EP0267559A1 - Soufflante à piston rotatif - Google Patents

Soufflante à piston rotatif Download PDF

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Publication number
EP0267559A1
EP0267559A1 EP87116469A EP87116469A EP0267559A1 EP 0267559 A1 EP0267559 A1 EP 0267559A1 EP 87116469 A EP87116469 A EP 87116469A EP 87116469 A EP87116469 A EP 87116469A EP 0267559 A1 EP0267559 A1 EP 0267559A1
Authority
EP
European Patent Office
Prior art keywords
piston
foam
rotary piston
blower according
recesses
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
EP87116469A
Other languages
German (de)
English (en)
Other versions
EP0267559B1 (fr
Inventor
Roland Nuber
Werner Schubert
Wolfgang Sohler
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.)
Wankel GmbH
Original Assignee
Wankel GmbH
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 Wankel GmbH filed Critical Wankel GmbH
Publication of EP0267559A1 publication Critical patent/EP0267559A1/fr
Application granted granted Critical
Publication of EP0267559B1 publication Critical patent/EP0267559B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid
    • F04C27/003—Radial sealings for working fluid of resilient material
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • 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
    • F01C21/08—Rotary pistons
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid
    • F04C27/004—Radial sealing elements specially adapted for intermeshing-engagement type pumps, e.g. gear 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
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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

