EP0337950B1 - Moteur à piston rotatif à axe interne - Google Patents

Moteur à piston rotatif à axe interne Download PDF

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Publication number
EP0337950B1
EP0337950B1 EP89810265A EP89810265A EP0337950B1 EP 0337950 B1 EP0337950 B1 EP 0337950B1 EP 89810265 A EP89810265 A EP 89810265A EP 89810265 A EP89810265 A EP 89810265A EP 0337950 B1 EP0337950 B1 EP 0337950B1
Authority
EP
European Patent Office
Prior art keywords
rotor disk
partition body
rotary piston
rotors
shaft
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
EP89810265A
Other languages
German (de)
English (en)
Other versions
EP0337950A2 (fr
EP0337950A3 (en
Inventor
Felix Dr.H.C. Wankel
Frank Obrist
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.)
Meysen Fried
Renz Gerhard
Original Assignee
Meysen Fried
Renz Gerhard
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 Meysen Fried, Renz Gerhard filed Critical Meysen Fried
Priority to AT89810265T priority Critical patent/ATE78080T1/de
Publication of EP0337950A2 publication Critical patent/EP0337950A2/fr
Publication of EP0337950A3 publication Critical patent/EP0337950A3/de
Application granted granted Critical
Publication of EP0337950B1 publication Critical patent/EP0337950B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/103—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to an inner-axis rotary lobe machine with at least two inner rotors fastened to a common shaft and a corresponding number of outer rotors, which are enclosed by a common housing and are arranged axially next to one another, the engagement parts of the outer rotors in the circumferential direction with one another and in the axial direction with those of the adjacent one Outer rotor are rigidly connected by an annular, axially inner rotor disk, so that it surrounds the shaft of the inner rotor and axially divides the working spaces of the machine.
  • Machines of this type are known, for example, from FIGS. 22 and 27 of US Pat. No. 3,954,355. These machines are designed in such a way that their inner runners always laterally cover the space enclosed by the axially inner rotor disk, so that the axially adjacent working spaces are sealed off from one another. According to FIG. 27 of this US Pat. No. 3,954,355, the gear drive connection between an inner rotor pair and an outer rotor pair is arranged in this space enclosed by the rotor disk.
  • the invention has for its object to find a machine of the type mentioned that the stiffening connection between a plurality of external runners, or. the axial subdivision of an outer rotor is also made possible for machines whose working spaces extend radially inward beyond the possible radially inner boundary of an outer rotor disk, so that the machine has an increased throughput volume.
  • the aforementioned radially inner boundary of an outer rotor disk is structurally due to the necessary radially offset arrangement of the shaft of the inner rotor relative to the axis of rotation of the outer rotor.
  • this object is achieved in that the space enclosed by the axially inner rotor disk is filled by a partition wall body, a bearing being provided between the rotor disk and the partition wall body and between the shaft and the shaft, and working spaces of the machine up to the partition wall body reach up.
  • the partition body is not connected to a stationary part, and although it is only connected to rotating parts, i.e. In the radial direction, on the one hand, it borders on the rotor disk enclosing it and, on the other hand, on the shaft enclosed by it, it stands still. This results from the radial displacement of the axes of the two bearings mentioned.
  • the inner rotors 2, 3 and the outer rotors 4, 5 of the rotary piston machine shown rotate about axes 7, 8 which are fixed relative to the common machine housing 6, so that very high rotational speeds are possible.
  • the three engagement parts 4a, 4b, 4c of the outer rotor 4 could easily be produced from rod material with a relatively large axial length due to their constant cross-section in the axial direction. Due to bending loads due to centrifugal forces, the free axial length of the engagement parts 4a, 4b, 4c is limited by an axially inner rotor disk 9, which rigidly connects these engagement parts 4a, 4b, 4c to one another in the circumferential direction.
  • the rigid connection is provided, for example, by a one-piece production of the engagement parts 4a, 4b, 4c with the rotor disk 9.
  • the axially adjacent outer and inner rotors 2 to 5 are preferably offset from one another in the circumferential direction by 180 °. The load peaks resulting from the compression in the machine consequently occur on both axially adjacent rotors 2, 3 and 4.5 not at the same time.
  • the size of the inner diameter of the axially inner rotor disk 9 is in the range due to the eccentricity of the shaft axis 7 of the inner rotor 2, 3 relative to the axis of rotation 8 of the outer rotor 4, 5 and the outer diameter of the shaft 12 of the inner rotor 2, 3 of the rotor disk 9, whereby the required arrangement of a bearing 13 on the inner diameter 14 must also be taken into account, which keeps the frictional resistance between a partition wall body 15 enclosed by the rotor disk 9 and stationary relative to the machine housing 6 low.
  • This bearing 13 is therefore preferably designed as a roller bearing. In the illustrated embodiment, this bearing 13 is enclosed in circumferential grooves of the rotor disk 9 and the partition wall body 15, so that it is sealed against the working spaces 16 of the machine.
  • bearing 13 or. the roller bearing can also be provided in only one circumferential groove of the rotor disk 9 or the partition wall body 15.
  • the axial sealing of the annular gap between the rotor disk 9 and the partition wall body can be carried out by its narrow dimensions or by sealing rings 17, 18 engaging in a groove.
  • the working spaces 16 of a rotary piston machine extend radially inward substantially beyond the inner diameter 14 of the axially inner rotor disk 9 and become therein Extent area 19 limited in the axial direction by the partition wall body 15, which extends in the same plane as the rotor disk 9 and thus forms the radially inner continuation of the side surfaces 9a, 9b delimiting the working spaces 16.
  • the combination of the axially inner rotor disk 9 with the thus also axially inner partition wall body 15 results in an axial one Subdivision of the working spaces 16 of the machine, so that an axially separated area of the machine can be arranged as a high-pressure stage behind a first low-pressure stage.
  • FIG. 3 shows the flow channels 20, 21 between a low-pressure part 22 and a high-pressure part 23 of a rotary piston machine according to the invention, which are guided via an intercooler 24 around the gas heated by the compression in the low-pressure part 22 before it is further compressed in the high-pressure part 23 cool down.
  • the coolant circulates through the pipes 25, 26.
  • the outer rotor unit formed from the two outer rotors 4, 5 carries annular end bodies 30, 31 which are connected to the engaging parts 4a, 4b, 4c; 5a, 5b, 5c are screwed on, as indicated by lines 32, 33.
  • the outer rotor unit 4.5 is supported by means of roller bearings 34, 35, which are supported on filler bodies 38, 39 that are firmly connected to housing side plates 36, 37.
  • the gear-gear connection 10, 11 between the outer and inner rotor units 4, 5; 2, 3 in the speed ratio of 2: 3 is arranged between an outer and inner filler body 38, 40, which are screwed together.
  • the shaft 12 of the inner rotor unit 2, 3 is mounted in roller bearings 41, 42, which are held in the filler bodies 38, 39.
  • the bearing 43 between the axially inner partition wall body 15 and the shaft 12 is less stressed, since the bearing forces occurring there merely cause the partition wall body to also rotate 15 to prevent with the axially inner rotor disc 9.
  • This bearing can accordingly be formed by a thin bearing shell 43.
  • the machine's inlet and outlet ports 44, 45 are located on the circumference of the housing 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Toys (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Reciprocating Pumps (AREA)

