EP1362188B1 - Drehkolbenmaschine für verdichtbare medien - Google Patents

Drehkolbenmaschine für verdichtbare medien Download PDF

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Publication number
EP1362188B1
EP1362188B1 EP02711735A EP02711735A EP1362188B1 EP 1362188 B1 EP1362188 B1 EP 1362188B1 EP 02711735 A EP02711735 A EP 02711735A EP 02711735 A EP02711735 A EP 02711735A EP 1362188 B1 EP1362188 B1 EP 1362188B1
Authority
EP
European Patent Office
Prior art keywords
disk
rotary piston
rotor
piston machine
machine according
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
EP02711735A
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German (de)
English (en)
French (fr)
Other versions
EP1362188A1 (de
Inventor
Ulrich Becher
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.)
Ateliers Busch SA
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Ateliers Busch SA
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Filing date
Publication date
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Publication of EP1362188A1 publication Critical patent/EP1362188A1/de
Application granted granted Critical
Publication of EP1362188B1 publication Critical patent/EP1362188B1/de
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
    • 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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • F04C18/123—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 or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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

Definitions

  • the present invention relates to a Rotary piston machine for compressible media, with at least two stored in a common housing, tight enclosed, inevitably rotatable with each other Rotary pistons, wherein the rotary pistons a plurality in pairs interlocking disc-shaped sections whose thickness in the direction of the pressure side, each having Disc at least a lateral surface and a core surface which passes through along circular arc with center on the Axis of the respective rotary piston guided guidelines are formed and each through an intermediate surface are connected.
  • Rotary piston for vacuum pumps or positive displacement pumps for Gases are usually in the form of screw pairs produced.
  • Screw pairs For displacement or compression have this Screw spindles on a variable pitch.
  • screw compressors for gases with two interlocking screws whose pitch is against the Pressure side down steadily reduced, known.
  • Such compressors Although you can achieve high degrees of compaction, but is the production of screw pairs with variable Gradient technically difficult, especially as the screws should play together as free of play as possible To keep pressure losses small. Thus, the production is This type of screw compressor is expensive.
  • Roots blowers are known, with two intermeshing disc-shaped Rotary piston.
  • the air flow is transverse to the Rotary axes of the rotary piston, so that such compressors for large volumes of air, but only for small ones Degree of compaction, are suitable.
  • DE-2934065 discloses such helical stage rotary pistons in a rotary engine of the type mentioned.
  • the spindles have a pseudo-thread-like groove on, which by step-shaped, in the helix successive, with the spindle axes at right angles provided standing flat boundary surfaces, recesses is formed.
  • this groove intervenes, in by the two Spindle axes certain level, a correspondingly shaped Threaded comb of the counter spindle and includes each groove from a groove volume, so that during the rolling the spindles of the comb the groove volumes with compressible medium shifted from the inlet to the outlet, wherein the groove volumes be changed and the desired pressure difference between Inlet and outlet is achieved.
  • the spindles point in Cross-section of a semicircular contour with a detail, the through the core surface and two step-forming Intermediate surfaces is limited to.
  • the sector angle of the outer lateral surfaces and inner core surfaces have the same Value, namely 180 °.
  • the disadvantage of this Rotary piston machine the high number of step-shaped Boundary surfaces which are necessary to the pseudo-thread-like Groove form whose production is a high Number of chip removing operations needed. adversely is furthermore the high precision of the intermediate surfaces, which necessary to increase the pressure losses from stage to stage minimize.
  • the document AT-261792 also describes a Rotary piston machine of this kind in which the Spiral stage rotary piston identical in the face section Single discs exist.
  • Each disc has two diametrical ones opposite outer lateral surfaces and two themselves diametrically opposed inner core surfaces whose Sector angles are all the same (90 °).
  • the coat and Core surfaces are therefore connected by intermediate surfaces, the are designed as elongated epicycloids to the Seal between the panes to effect. Consequently, must both their profile and the exterior Synchronizer of the machine very precise - and consequently consuming - to be produced.
