EP0087746A1 - Abgasbetriebener Rotationskolbenlader - Google Patents

Abgasbetriebener Rotationskolbenlader Download PDF

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Publication number
EP0087746A1
EP0087746A1 EP83101745A EP83101745A EP0087746A1 EP 0087746 A1 EP0087746 A1 EP 0087746A1 EP 83101745 A EP83101745 A EP 83101745A EP 83101745 A EP83101745 A EP 83101745A EP 0087746 A1 EP0087746 A1 EP 0087746A1
Authority
EP
European Patent Office
Prior art keywords
rotary piston
rotor
loader according
outer rotor
rotary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP83101745A
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German (de)
English (en)
French (fr)
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
Publication of EP0087746A1 publication Critical patent/EP0087746A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines
    • 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
    • F01C1/104—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 one member having simultaneously a rotational movement about its own axis and an orbital movement
    • 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
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C18/10—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 internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member

Definitions

  • the invention relates to an exhaust gas-operated rotary piston loader for the mechanically independent arrangement on the exhaust pipe of an internal combustion engine with two rotary piston machines in drive connection with one another, one of which forms the loading unit and the other the exhaust unit of the rotary piston loader.
  • an exhaust gas-operated rotary piston charger of this type is known, the charging unit and exhaust unit of which are each formed by an external-axis rotary piston machine with a stationary working chamber wall.
  • this known rotary piston supercharger has the advantage over mechanically driven superchargers that the internal combustion engine is charged as a function of the exhaust gas flow, i.e. in line with the actual air requirement.
  • mechanically driven superchargers compressors
  • an adjustable gearbox is required to adapt to the actual air requirement, since the air requirement is not directly dependent on the speed of the internal combustion engine.
  • a mechanically operated supercharger removes useful power from the internal combustion engine.
  • the utilization of the energy of the exhaust gas flow can contribute to reducing the noise, so that the technical outlay for the "exhaust" system of the internal combustion engine is reduced.
  • turbochargers The disadvantage of turbochargers is also well known. It is caused by the non-proportional power curve, which is characteristic of turbines, so that charging in the lower speed ranges and load conditions of the internal combustion engine is inadequate and is only optimal when the engine is at full power. In order to reduce this misunderstanding, it has started to reduce the diameter of the exhaust gas turbine in such a way that it already has the high speed required for the supercharging when the engine is a quarter or a half power.
  • the above-mentioned DE-PS 2 232 592 was based on the task of creating an exhaust gas-operated charging device which ensures optimal charging both in the lower speed ranges and load conditions and in the upper ones.
  • Optimal supercharging in the upper speed ranges could not be achieved with the previously known exhaust-powered rotary piston loaders because of their excessive internal power requirement due to squeezing flow losses. These squeezing flows arise when the piston of one rotor engages in the gap of the counter rotor.
  • the already known rotary piston superchargers were consequently not superior to the turbocharger in the upper speed range and less importance was attached to the performance improvement in the lower three-speed range, the experts have so far paid no attention to them.
  • the previous exhaust-gas-operated rotary piston loader has the further disadvantage that its manufacture is relatively complex owing to the shape of its rotor and the required precise mutual geometrical assignment, particularly taking thermal loads into account.
  • the object of the present invention is to find an exhaust gas-operated rotary piston loader suitable for high speeds, which reduces energy losses and noise caused by squeezing currents to an insignificant extent, has no or only negligible harmful spaces and thus enables optimal charging in all speed ranges of an internal combustion engine.
  • it should cope with the high thermal and mechanical loads with the least possible design effort, so that it can be inexpensively manufactured as a permanent mass product.
  • an exhaust gas-operated rotary piston charger of the type mentioned at the outset is proposed, which is characterized according to the invention in that at least one of the rotary piston machines is an internal-axis rotary or rotary piston machine.
  • internal-axis rotary piston machines are not designed as rotary piston machines, but as rotary piston machines, i.e. with a rotor mounted on the rotating or eccentric journal of a crankshaft, special control devices must be provided on the outer housing if large control cross sections are to be achieved.
  • the internal-axis machines are designed as rotary piston machines, i.e. the rotors rotate around fixed axes of rotation, so that the external rotor can itself control large inlet and outlet channels of the fixed housing.
