US3724428A - Rotary piston engine - Google Patents

Rotary piston engine Download PDF

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Publication number
US3724428A
US3724428A US00147899A US3724428DA US3724428A US 3724428 A US3724428 A US 3724428A US 00147899 A US00147899 A US 00147899A US 3724428D A US3724428D A US 3724428DA US 3724428 A US3724428 A US 3724428A
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US
United States
Prior art keywords
piston
engine
cylinder
pinion
working
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Expired - Lifetime
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US00147899A
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English (en)
Inventor
G Mederer
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Individual
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Individual
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Publication date
Priority claimed from DE19702027109 external-priority patent/DE2027109C/de
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    • 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
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/063—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines

Definitions

  • a rotary piston engine comprises an annular clrcularsectioned cylinder, a working piston and a contra- (g1 ..123/8;1(;72, piston both p annular and circulabsectioned and both mounted for rotation in Said cylinder, a chamber [58] Field of Search ..123/8.47,418/33,36, 37 defined in said cylinder, between Said pistons com [56] References Cited stituting a working chamber of the engine and undergoing cycle changes in volume during rotation of UNITED STATES PATENTS Said p 3,552,363 1/1971 Funakoshi ..418/33 X 3 Claims, 5 Drawing Figures PATENTEDAPR 3 ms SHEET 1 0F 5 INVENTOR. GERHARD MEDERER lwzwwd Chem/z 9 m ATTORNEYS.
  • PATENTEDAPR 3 I973 SHEET h [1F 5 INVENTOR. GERHARD mzosmzn BY Hula/var! (7 ma 6' 710mm ATTORNEYS.
  • ROTARY PISTON ENGINE This invention relates to a rotary piston engine.
  • An object of the present invention is to provide a rotary piston internal-combustion engine which is compact and can give high performance and have a high compression ratio.
  • the invention provides a rotary piston engine comprising an annular circular-sectioned cylinder, a part-annular working piston disposed in the cylinder and drivingly connected to an output shaft, a contra-piston also disposed in the cylinder for following the working piston at a distance which varies during working of the engine and automatic device for adjusting the distance between the working piston and the contra-piston being provided, and the chamber defined between the pistons varying during working of the engine so as to constitute a working chamber of the engine which undergoes cycle changes in size during working of the engine.
  • the device for adjusting the spacing between the pistons effecting a change in the size of the chamber during rotation.
  • the control device is effective to ensure that the chamber is greatest in size for intake of fuel or air and becomes smaller during subsequent compression and has its smallest value at the ignition point.
  • Ignition can be effected by a spark plug in the case of a fuel/air mixture or can be be injection of diesel fuel in the case of an engine working on the diesel cycle.
  • the expanding combustion gases bring about an increase in the spacing between the pistons, by the working piston moving in a forward direction away from the contrapiston, the development of a useful torque at an output shaft of the engine.
  • expulsion of spent combustion gases occurs and, on further movement of the pistons enlargement of the chamber and intake of further fuel/air mixture or air into the chamber for the next working cycle.
  • the pistons have passed the intake region on their path of movement, the mutual spacing of the pistons is reduced, so that the air or fuel/air mixture is compressed.
  • the mutual piston spacing is at its smallest in the ignition region and so here maximum compression occurs.
  • the working cycle is then repeated.
  • the hollow circular circular disc is composed of two discs spaced apart by a distance piece connected securely to the working piston and securely to the discs.
  • the contra-piston is fastened to a U-section sliding rail, which is pivotally linked to a first lever, which is pivotally connected to a circular disc, which is mounted for rotation on an eccentric of a shaft, which is itself mounted for rotation in the bearing discs and is connected securely to a pinion which meshes with a stationary counter-pinion fixed to the output shaft, the circular disc being guided frontally in circular recesses in the side wall of the hollow circular disc.
  • a high compression ratio which can be between 1:10 and 1:40, becomes possible because the working piston and the contra-piston have their opposed faces lying in respective radially extending planes.
  • FIG. 1 is a longitudinal section through a preferred embodiment of rotary piston engine conforming to the invention
  • FIG. 2 is a section along the line IIII of FIG. 1;
  • FIG. 3 is a section along the line IIIIII of FIG. 1'
  • FIG. 4 is a section along the line IVIV of FIG. 1;
  • FIG. 5 is a section along the line VV of FIG. 1.
  • a preferred embodiment of rotary piston engine conforming to the invention comprises a working piston 1 (FIG. 2) which is part-annular and mounted for rotation in an annular cylinder 2.
  • the working piston 1 is connected securely to an annular distance piece 3, which is accommodated in a slot dis posed inwardly of the cylinder 2.
  • Circular discs 4, 4' are arranged on both sides of the distance piece 3. These discs 4, 4' are connected, for example by pins or bolts 5, to the distance piece 3.
  • the discs 4, 4' and the annular distance piece 3 form a circular disc having a hollow interior space 6.
  • the discs 4, 4' are connected, by their outer sides 7, 7 to two shaft parts 8, 8' which together form an output shaft of the engine.