  • these Pamphlet provides, the thermal loads of To reduce flank tips by a rounded shape These can not be avoided during gas reflux.
  • the object of the present invention is the production a rotary engine with a high degree of compaction, in particular a vacuum pump in which the final vacuum better should be as with rotary valve, about similar to that multi-stage roots pumps.
  • the production should be less be complicated as that of multi-stage pumps and also less expensive than that of Screw pumps.
  • an inner Compression of the compressible medium or gas take place to reduce energy consumption and Operating temperature to achieve.
  • the Noise during operation should be as low as possible.
  • Rotary piston a staggered helical gear with horizontal intermediate sections between two chambers formed, with varying step height. It will be in achsialer Direction a chamber sequence formed, with optional variable Volume, i. optionally variable internal compression, by selectable thickness variation of the disc-shaped sections.
  • each rotary piston be made in one piece, which the dimensional stability during operation significantly improved, and thermally less critical than a stack of single panes. Is the operating temperature of the Rotary piston engine application low, so can the Rotary pistons also from sequences axially to each other arranged individual profile discs are assembled, whereby manufacturing costs are saved.
  • the theoretically cycloid-shaped curved Interfaces i.e. the parallelepiped surfaces, the each lateral surface and core surface, i. Outer cylinder and Core cylinder, a disc-shaped profile section, at opposite direction of rotation of the rotary piston, connect, meet no critical, functionally essential sealing function and thus describe a theoretical maximum contour.
  • a Profile contour of the interface which is slightly smaller, or flattened, than this theoretical maximum contour and easier to produce, such as an undecorated and / or nearly straight contour, can therefore be preferred and is quite functional. This will continue the increased angular play during operation.
  • both have adjacent discs a disc with an outer lateral surface, whose Sector angle greater than the sector angle of the core surface is, outer lateral surfaces on whose sector angle smaller are the sector angle of the core surfaces.
  • the difference between the Sector angle of the outer lateral surface and the core surface a disc-shaped section large.
  • the Sector angle of this lateral surface smaller than 90 ° and more preferably, less than 60 °.
  • Such a disc lies a slice of the other rotary piston, with a Sector angle of the outer lateral surface corresponding to greater than 270 °, or greater than 300 °, is opposite.
  • the chambers of a respective Rotary piston designed so that the intermediate surfaces of a Slice each with an intermediate surface of an adjacent Slice a continuous interface with common Form a guideline.
  • the synchronizer of the inventive Rotary piston machine can be selected in such a way that the two outer-axis rotary pistons have an opposite Have direction of rotation.
  • the outer diameter of the rotary piston, the Diameter of the core cylinder and the translation can then be selected so that the pistons roll against each other without sliding, the lateral surface of a disc-shaped Section on the core surface of the opposite Unrolls section.
  • a translation of 1: 1 is to be selected. Are however these numbers are different, so is the translation select accordingly.
  • the two rotary pistons inside axis i. as an outer rotor and Inner rotor, with an additional G-rotor, formed.
  • rotary piston In several embodiments of the rotary piston, have the disc-shaped sections of a respective rotary piston only two alternating incision profile contours on.
  • the diameter of the shell cylinder and Core cylinders of outer-axis rotary pistons should be the same being in a same, perpendicular to the piston axis Plane, the section of the first piston the one incision profile contour while facing the opposite Section of the second piston, the other endcut profile contour having.
  • the two rotary pistons can also be used as main rotor and Maumatir, with different diameters, and thus different wave performances - up to 100: 0% - be designed, what advantages in the execution of the Synchronizer provides.
  • the rotary piston alternate sequences of sections with different ones Cross-section profile contours with circular locking discs, so that a respective piston sections with three or more has different profile contours.
  • the rotary piston are outboard and parallel axis in a (not shown) housing with two cylindrical bores, with external synchronizer, stored.
  • the rotary pistons have an opposite direction of rotation.
