecting groove 62 which is arranged as a drainage space between each bearing 18 and a sealing element 64 and is connected to the associated oil collecting space 56 and 58 by a channel 66 in each case is.
  • the oil collecting space 56 is connected to the reservoir 46 via an outlet channel 68.
  • the gas space of the reservoir 46 is also connected to the suction line 22 via a compensating line 70.
  • the oil collecting groove 62 which is under low pressure and is arranged between each bearing 18 and the working space 12, effectively leaks oil from the bearing 18 to the working space 12 or vice versa, leaks gas from the working space 12 to the bearing 18 largely prevented.
  • the additional sealing elements 64 are therefore not particularly demanding, it can be simple and very short elements such. B. act short labyrinths or swim rings. These can also be supplied with oil and lubricant pressure through appropriate housing bores, as shown for the pressure-side sealing element.
  • the oil therein can only contain relatively small amounts of a soluble gas, e.g. B. refrigerant, dissolved.
  • a soluble gas e.g. B. refrigerant
  • the corresponding proportion in the reservoir 46 at a pressure of z. B. 5 bar and a temperature of 70 ° C significantly less than 5%, which practically does not affect the viscosity of the oil.
  • a level switch 74 with lower and upper limit contact controls on the one hand a solenoid valve 76, which connects the line 36 to the reservoir 46, and also a solenoid valve 78, which connects the line 52 to the suction line 22 of the compressor.
  • the solenoid valve 76 is opened and oil can get into the container 46 from the pressure container 30. If the oil level in the container 46 rises excessively, the valve 78 opens and excess oil from the container 46 enters the suction line and from there with the gas through the compressor into the reservoir pressure container 30.
  • FIG. 2 shows a simplified embodiment for those applications in which there is no risk of the viscosity of the oil being reduced by dissolved gas because of low working pressures or with gases which are not soluble in oil.
  • the same compressor design as in Fig. 1 can be used without structural changes.
  • Is omitted and the outlet opening 68 of the oil collecting space 56, which is no longer required, is closed with a stopper 80.
  • one of two bores 82, 84 is optionally opened, which connect the longitudinal channel 60 to the intake port 24 or the working chamber 12 of the compressor and of which the other bore or, when used according to FIG. 1, both bores with suitable ones Stopper 86 are closed.
  • the resulting differential pressure between the pressure container 30 and the lubrication or injection points on the compressor is sufficient to the compressor to supply with oil without fear of gas breakthrough to the bearings due to the relatively low lubricant pressure in the bearing.

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

Claims (4)

1. Compresseur rotatif, en particulier compresseur à rotor à vis, dans lequel chaque extrémité de l'arbre (16) du ou de chaque rotor (14) est montée dans le carter (10) au moyen d'un palier lisse (18) et est entourée, entre ce dernier et la chambre de travail (12) du compresseur, d'un dispositif d'étanchéité d'arbre (64) et dans lequel il est prévu, pour la lubrification des paliers, un circuit d'huile lubrifiante comportant un réservoir de lubrifiant (46), à partir duquel l'huile lubrifiante est envoyée dans les paliers (18) au moyen d'une pompe à huile (48) et de conduites (52) et dans lequel l'huile lubrifiante, qui s'écoule de chaque palier dans une chambre de palier (56, 58) située du côté opposé à la chambre de travail (12) par rapport au palier, est renvoyée par des conduits de retour d'huile (60, 68), caractérisé en ce qu'il est prévu, entre le circuit d'huile lubrifiante (46, 52, 56, 58, 60, 68) et le côté aspiration du compresseur, une jonction d'égalisation de pression (70) par laquelle tout le circuit d'huile lubrifiante, du côté aspiration de la pompe à huile (48), est pratiquement sous la pression d'aspiration du compresseur, et en ce qu'il est disposé, entre le dispositif d'étanchéité d'arbre (64) et le palier (18), une chambre de drainage (62) entourant l'arbre en anneau pour intercepter l'huile lubrifiante qui sort du palier (18) de ce côté, ainsi que le gaz de fuite qui passe éventuellement à travers le dispositif d'étanchéité d'arbre (64), chambre qui est reliée par un conduit de drainage (66) à la chambre de palier (56, 58) correspondante et que, de la sorte, est également sous la pression d'aspiration du compresseur.
2. Compresseur selon la revendication 1, caractérisé en ce que la jonction d'égalisation de pression comprend, à partir de chaque chambre de drainage (62), le conduit de drainage (66), la chambre de palier associée (56,58), le conduit de retour d'huile lubrifiante (60) ainsi que la chambre à gaz fermée du réservoir d'huile lubrifiante (46) qui est reliée à la conduite d'aspiration (22) du compresseur par une conduite d'égalisation (70).
3. Compresseur selon la revendication 1 ou 2, caractérisé en ce que pour le retour à volonté d'huile et, le cas échéant, de gaz de fuite, soit dans la chambre à gaz du réservoir d'huile lubrifiante (46), soit directement dans la tubulure d'admission (24) ou la chambre de travail (12) du compresseur, il est prévu des ouvertures obturables (68, 82, 84) entre le conduit de retour d'huile lubrifiante (60) ou une chambre de palier (56) d'une part et le réservoir d'huile lubrifiante (46), la tubulure d'admission (24) ou la chambre de travail (12) du compresseur d'autre part.
4. Compresseur selon l'une quelconque des revendications 1 à 3, comportant un circuit d'huile supplémentaire, pour l'alimentation en fluide de refroidissement et d'étanchéité de la chambre de travail du compresseur, qui présente un récipient séparateur (30), raccordé à la sortie (28) du compresseur, pour le lubrifiant entraîné par le courant de gaz et une conduite d'huile (36, 42) s'étendant entre le récipient séparateur (30) et la chambre de travail (12) du compresseur, caractérisé en ce que le récipient séparateur (30) est relié au réservoir d'huile lubrifiante (46) par une conduite de jonction (36) munie d'une soupape (76) qui peut être commandée au moyen d'un commutateur (64) réagissant au niveau dans le réservoir d'huile lubrifiante (46).
EP80106829A 1979-12-05 1980-11-06 Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers Expired EP0030619B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19792948992 DE2948992A1 (de) 1979-12-05 1979-12-05 Rotorverdichter, insbesondere schraubenrotorverdichter, mit schmiermittelzufuhr zu und schmiermitteldrainage von den lagern
DE2948992 1979-12-05

