EP0069859A2 - Dispositif à compresseur - Google Patents

Dispositif à compresseur Download PDF

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Publication number
EP0069859A2
EP0069859A2 EP82104890A EP82104890A EP0069859A2 EP 0069859 A2 EP0069859 A2 EP 0069859A2 EP 82104890 A EP82104890 A EP 82104890A EP 82104890 A EP82104890 A EP 82104890A EP 0069859 A2 EP0069859 A2 EP 0069859A2
Authority
EP
European Patent Office
Prior art keywords
hollow cylinder
housing
compressor
pump
gap
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.)
Granted
Application number
EP82104890A
Other languages
German (de)
English (en)
Other versions
EP0069859A3 (en
EP0069859B1 (fr
Inventor
Siegfried Schönwald
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Priority to AT82104890T priority Critical patent/ATE16518T1/de
Publication of EP0069859A2 publication Critical patent/EP0069859A2/fr
Publication of EP0069859A3 publication Critical patent/EP0069859A3/de
Application granted granted Critical
Publication of EP0069859B1 publication Critical patent/EP0069859B1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/06—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B27/0606—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0261—Hermetic compressors with an auxiliary oil pump

Definitions

  • the invention relates to a compressor unit in which the compressor and its drive motor designed as an external rotor motor are arranged on a common fixed axis in a unit housing and in which a lubricant feed pump designed as a friction pump is provided on the end of the fixed axis facing away from the compressor, with its output opens into a bore channel provided in the fixed axis and projects with its inflow opening into the lubricant reservoir at the bottom of the unit housing, which also has as an impeller a hollow cylinder coupled to the external rotor.
  • Such a compressor unit is known from DE-A1-15 03 408.
  • the friction pump is formed in this unit by the bearing sleeve designed as a hollow cylinder and spiral grooves provided in the area of the bearing sleeve in the fixed axis. Although such a friction pump is very simple in construction, it can only pump a small amount of oil.
  • a friction pump is known per se, in which a shaft rotates in a hollow cylinder as an impeller. There is a gap between the shaft and the hollow cylinder, in which the medium to be conveyed is carried along by the rotating shaft. The gap extends over a partial circumference of the hollow cylinder and is delimited on both sides by an interrupter narrowing the gap. The medium to be conveyed enters and exits at the beginning and end of the gap.
  • To increase the delivery volume several gap spaces are provided in the known friction pump over the circumference of the hollow cylinder. To this Although the delivery volume can be increased, the delivery pressure drops sharply because the length of the individual gap spaces is shortened.
  • the invention has for its object to provide a compressor unit of the type described in such a way that the oil necessary for lubricating and sealing the mutually movable parts of the compressor is pumped to a sufficient extent and also with the required pressure.
  • a pump housing having an annular space between an inner and an outer housing part is arranged on the axis and the hollow cylinder protrudes into the annular space, so that a between the housing parts of the pump housing and the hollow cylinder inner and an outer gap is formed that further a connection is provided between the inner and outer gap and at least one constriction acting as an interrupter is provided on both sides of the hollow cylinder on the pump housing. Because a gap is provided on both sides of the hollow cylinder, the available gap space is almost doubled without the gap length and thus the delivery pressure being reduced. In addition, this enlargement of the gap is achieved without additional design effort.
  • the hollow cylinder is advantageously formed on the bearing cap of the external rotor. This will make the Assembly effort reduced. Characterized in that several through holes are provided in the wall of the hollow cylinder, pressure and volume flows of the inner and outer gap can compensate.
  • a radial piston compressor 2 and an external rotor motor 3 are together on a fixed one Axis 4 arranged.
  • a bore channel 5 which extends from its end 6, which is opposite the radial piston compressor 2, to the radial piston compressor 2.