  • the rotary pistons have 14 disc-shaped sections, Namely, two end portions (0, 13) for the inlet and outlet of the medium, and two profile sections (1-12) different, alternating profile contours, each one a section having an outer lateral surface (m1) with a small sector angle has alternated with a section, which has a lateral surface (M1) with a large sector angle having.
  • these have Sector angle values each slightly smaller than 36 ° and slightly smaller than 144 °, so that get an angular play remains.
  • Figures 3 and 4 illustrate the progressively twisted angular position from one section to the next, i.e. 72 ° from a section to the identical next but one Section, wherein an intermediate surface (z1) of a section each above, or below, seen in the axial direction, one Intermediate surface of an adjacent section of the other Profile contour is arranged.
  • This will each become a chamber formed (see Figure 2) by parts of the core surfaces (k1 ', K1 ') and intermediate surfaces (z1') of adjacent sections is, and thus an axial chamber sequence with variable Volume, wherein the internal compression by thickness variation of the Profile sections is achieved: to the realization of the inner Compression decreases, the axial extent of the sections, and thus the chambers, gradually from the inlet to the outlet.
  • Sections 1 and 2 have the same thickness. From section 2 to section 3, the thickness increases by a factor of about 1.4 from; the thicknesses of sections 3 and 4 are the same again, etc. In this distribution of the thicknesses of the sections where two successive and opposite sections of the one and the other rotary pistons have the same thickness, Energy distribution accounts for about 50:50% of each Rotary pistons.
  • the thickness of the sections could also vary from each section to the other, according to one selectable geometric rule.
  • a second, not separate in the figures illustrated embodiment have the disc-shaped Sections of the two rotary pistons the same profile incision contours and the same angular displacements as in the Figures 3 and 4.
  • the difference to the first Embodiment lies in the thickness distribution of the sections.
  • the sections 1, 3, 7, etc ... are thick sections, where however, from the thickest section 1, the thickness gradually until last section on the print side decreases.
  • the sections 0, 2, 4, 6, etc ... are all thin slices.
  • a rotary piston takes over the role a main rotor, while the other rotary piston the role a sideline takes over.
  • the energy distribution between Major and minor can move up to approximately 85:15% become.
  • Embodiments of the pistons are outboard and parallel axis in two cylindrical holes of a (not shown) housing with external synchronizer stored. They are asymmetrical, with very different ones Wave performance, up to 100: 0%. The minimum number of different profile contours of the piston sections depends on the design of the profile sequences.
  • FIGS. 5, 6, 7, 8 Embodiment are the diameters of the main rotor and the Mausonsrs strongly different.
  • the main runner has two alternating different profile contours, with the one Profile contour an outer lateral surface (m3) with a small Sector angle, and alternated with a profile contour, whose outer lateral surface (M3) has a large sector angle having.
  • the same alternance (m3 ', M3') applies to the Mausonr too.
  • the main rotor has eleven disk-shaped sections.
  • This main runner has five thickness sections, 1, 3, 5, 7, 9, the thickness gradually decreases in the direction of the pressure side and whose outer lateral surface (m3) has a small sector angle Has. These five sections form pump sections P1-P5. she are separated by six sections 0, 2, 4, 6, 8, 10 and surrounded, which only a short-angled Kern lakeaurough (k3), and each form a control section S, which forwards the gas to the next pump section. For example, the thickness of the five pump sections, from P1 up to P5, from about 70 millimeters in each case by a third, up to a thickness of 13 millimeters while each decrease Control section S has a thickness of 10 millimeters. The Total length of the main runner then measures about 240 millimeters.
  • main and secondary rotor is an energy distribution of almost 100% on the main rotor and 0% on the minor.
  • Fig. 10 diagrammatically illustrates a fifth embodiment
  • the main runner has two alternating different Forehead profiles, each with two identical outer Lateral surfaces and two equal core surfaces, each diametrically opposite, having.
  • the relative sector angle dimension The shell and core surfaces vary from section to section Section as in the previous embodiments.
  • Of the Mausonr has only one outer lateral surface and a core surface, alternating large and small angles.
  • the Synchronizer is designed so that the Tour number of the Mauillonrs twice the number of touring the Main runner is. With this construction becomes a strong asymmetrical energy distribution achieved, namely around 85% on the main runner and about 15% on the runner.
  • the fourth and the fifth Embodiment are the intermediate surfaces of the main rotor undecided, what individual operations simplified during production.