  • the rotary lobe machines are more suitable than rotary lobe machines due to their balancing ability and the lack of centrifugal bearings.
  • an exhaust gas-operated rotary piston loader thus works, in contrast to turbomachines, according to the displacement principle and, in contrast to the prior art according to DE-PS 2 232 592, the displacement movement does not lead to any significant squeezing currents and, moreover, harmful spaces are avoided, the engine results in every speed range optimal charging.
  • Charging is optimal because the amount of air supplied by the charger of the supercharger to the engine is directly related to the amount of exhaust gas flow that drives the exhaust unit of the charger, i.e. the exhaust gas flow directly controls the charger in an optimal way.
  • FIG. 1 and 2 show, in two sectional views, the charging unit 2 of the exhaust gas-operated charger shown overall in FIG. 3.
  • the exhaust gas unit 3 is of essentially the same design as the loading unit, and its inner runners 4 are rigidly connected via a common rectilinear main shaft 6 of the charger.
  • the inner rotors 4, 4 'of the two machine units, which are eccentrically mounted on the shaft 6, are angularly offset from one another, e.g. are arranged at 90 °, so that the starting of the loader is facilitated or even with a dead center position of one of the units is possible without an external drive.
  • the start-up takes place due to a vacuum in the pressure line 7 of the charging unit caused by the internal combustion engine and an excess pressure in the inflow line of the exhaust gas unit of the charger, not shown.
  • the inner rotor 4 has a circular cross section and rotates in an eccentric movement about the shaft 6, which only rotates about its own axis.
  • the shaft 6 is rigid with the side housing covers 11, 12 by two needle or roller bearings 9, 10 connected sealing and bearing bodies 13, 14 mounted.
  • the sealing and bearing bodies 13, 14 also allow a much larger diameter of the shaft 6 of the inner rotor, which is of particular advantage for a large axial length of the rotary piston unit and in the case of a hollow version of the shaft. In addition, they allow a greater distance between the bearing axes of both rotors, which leads to a greater throughput of the rotary piston machine.
  • the outer runner 18 enclosing the inner runner 4 consists of two crescent-shaped peripheral parts 24, 25 lying opposite one another and two side parts 26, 27 closing them between them.
  • the connection to one another is made by pins 28 and screw bolts 29.
  • the inner surfaces 30, 32 of the outer runner directed towards one another run planar and at least parallel to each other in the direction parallel to the axis of rotation, so that the inner rotor can execute a reciprocating movement in the working space 22 delimited by these surfaces 30, 32.
  • This relatively linear movement of the inner rotor 4 relative to the outer rotor 18 despite the rotational movement of both rotors results from the kinematics of gimbals.
  • the inner rotor 4 which can also be referred to as a rotary piston, comes into meshing engagement with two gaps in the outer rotor so that it rotates at twice the speed of the outer rotor.
  • the transmission ratio corresponds to 1: 2, so that the pitch circle of the pinion 34 of the drive transmission 23 between the inner and outer rotor is half the diameter of the pitch circle of the hollow gear 35 points.
  • 5 to 7 show, however, that the transmission ratio of 1: 2 can also be achieved in other ways, as will be explained in more detail below.
  • FIG. 4 shows the relative positions that result one after the other during the rotation of both rotors, from which the mode of operation of the charging and exhaust gas unit 2, 3 of the charger becomes clear. Due to the back and forth movement of the inner rotor 4 in the working space 22 enclosed by the outer rotor, air is sucked in via the intake duct 8 in the direction of the arrow shown in FIG. 4a in the loading unit and expelled via the pressure line 7 in the direction of the arrow shown. 4a shows a rotational position in which the center of the inner rotor coincides with the center of the outer rotor and thus also the center of the surrounding housing wall. The rotors rotate in the direction of the arrows shown in FIG.
  • a pinion 34 is attached to the end of the shaft 6 of the loader, which pinion is intended to drive the external rotor 18 at half the rotational speed.
  • the axis of the shaft 6 from the axis of the outer rotor and with the same transmission ratio a larger diameter of the shaft 6 and a correspondingly larger diameter of the pinion 34 can be realized, so that the shaft for cooling the inner rotor 4 as shown in Fig. 11th can be made hollow and / or for a greater axial length of the rotor a higher strength, in an advantageous embodiment of the invention according to the schematic representations of FIGS.
  • FIGS. 8 and 9 show an advantageous embodiment of the mounting of the outer rotor 18 on a sealing and bearing body 50 in order to reduce the speeds of the bearings.
  • three rollers 52, 53, 54 are used, two of which are supported by a journal 56 in the sealing and bearing body 50, while the third is supported on the shaft 6.
  • These rollers 52-54 which are made of hardened material, roll on a bearing ring 58 made of hardened steel, which is inserted into a lateral hub part 60 of the outer rotor.
  • a lateral end face of the hollow gear 62 secures the axial position of this bearing ring 58.
  • a sealing ring 66 is arranged between the outer circumference of the hub part 60 and the lateral housing part 65, which ensures the sealing of the part of the loading unit provided with lubricant.
