EP0606965A1 - Procédé et dispositif d'élimination de petites quantités des fuites de liquide de lubrification ou de réfroidissement - Google Patents

Procédé et dispositif d'élimination de petites quantités des fuites de liquide de lubrification ou de réfroidissement Download PDF

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Publication number
EP0606965A1
EP0606965A1 EP94250002A EP94250002A EP0606965A1 EP 0606965 A1 EP0606965 A1 EP 0606965A1 EP 94250002 A EP94250002 A EP 94250002A EP 94250002 A EP94250002 A EP 94250002A EP 0606965 A1 EP0606965 A1 EP 0606965A1
Authority
EP
European Patent Office
Prior art keywords
compressor
line
shaft
shaft sealing
bore
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.)
Withdrawn
Application number
EP94250002A
Other languages
German (de)
English (en)
Inventor
Gerhard Ing. Grad. Herbert
Reinhard Dr. Ing. Schüler
Ulrich Dipl.-Ing. Thomes
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.)
Vodafone GmbH
Original Assignee
Mannesmann 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
Application filed by Mannesmann AG filed Critical Mannesmann AG
Publication of EP0606965A1 publication Critical patent/EP0606965A1/fr
Withdrawn legal-status Critical Current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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0028—Internal leakage control
    • 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

Definitions

  • the invention relates to a method for removing small amounts of lubricant and coolant leakage that emerge in the shaft sealing area behind a shaft sealing ring of a liquid-lubricated compressor.
  • the type of sealing of the drive shaft extending from the compressor housing is known, a radial shaft sealing ring usually taking over the main function of the seal and an upstream sealing ring ensuring that no dirt particles can get into the sensitive lip sealing area of the radial shaft sealing ring.
  • a radial shaft sealing ring usually taking over the main function of the seal and an upstream sealing ring ensuring that no dirt particles can get into the sensitive lip sealing area of the radial shaft sealing ring.
  • a generic method and a corresponding device can be found in DE 82 29 577 U1.
  • This has a liquid-lubricated compressor, the drive shaft journals are sealed and extends through a cover attached to the housing.
  • a shaft sealing ring is arranged in the bore of the cover and an annular space is provided on the outside of the shaft sealing ring, which can be connected via a line to the working space of the compressor, specifically either to the suction port or pressure port area.
  • the annular space is preferably formed by a Z-shaped cross section of sheet metal box which is attached to the outside of the cover and at the lowest point of which the suction line is connected.
  • This construction has the disadvantage that the sheet metal box must also be sealed due to the creep properties of the lubricating oil used. In addition, such a protruding part and the exposed wire can be easily damaged and bent.
  • Another disadvantage is that the specially made sheet metal box is only designed for one compressor size and each variation in the drive shaft area means the production of a different sheet metal box.
  • the object of the invention is to provide, while avoiding the disadvantages described, a method and a device with which small and reliable quantities of lubricating and cooling fluid that escape can be removed and existing compressor systems cannot be easily equipped.
  • the leakage quantities emerging in the shaft sealing area are extracted through a bore which extends from the outer circumference to the shaft sealing area of the cover closing the compressor housing and is connected to the suction area of the compressor via a line.
  • the effect of this extraction can be improved if the system sealing pressure of the compressor system is additionally applied to the shaft sealing area via a further radial bore.
  • the design of the device for carrying out the method can be very different.
  • the line connected to the suctioning bore can open, for example, in the intake line of the compressor system upstream of the intake regulator or alternatively in the area of the intake connection after the intake regulator.
  • the line connecting the acting bore can be connected to the clean air side behind the fine separator or to the ventilation line of the actuating cylinder for the suction regulator. Alternatively, it is also possible to connect this line to the system relief line.
  • a valve is arranged in the suction line, this valve also being an integral part of the control and relief valve of the system.
  • the advantage of the device according to the invention can be seen in the fact that, with two bores in the cover of the shaft passage that are easy to manufacture, even small amounts of leakage of lubricant and coolant can be safely sucked off and thus do not get into the environment.
  • the holes in the cover can be connected to the compressor system using easy-to-lay cables.
  • Figure 1 shows a basic circuit diagram of a conventional compressor system.
  • the medium to be compressed preferably air
