EP0116136A2 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
EP0116136A2
EP0116136A2 EP83111989A EP83111989A EP0116136A2 EP 0116136 A2 EP0116136 A2 EP 0116136A2 EP 83111989 A EP83111989 A EP 83111989A EP 83111989 A EP83111989 A EP 83111989A EP 0116136 A2 EP0116136 A2 EP 0116136A2
Authority
EP
European Patent Office
Prior art keywords
rotor
side plates
rotary compressor
oil
end faces
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Withdrawn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
EP83111989A
Other languages
German (de)
English (en)
Other versions
EP0116136A3 (fr
Inventor
Hans Unger
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.)
Knorr Bremse AG
Original Assignee
Knorr Bremse 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 Knorr Bremse AG filed Critical Knorr Bremse AG
Publication of EP0116136A2 publication Critical patent/EP0116136A2/fr
Publication of EP0116136A3 publication Critical patent/EP0116136A3/fr
Withdrawn legal-status Critical Current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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]

Definitions

  • the invention relates to a rotary compressor according to the preamble of claim 1.
  • Rotary piston compressors For rotary compressors based on the design of multi-cell compressors.
  • Rotary piston compressors or similar construction runs within a housing, 'eccentrically mounted, a rotor or rotor; wings or slides extend from this and, in interaction with the inner wall of the housing, form suction and pressure chambers.
  • When compressing air as with conventional piston compressors, care must also be taken to ensure that sufficient cooling and lubrication of the moving parts and of the components exposed to thermal stress are achieved.
  • Rotary compressors are known in which oil is injected into the working chambers during compression; this oil is used for lubrication and cooling at the same time.
  • the disadvantage of such compressors is that the compressed air-oil mixture has to be subjected to a special treatment after it has left the compressor, i.e. the oil has to be removed from the compressed air. In general, a separate separator is used for this purpose, from which the separated oil is returned to the oil circuit.
  • the object of the invention is to design a rotary compressor of the type in question so that it can work with so-called insufficient lubrication, i.e. only such a minimal amount of lubricating oil should be used that it may also be present in the compressed air delivered.
  • insufficient lubrication it should be possible to do justice to the thermal problems as well as the sealing problems; in particular, it should be possible to properly seal the end faces of the rotor from the associated side walls of the rotor housing.
  • the side plates of the compressor which are preferably made of a sintered metal, such as sintered steel, have a dual function, they serve to feed oil into the working chambers of the compressor, preferably into the suction chambers of the same, and at the same time they serve to seal the end faces of the rotor at the side.
  • the lateral pressing of the side plates takes place in an automatically regulating manner, ie the lateral pressing forces are greatest when the compressor delivers the highest working pressures.
  • the lateral pressing of the side plates is preferably carried out in the area of the working chambers where the strongest reaction forces are required; this is in the field of printing chambers of the rotor, that is, in the area of the compressed air outlet, while in the area of the suction side, at the air inlet of the compressor, no comparatively large contact forces are required.
  • the oil used for internal cooling of the rotor is also used for so-called insufficient lubrication, with the oil being able to pass through the side plates impregnated with oil in minimal quantities.
  • the minimum feed with lubricating oil can also be determined precisely, since the side plates can be blocked from the passage of oil by means of plastic coating etc. in the area where the feed of the oil is not desired.
  • a rotary compressor of the multi-cell compressor type is shown; the rotary compressor has in a housing 1 a rotor 5 connected to a drive shaft 3, which is mounted in a manner known per se rotationally asymmetrically with respect to the interior of the housing.
  • a rotor 5 connected to a drive shaft 3, which is mounted in a manner known per se rotationally asymmetrically with respect to the interior of the housing.
  • slots 7 of the rotor 5 slide 9 are guided, which slide in a known manner on the inner wall of the housing 1 under sealing, such that 9 chambers are formed between the individual slides, the volume of which due to the eccentric mounting of the rotor at the Change rotation.
  • An air inlet 11 opens into the housing 1, through which air is introduced into the suction chambers 13 which form in this area.
  • a compressed air outlet 13 is provided on the upper area of the housing 1, as shown, which is connected via a check valve 15 to a collecting duct 17 and ducts 19 branching therefrom.
  • the channels 19 open as shown in Figs. 1 and 2 in the area of highest compression between the rotor and the housing inner wall, i.e. in the area of the pressure chamber 21 which decreases in volume there.
  • chambers 23 for receiving a coolant are provided in the housing 1 of the rotary compressor.
  • the chambers 23 are arranged within a closed coolant circuit and are preferably used in the area of air compression for cooling the housing and thus also for cooling the compressed air.
  • the rotary compressor is also equipped with internal cooling.
  • the rotor 5 is provided with bores 25 which extend in the longitudinal direction thereof and which preferably have the same angular distance from one another own and are closed at their ends.
  • the bores 25 are connected via radially extending channels 27 to a bore 29 provided centrally in the drive shaft 3.
  • a supply line (not shown) for oil opens into the bore 29 or the bore section 31, the supply line being connected to the cooling oil circuit of the motor of the motor vehicle.
  • a sealing element 33 is provided between the bore 29 and the bore portion 31, which has the task of guiding the oil supply in such a way that the oil first flows into the one shown in FIG . channels 27 on the right and in the further circuit / the further channels and bores.
  • any other type of ducting and bore arrangement can also be used for the so-called internal cooling.