  • 10 and 11 show advantageous design options, in particular for the exhaust gas unit 3 of the charger which is exposed to high temperature loads.
  • 10 in the crescent-shaped circumferential parts 24, 25 of the outer rotor 18 ', longitudinal air channels 70 are provided, the number, cross-sectional size and cross-sectional shape of which are not visible in the illustration according to FIG. 10, taking into account the data from the illustration in FIG 1 obvious possibilities for the arrangement and the strength requirements can be designed differently.
  • a circular cross section is of course easier to produce.
  • These air ducts 70 continue in the side parts 26 ', 27' and form short deflection bends 72, 73 there for connection to inlet openings 75 and outlet openings 76 in the housing side part 12 'and housing circumferential part 78, which are radially offset with respect to the duct 70, or for the arrangement of fan blades indicated by dash-dot lines.
  • These inlet and outlet openings 75, 76 can be arranged in a grid-like manner in large numbers with webs between them or form larger, circumferential slots, as the inlet slots 80 of the exemplary embodiment according to FIG. 3 show.
  • the rotational movement of the outer rotor 18 thus causes an air flow through the channel 70 in a fan-like manner, so that there is effective cooling of the outer rotor and adjacent parts.
  • FIG. 11 shows an embodiment of the inner rotor 4 ', the hollow interior 82 of which is also connected to hollow shaft parts 6' for reasons of balancing.
  • Blower-like blades 83 which in the example shown are only arranged on the inflow side of the air flowing in the direction of the arrow 84, bring about sufficient Flow through the rotation of this inner rotor.
  • the curvature of these blades 83 is indicated schematically by dash-dot lines, as is the case in the deflection arches 72, 73 according to FIG. 10.
  • the housing peripheral parts 86, 87 of the charging unit 2 and the exhaust gas unit 3 are provided with cooling fins 88, as can best be seen from the overall illustration in FIG. 3.
  • the charging unit is shown on the left-hand side and shows the intake duct 8 for fresh air and the outlet connection 7 leading to the internal combustion engine.
  • the exhaust gas unit 3 offset by 90 °, the inflow connection and the outflow connection for the exhaust gas are shown in FIG. 3 the internal combustion engine not visible.
  • the exhaust gas unit effects a permanently effective closure of the exhaust gas line of the internal combustion engine, since there is no direct connection between the inlet and outlet channels 8, 7 in any of the rotary positions of the rotors 4, 18 shown in FIGS. 4a to 4h.
  • the exhaust gas can therefore only flow into the open after it has released a substantial part of its energy to the exhaust-gas-operated rotary piston charger according to the invention. This also results in a substantial reduction in the sound waves transmitted via the exhaust gas flow and a correspondingly low outlay for the exhaust gas pipe or exhaust pipe connected to the exhaust gas unit 3 on the outflow side.
  • the gearwheel-gear connection between the inner and outer rotor can be avoided by arranging a plurality of identically shaped rotary piston units next to one another on the same main shaft 6.
  • the drive transmission then takes place directly from one rotor to the other, and corresponding rotors from axially adjacent rotary piston units are then connected to one another rigidly and at an angle. If there is nevertheless a gear connection between the inner and outer rotors, one is sufficient for several rotary piston units arranged next to one another, i.e. Charger and / or exhaust units.
  • a reduction in flow losses results from the widest possible radially directed openings 38, 40 in the outer rotor 18, which are preferably wider than the opening width of the housing openings 7, 8.
  • the mutually parallel surfaces 30, 32 of the outer rotor can extend outwards. so that the openings 38, 40 do not form a constriction.
  • a small part of the fresh air conveyed by the loading unit can be supplied via axially directed connection channels (not shown) for cooling the exhaust gas unit which is subjected to higher thermal loads.
  • FIG. 12 shows for various rotational positions a to d of the rotor 4 ', 18' of an exhaust gas unit the relative positions of the inflow and outflow channel 8, 7 and the direction of the exhaust gas inflow.
  • the rotational positions shown show that the pressure of the exhaust gas flowing in in the direction of the arrows 90 acts, especially when the cross section of the inflow channel 8 is fully open, in a direction which acts on the inner rotor due to the largest lever arms in these rotational positions, based on the rotational axis A ', leads to the greatest torque.
  • Both channels 8, 7 run at an obtuse angle to one another, so that the flow through the exhaust gas unit takes place without a significant change in the flow direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Hydraulic Motors (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Rotary-Type Compressors (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Toys (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • General Details Of Gearings (AREA)
EP83101745A 1982-03-03 1983-02-23 Abgasbetriebener Rotationskolbenlader Withdrawn EP0087746A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1302/82 1982-03-03
CH1302/82A CH664193A5 (de) 1982-03-03 1982-03-03 Abgasbetriebener rotationskolbenlader.