  • the medium to be compressed is sucked in via an air filter 1 via a line 20 and fed to the compressor 4 via a suction control valve 2.
  • the oil-lubricated compressor 4 is driven by a motor 3, which can optionally be an internal combustion engine or an electric motor.
  • the compressed air-oil mixture reaches the pre-separator 6 via a line 20, a remote thermometer 5.1 and a temperature switch 5 being arranged in the pressure line 21 to monitor the process.
  • In the pre-separator 6 most of the oil is separated from the mixture, which is returned to the compressor 4 via a line 22 under system pressure.
  • An oil cooler 10, an oil filter 12 and a temperature control valve 11 are arranged in the return line 22.
  • a safety valve 9 is arranged on the pre-separator 6.
  • the remaining separation of the oil except for a residual oil content of less than 5 mg / cbm air takes place in one Fine separator 7, which is usually designed as an exhaust filter.
  • the remaining separated oil is returned to the compressor 4 via a line 23 under system pressure.
  • a check valve 13 and an orifice 14 are arranged as a throttle element.
  • the compressed and de-oiled air is fed from the fine separator 7 via a pressure-maintaining and non-return valve 15 arranged in the line 24 and via an aftercooler 16 to the consumer (not shown here).
  • a pressure switch 17 is also arranged between the pressure holding and control valve 15 and the aftercooler 16.
  • a measuring, control and blow-off line 25 branches off from the clean air side 24, in which a remote pressure display 18.1 and a pressure sensor 18 and a solenoid valve 19 are arranged.
  • the latter solenoid valve 19 is connected to the air filter 1 via a blow-off line 26 and to the actuating cylinder 2.1 of the throttle valve 2.2 via a control line 27.
  • This control line 27 opens into the intake line 20 via a throttle 14.
  • the cover 32 according to the invention is shown in a longitudinal section and in a cross section along the line AB in FIG.
  • the housing 30 of the compressor 4 has an opening through which the drive shaft piece 31 extends through the cover 32.
  • the seal required for the shaft passage is arranged on a bushing 33.
  • the main seal is taken over by a radial shaft sealing ring 34, which is supported in a recess 35 in the cover 32. So that the proper functioning of the radial shaft sealing ring 34 is not impaired by penetrating dirt, a felt ring 36 is connected upstream of it.
  • the felt ring 36 is supported from both sides with cover disks 37, 37 '.
  • the space between the felt ring 36 and the radial shaft sealing ring 34 is in this embodiment by two Locked spring washers 38,38 '.
  • the cover 32 is provided radially with a bore 39 which extends from the outer circumferential surface 40 to the sealing area.
  • the end region is provided with a threaded section 41.
  • a laxative radial bore 42 which is also provided with a threaded section 43 for connecting a line in the end region.
  • the two spring rings 38, 38 ' are arranged offset to one another, so that a connection is created from the respective bore 39 or 42 to the shaft sealing area.
  • FIG. 4 in a first embodiment, only the suction bore 42 is connected to a line 45 via the threaded connection 43. This ends in the suction line 20 in front of the suction regulator 2. In the suction line 20 there is a slight negative pressure, so that the small amount of leakage that emerges behind the shaft sealing ring 34 is sucked off in an environmentally friendly manner via the connecting line 45. This effect of the suction can be increased if, as shown in FIG. 5, the supplying bore 39 is subjected to the system pressure. For this purpose, the clean air side 24 is connected to the threaded connection 51 via a line 46. So that the pressure can be set in terms of pressure, there is a throttle 47 in line 46 arranged.
  • FIG. 6 A modification of the arrangement according to FIG. 4 is shown in FIG. 6.
  • the suction connecting line 45 opens behind the suction regulator 2 directly in the suction area of the compressor 4.
  • the suction of the air-oil mixture is controlled via a valve 48.
  • valve 48 When switching off the system, valve 48 must be closed, otherwise oil mist can escape.
  • FIG. 7 A further variant in addition to FIG. 6 is shown in FIG. 7.
  • the connecting line 46 is connected to the actuating cylinder 2.1 for the application.
  • the connecting line 46 is connected to the system relief line 26 for the application.
  • FIG. 9 A modification of FIG. 8 is shown in FIG. 9.
  • the connecting line 45 opens out, as already shown in FIG , but the valve 48 is integrated in the solenoid valve 19 for the control and blow-off line. In this embodiment, too, the system is relieved via the bore 39 and the shaft seal 36 when the system is switched off.
  • FIG. 10 A further variant is shown in FIG. 10.
  • a check valve 49 is arranged in the exhausting bore 42 and the suction is carried out via a cover 32 Transverse channel 50 opening into the bore 42, which is connected via a line 51 directly to the suction area of the compressor 4.
  • the bore 42 in the threaded portion 43 is closed (not shown here).

