EP2137412A1 - Machine de refoulement construite selon le principe de la spirale - Google Patents

Machine de refoulement construite selon le principe de la spirale

Info

Publication number
EP2137412A1
EP2137412A1 EP07720172A EP07720172A EP2137412A1 EP 2137412 A1 EP2137412 A1 EP 2137412A1 EP 07720172 A EP07720172 A EP 07720172A EP 07720172 A EP07720172 A EP 07720172A EP 2137412 A1 EP2137412 A1 EP 2137412A1
Authority
EP
European Patent Office
Prior art keywords
lubricant
pressure
chamber
bearing
displacement machine
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
EP07720172A
Other languages
German (de)
English (en)
Other versions
EP2137412B1 (fr
Inventor
Fritz Spinnler
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.)
Spinnler Engineering
Original Assignee
Spinnler Engineering
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 Spinnler Engineering filed Critical Spinnler Engineering
Publication of EP2137412A1 publication Critical patent/EP2137412A1/fr
Application granted granted Critical
Publication of EP2137412B1 publication Critical patent/EP2137412B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids 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
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/21—Pressure difference

Definitions

  • the present invention relates to a displacement machine for compressible media according to the preamble of the claim
  • Spiral-type displacement machines are known, for example, from DE-A-3 347 081.
  • a compressor constructed according to this principle is characterized by a low-pulsation delivery of the gaseous working medium, e.g. Air, from and could therefore be used with advantage, inter alia, for charging purposes in internal combustion engines.
  • the gaseous working medium e.g. Air
  • a plurality of approximately crescent-shaped working spaces are trapped in the displacer chamber between the spirally-formed displacer and the two peripheral walls, moving from the inlet through the displacer chamber to the outlet, constantly reducing its volume and pressure of the working fluid is increased accordingly.
  • the displacement body is driven by means of an eccentric shaft and held by a guide arrangement, not shown.
  • the machine consists essentially of two housing halves, in which spiral channels are incorporated.
  • the displacer is mounted by means of a bearing on the eccentric of the eccentric shaft.
  • This storage also referred to as the main eccentric bearing
  • suitable lubrication is shown for example in EP-AO 614 012, which has a positive displacement machine of the type mentioned in the subject.
  • a liquid lubricant lubricating oil
  • the lubricating oil passes through a radially angeordeten channel in the main eccentric bearing. From this camp, the lubricating oil then flows through a second, also radially disposed channel in the direction of the center of the drive shaft and there opens into a coaxially or parallel to the feed channel arranged return channel through which the lubricating oil reaches one end of the drive shaft, from where the lubricating oil by a Bore in one half of the housing can flow to the outside.
  • a pressure oil lubrication as described in EP-A-0 614 012, is suitable for operation under high load of the machine, as is the case in particular at high speeds.
  • Such forced lubrication allows a sufficiently large flow of oil to dissipate the resulting heat loss in the main eccentric bearing with the lubricating oil.
  • the sealing of the lubricating oil-containing oil space against the pumping chamber is effected by shaft seals, which are provided both in the bearings of the drive shaft in the housing and the bearing of the displacer on the eccentric (main eccentric). Since, depending on the load case of the machine, the pressure in the delivery chamber may exceed those in the oil chamber in which collects the effluent from the bearings lubricating oil, there is a risk that in such an operating condition, the shaft seals of the shaft respectively. be lifted off the eccentric and thereby the Pumped fluid (eg air) can reach the lubricating oil side of the shaft seals and escapes through the oil return line. Especially at low speeds, where such positive displacement machines must be very dense, any further loss of fluid is disadvantageous, since in the case of use as a supercharger for internal combustion engines achievable torque can be significantly affected.
  • shaft seals which are provided both in the bearings of the drive shaft in the housing and the bearing of the displacer on the eccentric (main eccentric). Since, depending on the load case of the