  • These shaft parts 8, 8' are mounted for rotation in bearing discs 9, 9', which butt for sliding movement against the outer sides 7, 7 and are supported by ball bearings 10, 10' on the cylinder 2
  • the shaft parts 8, 8 penetrate counter-pinions 13, 13 which are fastened stationarily to the engine housing and which mesh with pinions I2, 12.
  • the counter pinions 13, 13' are mounted in the housing, and a flywheel 14 is fastened on the shaft part 8 via which the power delivery is effected.
  • the contra-piston 15 is mounted for rotational movement behind the working piston 1 with a variable spacing A between them in the cylinder 2.
  • the contrapiston is fastened to a U-section sliding rail 16, whose limbs 17, 18 embrace the hollow disc 3, 4, 4 for sliding movement.
  • the sliding rail 16 is linked via a pivot consisting of a pin 19 and a bush 20 to a lever 21, which is mounted for swinging movement at 22 in a nose 23 fixed to an eccentric 24.
  • the central point of the eccentric 24, which is circular, lies at 25.
  • the eccentric 24 is mounted for rotary movement on a circular shaped eccentric 26, which is mounted fixedly on both sides, to the shaft 27, the shaft 27 being mounted in the bearing discs 9, 9' and securely carrying the pinions 12, 12'.
  • the opposed surfaces 28, 29, of the pistons 1 and 15 are flat, i.e., they extend as radial planes.
  • the spacing A is at its minimum in the position, shown in FIG. 2, and at this position the volume of thechamber 30 bounded by the pistons 1 and 15 has been brought to its minimum value, fuel/air mixture or air present in this chamber is at its highest degree of compression.
  • the fuel/air mixture can now be ignited by a spark or diesel fuel injected to cause ignition.
  • the contra-piston 15 remains initially at rest, held by the control device.
  • the-working piston 1 is move by the expanding combustion gases in the direction of the arrow B.
  • the combustion gases can flow out via outlet orifice 31; they are then completely expelled by the lagging contra-piston 15.
  • the suction port 32 is freed, so that a fuel/air mixture, or air is sucked into the now comparatively large chamber.
  • the contra-piston 15 is moved faster than the working piston, so that the fuel/air mixture or the air is compressed on the path from c to d.
  • ignition is effected once again and the working cycle repeated.
  • the eccentric disc 24 is mounted with a close fit in circular recesses 33, 33 formed in the discs 4, 4' and can move slidingly in these recesses.
  • the nose 23 is kept narrower than the mutual spacing S of the discs 4, 4' and extends into the hollow space 6.
  • the working piston 1 On its path of revolution in the direction of the arrow B, the working piston 1 entrains the discs 4, 4 and therewith the eccentric 24 guided in the recesses 33, 33' thereof. Consequently the axis 34 of the shaft 27 is moved on a circular arc K at a spacing T in relation to the axis 35 of the output shaft 8. As this occurs, the pinions 12, 12' rolls on the counter pinions 13, 13' so that the eccentric 26 is rotated and therewith the lever 24 is swung with its nose 23 and the pivot point 22.
  • the number of ignitions upon one rotation of the pistons depends on the transmission ratio of the toothing of pinions 12, 12 and counter pinions 13, 13'.
  • the design can readily be selected in such a way that two or more ignitions are effected on one revolution. A prerequisite for this is that an integral or whole-numbered transmission ratio is selected.
  • the ejection and intake of air or fuel/air mixture can, if need be, be controlled via valves or slides.
  • a fuel/air mixture i.e., a petrol engine or gas engine an ignition plug can be situated in the working piston 1 or adjacent the point d. If air is compressed an injection nozzle can be provided in the piston l or adjacent point d to inject diesel fuel to cause ignition by compression.
  • a high compression ratio can be achieved, which is in addition variable, in that the spacing A can be adjusted.
  • the number of revolutions can be selected comparatively high. With small dimensions, a comparatively high performance is achieved. The efliciency of the engine is comparatively high.
  • the engine can compress a mixture of petrol or gas with air and ignite this mixture, after compression, with a spark, or can compress air and inject diesel fuel to cause ignition by compression.
  • the engine can thus be a petrol or gas engine or a diesel engine.
  • the engine can, of course, also work on the two-stroke principle. If inlet valves and operating mechanisms are provided the engine can be a steam engine or a hot gas engine. Many other variations are, of course, possible.
  • a rotary piston engine comprising an annular circular-sectioned cylinder, a part-annular working piston disposed in the cylinder and drivingly connected to an output shaft, a contra-piston disposed in the cylinder for following the working piston at a variable distance during working of the engine, the chamber defined between the pistons constituting a working chamber which undergoes cyclic changes in size, a hollow circular disc provided centrally of the cylinder with its sides being centrally connected to parts of an output shaft, the working piston being connected securely to the disc, bearing discs supported for rotary movement and supporting the parts of the output shaft, means for controlling the spacing between the pistons, said controlling means comprising the contra-piston being 2.
  • the engine as set forth in claim 1, characterized in i that the pinion and counter-pinion have equal numbers of teeth.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Transmission Devices (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
US00147899A 1970-06-03 1971-05-28 Rotary piston engine Expired - Lifetime US3724428A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19702027109 DE2027109C (de) 1970-06-03 Mittelachsiger Umlaufkolbenmotor