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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)
EP94250002A 1993-01-15 1994-01-07 Procédé et dispositif d'élimination de petites quantités des fuites de liquide de lubrification ou de réfroidissement Withdrawn EP0606965A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19934301293 DE4301293C2 (de) 1993-01-15 1993-01-15 Vorrichtung zum Entfernen kleiner Schmier- und Kühlflüssigkeitsleckagemengen
DE4301293 1993-01-15

Publications (1)

Publication Number Publication Date
EP0606965A1 true EP0606965A1 (fr) 1994-07-20

Family

ID=6478484

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94250002A Withdrawn EP0606965A1 (fr) 1993-01-15 1994-01-07 Procédé et dispositif d'élimination de petites quantités des fuites de liquide de lubrification ou de réfroidissement

Country Status (2)

Country Link
EP (1) EP0606965A1 (fr)
DE (1) DE4301293C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5795136A (en) * 1995-12-04 1998-08-18 Sundstrand Corporation Encapsulated rotary screw air compressor
DE29807796U1 (de) * 1998-04-30 1999-09-09 GHH-RAND Schraubenkompressoren GmbH & Co. KG, 46145 Oberhausen Dichtungsanordnung für einen Wellenzapfen eines trockenlaufenden Rotationsschraubenverdichters
EP2072765A1 (fr) * 2007-12-21 2009-06-24 ABB Turbo Systems AG Dispositif d'adaptation de la pression

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19822283A1 (de) * 1998-05-18 1999-11-25 Sgi Prozess Technik Gmbh Drehzahnverdichter und Verfahren zum Betrieb eines solchen

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2853020A (en) * 1955-08-10 1958-09-23 Fuller Co Shaft seal
FR2242579A1 (fr) * 1973-09-03 1975-03-28 Svenska Rotor Maskiner Ab
US4594992A (en) * 1984-07-02 1986-06-17 Toyota Jidosha Kabushiki Kaisha Supercharger of an internal combustion engine having Roots pump
DE3503039A1 (de) * 1985-01-30 1986-07-31 Wankel Gmbh, 1000 Berlin Wellendichtung zwischen kaeltekompressor und antriebsmotor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE478577C (de) * 1927-08-07 1929-06-28 Hubert Dickmann OElfuehrung in Kompressoren o. dgl.
DE8229577U1 (de) * 1982-10-21 1983-03-31 Aerzener Maschinenfabrik Gmbh, 3251 Aerzen Kompressor
CH675278A5 (fr) * 1988-02-25 1990-09-14 Burckhardt Ag Maschf

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2853020A (en) * 1955-08-10 1958-09-23 Fuller Co Shaft seal
FR2242579A1 (fr) * 1973-09-03 1975-03-28 Svenska Rotor Maskiner Ab
US4594992A (en) * 1984-07-02 1986-06-17 Toyota Jidosha Kabushiki Kaisha Supercharger of an internal combustion engine having Roots pump
DE3503039A1 (de) * 1985-01-30 1986-07-31 Wankel Gmbh, 1000 Berlin Wellendichtung zwischen kaeltekompressor und antriebsmotor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5795136A (en) * 1995-12-04 1998-08-18 Sundstrand Corporation Encapsulated rotary screw air compressor
DE29807796U1 (de) * 1998-04-30 1999-09-09 GHH-RAND Schraubenkompressoren GmbH & Co. KG, 46145 Oberhausen Dichtungsanordnung für einen Wellenzapfen eines trockenlaufenden Rotationsschraubenverdichters
EP2072765A1 (fr) * 2007-12-21 2009-06-24 ABB Turbo Systems AG Dispositif d'adaptation de la pression
WO2009080521A1 (fr) * 2007-12-21 2009-07-02 Abb Turbo Systems Ag Turbocompresseur de suralimentation entraîné par gaz d'échappement et doté d'un dispositif d'adaptation de pression

Also Published As

Publication number Publication date
DE4301293C2 (de) 1996-07-11
DE4301293A1 (de) 1994-07-21

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