EP0167846B1 - Innenachsige Drehkolbenmaschine - Google Patents

Innenachsige Drehkolbenmaschine Download PDF

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Publication number
EP0167846B1
EP0167846B1 EP85107098A EP85107098A EP0167846B1 EP 0167846 B1 EP0167846 B1 EP 0167846B1 EP 85107098 A EP85107098 A EP 85107098A EP 85107098 A EP85107098 A EP 85107098A EP 0167846 B1 EP0167846 B1 EP 0167846B1
Authority
EP
European Patent Office
Prior art keywords
rotor
internal
external
lateral faces
external rotor
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
EP85107098A
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German (de)
English (en)
French (fr)
Other versions
EP0167846A1 (de
Inventor
Felix Dr. H.C. Wankel
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AT85107098T priority Critical patent/ATE51432T1/de
Publication of EP0167846A1 publication Critical patent/EP0167846A1/de
Application granted granted Critical
Publication of EP0167846B1 publication Critical patent/EP0167846B1/de
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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/14—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • 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 internal-axis rotary lobe machine with the features of the preamble of patent claim 1.
  • a machine of the type mentioned is known from US-A-1 753 476.
  • the inner rotor of this machine has semicircular circumferential surfaces, the radius of curvature of which, due to kinematics, is considerably smaller than that of the circular surface which encloses the outer rotor.
  • the inner rotor can only incompletely displace the medium from the recesses of the outer rotor.
  • An arc-shaped adaptation of the radially outer region of the recesses of the outer rotor to the circular peripheral surfaces of the inner rotor, in order to reduce the harmful spaces, in a form similar to that of a machine according to DE-A-2 46 252, would make the opening cross sections of the recesses even narrower to let.
  • the then crescent-shaped delimitation areas of the recesses would be subjected to bending deformations by centrifugal forces, and crushing currents would occur there to an increased extent.
  • the invention has for its object to find an improved machine of the type mentioned, which has a higher throughput due to the shape of their runners, based on their construction volume and very small harmful spaces and thereby enables high speeds of rotation of their runners.
  • the invention results in a cross-sectional shape of the rotor which enables high rotational speeds, although the inner rotor can move to the outer circumference of the outer rotor or even beyond in order to achieve very small, harmful spaces.
  • the machine according to the invention has surprisingly large working spaces in relation to the overall dimensions of the machine.
  • the side surfaces of the outer rotor that delimit the inner working spaces are preferably designed to be flat, wherein opposite inner side surfaces can advantageously run parallel to one another, so that large cross sections of the working spaces and large control openings on the outer rotor result.
  • outer corner regions of the inner rotor and the inner corner regions of the outer rotor are advantageously rounded off with a constant or variable cross-sectional curvature.
  • the inner corner areas of the outer rotor are guided radially inwards so that they come close to its shaft.
  • At least one adjustable wall piece which is provided on the inside of the housing and along which the circumference of the outer rotor moves, enables the delivery rate and / or the delivery pressure to be controlled by changing the time of inflow and thus the Size of the filling and / or the time of the outflow and thus the pressure level of the overflow in the pressure line changed.
  • a machine according to the invention can also be an internal combustion engine.
  • the cross-sectional view shows three main parts of the machine, i. H. an inner rotor 1, an outer rotor 2, with three rigidly connected rotor parts 2a, 2b and 2c and the housing 3 enclosing both of them.
  • the cross-sectional illustration in the illustration according to FIG. 1 visible boundary surfaces of these parts parallel to the axes of rotation of the rotor, while their invisible end boundary surfaces are perpendicular to these axes.
  • the wall of the housing 3 merges into an inflow and outflow channel 4, 5, it depending on the use of the machine whether the inflow channel 4 is an intake channel or an inflow channel for a propellant.
  • Both runners 1, 2 rotate about fixed axes 6, 7, which are spaced apart.
  • the speed ratio is 3: 2, corresponding to the ratio between the number of recesses 8, 9, 10 of the outer rotor forming working spaces to the number of engaging parts 11, 12 of the inner rotor extending from the axis 6.
  • this ratio is 4: 3, corresponding to four recesses 14, 15, 16, 17 and three parts 18, 19, 20 of the inner rotor that move into and out of the recesses.
  • the sequence of movements of the two runners 1, 2 relative to one another and relative to the machine housing 3 can be seen in the illustrations in FIG. 3.
  • the uninterrupted sealing between the inner and outer rotor results from the fact that both runners mutually create their shape when they move relative to each other.
  • the four outer corner regions 22-25 of the inner rotor according to FIG. 1 and the three inner corner regions 26, 27, 28 of the outer rotor are used for generating curves.
  • the corner regions of the inner rotor move or produce along the inner side surfaces 30, 31 of the outer rotor, and the inner corner regions 26, 27, 28 of the outer rotor move along or on the outer peripheral surfaces 32, 33 of the inner rotor generate these. This is illustrated by the movement positions shown in FIG.
  • the seal between the inner side surfaces 30, 31 of the outer rotor and the side surfaces 34, 35 of the inner rotor results from a tooth flank-like contact between the two.