Publications (1)

Publication Number Publication Date
EP0087746A1 true EP0087746A1 (de) 1983-09-07

Family

ID=4207255

Family Applications (2)

Application Number Title Priority Date Filing Date
EP83101745A Withdrawn EP0087746A1 (de) 1982-03-03 1983-02-23 Abgasbetriebener Rotationskolbenlader
EP83101746A Expired EP0087747B1 (de) 1982-03-03 1983-02-23 Innenachsige kurbelwellenlose Rotationskolbenmaschine

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP83101746A Expired EP0087747B1 (de) 1982-03-03 1983-02-23 Innenachsige kurbelwellenlose Rotationskolbenmaschine

Country Status (6)

Country Link
US (1) US4540356A (enrdf_load_stackoverflow)
EP (2) EP0087746A1 (enrdf_load_stackoverflow)
JP (3) JPS58180724A (enrdf_load_stackoverflow)
AT (1) ATE19900T1 (enrdf_load_stackoverflow)
CH (1) CH664193A5 (enrdf_load_stackoverflow)
DE (1) DE3363572D1 (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989002985A1 (en) * 1987-10-02 1989-04-06 Renate Ruf Rotary piston compressor
WO1990012210A1 (de) * 1989-03-31 1990-10-18 Imt Ingenieurgemeinschaft Für Motoren-Technik Gmbh Drehkolbenverdichter
DE102014209864A1 (de) * 2014-05-23 2015-12-17 Bayerische Motoren Werke Aktiengesellschaft Laststeuerorgan für eine mengengeregelte Brennkraftmaschine

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH667491A5 (de) * 1985-08-31 1988-10-14 Wankel Felix Innenachsige drehkolbenmaschine.
AT410965B (de) * 2000-07-11 2003-09-25 Buchelt Benno Verbundmotor
KR100516506B1 (ko) * 2004-12-11 2005-09-26 (주)힘틀 맴돌이 펌프
CZ302294B6 (cs) * 2008-07-29 2011-02-09 Dvorák@Jirí Rotacní motor na stlacitelná média
TR200805753A2 (tr) 2008-08-04 2009-03-23 Yaşar Tuncer Yilmaz Rotatif içten patlamalı motor
DE102009040051B4 (de) * 2009-09-03 2014-05-08 Siemens Aktiengesellschaft Freikolbenmaschine mit magnetischer Lagerung des Kolbens
RU2664725C1 (ru) * 2017-05-12 2018-08-22 Михаил Владимирович Давыдов Роторно-поршневой двигатель

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1197958A (en) * 1967-11-21 1970-07-08 Eugen Wilhelm Huber Hot-Gas Rotary Piston Machine
US3813195A (en) * 1972-03-06 1974-05-28 Copeland Corp Induction system for rotary mechanism
DE2438189A1 (de) * 1973-08-27 1975-03-06 Paul Jun Drehenergieumformer
FR2262731A1 (en) * 1974-03-01 1975-09-26 Torro Roger Sliding vane motor or compressor - has vane guided by eccentric preventing direct contact between vane and casing
DE2456252A1 (de) * 1974-11-28 1976-06-10 Kernforschungsanlage Juelich Kolbenmaschine zum komprimieren oder zum expandieren von gasen
DE2547208A1 (de) * 1975-10-22 1977-04-28 Kloeckner Humboldt Deutz Ag Arbeitsraumbildende brennkraftmaschine mit einem unterteilten viertaktarbeitsprozess
DE2605108A1 (de) * 1976-02-10 1977-08-11 Paul Drees Schiffchengesteuerte rotationsmaschine, insbesondere rotationsbrennkraftmaschine
DE2838670A1 (de) * 1978-09-05 1980-03-13 Klaus Krismer Dampfkraftanlage
EP0012329A1 (de) * 1978-12-04 1980-06-25 Ernst Dipl.-Ing. Kickbusch Rotations-Schwinglader für Verbrennungskraftmaschinen
DE2905824A1 (de) * 1979-02-15 1980-11-13 Alfred 4300 Essen Scholten Kreiskolbenmotor

