EP2065560A2 - Moteur à combustion interne - Google Patents

Moteur à combustion interne Download PDF

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Publication number
EP2065560A2
EP2065560A2 EP08170365A EP08170365A EP2065560A2 EP 2065560 A2 EP2065560 A2 EP 2065560A2 EP 08170365 A EP08170365 A EP 08170365A EP 08170365 A EP08170365 A EP 08170365A EP 2065560 A2 EP2065560 A2 EP 2065560A2
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EP
European Patent Office
Prior art keywords
internal combustion
pistons
combustion engine
gears
engine 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.)
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Application number
EP08170365A
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German (de)
English (en)
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EP2065560A3 (fr
Inventor
Fritz Mondl
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Individual
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Individual
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Publication date
Application filed by Individual filed Critical Individual
Publication of EP2065560A2 publication Critical patent/EP2065560A2/fr
Publication of EP2065560A3 publication Critical patent/EP2065560A3/fr
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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
    • F01C1/077—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 having toothed-gearing type drive

Definitions

  • the invention relates to an internal combustion engine according to the preamble of claim 1.
  • oscillating piston engines As a further alternative to reciprocating engines so-called oscillating piston engines have become known. In these oscillating piston engines usually rotate two pairs of pistons in a housing with a circular cross-section, which is enforced by a special mechanism, an oscillating angular velocity of the piston pairs. As a result, the angular distance between the pistons of the piston pairs fluctuates cyclically, which can be utilized for carrying out the combustion process.
  • Rotary piston engines of the type described are, for example, from GB 1 034 023 A , of the US 4,419,057 A , of the FR 2 730 274 A or the US 3,858,560 A known.
  • Gear drives are used to cause the uneven piston movement.
  • at least one non-circular, usually elliptical gear is engaged with an eccentrically mounted gear to form a transmission with a variable transmission ratio.
  • Such internal combustion engines are in the WO 01/34944 A , of WO 95/17582 A , of the US 4,028,019 A , of the DE 197 44 591 A , of the DE 27 39 326 A or the US 3,302,625 A described.
  • the disadvantage here that relatively massive gear are required to ensure the required functionality.
  • These transmissions are usually arranged next to the rotor housing and require appropriate space. In general, it is only possible to supply one or two rotor housings or piston pairs with one transmission. In order to connect several piston pairs mechanically, therefore, expensive additional gear are required to cause friction losses and stress space.
  • the RU 2 257 476 C shows an oscillating piston engine with two pairs of pistons, which are connected via gears with elliptical internal gears with a shaft.
  • the achievable phase difference between the pairs of pistons is only relatively small, so that a compression ratio that is too low for internal combustion engines results.
  • the annular cylindrical rotor housing leads to significant problems in the sealing when the machine is to be operated as an internal combustion engine.
  • the primary object of the present invention is to avoid these disadvantages and to provide a practically usable internal combustion engine which has a sufficient compression ratio and which can be sealed in a safe and cost-effective manner.
  • Another object of the invention is to avoid these disadvantages and to develop an internal combustion engine of the type described above so that a simple structure and an optimized type of power transmission can be achieved.
  • a transmission is to be created, which is compact and requires little space. It should also be possible in this way to provide multiple pairs of pistons, without the need for complex additional gear.
  • the piston drive which causes the oscillating angular velocity of the pistons, to be formed in a very simple manner as a gear transmission.
  • a gear transmission Through the use of ring gears a large overlap of the teeth and thus a very favorable engagement behavior is achieved, so that the gears are loaded comparatively low and thus can be performed in a relatively small size.
  • the transmission can be arranged in the installation space within the range of movement of the pistons, which minimizes the required installation space.
  • the ring gears have a major axis and a minor axis perpendicular thereto and if they are symmetrical with respect to the main axis and with respect to the minor axis.
  • the ring gears like an ellipse, are composed of four mirror-symmetrical quadrants.
  • the ring gears are elliptical, resulting in a substantially sinusoidal acceleration and deceleration of the pistons.
  • the gears with which the ring gears mesh are circular and eccentric.
  • a particularly advantageous embodiment variant of the invention provides that the ring gears in the region of the secondary vertices, ie the end points of the minor axis, have a convex portion.
  • ring gears have outer surfaces which form parts of the piston raceway. In this way, separate components can be omitted for power transmission.
  • a plurality of rotor housings are arranged axially next to one another.