  • the present invention is based on the object, in operation to prevent lifting of the shaft seals from the shaft at high delivery pressures of the fluid.
  • FIG. 1 in front view and in the direction of the arrow A in Fig. 2 the drive-side housing part, 2 shows the displacement machine according to FIG. 1 in a longitudinal section along the line II-II in FIG. 1, FIG.
  • FIG. 3 shows a detail from FIG. 2 in a comparison with FIG. 2 enlarged scale
  • FIG. 4 in a representation corresponding to FIG. 3, a second embodiment of a pressure control valve.
  • the displacement machine shown in FIGS. 1 and 2 in front view or in section has a housing consisting of two housing halves 1a, 1b, in which a displacement body 2 is mounted.
  • the two housing halves Ia, Ib are bolted together in a manner not shown.
  • the one housing half Ia (Fig. 2) is removed.
  • the displacement body 2 has a disc 3, which carries on each side a spiraling displacement elements 4, 5.
  • the displacement elements 4, 5 are formed as protruding from the disc 3 strips.
  • a drive shaft 6 is provided, whose axis of rotation is denoted by ⁇ a.
  • the drive shaft 6 is mounted in the housing halves Ia, Ib by means of bearings 7 and 8 and has an eccentric disk 9, whose axis of symmetry is designated by 9a.
  • the distance between the axis of rotation ⁇ a of the drive shaft 6 and the axis of symmetry 9a of the eccentric disc 9 (eccentricity) is designated e in FIG.
  • a drive pulley 11 is fastened by means of a screw 10.
  • the hub 13 of the disc 3 is supported by means of a bearing 12, which is a rolling bearing in the present case.
  • the disk 3 and thus the displacement body 2 are driven via the drive shaft ⁇ and the eccentric disk 9.
  • the driving force is transmitted via the bearing 12 to the hub 13 of the disk 3.
  • the guide of the displacement body 2 via a rocker 14 which is rotatably mounted at one end on a shaft 15 (Fig. 1).
  • the rocker 14 carries a bolt 16 which is rotatably mounted in an eye 17 of the disc 3.
  • the housing 1 has an inlet 18 and an outlet 19 for the conveying medium, preferably air, as well as two delivery chambers 20, 20 '.
  • a passage 21 (or more passages) is present, through which the fluid can pass from the delivery chamber 20 in the winninghoffm 20 '.
  • two counterweights 22, 23 are arranged on the drive shaft 6.
  • a Schmierstoffzu GmbHsyste ⁇ i 24 (Fig. 2) which supplies the bearing 12 with a lubricant, preferably lubricating oil.
  • This lubricant supply system 24 has a supply line 25 connected to the housing 1, which is connected to the pressure side of a pressure-controlled feed pump 26.
  • a pressure-controlled feed pump 26 Such pumps with pressure control, which in Internal combustion engines are used, produce a lubricant delivery pressure, which remains within operating limits within operating limits.
  • the feed pump 26 On the suction side, the feed pump 26 is connected via a suction line 27 with a lubricant container 28, which communicates via a connecting line 29 with the environment.
  • the ambient air pressure always acts on the surface of the lubricant 30 in the lubricant container 28.
  • the drive shaft 6 has a lubricant supply passage 32 and a lubricant return passage 33 which are coaxial with the rotation shaft 6a of the drive shaft 6 (FIGS. 2 and 3).
  • a tubular guide sleeve 35 is inserted into a longitudinal bore 34 in the drive shaft 6, which has on its outer side a portion with a smaller outer diameter, which extends over part of the length of the guide sleeve 35, and with the wall the longitudinal bore 34 forms the lubricant return passage 33.
  • the lubricant supply passage 32 running in the interior of the guide sleeve 35 is in communication with an inflow passage 36, which runs in the radial direction in the eccentric disk 9 and opens into a first lubricant chamber 37 on one side of the bearing 12 (FIG. 3).
  • This first lubricant chamber 37 is sealed off from the delivery chamber 20 by means of an annular sealing element 38, which bears against the eccentric disk 9.
  • On the other side of the bearing 12 is a second lubricant chamber 39, the is sealed relative to the delivery chamber 20 'by means of an annular sealing element 40, which also bears against the eccentric disc 9.
  • This second lubricant chamber 39 communicates with the lubricant return passage 33 via a radial outflow channel 41 in the eccentric disk 9.
  • a radial communication passage 42 in the drive shaft 6 connects the lubricant return passage 33 with a lubricant return passage 43, which belongs to a designated at 44 lubricant recirculation.
  • the lubricant return line 43 is connected to the inlet of a pressure control valve 45 whose output is connected via a return line 46 to the lubricant reservoir 28.