  • the oil supplied in the aforementioned manner also serves for lubrication purposes, ie the two bearings 35 and 37 of the compressor are lubricated, with suitable bores of a predetermined diameter being provided for this purpose (FIG. 2). Furthermore, the oil is used to lubricate the slide 9 with respect to the inner wall of the housing 1 and also with respect to side plates 39 of the construction and mode of operation described below.
  • the rotor 5 with the sliders 9 is laterally delimited by side plates 39 which have essentially the same radial extent as the rotor, that is to say are guided on the inside only with respect to the rotor.
  • the side plates 39 are held stationary, ie they do not rotate with the rotor, for which purpose pins 41 are provided, for example, which extend axially directed from the housing 1 into the outer wall of the side plates.
  • the side plates 39 are in the axial direction displaceable, ie they can be pressed in the direction of the rotor 5.
  • the side plates are pressed on using compressed air; for this purpose, channels 43 branch off from the collecting channel 17 (FIG. 2), which open into lateral chambers 45.
  • the chambers 45 are delimited by sealing rings 47, which cover a predetermined area in the area of the pressure chambers 21 of the rotary compressor, since the side plates 39 are to be pressed more strongly against the rotor in this area due to the existing higher pressure forces of the compressed air.
  • the chamber 45 is approximately kidney-shaped and is located radially somewhat within the region of the compressed air generation and discharge via the channels 19. Other contours can be provided for the chambers 45 in accordance with the respective intended use; Likewise, it is also possible to provide several chambers in a precisely defined position.
  • the chambers into the region of the outer side wall of the side plates and to provide means for guiding the side plates in a position-changing manner, ie the side plates can be rotated slightly in the circumferential direction and in turn fixed in this position, for example by means of pins.
  • the contour of the chambers 45 moves along, so that the area of the contact pressure can be varied.
  • the side plates are sealed on their inner circumference by means of grooved rings or the like.
  • Suitable seals 49 with respect to the drive shaft 3 while a trapezoidal sealing ring 51 and additionally an O-ring 53 are provided on the outer circumference, as can be seen from the enlarged section in FIG Fig. 2 results.
  • the type of sealing shown in FIG. 2 or in the enlarged detail proves to be advantageous at the high working pressures; however, others can do the same Appropriate sealing elements are used, which ensure that a lateral escape of the compressed air from the pressure chambers between the slides is prevented.
  • the sealing elements used also have the task of pressing the side plates onto the rotor in the so-called idling phase, that is to say when compressed air is not available or is not yet available.
  • spring elements of any shape and material composition can also be used.
  • the slides 9 are guided in the slots 7.
  • the slides 9 are slightly shorter than the axial dimension of the rotor 5, which means that the side plates only touch the rotor 5 when pressed, but not the end faces of the slides 9.
  • This sealing contour is a sealing surface which, as stated above, does not correspond to the total surface on the end faces of the rotor, but is smaller than this.
  • the end faces of the bores 25 lie in surface sections which are slightly lower than the end faces of the rotor 5. In FIG. 2, this height difference is represented by d.
  • the side plates 39 and the slide 9 are preferably made of a sintered material, such as sintered steel.
  • Sintered steel offers the possibility of adding graphite, MoS 2 or other substances to improve the sliding and emergency running properties.
  • sintered steels have pore spaces of up to 20% of the volume, which is why it is possible to impregnate both the slides 9 and the side plates with oil. This oil diffuses when heated by friction and, in the case of the slides, also diffuses in the direction of the sliding surfaces due to the centrifugal force. This provides additional lubrication for the gate valves in the critical running-in phase.
  • the sintered steel also has very high thermal conductivity and thermal expansion corresponding to the rotor or slide. This makes it possible to keep the axial gap between the slides and the side plates very small and thus also to minimize leakage losses.
  • the pore spaces of the side plates are also soaked with oil.
  • the subsequent supply of the side plates with oil takes place from the gap-shaped space 55, which is provided between the side plates and the bearing caps 57.
  • the space 55 extends along the entire end face of the rotor 5, being interrupted by the chamber 45 in the region of the pressure chambers, that is to say in the high-pressure region of the rotor.
  • the space 55 is therefore composed, also as a result of the existing contouring of the sealing surface of the rotor, from a plurality of interconnected individual spaces which are supplied with the oil from the oil circuit.
  • the refilling of the side plates with oil takes place in a targeted manner, ie the side plates are subjected to a specific treatment to ensure that the oil escapes in the direction of the Working chambers of the compressor are preferably only in the area of the suction chambers, but not in the area of the pressure chamber 21.
  • the side plates can be coated with plastic prior to their installation, for example with Teflon, this coating, evaporation and the like preferably taking place in those surface areas which after installation have their position after the pressure chambers or are assigned to the compressed air outlet of the compressor.
  • the coating can be carried out both on the inside of the side panels and on their outside; This targeted coating, which is fixed to a specific surface area, ensures that the pores in the side plate to be impregnated with oil are closed in this area and therefore do not release any oil.
  • the oil which is used both for internal cooling and for lubrication, flows, as described above, in the oil circuit of the compressor provided for this purpose, which can be connected to the oil circuit of the motor vehicle or the like.
  • the oil is drained off.
  • the cooling water of the external cooling is drained off via the outlet 63 (FIG. 2), which is connected to the chambers 23 of the housing. Oil can of course also be used for the external cooling in the same way as for the internal cooling.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP83111989A 1983-01-14 1983-11-30 Compresseur rotatif Withdrawn EP0116136A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3301098 1983-01-14
DE19833301098 DE3301098A1 (de) 1983-01-14 1983-01-14 Rotationskompressor