Definitions

  • the invention relates to a rotary piston blower with working or shut-off parts and working space walls which start up contactlessly at a relative speed and form a gap seal between them.
  • gap widths of a few tenths of a millimeter can be achieved between the machine parts that form the work space.
  • a coating with a plastic with good sliding properties as described in DE-OS 36 21 178.8, much better results can be achieved, since such a coating can grind itself down to a few hundredths of a millimeter in operation.
  • it can only be applied to the piston blanks precisely with greater manufacturing difficulties and requires considerable machining by turning or the like, but it has the disadvantage above all that it can result under the influence of the operating heat, which can reach 120 ° C. and more Centrifugal force effect.
  • the object of the invention was to carry out the work space-forming parts of the machines mentioned at the outset, which, with the greatest possible precision, without increased design and cost expenditure, above all without subsequent revision after shaping, allowed the formation of narrowest sealing gaps among one another and also withstood higher operating temperatures .
  • the parts coated with or made from the foamed plastic run into the narrowest possible gaps on the counter surface.
  • a surface or edge made of foamed plastic runs against a counter surface or edge made of metal, the metal surface should be so rough that the foam counter surface is ground off when touched. This roughness, which is said to be approximately 100 to 150 ⁇ m, can be produced well with sandblasting but also with etches, through which the crystallite structure of the metal is exposed. It is therefore to be avoided, just as metal should not tarnish against metal, to pair foam surfaces with foam surfaces.
  • the bonding of the foam parts to the metal structures carrying them can also be improved very much by producing a roughness of the metal surfaces to be connected to the foam by the resulting enlargement of the bonding area. This can be done by sandblasting or by etching.
  • the production of the foam parts takes place in external tools which, while observing the appropriate tolerances for shrinkage or growth of the foam, precisely measure the negative form of the represent part to be preserved, by foaming.
  • the metal parts to which the foam is to be attached are to be inserted into these tools after roughening, and any cavities in the foam which produce mold cavities and which are pulled out after molding.
  • the foam is preferably polyurethane foamed with water. Foaming with fluorocarbons is to be avoided, since the fluorine-containing gas emitted by the foam during operating heat corrodes the metal parts of the machine. In the case of water-foamed polyurethane, there are also no thermal expansions caused by blowing agents, even at operating temperatures.
  • the machine parts according to the invention since they are mostly rotary bodies with axially parallel cylinder surfaces, can be produced from roughened, extruded aluminum parts in the manner described above without further reworking. Running in or grinding in only requires short machine runtimes, whereby the processed material of the foam accumulates as harmless dust and is blown out of the machine.
  • blowers according to the invention are therefore very suitable for cheap mass production. They point as a result Their very high level of tightness achieves performance that such blowers have so far not been able to provide.
  • the piston of the half-roll design shown in FIG. 1 has a wing 1 with a cylindrical surface 2 with a large radius and a cylindrical surface 3 with a small radius.
  • the cylindrical surface 2 with a large radius extends over 135 °, the cylindrical surface 3 with a small radius over 180 °, measured with the cylinder axis as the center.
  • symmetrical engagement surfaces 4 and 5 are provided, each of which is bent outwards at an angle of 120 ° around a convex curve 6 and 7, and each consist of an outer flat engagement surface 8 and a flat inner engagement surface 9 .
  • the inner engagement surfaces 9 merge into concave curves 10 and 11 in the cylindrical surface 3 with a small radius.
  • the outer flat engagement surfaces 8 cut the cylinder surface 2 at an obtuse angle of 120 °.
  • the inner engagement surfaces 9 therefore lie in the parting plane 12 between the wing 1 and the cylindrical surface 3 with the small radius.
  • the wing 1 consists essentially of the plastic body 13 made of foamed polyurethane, which forms a solid non-porous wall on its outer walls, since it is formed by foaming in a closed tool and therefore the plastic foam after the walls of the tool up to extensive pore clearance due to its inner Compressed pressure.
  • the force introduction of drive pins 14 into this plastic body 13 takes place through a section of an extruded light metal profile 15 foamed into the plastic body 13.
  • the piston part 16 forming the cylindrical surface 3 with a small radius is part of the extruded light metal profile 15 and is filled with lead as a counterweight 17 to the wing 1.
  • the shaft journals 18 are inserted on the left in FIG. 2 and 19 on the right side, which have disks 22, 23 running in turns of the housing side walls 20, 21. With the disks 22, 23, the stub shafts 24 are screwed to the light metal profile 15.
  • the plastic body 13 is anchored in the light metal profile 15 in its ribs 26, 27, 28, 29, 30.
  • These ribs 26, 27, 28, 29, 30 are shown in different embodiments in FIG. 1. They can have lateral anchoring ribs 31, 32, 33 and openings 34 in these ribs. This forms sufficient undercuts in which the very rigid and solid plastic body 13 is securely held against the centrifugal forces generated during operation.
  • the ribs 26, 27, 28, 29, 30 run just like the anchoring ribs 31, 32, 33 axially and can be pulled out without difficulty when extruding the light metal profile 15. When it foams, the plastic enters all cavities and undercuts in the light metal profile, so that a hardened piston is created when hardened, which can absorb and transmit all forces occurring during operation.
  • the outer ribs 26 and 30 are at the same time part of the outer engagement surface 8.
  • the inner engagement surface 9 is formed by the light metal profile 15.
  • These two engagement surfaces 8 and 9 have no sealing function and can therefore be disregarded.
  • the sealing during the transition from the rolling of the two-sided cylinder surfaces 2 and 3 is carried out by the convex curves 6 and 7, which run against one another without contact between the engagement surfaces 8 and 9, to seal the leakage path between the two pistons.
  • the right curve 7 of the piston shown in FIG. 2 is formed from the same foam as that of the foam body 13 when it is foamed out by passing through the opening 35 in the light metal profile 15.
  • the left curve 6 of this piston consists of metal.