  • the corner regions 22-28 of both runners are preferably rounded instead of sharp-edged, so that the rounding on the other rotor creates an equidistant to the center of curvature of the rounding.
  • the inner corner region 28 of the outer rotor 2 is relatively close to the axis of the inner rotor, as a comparison with the prior art according to the aforementioned DE-A-2 456 252 shows.
  • the throughput volume is, for example, 1 dm 3 .
  • the inner side surfaces 30, 31 of the outer rotor run parallel to one another, so that the opening of the recesses 8, 9, 10 of the outer rotor, which moves past the housing openings at a very high speed, is correspondingly advantageously large.
  • this opening cross section of the recesses of the outer rotor is advantageously large.
  • the exemplary embodiment according to FIG. 7 shows inner side surfaces of the outer rotor which run slightly towards one another radially outward.
  • the outer circumferential surfaces 32, 33 of the inner rotor move up to the outer circumference of the outer rotor, so that the harmful space results due to the different curvature of the circumferential surface of the inner rotor and the circumferential surface of the outer rotor. Since the outer circumferential surfaces 32, 33 of the inner rotor can also take over the sealing alone when passing through the sealing region 42 between the two channels 4, 5 of the housing, it is possible that these circumferential surfaces 32, 33 also move beyond the circumference of the outer rotor.
  • the seal between the outer rotor 2 and the housing inner wall on the side of the housing diametrically opposite the sealing area 42 between the channels 4, 5 is provided by means of a wall piece 43 which is adjustable in the circumferential direction, so that the internal compression of the machine can be changed from zero.
  • 1 shows a position of the wall piece 43 through which there is no internal compression, while in the position according to FIG. 2 the internal compression takes place up to the rotational position shown, until the working space 8 opens by the trailing edge 44 of the outer rotor away from the wall piece 43.
  • an actuating member not shown, which extends outwards through a slot in the housing wall.
  • Fig. 4 shows another embodiment for the design of means for the changes throughput and / or internal compression of the machine.
  • These means consist of a plurality of circular arc-shaped radial slides 46, 47 arranged next to one another in the circumferential direction on the inflow and outflow side of the machine when the rotor rotates in the direction of the arrow 48 an inflow takes place in the working space 8 'enclosed by both runners in the direction of arrow 49.
  • 4 shows two inflow-side radial slides 46 in a radially outer position, while the radial slides adjoining in the direction of rotation have their radially innermost position, so that maximum internal compression is achieved when the machine is operated as a compressor.
  • the strength of the internal compression can be gradually changed in this exemplary embodiment according to FIG. 4, corresponding to the number of radial slides 47 which are retracted radially outward from the position shown.
  • this means 43, 46, 47 for changing the delivery rate and / or the internal compression can be used on any machine in which there is an outer rotor rotating about a fixed axis, the recesses of which form radially outwardly open working spaces move past housing openings.
  • FIG. 6 shows how a machine according to the invention according to FIG. 7 can look in the axial cross section.
  • the parts of the machine according to FIGS. 6 and 7 already described with reference to FIG. 1 have the same reference numbers.
  • the parts 2a, 2b, 2c of the outer rotor are rigidly connected to one another at the two axial ends of the rotor by side plates 50, 51.
  • a hub 52 or 53 projects axially outward from these side plates, via which the outer rotor is mounted on the housing side plates 56, 57 by means of a ball bearing 54 or 55 of large diameter.
  • these bearings have extraordinarily high running speeds of the rolling elements, which can lead to premature wear, so that the above-mentioned embodiment according to their EP-A-0087747 by the same applicant is recommended.
  • the hub 53 of the outer rotor has an internal toothing 58 which meshes with a gearwheel 60 fastened on the shaft journal 59 of the inner rotor 1.
  • This existing drive connection is recommended for an exact run of the two runners to each other, so that there is always an optimal gap seal between the two runners, although the tooth-flank-like contact between the side surfaces of both runners could make the additional gear connection 58, 60 superfluous.
  • the side plates 50, 51 of the outer rotor enclose circular lateral sealing plates 62, 63 which are screwed onto the housing sides 56, 57 and which adjoin the end surfaces 64, 65 of the inner rotor with a sealing gap distance.
  • These sealing plates also enclose the two shaft journals 59, 66 of the inner rotor.
  • the outer bearing 44 of the outer rotor also encloses the roller bearing 67, 68 which supports the shaft journals 59, 66.
  • the on the shaft journal 59 of the inner rotor laterally protruding via the housing plate 57 gear 69 serves either to drive the machine when it is used as a blower or compressor or as an output gear when the machine as a motor or driver through an inflowing medium, such as . B. the exhaust gas of an internal combustion engine is driven.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • X-Ray Techniques (AREA)
  • Steroid Compounds (AREA)
  • Toys (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Confectionery (AREA)
  • Formation And Processing Of Food Products (AREA)
EP85107098A 1984-06-12 1985-06-08 Innenachsige Drehkolbenmaschine Expired - Lifetime EP0167846B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85107098T ATE51432T1 (de) 1984-06-12 1985-06-08 Innenachsige drehkolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2822/84 1984-06-12
CH2822/84A CH664423A5 (de) 1984-06-12 1984-06-12 Innenachsige drehkolbenmaschine.