Claims (5)

1. Machine à piston rotatif à axe intérieur avec au moins deux rotors intérieurs (2, 3) fixés sur un arbre commun (12) et avec un nombre correspondant de rotors extérieurs (4, 5) qui sont contenus dans un carter commun (6) et qui sont disposés côte à côte axialement, les éléments d'engagement (4a, 4b, 4c) des rotors extérieurs (4, 5) étant, en direction périphérique, reliés rigidement les uns aux autres et étant, en direction axiale , reliés rigidement aux éléments d'engagement du rotor extérieur voisin (4, 5) au moyen d'une disque de rotor (9) axial intérieur en forme de segment de cercle, de telle sorte que ce disque de rotor (9) enveloppe l'arbre (12) des rotors intérieurs (2, 3) et subdivise axialement les enceintes de travail de la machine, caractérisée en ce l'enceinte enveloppée par le disque de rotor (9) intérieur axial est occupée par un corps de paroi de séparation (15), tandis qu'entre le disque de rotor (9) et le corps de séparation (15) ainsi qu'entre ce corps et l'arbre (12) il est prévu des paliers (13, 43) et que les enceintes de travail (16) de la machine se prolongent jusqu'au corps de séparation (15).
2. Machine à piston rotatif suivant la revendication 1, caractérisée en ce que le disque de rotor axialement intérieur (9) avec le corps de séparation (15) subdivise la machine en une partie basse pression (22) axialement plus longue et une partie haute pression (23) axialement plus courte, qui sont reliées l'une à l'autre par l'intermédiaire d'un conduit de transfert (21) disposé à l'extérieur du carter d'enveloppe (6).
3. Machine à piston rotatif suivant la revendication 1, caractérisée en ce qu'entre le disque de rotor (9) et le corps de séparation est prévu un palier à roulement (13) et en ce qu'entre l'arbre (12) et le corps de séparation (15) est prévu un palier à glissement (43).
4. Machine à piston rotatif suivant la revendication 1, caractérisée en ce que les rotors extérieurs et intérieurs axialement voisins (4, 5; 2, 3) sont, en direction périphérique, fixés de manière décalée les uns par rapport aux autres.
5. Machine à piston rotatif suivant la revendication 4, caractérisée en ce que le décalage est de 180° .
EP89810265A 1988-04-15 1989-04-06 Moteur à piston rotatif à axe interne Expired - Lifetime EP0337950B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89810265T ATE78080T1 (de) 1988-04-15 1989-04-06 Innenachsige rotationskolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3812637 1988-04-15
DE3812637A DE3812637C1 (fr) 1988-04-15 1988-04-15