  • the eccentrically mounted gears of several rotors are mounted on a common output shaft.
  • the inner wall of the rotor housing is curved in a toroidal shape.
  • a special case of the toroidal design is a spherical design of the rotor housing.
  • Radially arranged distribution channels are preferably provided in the toothed wheels for transporting a lubricant.
  • the oil is conveyed by the centrifugal force in the direction of the piston.
  • the distribution channels open into a space between piston rings. In this way, the lubricant is guided purposefully to the parts of the piston to be lubricated.
  • the transmission has non-circular gears whose ratio of the main axis to the minor axis is between 1.2 and 1.9, preferably between 1.3 and 1.6. Together with the width of the piston in the circumferential direction and with the desired compression ratio results in an optimum value for the fluctuation range of the transmission ratio, resulting in the ratio of the main axis to the minor axis.
  • An alternative embodiment of the invention provides an internal combustion engine, which is designed as a rotary piston engine as described above, with at least one rotor housing of circular cross-section in which run several groups of pistons in a rotary motion, wherein a gear with non-circular gears and eccentrically mounted Gears is provided which oscillates the angular velocity of each group of pistons in opposite directions to other groups, so that the angular distance between the individual pistons changes during the circulation.
  • a group of pistons may comprise three or four pistons, which are each connected to a non-circular gear formed as a ring gear, but also on the other hand, that more than two ring gears may be provided. In this way, the structural density can be increased.
  • the internal combustion engine of Fig. 1 consists of a rotor housing 1, which is constructed substantially disc-shaped and has a toroidal cylinder chamber.
  • an output shaft 2 is mounted on bearings 28. Fixed to the output shaft 2, two eccentrically mounted gears 13, 14 are connected, which mesh with non-circular ring gears 3, 4. The two ring gears 3, 4 are connected to pistons 5, 7 and 6, 8, which are arranged movably in the cylinder space. Between each two of the pistons 5, 7 and 6, 8 working spaces 9, 10, 11, 12 are formed. Due to the non-uniform transmission ratio of the gears, which are formed by the internally toothed or eccentrically mounted gears 3 and 4 and 13 and 14, the pistons 5, 6, 7, 8 approach each other alternately during one revolution and in turn move away. As a result, the volume of the working spaces 9, 10, 11, 12 changes cyclically. When in the Fig. 1 illustrated position of the pistons 5, 6, 7, 8, the working spaces 9 and 11 are minimal and the working spaces 10 and 12 maximum.
  • an inlet opening 15 and an outlet opening 16 are provided, via which the gas exchange takes place.
  • internal combustion engine operates in four-stroke principle, no valves or other control elements are required because the piston 5, 6, 7, 8, the inlet opening 15 and the outlet opening 16 automatically close and release.
  • the pistons 5, 6, 7, 8 consist of piston bodies with a plurality of piston rings 21, which are constructed in a similar way to conventional piston engines.
  • the pistons 5, 6, 7, 8 are attached via rods 20 and armature 27 to the ring gears.
  • Spark plugs 17 and 25 serve for ignition, the internal combustion engine operating according to the Otto method. If the internal combustion engine is operated with auto-ignition, an injection nozzle is provided at a comparable location.
  • the lubrication takes place via a nozzle 30, the oil in the interior 29 of the transmission 3, 4; 13, 14 injects.
  • Radially arranged distribution channels 22 transport the oil further into the region of the pistons 5, 6, 7, 8.
  • the excess oil is discharged via discharge channels 24 on the underside of the internal combustion engine.
  • the cooling of the internal combustion engine via a water jacket 26 outside the piston barrel.
  • the outer peripheral surfaces of the ring gears 3, 4 represent the inner parts of the piston raceway and are sealed by sealing surfaces 31 against each other and against the housing.
  • Fig. 3a, 3b and 3c to Figs. 14a, 14b and 14c are schematically illustrated the piston positions during a piston revolution.
  • the Fig. 3a to 14a the position, ie angular position of the internal gear 3 and thus the piston 6 and 8
  • the Fig. 3c to 14c the position, ie angular position of the internally toothed gear 4 and thus the piston 5 and 7.
  • the Fig. 3b to 14b the angular positions are shown together and at the same time entered the working cycles, which are assigned to the individual workrooms 9, 10, 11, 12.
  • Fig. 15 schematically shows the time course of the piston movement and thus the individual work cycles. It is off Fig. 15 It can be seen that the compression stroke and the exhaust stroke are delayed while the intake stroke and the power stroke occur during an accelerated phase of the piston movement.
  • the invention makes it possible to provide a motor construction which is free of reciprocating masses, requires no valves and the like, so that the number of moving parts is minimal.
  • the internal combustion engine according to the invention is simple, compact and has an extremely high efficiency.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transmission Devices (AREA)
EP08170365A 2007-11-30 2008-12-01 Moteur à combustion interne Withdrawn EP2065560A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT19602007A AT506123B1 (de) 2007-11-30 2007-11-30 Brennkraftmaschine mit innerer verbrennung