Publications (2)

Publication Number Publication Date
EP0167846A1 EP0167846A1 (de) 1986-01-15
EP0167846B1 true EP0167846B1 (de) 1990-03-28

Family

ID=4242370

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85107098A Expired - Lifetime EP0167846B1 (de) 1984-06-12 1985-06-08 Innenachsige Drehkolbenmaschine

Country Status (6)

Country Link
US (2) US4714417A (sv)
EP (1) EP0167846B1 (sv)
JP (1) JPH0612045B2 (sv)
AT (1) ATE51432T1 (sv)
CH (1) CH664423A5 (sv)
DE (2) DE3432915C2 (sv)

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.
CH667492A5 (de) * 1985-08-31 1988-10-14 Wankel Felix Innenachsige drehkolbenmaschine.
CH669975A5 (sv) * 1986-06-13 1989-04-28 Wankel Felix
DE3631574C1 (en) * 1986-09-17 1988-02-25 Pierburg Gmbh Device for controlling a rotary engine
FR2603944A1 (fr) * 1986-09-17 1988-03-18 Pierburg Gmbh Dispositif pour commander un moteur a piston rotatif
DE3702558A1 (de) * 1987-01-29 1988-09-01 Pierburg Gmbh Innenachsige drehkolbenmaschine
DE3706588C2 (de) * 1987-02-26 1993-12-02 Mannesmann Ag Antriebseinrichtung für Rotationskolbenverdichter
JPS63243482A (ja) * 1987-03-31 1988-10-11 Aisin Seiki Co Ltd 回転ロ−タ装置
DE3716083A1 (de) * 1987-05-14 1988-11-24 Kuehnle Kopp Kausch Ag Innenachsige drehkolbenmaschine
DE3717346A1 (de) * 1987-05-22 1988-10-13 Daimler Benz Ag Innenachsige drehkolbenmaschine
JPS6483801A (en) * 1987-09-25 1989-03-29 Aisin Seiki Rotor device
US4948352A (en) * 1987-09-25 1990-08-14 Aisin Seiki Kabushiki Kaisha Rotor unit with peripheral projections and clearances for centrifugal deflection
JPH0192595A (ja) * 1987-09-30 1989-04-11 Aisin Seiki Co Ltd 回転ロータ装置
DE3812637C1 (sv) * 1988-04-15 1989-07-27 Felix Dr.H.C. 8990 Lindau De Wankel
DE3817318C2 (de) * 1988-05-20 1997-05-28 Mueller Alander Gerd Dipl Ing Hubkolben-Brennkraftmaschine mit wenigstens einem Drehkolben-Lader der Verdrängerbauart
DE3825481A1 (de) * 1988-07-27 1990-02-01 Pierburg Gmbh Rotationskolbenmaschine
US5046932A (en) * 1989-11-17 1991-09-10 Compression Technologies, Inc. Rotary epitrochoidal compressor
CH682939A5 (de) * 1990-03-09 1993-12-15 Voith Gmbh J M Innenzahnradpumpe.
CH682587A5 (de) * 1990-12-28 1993-10-15 Gerhard Renz Fried Meysen Thom Rotationskolbenmaschine.
CH689427A5 (de) * 1991-07-09 1999-04-15 Daimler Benz Ag Abdichtung an einem rotierenden Koerper.
EP0563661A1 (de) * 1992-03-19 1993-10-06 J.M. Voith GmbH Sichellose Innenzahnradpumpe mit radial beweglichen Dichtelementen zur Radialkompensation
CH685447A5 (de) * 1992-04-01 1995-07-14 Lindau Tech Forsch & Entw Gmbh Innenachsige Drehkolbenmaschine.
US7186101B2 (en) 1998-07-31 2007-03-06 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle Engine