  • Rotary piston When assembled from individual profile discs Rotary piston is the number of different Einselmaschine by the Use of the same control and lock washers reduced.
  • the rotary piston pair in the Figures 11 to 15 consists of a Non-contact, parallel-axis, two-axis, external axis, constant rotating displacement machine, with a housing with two cylindrical holes and external Synchronizer, wherein the two rotary pistons the have the same direction of rotation.
  • FIG. 11 shows the full structure of a Embodiment with 17 disk-shaped sections, Namely two end plates (E), 0 and 16; three full sequences S-P-S-K, the four sections just described, 1 to 4, 5 to 8, 9 to 12; and an incomplete sequence, S-P-S, i. with a first control disk 13, a pumping stage 14 and a second control disk 15th
  • the control disks S of the main rotor can all consist of thin disks, since they serve only to transfer the medium from one pump stage P into the following channel K and again into the next pump stage.
  • the graduation of the axial extent of the pumping stages and the channel stages may be subject to various computational rules for practical purposes.
  • the taffel 1 shows an example of two gradations, in which the thickness of the thickest stage, namely the pumping stage 1, was arbitrarily used with 1.
  • Example 2 P1 1 1 K1 0.8 0.5 P2 0.6 0.64 K2 0.46 0.32 P3 0.36 0.42 K3 0.29 0.21 P4 0.21 0.28
  • both rotary pistons generally cylindrical, with parallel axes of rotation.
  • the Guidelines the implementation of which Lateral surfaces, core surfaces and intermediate surfaces of the forming disc-shaped sections are cylindrical Guidelines, with the generatrices parallel to the axes of rotation are.
  • the rotary piston also conically shaped the Guidelines, whose diversion the Circumferential surfaces of the discs define the guidelines of a Cones are so that the discs are conical at their periphery are, and their diameters in the direction of the pressure side gradually decrease.
  • the axes of rotation of the two pistons are then not parallel, but have an intersection. at In these embodiments, the diameter variation causes a internal compression. This diameter variation may additionally to the variation of the thickness of the discs or instead of the Variation of the thickness of the discs can be used.
  • FIGS. 17 to 22 represent a seventh Embodiment, Namely a non-contact, parallel-axis, biaxial, internal-axis, constantly rotating Displacement machine dar.
  • the machine has a hollow Outer rotor, an inner rotor and a sickle-shaped G-rotor, which lies between the outer and inner rotor.
  • the rotors have the same sense of rotation as shown in FIG. 17.
  • Outer rotor (A) and the inner rotor (I) have a plurality pairwise interlocking disk-shaped sections, the thickness of which decreases in the direction of the pressure side, each one Disc at least a lateral surface and a core surface which passes through along circular arc with center on the Trained axis of each rotor guided guidelines are and in each case by an intermediate surface (z7), or (z7 ') are connected.
  • Figures 17 to 22 show the disks of the outer and inner rotor two different, along the piston axes periodically - in this embodiment alternating - recurring Face profile contours on.
  • each disc is to the two adjacent disks of the same rotor in angularly offset in such a way that these three slices over a section of their core surfaces and intermediate surfaces one have common guideline and form a chamber.
  • This embodiment realizes an axial Chamber sequence in an internal-axis machine. It will be one Synchronizer 1: 1 used.
  • the Synchronizer can inside the outer rotor to be ordered.
  • a simple lubricant-free Coupling mechanism can be used for this purpose.
  • An eighth embodiment also consists of a non-contact, two-axis, internal-axis, constant rotating displacement machine, with an external rotor, one Inner rotor and a sickle-shaped G-rotor between outer and inner rotor.
  • the rotors have the same direction of rotation. It a translation of 1: 1 is used.
  • the two axes of rotation arranged obliquely, so that the diameter of the rotors vary according to a conical course.
  • the outer rotor and the inner rotor have a plurality in pairs interlocking sections on, in Difference to the previously described seventh Embodiment, not as cylindrical discs with flat End faces, but as curved sections, namely as Ball shell sections, are formed.
  • the synchronizer can as a simple lubricant-free coupling mechanism, eg as Universal joint, inside the positive displacement machine, or Vacuum pump, be realized.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP02711735A 2001-02-23 2002-02-25 Drehkolbenmaschine für verdichtbare medien Expired - Lifetime EP1362188B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH332012001 2001-02-23
CH3322001 2001-02-23
PCT/CH2002/000106 WO2002066836A1 (de) 2001-02-23 2002-02-25 Drehkolbenmaschine für verdichtbare medien