  • Trained as a diaphragm valve pressure control valve 45 has a diaphragm 47 which divides the interior of the pressure control valve 45 into two chambers 45 a and 45 b.
  • a control body 48 is mounted, which regulates the lubricant outflow from the lubricant return line 43 in .
  • the chamber 45a in a manner to be described.
  • the chamber 45a of the pressure control valve 45 opposite the chamber 45a is connected via a connecting line 49 to the delivery chamber 20 '. This means that the pressure in this chamber 45b corresponds to the working pressure in the delivery chamber 20 '.
  • the delivery chamber 20 ' is sealed to the outside by means of an annular sealing element 50, which bears against the drive shaft 6.
  • the conveyed by the pump 26 lubricant passes through the supply line 25, the From this first lubricant chamber 37, the lubricant flows through the bearing 12 into the second lubricant chamber 39. From the second lubricant chamber 39, the lubricant passes via the discharge channel 41, the lubricant return channel 33, the connecting channel 42 and the lubricant return line 43 into the chamber 45a of the pressure control valve 45. From this chamber 45a, the lubricant flows via the return line 46 back into the lubricant container 28th
  • the membrane 47 is more or less strongly deflected downwards in the direction of the inlet opening 4 ⁇ a the return line 46.
  • the distance between the control body 48 and the inlet opening 46a of the return line 46 is greater or smaller, with the result that the amount of the out of the chamber 45a in the Return line 46 flowing lubricant is controlled accordingly. In this way, the pressure in the lubricant return line 43 and thus also in the lubricant spaces 37 and 39 is changed depending on the delivery or working pressure in the delivery chamber 20 '.
  • FIG. 4 Another embodiment of the pressure control valve will be described.
  • the same reference numerals are used for corresponding components as in FIG. 3.
  • the housing 51a and the diaphragm 47 are connected to the control body 48 of FIG. 4
  • Pressure control valve 51 attached directly to the housing half Ia, e.g. by means of a snap ring 52.
  • the chamber 51 'formed by the housing 51a and the membrane 47 is connected via the connecting line 49 to the delivery chamber 20' in connection.
  • the lubricant return line 43 opens into a formed in the housing half Ia, part of the pressure control valve 51 forming chamber 53 which is closed by the membrane 47 and to which the
  • control body 48 of the membrane 47 is as in the embodiment according to
  • Fig. 3 of the inlet opening 4 ⁇ a the return line 46th opposite and serves to regulate the amount of the lubricant flowing through this inlet opening 46a.
  • the operation of the pressure control valve 51 is the same as the already described operation of the pressure control valve 45 according to FIG. 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une machine de refoulement dans laquelle un palier (12) est agencé entre le moyeu (13) du disque (3) du corps de refoulement (2) et un disque excentrique (9) relié à un arbre d'entraînement (6). Un système d'apport de lubrifiant (24) pour la lubrification du palier (12) permet, par l'intermédiaire d'un canal d'apport de lubrifiant (32) situé à l'intérieur de l'arbre d'entraînement (6), l'apport de lubrifiant à une première cavité à lubrifiant (37) située sur le premier côté du palier (12). Sur l'autre côté du palier (12) se trouve une seconde cavité à lubrifiant (39) qui est reliée à une conduite de reflux de lubrifiant (43) par l'intermédiaire d'un canal de reflux de lubrifiant (33). Les deux cavités à lubrifiant (37, 39) sont rendus étanches vis-à-vis de la chambre de refoulement (20, 20') grâce à des éléments d'étanchéité annulaires (38, 40). La conduite de reflux de lubrifiant (43) est raccordée à une soupape de régulation de pression (43), de laquelle part une conduite de reflux (46). Cette soupape de régulation de pression (45) garantit le maintien essentiellement constant de la différence entre la pression agissant sur le premier côté des éléments d'étanchéité (38, 40) dans la chambre de refoulement (20, 20') et la pression agissant dans les cavités à lubrifiant (37, 39) sur l'autre côté de ces éléments d'étanchéité (38, 40).
EP07720172A 2007-04-17 2007-06-01 Machine de refoulement construite selon le principe de la spirale Not-in-force EP2137412B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH6292007 2007-04-17
PCT/CH2007/000275 WO2008124950A1 (fr) 2007-04-17 2007-06-01 Machine de refoulement construite selon le principe de la spirale