US6427453B1 (en) * 1998-07-31 2002-08-06 The Texas A&M University System Vapor-compression evaporative air conditioning systems and components
US7726959B2 (en) * 1998-07-31 2010-06-01 The Texas A&M University Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US6273695B1 (en) 1999-03-26 2001-08-14 Voith Turbo Gmbh & Co. Kg Sickleless internal gear wheel pump with sealing elements inserted into the tooth tips
EP1240432A1 (en) * 1999-09-20 2002-09-18 Sealed Air Corporation (US) Internally generated rotor set for low viscosity and abrasive metering applications
US6465645B1 (en) * 2001-04-17 2002-10-15 Ciba Specialty Chemicals Corporation Long chain hindered amines and compositions stabilized therewith
EP1472434A2 (en) * 2002-02-05 2004-11-03 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
JP4366197B2 (ja) * 2004-01-21 2009-11-18 Ｈｏｙａ株式会社 ステージ装置及びこのステージ装置を利用したカメラの手振れ補正装置
CA2554277A1 (en) * 2004-01-23 2005-08-11 Starrotor Corporation Gerotor apparatus for a quasi-isothermal brayton cycle engine
KR20070072916A (ko) * 2004-10-22 2007-07-06 더 텍사스 에이 & 엠 유니버시티 시스템 준등온 브레이튼 사이클 엔진을 위한 지로터 장치
US7281513B1 (en) 2006-02-24 2007-10-16 Webb David W Inverted Wankel
WO2022175904A1 (en) 2021-02-19 2022-08-25 1158992 B.C. Ltd. Fluid transfer device

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Publication number Priority date Publication date Assignee Title
US1753476A (en) * 1927-06-29 1930-04-08 Joseph R Richer Rotary pump or blower
DE2456252A1 (de) * 1974-11-28 1976-06-10 Kernforschungsanlage Juelich Kolbenmaschine zum komprimieren oder zum expandieren von gasen

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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
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SU652335A1 (ru) * 1977-06-09 1979-03-15 Всесоюзный Научно-Исследовательский И Проектный Институт По Переработке Газа Роторна машина
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JPS5660801A (en) * 1979-10-20 1981-05-26 Kawasaki Heavy Ind Ltd Rotary fluid machine
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1753476A (en) * 1927-06-29 1930-04-08 Joseph R Richer Rotary pump or blower
DE2456252A1 (de) * 1974-11-28 1976-06-10 Kernforschungsanlage Juelich Kolbenmaschine zum komprimieren oder zum expandieren von gasen

Also Published As

Publication number Publication date
DE3432915C2 (de) 1987-01-02
JPS614802A (ja) 1986-01-10
DE3576839D1 (de) 1990-05-03
EP0167846A1 (de) 1986-01-15
DE3432915A1 (de) 1985-12-12
CH664423A5 (de) 1988-02-29
US4801255A (en) 1989-01-31
ATE51432T1 (de) 1990-04-15
JPH0612045B2 (ja) 1994-02-16
US4714417A (en) 1987-12-22

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