EP0614012B1 - Verdrängermaschine nach dem Spiralprinzip - Google Patents

Verdrängermaschine nach dem Spiralprinzip Download PDF

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Publication number
EP0614012B1
EP0614012B1 EP94810009A EP94810009A EP0614012B1 EP 0614012 B1 EP0614012 B1 EP 0614012B1 EP 94810009 A EP94810009 A EP 94810009A EP 94810009 A EP94810009 A EP 94810009A EP 0614012 B1 EP0614012 B1 EP 0614012B1
Authority
EP
European Patent Office
Prior art keywords
oil
drive shaft
housing
bearing
sliding bearing
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
EP94810009A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0614012A1 (de
Inventor
Fritz Spinnler
Roland Kolb
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.)
Aginfor AG
Original Assignee
Aginfor AG fuer industrielle Forschung
Aginfor 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 Aginfor AG fuer industrielle Forschung, Aginfor AG filed Critical Aginfor AG fuer industrielle Forschung
Publication of EP0614012A1 publication Critical patent/EP0614012A1/de
Application granted granted Critical
Publication of EP0614012B1 publication Critical patent/EP0614012B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F01C1/0223—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
    • 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
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • the invention relates to a displacement machine for compressible media according to the preamble of patent claim 1.
  • Displacement machines of the spiral type are known for example from DE-C3-2 603 462.
  • a compressor constructed according to this principle is characterized by an almost pulsation-free delivery of the gaseous working medium, which consists, for example, of air or an air-fuel mixture, and could therefore also be used advantageously for charging internal combustion engines, among other things.
  • the gaseous working medium which consists, for example, of air or an air-fuel mixture
  • several, approximately sickle-shaped working spaces are enclosed between the spiral-shaped displacement body and the two peripheral walls of the displacement chamber, which move from the inlet through the displacement chamber to the outlet, their volume constantly decreasing and the pressure of the work equipment is increased accordingly.
  • EP 0 354 342 A machine of the type mentioned at the outset is known from EP 0 354 342.
  • the drive shaft is supported in an angularly synchronous manner with the drive shaft Bearings. This is particularly evident in the displacement machine according to EP 0 354 342, in which the drive shaft is mounted in the housing in two ball bearings and the eccentric collar arranged on the drive shaft is supported by a needle bearing.
  • the rotor is penetrated by the drive shaft, so there are two sealing points on it.
  • the lubricating oil must be fed in and out from one side to the eccentric disk of the drive shaft.
  • the oil is fed in and out from the drive side or from the air side of the housing.
  • the drive shaft penetrates the housing on the drive side, which would make it two more places to seal with shaft sealing rings if the main eccentric bearing is supplied with the lubricating oil from this side. If the main eccentric bearing is supplied from the delivery or air side of the machine, only an additional shaft sealing point is necessary, since the drive shaft does not penetrate the housing on the delivery side.
  • the absolute minimum of the necessary shaft seals is therefore three.
  • a spiral machine is known from the unpublished EP-A-547 470, in which an eccentric disk is arranged on the drive shaft, on which the rotor is mounted by means of an oil-lubricated bearing.
  • a sliding bearing is provided for the orbiting rotor on the rotating eccentric disc, the oil supply being provided via a hole in the eccentric disc.
  • Means for air-free oil supply in the plain bearing gap are arranged within the eccentric disc.
  • the oil flowing out of the longitudinal bore on the air-side end face of the drive shaft is guided into a shaft bearing designed as a plain bearing. This is closed at both axial ends by oil spaces.
  • the two oil spaces communicate with each other via a channel which is open towards the drive shaft in its axial extent.
  • the invention is based on the object of realizing an oil guide which reduces the number of shaft sealing rings to the absolutely necessary minimum and in which the distribution of the oil flows (inflow and outflow) is defined at the drive shaft / housing interface.