  • a hollow cylinder 8 is formed on the bearing cap 7 of the external rotor motor 3 and forms the rotor of a friction pump.
  • the hollow cylinder 8 projects into an annular space 9, which is formed between an inner and an outer housing part 10 or 11 of a pump housing 12.
  • the inner housing part 10 consists of an integrally formed on a housing end plate 13 ring wall which is pushed over the end 6 of the fixed axis 4.
  • the housing end plate 13 is by means of. Screws 14 connected to the outer housing part 11.
  • a cover plate 16 the diameter of which is at least equal to the diameter of the outer rotor of the outer rotor motor 3, is fastened to the outer housing part 11 above the oil level 15.
  • the ring wall forming the inner housing part 10 has a passage opening 17 which overlaps with a bore 18 opening into the bore channel 5. This passage opening 17 forms the outlet of the pump.
  • annular disks 20 are inserted one above the other. Through these annular disks 20, the total width of the axial gap is divided into several parallel columns of smaller width. The smaller gaps provide a higher resistance to the flow, so that the leakage current through the axial gap is greatly reduced.
  • the total height of the stacked disks 20 is dimensioned such that it corresponds to the minimum width of the axial gap due to tolerances. This means that regardless of the actual width of the axial gap, the same number of washers can always be inserted into the axial gap. 2 shows that there is an inner gap 21 and an outer gap 22 between the hollow cylinder 8 and the two housing parts 10 and 11.
  • a radial channel 23 which is formed in the pump housing 12 and extends under the hollow cylinder 8, the oil flows into an axial channel 24 which extends on both sides of the hollow cylinder 8. From here, the oil is passed through the rotating hollow cylinder 8 into the two gaps 21 and 22 dragged along. At the end of the conveying path, an interrupter 25 is arranged on both sides of the hollow cylinder 8, through which the two gaps 21 and 22 are narrowed. The 01 carried by the hollow cylinder 8 is accumulated as a result of this narrowing of the gap and pressed through the passage opening 17 and the bore 18 into the bore channel 5. From there it arrives at the radial piston compressor 2.
  • axially extending outlet channels 27 are provided in front of the interrupters 25 in the inner and outer housing parts 10 and 11, which are connected to the outlet opening 17 stay in contact.
  • the hollow cylinder 8 itself also has through holes 28, through which the pressure and the volume flows between the inner and outer gap 21 and 22 can be evenly balanced.
  • the inner and outer housing parts 10 and 11 are cylindrical on its side assigned to the hollow cylinder 8, so that these housing parts can be easily manufactured accordingly.
  • the interrupters 25 form separate components which are inserted in corresponding recesses 29 on the two housing parts 10 and 11.
  • the interrupters 25 can be inserted loosely into these recesses 29.
  • a lubricating film is formed which guarantees a short distance, so that no sliding wear occurs during operation.
  • two interrupters 25 are arranged on the circumference of the housing parts 10 and 11. It is also possible to provide only one interrupter or more than two interrupters. The number of interrupters also corresponds to the number of radial inlet channels 23 and through openings 17.
  • the gas in the compressor housing 1 is set in rotation by the external rotor of the external rotor motor 3. This rotation creates a centrifugal pressure field which forces the 01 inwards at the bottom of the compressor housing 1.
  • a cover plate 16 is provided on the pump housing 12 which repels the oil from the rotating outer rotor.
  • the oil pumped into the bore channel 5 by the friction pump is conducted via this bore channel to the compressor and possibly also to the bearing points of the drive motor.
  • additional channels branch off from the bore channel at the corresponding points, through which the 01 then arrives at the desired points.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
  • Rotary Pumps (AREA)
EP82104890A 1981-06-15 1982-06-03 Dispositif à compresseur Expired EP0069859B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82104890T ATE16518T1 (de) 1981-06-15 1982-06-03 Verdichteraggregat.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3123631 1981-06-15
DE19813123631 DE3123631A1 (de) 1981-06-15 1981-06-15 Verdichteraggregat

Publications (3)