Publications (2)

Publication Number Publication Date
EP2137412A1 true EP2137412A1 (fr) 2009-12-30
EP2137412B1 EP2137412B1 (fr) 2012-12-05

Family

ID=38922804

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07720172A Not-in-force EP2137412B1 (fr) 2007-04-17 2007-06-01 Machine de refoulement construite selon le principe de la spirale

Country Status (4)

Country Link
US (1) US8051813B2 (fr)
EP (1) EP2137412B1 (fr)
CN (1) CN101652569B (fr)
WO (1) WO2008124950A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2012296526B2 (en) 2011-08-16 2016-09-22 Weir Floway, Inc. Bearing assembly for a vertical turbine pump
US10415706B2 (en) 2013-05-17 2019-09-17 Victor Juchymenko Methods and systems for sealing rotating equipment such as expanders or compressors
FR3079886B1 (fr) * 2018-04-05 2020-04-24 Pfeiffer Vacuum Pompe a vide de type seche

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT340031B (de) 1976-03-03 1977-11-25 Hoerbiger Ventilwerke Ag Steueranordnung fur die oleinspritzung in einen schraubenverdichter
DE3320086A1 (de) 1983-06-03 1984-12-06 Volkswagenwerk Ag, 3180 Wolfsburg Lager-schmiereinrichtung
DE3344015A1 (de) 1983-12-06 1985-06-13 Pierburg Gmbh & Co Kg, 4040 Neuss Spiral- bzw. ringkolbenpumpe
DE3347081A1 (de) 1983-12-24 1985-07-04 Pierburg Gmbh & Co Kg, 4040 Neuss Kreis-, ring- oder spiralkolbenpumpe
DE58906623D1 (de) * 1988-08-03 1994-02-17 Aginfor Ag Verdrängermaschine nach dem Spiralprinzip.
JP2817751B2 (ja) * 1992-04-13 1998-10-30 三菱電機株式会社 スクロール流体機械
EP0614012B1 (fr) * 1993-01-19 1996-09-18 AGINFOR AG für industrielle Forschung Machine de déplacement de fluide du type à spirales
JP3286432B2 (ja) * 1993-11-29 2002-05-27 三洋電機株式会社 回転式スクロール圧縮機
DE4341225C2 (de) * 1993-12-03 2000-01-05 Wap Reinigungssysteme Pumpe
JP2001041162A (ja) * 1999-07-26 2001-02-13 Hitachi Ltd 容積形流体機械
US6261069B1 (en) * 2000-03-08 2001-07-17 Stanadyne Automotive Corp. Shaft seal with pressure equalizing shuttle

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2008124950A1 *

Also Published As

Publication number Publication date
US20100034682A1 (en) 2010-02-11
CN101652569B (zh) 2012-12-12
WO2008124950A1 (fr) 2008-10-23
US8051813B2 (en) 2011-11-08
CN101652569A (zh) 2010-02-17
EP2137412B1 (fr) 2012-12-05

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