Publications (2)

Publication Number Publication Date
EP0030619A1 EP0030619A1 (fr) 1981-06-24
EP0030619B1 true EP0030619B1 (fr) 1985-01-02

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EP80106829A Expired EP0030619B1 (fr) 1979-12-05 1980-11-06 Compresseur à rotor, en particulier compresseur à vis avec alimentation en lubrifiant et drainage du lubrifiant des paliers

Country Status (9)

Country Link
US (1) US4394113A (fr)
EP (1) EP0030619B1 (fr)
JP (1) JPS5688986A (fr)
AR (1) AR222589A1 (fr)
AU (1) AU537335B2 (fr)
BR (1) BR8007894A (fr)
CA (1) CA1156627A (fr)
DE (2) DE2948992A1 (fr)
IN (1) IN154526B (fr)

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CN109458343A (zh) * 2017-09-06 2019-03-12 株式会社神户制钢所 压缩装置
WO2021259656A1 (fr) 2020-06-25 2021-12-30 Nidec Gpm Gmbh Bague d'étanchéité d'arbre, en particulier bague d'étanchéité d'arbre à deux étages

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US2721747A (en) * 1951-12-21 1955-10-25 Read Standard Corp Hydraulic shaft seal
FR1564294A (fr) * 1967-05-03 1969-04-18
DD105868A1 (fr) * 1973-08-30 1974-05-12
GB2020362A (en) * 1978-03-13 1979-11-14 Imi Fluidair Ltd Rotary compressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109458343A (zh) * 2017-09-06 2019-03-12 株式会社神户制钢所 压缩装置
CN109458343B (zh) * 2017-09-06 2020-06-26 株式会社神户制钢所 压缩装置
WO2021259656A1 (fr) 2020-06-25 2021-12-30 Nidec Gpm Gmbh Bague d'étanchéité d'arbre, en particulier bague d'étanchéité d'arbre à deux étages
DE102020116771A1 (de) 2020-06-25 2021-12-30 Nidec Gpm Gmbh Wellendichtring, insbesondere 2-stufiger Wellendichtring

Also Published As

Publication number Publication date
AU537335B2 (en) 1984-06-21
CA1156627A (fr) 1983-11-08
IN154526B (fr) 1984-11-03
AR222589A1 (es) 1981-05-29
US4394113A (en) 1983-07-19
BR8007894A (pt) 1981-06-16
DE3069916D1 (en) 1985-02-14
AU6468580A (en) 1981-06-11
JPH0116350B2 (fr) 1989-03-23
JPS5688986A (en) 1981-07-18
EP0030619A1 (fr) 1981-06-24
DE2948992A1 (de) 1981-06-11

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