Publication Number Publication Date
EP0069859A2 true EP0069859A2 (fr) 1983-01-19
EP0069859A3 EP0069859A3 (en) 1984-03-21
EP0069859B1 EP0069859B1 (fr) 1985-11-13

Family

ID=6134717

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104890A Expired EP0069859B1 (fr) 1981-06-15 1982-06-03 Dispositif à compresseur

Country Status (7)

Country Link
US (1) US4436490A (fr)
EP (1) EP0069859B1 (fr)
JP (1) JPS57212384A (fr)
AT (1) ATE16518T1 (fr)
DE (2) DE3123631A1 (fr)
DK (1) DK151147C (fr)
IE (1) IE52864B1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4681510A (en) * 1986-01-02 1987-07-21 Trd Corporation Pump for saturated liquid
US4899704A (en) * 1989-05-08 1990-02-13 Tecumseh Products Company Self-lubricating bearing
DE102006001174A1 (de) * 2006-01-08 2007-07-12 Obrist Engineering Gmbh Hubkolbenkompressor

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE548405C (de) * 1932-04-19 Sulzer Akt Ges Geb OElfangvorrichtung fuer stehende Brennkraftmaschinen
US2423719A (en) * 1940-01-05 1947-07-08 Muffly Glenn Motor-compressor unit lubrication
US2294742A (en) 1941-03-28 1942-09-01 Douglas Fraser & Sons Ltd Wharve driven flyer spindle
US2440593A (en) 1946-10-23 1948-04-27 Harry B Miller Radial vane pump mechanism
DE1016074B (de) * 1953-11-04 1957-09-19 Klein Schanzlin & Becker Ag Schmieroelfoerdereinrichtung mit einem trommelartigen Schleuderring
DE959435C (de) * 1954-04-18 1957-03-07 Voith Gmbh J M Reibungspumpe
US3037457A (en) * 1959-08-26 1962-06-05 Gen Electric Pumps
DE1503408A1 (de) * 1966-10-15 1970-02-26 Danfoss As Gekapselter Motorverdichter,insbesondere fuer Kaeltemaschinen
DE1909610A1 (de) * 1969-02-26 1970-09-24 Licentia Gmbh Verdraengerpumpe
DE2428932C3 (de) * 1974-06-15 1979-11-08 Glyco-Metall-Werke Daelen & Loos Gmbh, 6200 Wiesbaden Flüssigkeitspumpe
DE2710734B2 (de) * 1977-03-11 1979-02-08 Siemens Ag, 1000 Berlin Und 8000 Muenchen Verdichteraggregat, bestehend aus einem Antriebsmotor und einem Verdichter mit exzentrisch geführten, frei beweglichen Kolben
US4131396A (en) * 1977-04-07 1978-12-26 Sundstrand Corporation Hermetic compressor lubrication system with two-stage oil pump
US4239448A (en) 1977-10-25 1980-12-16 Beloit Corporation High pressure pump for fluid jet slitter
DE7736989U1 (de) * 1977-12-03 1979-05-03 Peschke, Rudolf, 6101 Gross-Bieberau Reibungspumpe
AT354256B (de) * 1978-02-06 1979-12-27 Steyr Daimler Puch Ag Pumpe mit geringer foerderleistung fuer viskose fluessigkeiten, insbesondere schmieroel

Also Published As

Publication number Publication date
EP0069859A3 (en) 1984-03-21
JPS636755B2 (fr) 1988-02-12
DE3123631A1 (de) 1982-12-30
JPS57212384A (en) 1982-12-27
DK151147B (da) 1987-11-09
DK151147C (da) 1988-04-11
DK265182A (da) 1982-12-16
DE3267390D1 (en) 1985-12-19
ATE16518T1 (de) 1985-11-15
IE821412L (en) 1982-12-15
EP0069859B1 (fr) 1985-11-13
US4436490A (en) 1984-03-13
IE52864B1 (en) 1988-03-30

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