Publications (2)

Publication Number Publication Date
EP0116136A2 true EP0116136A2 (fr) 1984-08-22
EP0116136A3 EP0116136A3 (fr) 1986-02-19

Family

ID=6188308

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83111989A Withdrawn EP0116136A3 (fr) 1983-01-14 1983-11-30 Compresseur rotatif

Country Status (2)

Country Link
EP (1) EP0116136A3 (fr)
DE (1) DE3301098A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0793020A1 (fr) * 1994-12-20 1997-09-03 Zexel Corporation Compresseur a palettes
FR2766881A1 (fr) * 1997-08-01 1999-02-05 Magneti Marelli Spa Pompe a vide possedant des palettes
FR2780452A1 (fr) * 1998-06-24 1999-12-31 Luk Fahrzeug Hydraulik Dispositif de transport hydraulique
EP1013926A1 (fr) * 1998-12-18 2000-06-28 Hydraulik Ring GmbH Machine hydraulique à déplacement positif, en particulier pompe
WO2003071135A1 (fr) * 2002-02-18 2003-08-28 Luk Automobiltechnik Gmbh & Co. Kg Pompe a vide comprenant un raccord monobloc mis en place contre la partie boitier
EP1739280A1 (fr) * 2005-06-27 2007-01-03 Mighty Seven International Co., Ltd. Moteur d' un outil pneumatique

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4117936C2 (de) * 1991-05-31 1998-04-02 Andro Caric Rotationskolbenmaschine
DE102008036273B4 (de) 2008-08-04 2013-09-26 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Rotationskolbenpumpe mit Taschen für Schmiermittel

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH92226A (de) * 1920-10-07 1922-01-02 Schmied Walther Abdichtung von Drehkolben rotierender Maschinen.
CH150074A (de) * 1930-06-20 1931-10-15 Schmied Walther Einrichtung zur Erzielung eines Druckausgleiches an Dichtungskolben von Drehkolbenmaschinen mit mehreren Zellen.
US2044873A (en) * 1933-11-21 1936-06-23 Cecil J Beust Rotary compressor
US3311064A (en) * 1963-07-05 1967-03-28 Zahnradfabrik Friedrichshafen Vane-type rotary pumps

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH92226A (de) * 1920-10-07 1922-01-02 Schmied Walther Abdichtung von Drehkolben rotierender Maschinen.
CH150074A (de) * 1930-06-20 1931-10-15 Schmied Walther Einrichtung zur Erzielung eines Druckausgleiches an Dichtungskolben von Drehkolbenmaschinen mit mehreren Zellen.
US2044873A (en) * 1933-11-21 1936-06-23 Cecil J Beust Rotary compressor
US3311064A (en) * 1963-07-05 1967-03-28 Zahnradfabrik Friedrichshafen Vane-type rotary pumps

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0793020A1 (fr) * 1994-12-20 1997-09-03 Zexel Corporation Compresseur a palettes
EP0793020A4 (fr) * 1994-12-20 1998-09-09 Zexel Corp Compresseur a palettes
FR2766881A1 (fr) * 1997-08-01 1999-02-05 Magneti Marelli Spa Pompe a vide possedant des palettes
FR2780452A1 (fr) * 1998-06-24 1999-12-31 Luk Fahrzeug Hydraulik Dispositif de transport hydraulique
EP1013926A1 (fr) * 1998-12-18 2000-06-28 Hydraulik Ring GmbH Machine hydraulique à déplacement positif, en particulier pompe
US6450792B1 (en) 1998-12-18 2002-09-17 Hydraulik-Ring Gmbh Hydraulic displacement machine
WO2003071135A1 (fr) * 2002-02-18 2003-08-28 Luk Automobiltechnik Gmbh & Co. Kg Pompe a vide comprenant un raccord monobloc mis en place contre la partie boitier
FR2838790A1 (fr) * 2002-02-18 2003-10-24 Luk Automobiltech Gmbh & Co Kg Pompe
EP1739280A1 (fr) * 2005-06-27 2007-01-03 Mighty Seven International Co., Ltd. Moteur d' un outil pneumatique

Also Published As

Publication number Publication date
EP0116136A3 (fr) 1986-02-19
DE3301098A1 (de) 1984-07-19

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Inventor name: UNGER, HANS