  • the left rounding 6 is made of foam, corresponding to the rounding 7 of the piston shown in FIG. 3, while the right rounding 7 of the opposing piston is made of metal. There is therefore always a rounding of foam on a rounding of aluminum in the opposing piston.
  • the surface of the jacket raceways 36 and 37 of the housing (Fig. 3), the cylindrical surfaces with the small radius, the metallic curve 6 of the one piston and the metallic curve 7 of the counter-piston are roughened by sandblasting, so that a foam surface is always paired with a roughened aluminum surface and can grind in on it, but never foam with foam and just as little metal with metal. This means that metal meets foam on all sealing surfaces.
  • the light metal profile 15 Since the light metal profile 15 must also be roughened by sandblasting on the surfaces on which the foam body, including the curves 6 and 7, in order to increase the bonding area, the light metal profile 15 can be sandblasted on all sides in one operation. The same is possible with etching by dipping the light metal profile 15.
  • the housing is sealed off from the shaft passages in the side walls 20, 21 by means of disks 22, 23, which are arranged concentrically around the shaft journals 18, 19.
  • the seal was in the narrowest gap spaces between the peripheral surfaces of these disks 22, 23 and their recesses in the housing side walls 20, 21, because these gap spaces could be produced more easily by turning out than the gaps lying in the radial plane between the bottom of these recesses and the Discs 22, 23.
  • the task of this seal is not only to prevent leakage of the compressed gas but also to prevent bearing grease and lubricating oil from penetrating into the ar working rooms with negative pressure in these compared to the storage and gear rooms. Oil penetration results in undesirable oil contents in the production gas. Withdrawing the bearing grease causes the bearings to run dry.
  • concentrically circumferential recesses 36 are provided in the disks 22, 23, which, like the wings 1 of the pistons, are foamed with plastic in a die-casting process. These recesses 36 are of different depths so that the disks 22, 23 can act as counterweights.
  • the recesses 37 forming a semicircular ring are axially deeper than the recesses 38 forming the other semicircular ring on the side of the piston part 16 with a small radius. The difference results from the necessary mass of the counterweights, which can be adjusted in this way.
  • the piston of the quarter design shown in FIG. 3 is radially symmetrical and therefore does not require any balancing of its two wings 41 and 42. These consist in the same way as wing 1 of the two foam bodies 43 and one in them by foaming in the die-casting process with ribs 44, 45, 46, 47, 48, 49 anchored light metal profiles 50.
  • This light metal profile 50 is here the carrier of the two foam bodies 43 and transmits the force of the shaft 51 arranged in it to them.
  • the ribs 44, 45, 46, 47, 48, 49 which pass through in the axial direction have anchors 52 which, like the ribs themselves, can have different shapes, examples of which are shown in FIG. 1. Openings 53 are provided in these ribs, which have the same task as the openings 34 and FIG. 1.
  • the engagement surfaces 56 and 57 provided between the cylinder surfaces 54 with a large radius and the cylinder surfaces 55 with a small radius and the roundings 58 and 59 lying between them have the same geometry as those of the half-roller blade shown in FIG. 1.
  • the cylinder surfaces 54 with a large radius are formed from foam, but the cylinder surfaces 55 with a small radius are made of roughened metal.
  • the convex rounding 56 is made of roughened metal for both piston wings, while the rounding 57 on the other side of the piston wing consists of foam.
  • the connection of the latter with the foam bodies 43 is the same as for the pistons of a half-roll machine shown in FIG. 1.
  • the manufacturing process of such pistons is the same as there.
  • these convex roundings would have to be made of foam or metal, so that a rounding of foam would always start and run against a metal one this can grind in.
  • FIGS. 4 and 71 show embodiments of pistons of a half- or quarter-roll fan blown according to the invention, in which cavities 72 and 73 are formed in the foam bodies 70 in FIGS. 4 and 71 in FIG. 3 by mold cores inserted axially parallel in the foaming tool . After the foam has hardened, e.g. of the polyurethane foam can be pulled out axially.
  • FIG. 6 shows a conventional Roots blower, in which the convex surfaces 76 of the pistons 77 and 78 which run against the housing raceways 74, 75 and on the concave surfaces of the counter-piston are formed by foam bodies 79.
  • foam bodies 79 can at best be anchored to the aluminum piston with ribs in accordance with the above-described half and quarter roll blowers.
  • a foam surface always runs onto metal surfaces, which must be roughened in the manner described above.
  • FIG. 7 shows a rotary piston blower working in meshing engagement, which is driven by a piston 80 corresponding to the piston of the above-described Roots blower and a counterflow having three shut-off parts 81.
  • 82 is formed, which rotate in a cylindrical housing 83.
  • the piston 80 runs against the inner surfaces of the shut-off parts 81, which are lined with foam according to the invention on the contact surfaces 84.
  • the shut-off parts 81 in turn run against the housing raceway 86 with cylinder surfaces 85 lined with foam.
  • the foam bodies, which form the surfaces 84 are pressed against the shut-off parts 83 carrying them by the centrifugal forces. Therefore, only the foam bodies that form the surfaces 85 require special anchoring.
  • a conventional screw compressor is shown, in which the contact surface 90 of the right screw in the drawing and the flanks 91 and 92 of the threads of the counter screw 93 are lined with foamed plastic, so that they always start on roughened metal.
  • a known scroll compressor is shown, in which the housing with 100, the spiral wall fixed in this with 101 and the rotor with 102 are designated.
  • the rotor 102 has a coating 103 made of foamed plastic on its radially inner wall, which runs against the spiral wall 101 of the housing 100, while the counter surface 104 of the wall 101 consists of roughened metal.
  • the foam coating on the centrifugal force Gative side is arranged, that is, from the centrifugal force is always pressed against the wall carrying it, so that no special anchoring is required.
  • the foam always runs against roughened metal.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP87116469A 1986-11-08 1987-11-07 Soufflante à piston rotatif Expired - Lifetime EP0267559B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3638183 1986-11-08
DE3638183 1986-11-08
DE3712354 1987-04-11
DE19873712354 DE3712354A1 (de) 1986-11-08 1987-04-11 Rotationskolbengeblaese