  • the rotor of the machine is designated as a whole by 1.
  • Two, 180 ° offset, spiral-shaped displacers are arranged on both sides of the disk 2. These are strips 3a, 3b which are held vertically on the pane 2. In the example shown, the spirals themselves are formed from a plurality of circular arcs adjoining one another. 4 with the hub is designated with which the disc 2 is mounted on the bearing 22 on an eccentric 23. This eccentric disk is in turn part of the drive shaft 24.
  • FIG. 1 shows the housing half 7a shown on the left in FIG. 2 of the machine housing, which is composed of two halves 7a, 7b and is connected to one another via fastening eyes 8 for receiving screw connections.
  • 11a and 11b denote the delivery spaces, which are offset by 180 ° relative to one another and are worked into the two housing halves in the manner of a spiral slot. They each run from an inlet 12a, 12b arranged on the outer circumference of the spiral in the housing to an outlet 13 provided in the interior of the housing and common to both delivery spaces (FIG. 2). They have essentially parallel, uniformly spaced cylinder walls 14a, 14b, 15a, 15b, which in the present case, like the displacer bodies of the disk 2, comprise a spiral of approximately 360 °.
  • the displacers 3a, 3b engage between these cylinder walls, the curvature of which is dimensioned such that the strips almost touch the inner and outer cylinder walls of the housing at several, for example at two points. Seals are inserted in corresponding grooves on the free end faces of the strips 3a, 3b and the webs 45, 46. With them, the working rooms against the side walls of the housing respectively. sealed against the displacement disc.
  • the drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements 23, 24 and. 26, 27.
  • the drive shaft 24 is mounted on the drive side in a roller bearing 17 and on the air side in a slide bearing 18. At its end protruding from the housing half 7a, it is provided with a V-belt pulley 19 for the drive.
  • Counterweights 20 are arranged on the drive shaft 24 to compensate for the inertial forces arising when the rotor is eccentrically driven.
  • the guide shaft 27 is mounted within the housing half 7a by means of a roller bearing 28. In order to achieve clear guidance of the rotor in the dead center positions, the two eccentric arrangements are synchronized with a precise angle by a toothed belt drive 16.
  • This double eccentric drive ensures that all points of the rotor disc and thus also all points of the two strips 3a and 3b perform a circular displacement movement.
  • crescent-shaped workrooms enclosing the working medium result on both sides of the bars, which are displaced by the delivery chambers during the drive of the rotor disk in the direction of the outlet. The volumes of these working spaces decrease and the pressure of the working fluid is increased accordingly.
  • the bearings 18 and 22 are shown. These require an oil supply.
  • Lubricant preferably oil
  • lubricant is passed through a bore 29 in the housing half 7a to the plain bearing 18.
  • the fresh oil reaches the oil space 54 through a recess 30 in the slide bearing bore 18.
  • the recess 30 is open with respect to the drive shaft 24 and supplies the slide bearing 18 with oil.
  • the depression 30 causes the throttling and the quantity control of the oil fed into the bore 29 under pressure.
  • a longitudinal bore 53 is made in the drive shaft 24, in which the oil guide sleeve 39 is held at points 58, 58 ′, for example by a press fit in the drive shaft 24.
  • the outer diameter of the sleeve itself is tapered in the middle section 62, as a result of which a second oil channel 60 is formed in an extremely simple manner, which is separate from the first oil channel 59.
  • the oil flowing into the oil space 54 through the recess in the slide bearing 18 can pass through the central bore 59 in the sleeve 39 into the oil space 61 formed by the longitudinal bore 53 in the drive shaft 24, from where the oil through the radial bore 31 to the bearing 22 can reach.
  • the back-flowing oil passes through the radial bore 50 into the oil space 55, which is connected to the bore 57 in the housing 7a.
  • the oil space 55 is sealed by the shaft sealing ring 56 against the outlet 13 carrying the working medium.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP94810009A 1993-01-19 1994-01-10 Verdrängermaschine nach dem Spiralprinzip Expired - Lifetime EP0614012B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH165/93 1993-01-19
CH16593 1993-01-19