Publications (3)

Publication Number Publication Date
EP0337950A2 EP0337950A2 (fr) 1989-10-18
EP0337950A3 EP0337950A3 (en) 1990-02-28
EP0337950B1 true EP0337950B1 (fr) 1992-07-08

Family

ID=6352095

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89810265A Expired - Lifetime EP0337950B1 (fr) 1988-04-15 1989-04-06 Moteur à piston rotatif à axe interne

Country Status (5)

Country Link
US (1) US4960370A (fr)
EP (1) EP0337950B1 (fr)
JP (1) JPH01313601A (fr)
AT (1) ATE78080T1 (fr)
DE (2) DE3812637C1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7726959B2 (en) 1998-07-31 2010-06-01 The Texas A&M University Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US7186101B2 (en) 1998-07-31 2007-03-06 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle Engine
US6386836B1 (en) 2000-01-20 2002-05-14 Eagle-Picher Industries, Inc. Dual gerotor pump for use with automatic transmission
DE10023010C2 (de) * 2000-05-11 2003-03-06 Peter Ingelheim Innenachsige Mehrfachdrehkolbenmaschine
US7008200B2 (en) * 2002-02-05 2006-03-07 The Texas A&M University System Gerotor apparatus for a quasi-isothermal brayton cycle engine
US7663283B2 (en) 2003-02-05 2010-02-16 The Texas A & M University System Electric machine having a high-torque switched reluctance motor
JP2007524031A (ja) 2004-01-23 2007-08-23 スターローター コーポレーション 準等温ブレイトン・サイクル・エンジン用のジェロータ装置
US7695260B2 (en) 2004-10-22 2010-04-13 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle engine
CZ302294B6 (cs) * 2008-07-29 2011-02-09 Dvorák@Jirí Rotacní motor na stlacitelná média
US9074524B2 (en) * 2011-12-09 2015-07-07 Eaton Corporation Air supply system with two-stage roots blower
EP2762675A1 (fr) 2013-02-03 2014-08-06 Cornel Ciupan Moteur rotatif a combustion interne

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB394985A (en) * 1932-01-05 1933-07-05 Hugo Grasse Improvements in rotary pumps, blowers and motors, and in machines for use in producing the rotors thereof
US2490115A (en) * 1942-10-28 1949-12-06 Bendix Aviat Corp Variable displacement rotary pump
US2531808A (en) * 1946-03-27 1950-11-28 Eaton Mfg Co Pump
US3244111A (en) * 1965-09-14 1966-04-05 Dura Corp Dual pump
CH470579A (fr) * 1967-12-07 1969-03-31 Linder Rene Machine volumétrique rotative
US3551081A (en) * 1969-01-10 1970-12-29 Emerson Electric Co Hydraulic pump or motor
GB1284551A (en) * 1969-08-08 1972-08-09 Arthur E Brown Improvements in rotary positive-displacement fluid machines
US3954355A (en) * 1973-08-27 1976-05-04 Paul Jr Herman L Rotary energy converter
DE2402621A1 (de) * 1974-01-21 1975-07-24 Ulrich Dipl Ing Rohs Antriebsvorrichtung mit mindestens einer rotationskolbenmaschine mit kaemmeingriff
DE2918369A1 (de) * 1979-05-07 1980-11-13 Geothermal Energy Research And Rotations-expansionsmaschine
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.

Also Published As

Publication number Publication date
US4960370A (en) 1990-10-02
EP0337950A2 (fr) 1989-10-18
ATE78080T1 (de) 1992-07-15
EP0337950A3 (en) 1990-02-28
JPH01313601A (ja) 1989-12-19
DE58901795D1 (de) 1992-08-13
DE3812637C1 (fr) 1989-07-27

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