Publications (2)

Publication Number Publication Date
EP0267559A1 true EP0267559A1 (fr) 1988-05-18
EP0267559B1 EP0267559B1 (fr) 1991-04-24

Family

ID=25849195

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87116469A Expired - Lifetime EP0267559B1 (fr) 1986-11-08 1987-11-07 Soufflante à piston rotatif

Country Status (4)

Country Link
US (1) US4846642A (fr)
EP (1) EP0267559B1 (fr)
JP (1) JP2505501B2 (fr)
DE (2) DE3712354A1 (fr)

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EP0493315A1 (fr) * 1990-12-28 1992-07-01 TES WANKEL, TECHNISCHE FORSCHUNGS- UND ENTWICKLUNGSSTELLE LINDAU GmbH Elément d'étanchéité
EP2711551A3 (fr) * 2012-08-02 2014-06-11 Robert Bosch Gmbh Pompe, notamment pompe volumétrique

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DE3911314A1 (de) * 1989-04-07 1990-10-11 Leybold Ag Vakuumpumpe
DE3916858A1 (de) * 1989-05-24 1990-11-29 Kuehnle Kopp Kausch Ag Innenachsige drehkolbenmaschine
SE8904359L (sv) * 1989-12-22 1991-06-23 Opcon Autorotor Ab Skruvkompressor foer foerbraenningsmotorer
SE468122B (sv) * 1990-04-27 1992-11-09 Svenska Rotor Maskiner Ab Rotor foer en skruvrotormaskin, en skruvrotormaskin samt ett foerfarande foer tillverkning av en rotor
US5255432A (en) * 1990-12-28 1993-10-26 Tes Wankel Technische Forschungsund Entwicklungsstelle Method for manufacturing a seal between machine parts
SE502265C2 (sv) * 1991-09-03 1995-09-25 Opcon Autorotor Ab Rotor för en skruvrotormaskin
US5165881A (en) * 1991-09-16 1992-11-24 Opcon Autorotor Ab Rotor for a screw rotor machine
JPH08121367A (ja) * 1994-10-31 1996-05-14 Ishikawajima Harima Heavy Ind Co Ltd リショルムコンプレッサ用シール装置
US7192260B2 (en) * 2003-10-09 2007-03-20 Lehr Precision, Inc. Progressive cavity pump/motor stator, and apparatus and method to manufacture same by electrochemical machining
US7153112B2 (en) * 2003-12-09 2006-12-26 Dresser-Rand Company Compressor and a method for compressing fluid
US7179067B2 (en) * 2004-01-13 2007-02-20 Scroll Technologies Scroll compressor with wrap walls provided with an abradable coating and a load-bearing surface at radially outer locations
DE102005015685A1 (de) * 2005-04-06 2006-10-12 Leybold Vacuum Gmbh Vakuumpumpen-Rotor
US8100676B2 (en) * 2005-05-06 2012-01-24 Inter-Ice Pump Aps Rotor, a method for producing such rotor and a pump comprising such rotor
DE102010014248B4 (de) * 2010-04-08 2016-04-28 Netzsch Pumpen & Systeme Gmbh Kontaktelemente für Drehkolbenpumpen
EP2615307B1 (fr) * 2012-01-12 2019-08-21 Vacuubrand Gmbh + Co Kg Pompe à vide à vis
DE102012003287A1 (de) * 2012-02-20 2013-08-22 Netzsch Pumpen & Systeme Gmbh Drehkolben
AU2015218295B2 (en) * 2014-02-14 2018-08-16 Starrotor Corporation Improved performance of gerotor compressors and expanders
US11655816B2 (en) 2015-05-08 2023-05-23 Danfoss Power Solutions Gmbh & Co. Ohg Fluid working systems
DE102015213098B4 (de) * 2015-07-13 2017-05-04 Joma-Polytec Gmbh Flügel für eine Flügelzellenpumpe und Flügelzellenpumpe
CN106499629A (zh) * 2016-11-04 2017-03-15 西安航空动力控制科技有限公司 一种罗茨风机转子组件
DE202022104701U1 (de) * 2022-08-19 2023-11-22 Vogelsang Gmbh & Co. Kg Verdrängerkörper und Pumpengehäuse für eine Verdrängerpumpe

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Publication number Priority date Publication date Assignee Title
EP0012615A1 (fr) * 1978-12-15 1980-06-25 Sankyo Electric Company Limited Améliorations à des compresseurs à fluide du type à volutes imbriquées
GB2115875A (en) * 1982-02-24 1983-09-14 Plessey Co Plc Gear pumps
EP0109823A1 (fr) * 1982-11-18 1984-05-30 Ingersoll-Rand Company Machine rotative a déplacement positif
DE3321692A1 (de) * 1983-06-15 1984-12-20 Fresenius AG, 6380 Bad Homburg Zahnradpumpe
GB2157769A (en) * 1984-04-16 1985-10-30 Gilardini Spa A supercharger for heat engines of vehicles

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0493315A1 (fr) * 1990-12-28 1992-07-01 TES WANKEL, TECHNISCHE FORSCHUNGS- UND ENTWICKLUNGSSTELLE LINDAU GmbH Elément d'étanchéité
EP2711551A3 (fr) * 2012-08-02 2014-06-11 Robert Bosch Gmbh Pompe, notamment pompe volumétrique

Also Published As

Publication number Publication date
DE3712354A1 (de) 1988-05-11
JPS63179192A (ja) 1988-07-23
US4846642A (en) 1989-07-11
JP2505501B2 (ja) 1996-06-12
DE3769598D1 (de) 1991-05-29
EP0267559B1 (fr) 1991-04-24

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