Publications (1)

Publication Number Publication Date
US3724428A true US3724428A (en) 1973-04-03

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US00147899A Expired - Lifetime US3724428A (en) 1970-06-03 1971-05-28 Rotary piston engine

Country Status (10)

Country Link
US (1) US3724428A (xx)
JP (1) JPS554921B1 (xx)
AT (1) AT322289B (xx)
BE (1) BE767830A (xx)
CH (1) CH539773A (xx)
ES (1) ES391803A1 (xx)
FR (1) FR2095819A5 (xx)
GB (1) GB1349073A (xx)
NL (1) NL7107303A (xx)
SE (1) SE371249B (xx)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022552A (en) * 1976-03-17 1977-05-10 Wilson Donald G Vane type fluid power machine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017008704A1 (de) * 2017-09-18 2019-03-21 Arianit Gashi Ein Takt Motor

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1299588A (en) * 1919-01-29 1919-04-08 Roy Elmer Luikart Rotary engine.
US1981615A (en) * 1931-12-04 1934-11-20 Enderlin Joseph Rotary motor
US2142706A (en) * 1937-05-04 1939-01-03 Harry F Wolstenholme Rotary internal combustion engine
US2270976A (en) * 1937-07-13 1942-01-27 Eric Benjamin Rotary piston machine
US2840058A (en) * 1955-02-08 1958-06-24 Kenneth E Stringer Alternating piston type internal combustion engine
US3552363A (en) * 1967-11-06 1971-01-05 Eisuke Funakoshi Rotary engine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1299588A (en) * 1919-01-29 1919-04-08 Roy Elmer Luikart Rotary engine.
US1981615A (en) * 1931-12-04 1934-11-20 Enderlin Joseph Rotary motor
US2142706A (en) * 1937-05-04 1939-01-03 Harry F Wolstenholme Rotary internal combustion engine
US2270976A (en) * 1937-07-13 1942-01-27 Eric Benjamin Rotary piston machine
US2840058A (en) * 1955-02-08 1958-06-24 Kenneth E Stringer Alternating piston type internal combustion engine
US3552363A (en) * 1967-11-06 1971-01-05 Eisuke Funakoshi Rotary engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022552A (en) * 1976-03-17 1977-05-10 Wilson Donald G Vane type fluid power machine

Also Published As

Publication number Publication date
DE2027109A1 (de) 1971-12-16
DE2027109B2 (de) 1973-02-08
AT322289B (de) 1975-05-12
SE371249B (xx) 1974-11-11
GB1349073A (en) 1974-03-27
ES391803A1 (es) 1973-06-16
BE767830A (fr) 1971-10-18
FR2095819A5 (xx) 1972-02-11
JPS554921B1 (xx) 1980-02-01
NL7107303A (xx) 1971-12-07
CH539773A (de) 1973-07-31

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