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3097478A (en) * 1963-07-16 Exhaust gas driven compressor
DE10382C (de) * L. TAVERDON in Paris Verbesserungen an Matchinen mit rotirenden Kolben
US883271A (en) * 1907-09-16 1908-03-31 George Wilson Rotary pump.
FR699821A (fr) * 1929-07-18 1931-02-20 Powerplus 1927 Ltd Perfectionnements aux pompes rotatives
FR1556302A (enrdf_load_stackoverflow) * 1967-12-13 1969-02-07
DE1961134B1 (de) * 1969-12-05 1971-04-08 Kloeckner Humboldt Deutz Ag Mehrteiliger Kolben fuer innenachsige Rotationskolbenmaschine
US3905727A (en) * 1971-07-28 1975-09-16 John B Kilmer Gerotor type fluid motor, pump or the like
US3954355A (en) * 1973-08-27 1976-05-04 Paul Jr Herman L Rotary energy converter
JPS5228164A (en) * 1975-08-06 1977-03-02 Kurita Water Ind Ltd Disposal process waste water comprising fluorine
DE2604665A1 (de) * 1976-02-06 1977-08-11 Sullair Europ Corp Drehkolbenmaschine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1197958A (en) * 1967-11-21 1970-07-08 Eugen Wilhelm Huber Hot-Gas Rotary Piston Machine
US3813195A (en) * 1972-03-06 1974-05-28 Copeland Corp Induction system for rotary mechanism
DE2438189A1 (de) * 1973-08-27 1975-03-06 Paul Jun Drehenergieumformer
FR2262731A1 (en) * 1974-03-01 1975-09-26 Torro Roger Sliding vane motor or compressor - has vane guided by eccentric preventing direct contact between vane and casing
DE2456252A1 (de) * 1974-11-28 1976-06-10 Kernforschungsanlage Juelich Kolbenmaschine zum komprimieren oder zum expandieren von gasen
DE2547208A1 (de) * 1975-10-22 1977-04-28 Kloeckner Humboldt Deutz Ag Arbeitsraumbildende brennkraftmaschine mit einem unterteilten viertaktarbeitsprozess
DE2605108A1 (de) * 1976-02-10 1977-08-11 Paul Drees Schiffchengesteuerte rotationsmaschine, insbesondere rotationsbrennkraftmaschine
DE2838670A1 (de) * 1978-09-05 1980-03-13 Klaus Krismer Dampfkraftanlage
EP0012329A1 (de) * 1978-12-04 1980-06-25 Ernst Dipl.-Ing. Kickbusch Rotations-Schwinglader für Verbrennungskraftmaschinen
DE2905824A1 (de) * 1979-02-15 1980-11-13 Alfred 4300 Essen Scholten Kreiskolbenmotor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989002985A1 (en) * 1987-10-02 1989-04-06 Renate Ruf Rotary piston compressor
WO1990012210A1 (de) * 1989-03-31 1990-10-18 Imt Ingenieurgemeinschaft Für Motoren-Technik Gmbh Drehkolbenverdichter
DE102014209864A1 (de) * 2014-05-23 2015-12-17 Bayerische Motoren Werke Aktiengesellschaft Laststeuerorgan für eine mengengeregelte Brennkraftmaschine

Also Published As

Publication number Publication date
EP0087747B1 (de) 1986-05-21
JPS58180701A (ja) 1983-10-22
DE3363572D1 (en) 1986-06-26
JPH0325602B2 (enrdf_load_stackoverflow) 1991-04-08
ATE19900T1 (de) 1986-06-15
JPS58180724A (ja) 1983-10-22
EP0087747A3 (en) 1984-05-09
CH664193A5 (de) 1988-02-15
JPS58180728A (ja) 1983-10-22
US4540356A (en) 1985-09-10
EP0087747A2 (de) 1983-09-07

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