Publications (2)

Publication Number Publication Date
EP2065560A2 true EP2065560A2 (fr) 2009-06-03
EP2065560A3 EP2065560A3 (fr) 2010-09-22

Family

ID=40456681

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08170365A Withdrawn EP2065560A3 (fr) 2007-11-30 2008-12-01 Moteur à combustion interne

Country Status (2)

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EP (1) EP2065560A3 (fr)
AT (1) AT506123B1 (fr)

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1034023A (en) 1964-04-22 1966-06-29 Ford Motor Co Rotary piston internal combustion engines
US3302625A (en) 1964-05-15 1967-02-07 Cunningham Kelly Gore Engine
US3858560A (en) 1973-11-26 1975-01-07 Gen Motors Corp Reciprocating rotary engine
US4028019A (en) 1975-02-20 1977-06-07 Ernest Wildhaber Positive-displacement unit with coaxial rotors
DE2739326A1 (de) 1977-09-01 1979-03-15 Herbert Haardt Kraft- oder arbeitsmaschine und verfahren zu deren betrieb
US4419057A (en) 1980-02-06 1983-12-06 Societe Nationale D'etude Et De Construction De Moteurs D'aviation, "S.N.E.C.M.A." Rotary piston motor
WO1995017582A1 (fr) 1993-12-23 1995-06-29 Janosi Marcell Mecanisme d'entrainement a mouvement rotatif conçu notamment pour des moteurs a combustion interne
FR2730274A1 (fr) 1995-02-08 1996-08-09 Menioux Claude Charles Felix Moteur a pistons rotatifs et combustion externe
DE19744591A1 (de) 1997-10-09 1999-04-15 Walter Kreb Mechanik zur Steuerung eines Drehkolbenverbrennungsmotors und Entnahme eines Drehmomentes
WO2001034944A1 (fr) 1999-11-12 2001-05-17 Velimir Gruban Moteur rotatif a combustion interne
RU2257476C1 (ru) 2003-11-17 2005-07-27 Гридин Валерий Владиславович Роторно-лопастной двигатель внутреннего сгорания

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1701534A (en) * 1926-10-26 1929-02-12 Knopp Rudolph Rotary engine
US3034449A (en) * 1960-04-08 1962-05-15 Moore Clyde Maurice Alternating piston type engine
US3769946A (en) * 1969-07-14 1973-11-06 W Scherrer Rotary engines

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1034023A (en) 1964-04-22 1966-06-29 Ford Motor Co Rotary piston internal combustion engines
US3302625A (en) 1964-05-15 1967-02-07 Cunningham Kelly Gore Engine
US3858560A (en) 1973-11-26 1975-01-07 Gen Motors Corp Reciprocating rotary engine
US4028019A (en) 1975-02-20 1977-06-07 Ernest Wildhaber Positive-displacement unit with coaxial rotors
DE2739326A1 (de) 1977-09-01 1979-03-15 Herbert Haardt Kraft- oder arbeitsmaschine und verfahren zu deren betrieb
US4419057A (en) 1980-02-06 1983-12-06 Societe Nationale D'etude Et De Construction De Moteurs D'aviation, "S.N.E.C.M.A." Rotary piston motor
WO1995017582A1 (fr) 1993-12-23 1995-06-29 Janosi Marcell Mecanisme d'entrainement a mouvement rotatif conçu notamment pour des moteurs a combustion interne
FR2730274A1 (fr) 1995-02-08 1996-08-09 Menioux Claude Charles Felix Moteur a pistons rotatifs et combustion externe
DE19744591A1 (de) 1997-10-09 1999-04-15 Walter Kreb Mechanik zur Steuerung eines Drehkolbenverbrennungsmotors und Entnahme eines Drehmomentes
WO2001034944A1 (fr) 1999-11-12 2001-05-17 Velimir Gruban Moteur rotatif a combustion interne
RU2257476C1 (ru) 2003-11-17 2005-07-27 Гридин Валерий Владиславович Роторно-лопастной двигатель внутреннего сгорания

Also Published As

Publication number Publication date
EP2065560A3 (fr) 2010-09-22
AT506123B1 (de) 2009-08-15
AT506123A1 (de) 2009-06-15

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