Publications (2)

Publication Number Publication Date
EP1362188A1 EP1362188A1 (de) 2003-11-19
EP1362188B1 true EP1362188B1 (de) 2005-08-24

Family

ID=4502343

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02711735A Expired - Lifetime EP1362188B1 (de) 2001-02-23 2002-02-25 Drehkolbenmaschine für verdichtbare medien

Country Status (17)

Country Link
US (1) US6773243B2 (sh)
EP (1) EP1362188B1 (sh)
JP (1) JP4440543B2 (sh)
KR (1) KR100876029B1 (sh)
CN (1) CN100422560C (sh)
AT (1) ATE302908T1 (sh)
AU (1) AU2002231550B2 (sh)
BR (1) BR0207514B1 (sh)
CA (1) CA2438398C (sh)
CZ (1) CZ304588B6 (sh)
DE (1) DE50204023D1 (sh)
ES (1) ES2248528T3 (sh)
NZ (1) NZ528159A (sh)
PL (1) PL203773B1 (sh)
RS (1) RS50951B (sh)
SK (1) SK287849B6 (sh)
WO (1) WO2002066836A1 (sh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7753040B2 (en) * 2003-10-24 2010-07-13 Michael Victor Helical field accelerator
DE102007038966B4 (de) * 2007-08-17 2024-05-02 Busch Produktions Gmbh Mehrstufige Drehkolbenvakuumpumpe bzw. - verdichter
KR100971145B1 (ko) * 2008-08-09 2010-07-20 안상훈 임플란트 시술용 본캐리어
FR3117176B1 (fr) * 2020-12-04 2023-03-24 Pfeiffer Vacuum Pompe à vide

Family Cites Families (16)

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Publication number Priority date Publication date Assignee Title
DE1503663A1 (de) * 1965-06-14 1969-06-19 Paul Wormser & Co Rotationskolbenmaschine
AT261792B (de) 1965-06-15 1968-05-10 Paul Wormser & Co Rotationskolbenmaschine
US3472445A (en) * 1968-04-08 1969-10-14 Arthur E Brown Rotary positive displacement machines
US3894822A (en) * 1974-04-22 1975-07-15 Alfred Ibragimovich Abaidullin Interengaging rotor displacement machine
CH635403A5 (de) 1978-09-20 1983-03-31 Edouard Klaey Schraubenspindelmaschine.
US4224016A (en) * 1978-09-27 1980-09-23 Brown Arthur E Rotary positive displacement machines
US4324538A (en) * 1978-09-27 1982-04-13 Ingersoll-Rand Company Rotary positive displacement machine with specific lobed rotor profiles
DE2944714A1 (de) * 1979-11-06 1981-05-14 Helmut 1000 Berlin Karl Rotationskolbenmaschine
DE3110055A1 (de) * 1980-03-17 1982-03-18 Worthington Compressors, Inc., 14240 Buffalo, N.Y. Drehkolbenkompressor
US4406601A (en) * 1981-01-02 1983-09-27 Ingersoll-Rand Company Rotary positive displacement machine
DE3323327C1 (de) * 1983-05-25 1984-10-31 Dietrich Dipl.-Ing. 5206 Neunkirchen-Seelscheid Densch Stufenscheibenpumpe
ZA843864B (en) * 1983-05-25 1985-08-28 Dietrich Densch Stepped-disc pump
JPH0367085A (ja) * 1989-08-03 1991-03-22 Shuichi Kitamura 一枚羽根非接触ポンプ
JPH03149378A (ja) * 1989-11-06 1991-06-25 Shuichi Kitamura 非接触回転ポンプ
JPH04350301A (ja) * 1991-05-27 1992-12-04 Shuichi Kitamura 非接触回転機械の回転中心体
DE19537674C1 (de) 1995-10-10 1997-02-20 Adolf Dr Ing Hupe Drehkolbenmaschine

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Publication number Publication date
DE50204023D1 (de) 2005-09-29
SK287849B6 (sk) 2012-01-04
CN100422560C (zh) 2008-10-01
KR20030079989A (ko) 2003-10-10
PL203773B1 (pl) 2009-11-30
NZ528159A (en) 2005-07-29
WO2002066836A1 (de) 2002-08-29
JP4440543B2 (ja) 2010-03-24
BR0207514A (pt) 2004-07-27
RS50951B (sr) 2010-08-31
AU2002231550B2 (en) 2006-03-02
CZ20032207A3 (cs) 2004-11-10
CN1492971A (zh) 2004-04-28
CZ304588B6 (cs) 2014-07-23
JP2004520535A (ja) 2004-07-08
CA2438398A1 (en) 2002-08-29
CA2438398C (en) 2010-07-13
US20040096349A1 (en) 2004-05-20
US6773243B2 (en) 2004-08-10
PL368504A1 (en) 2005-04-04
BR0207514B1 (pt) 2011-04-19
KR100876029B1 (ko) 2008-12-26
EP1362188A1 (de) 2003-11-19
ATE302908T1 (de) 2005-09-15
ES2248528T3 (es) 2006-03-16
SK10482003A3 (sk) 2005-02-04
YU66703A (sh) 2004-09-03

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