Publications (2)

Publication Number Publication Date
EP0614012A1 EP0614012A1 (de) 1994-09-07
EP0614012B1 true EP0614012B1 (de) 1996-09-18

Family

ID=4180741

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94810009A Expired - Lifetime EP0614012B1 (de) 1993-01-19 1994-01-10 Verdrängermaschine nach dem Spiralprinzip

Country Status (4)

Country Link
US (1) US5397223A (ja)
EP (1) EP0614012B1 (ja)
JP (1) JPH06241181A (ja)
DE (1) DE59400648D1 (ja)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001317480A (ja) * 2000-04-28 2001-11-16 Hitachi Ltd スクリュー圧縮機
DE10308367A1 (de) * 2003-02-27 2004-12-02 Daimlerchrysler Ag Ölschleuderscheibe
WO2008124950A1 (de) * 2007-04-17 2008-10-23 Spinnler Engineering Verdrängermaschine nach dem spiralprinzip
US8425211B2 (en) * 2007-08-22 2013-04-23 Spinnler Engineering Positive displacement machine according to the spiral principle
DE102007043594B4 (de) 2007-09-13 2009-11-26 Handtmann Systemtechnik Gmbh & Co. Kg Spiralverdichter mit Doppelspirale
DE102007043595B4 (de) 2007-09-13 2009-12-24 Handtmann Systemtechnik Gmbh & Co. Kg Verdrängermaschine nach dem Spiralprinzip
DE102011103165A1 (de) * 2010-07-02 2012-01-05 Handtmann Systemtechnik Gmbh & Co. Kg Ladevorrichtung zur Verdichtung von Ladeluft für einen Verbrennungsmotor
DE102010052186B4 (de) * 2010-11-24 2012-08-30 Handtmann Systemtechnik Gmbh & Co. Kg Verdrängermaschine für kompressible Medien
DE102011119255A1 (de) * 2010-11-24 2012-05-31 Handtmann Systemtechnik Gmbh & Co. Kg Verdrängermaschine für kompressible Medien
GB2518540A (en) * 2012-11-21 2015-03-25 Gilo Ind Res Ltd Cooling systems for rotary engines
US10865793B2 (en) 2016-12-06 2020-12-15 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
DE102017215784A1 (de) * 2017-09-07 2019-03-07 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
US20200025199A1 (en) 2018-07-17 2020-01-23 Air Squared, Inc. Dual drive co-rotating spinning scroll compressor or expander
US11530703B2 (en) 2018-07-18 2022-12-20 Air Squared, Inc. Orbiting scroll device lubrication
US11898557B2 (en) * 2020-11-30 2024-02-13 Air Squared, Inc. Liquid cooling of a scroll type compressor with liquid supply through the crankshaft
US11885328B2 (en) 2021-07-19 2024-01-30 Air Squared, Inc. Scroll device with an integrated cooling loop

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE492112C (de) * 1930-02-19 Giustino Cattaneo Reinigungsvorrichtung fuer Schmiermittel von Brennkraftmaschinen innerhalb der Kurbelwelle
GB496230A (en) * 1936-05-27 1938-11-28 Bosch Robert Improvements in or relating to apparatus for regulating the lubricant feed in compressors
CH586348A5 (ja) * 1975-02-07 1977-03-31 Aginfor Ag
DE3320086A1 (de) * 1983-06-03 1984-12-06 Volkswagenwerk Ag, 3180 Wolfsburg Lager-schmiereinrichtung
DE3604351A1 (de) * 1985-02-14 1986-08-14 Volkswagen AG, 3180 Wolfsburg Lager-schmiereinrichtung
DE3627956A1 (de) * 1986-08-18 1988-03-03 Wankel Gmbh Exzenterwelle einer rotationskolbenbrennkraftmaschine
MX172715B (es) * 1987-11-05 1994-01-10 Emitec Emissionstechnologie Cigueñales y procedimiento para su fabricacion
EP0354342B1 (de) * 1988-08-03 1994-01-05 AGINFOR AG für industrielle Forschung Verdrängermaschine nach dem Spiralprinzip
EP0547470B1 (de) * 1991-12-16 1995-08-23 AGINFOR AG für industrielle Forschung Verdrängermaschine nach dem Spiralprinzip

Also Published As

Publication number Publication date
JPH06241181A (ja) 1994-08-30
US5397223A (en) 1995-03-14
DE59400648D1 (de) 1996-10-24
EP0614012A1 (de) 1994-09-07

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