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EP0637677A1 - Moteur à combustion interne à quatre temps - Google Patents

Moteur à combustion interne à quatre temps Download PDF

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Publication number
EP0637677A1
EP0637677A1 EP94111859A EP94111859A EP0637677A1 EP 0637677 A1 EP0637677 A1 EP 0637677A1 EP 94111859 A EP94111859 A EP 94111859A EP 94111859 A EP94111859 A EP 94111859A EP 0637677 A1 EP0637677 A1 EP 0637677A1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
internal combustion
combustion engine
stroke internal
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.)
Granted
Application number
EP94111859A
Other languages
German (de)
English (en)
Other versions
EP0637677B1 (fr
Inventor
Manfred Födisch
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Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0637677A1 publication Critical patent/EP0637677A1/fr
Application granted granted Critical
Publication of EP0637677B1 publication Critical patent/EP0637677B1/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
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0079—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having pistons with rotary and reciprocating motion, i.e. spinning pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
    • F01B3/06—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by multi-turn helical surfaces and automatic reversal
    • F01B3/08—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by multi-turn helical surfaces and automatic reversal the helices being arranged on the pistons
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the present invention relates to a four-stroke internal combustion engine according to the preamble of patent claim 1.
  • crank mechanism makes the reciprocating engine complex, heavy and space-consuming, which is ultimately reflected in the use of materials and fuel.
  • the present invention has for its object to provide a four-stroke internal combustion engine working on a novel principle, which is characterized by design simplicity, low weight and low fuel consumption.
  • a four-stroke internal combustion engine of the type specified in the preamble of claim 1 is characterized according to the invention in that the piston is axially and rotatably mounted in the cylinder and between the piston and the cylinder is a wavy winding positive guidance is provided, which impresses the piston at a rotation of 360 ° four axial strokes for the four work cycles, that the cylinder and the piston each have a combustion chamber half in their peripheral walls adjacent to their mutually adjacent end faces, which at the time of ignition of the fuel gas supplement a combustion chamber, so that fuel gas expanding in the combustion chamber exerts a torque on the piston, and that a coaxial shaft shaft is provided on the piston for deriving the rotary movement carried out by the piston.
  • the piston carries out four stroke movements for the four working cycles of suctioning - compressing - expanding (working) - ejecting during a rotation of 360 °.
  • the shaft power generated by the motor can be taken directly from the rotating piston.
  • the combustion chamber halves formed in the peripheral walls of the cylinder and piston, which complement one another into a combustion chamber, ensure that the expanding combustion gas immediately exerts a torque on the circumference of the piston during the expansion work cycle.
  • the rotational forces exerted on the piston are therefore considerably greater than the axial forces exerted on the piston.
  • the four-stroke internal combustion engine designed according to the invention combines to a certain extent the advantages of a reciprocating piston engine and a rotary piston engine. Since a crank mechanism is not required, it is simple in construction and comparatively light in weight. Since the forces exerted by the expanding fuel gas act primarily in the circumferential direction and act on the outer circumference of the piston, the engine operates with high efficiency, which is reflected in a correspondingly low fuel consumption. This is promoted by a good swirling of the fuel gas in the displacement, which is brought about primarily by the rotary movement of the piston. Because of the simple construction, the susceptibility to faults is low, so that the motor has a long service life.
  • the shaft shaft provided on the piston to compensate for the lifting movement and to transmit the rotary movement of the piston is mounted in an axially movable and rotationally fixed manner in a drive shaft which is rotatably and axially fixedly mounted in the cylinder.
  • the drive shaft thus immediately receives the torque generated by the engine.
  • the valve device preferably consists of a valve flange with a valve slot penetrating the valve flange, which is rotatably mounted in the end wall of the cylinder and rotates with the piston, so that the valve flange with the valve slot opens and closes the inlet and outlet openings in a timely manner. This further simplifies the internal combustion engine, since no separate intake and exhaust valves with valve control are required.
  • a further displacement is formed between the piston and the cylinder on the rear side facing away from the working side, each of which has a return line with the inlet channel and the
  • the outlet duct is connected in such a way that part of the exhaust gas (for example a third to a quarter of the quantity of exhaust gas) is returned from the outlet duct to the rear displacement and from there via the inlet duct together with fresh fuel gas to the working displacement.
  • the hot exhaust gas ensures rapid heating of the fuel gas and the entire engine to the operating temperature, which is particularly advantageous particularly in operating conditions with a heat deficit, such as during a cold start, since this ensures that the catalytic converter functions correctly immediately after starting.
  • the amount of pollutants in the exhaust gas is considerably reduced by the exhaust gas recirculation in its own cylinder.
  • the recirculated hot exhaust gas ensures good swirling of fuel and combustion air.
  • the four-stroke internal combustion engine designed according to the invention can be operated both as a gasoline engine and as a diesel engine.
  • the preferred field of application of the invention is the motor vehicle engine, but is not limited to this.
  • the cylinder-piston arrangement shown in Fig. 1 is formed by a housing in the form of a cylinder 2, which consists of a cylindrical peripheral wall 4 and two end walls 6a and 6b.
  • the end walls 6a, 6b are fixedly and sealingly connected to the peripheral wall in order to form a cylindrical space in the interior of the cylinder.
  • a cylindrical piston 10 is slidably supported by means of piston rings 12, so that the cylindrical interior is divided into a displacement 8 on the left side in FIG. 1 (working side) and a displacement 9 on the right side (return side) becomes.
  • the piston-cylinder arrangement shown in Fig. 1 is symmetrical in some respects with respect to a central plane III-III educated.
  • the parts located opposite one another on the working and return sides, which correspond, have therefore been identified with the same reference numerals with the addition of the letters a and b.
  • the piston 10 is provided on its opposite ends with a coaxial shaft shaft 14a, 14b, which is connected to a drive shaft 16a or 16b in a rotationally fixed but axially displaceable manner.
  • the shaft shafts 14a, 14b are designed as hexagonal or octagonal shafts, which extend into correspondingly designed inner hexagonal or octagonal guides of the drive shafts 16a, 16b.
  • the drive shafts 16a, 16b are in turn rotatably supported by bearings 18a, 18b in the end wall 6a and 6b and are axially immovable.
  • the piston 10 can perform both a rotational movement and an axially reciprocating stroke movement. As indicated in Fig. 1, the piston 10 has a comparatively large diameter. The axial length of the cylindrical interior is approximately 50% greater than the axial length of the piston.
  • a positive guide 20 is provided between the piston 10 and the peripheral wall 4.
  • the positive guide 20 has a wave-shaped circumferential groove 22 formed in the circumference of the piston and having a semicircular cross section with four approximately semi-sinusoidal winding sections, cf. 5.
  • two balls 24 are mounted at diametrically opposite locations with the aid of two screws 26, half of which engage in the groove 22 of the piston 10.
  • the winding portions of the groove 22 are shaped so that the piston makes four strokes for the four in one revolution Work cycles suction - compressing - expanding (working) - ejecting, as will be explained.
  • a combustion chamber half 32 and 34 is formed in the peripheral wall 4 of the cylinder and in the peripheral wall of the piston 10, adjacent to the end face of the cylinder or piston supplement the position of the piston 10 indicated by dashed lines in FIG. 3a to form a combustion chamber 30.
  • each of the combustion chamber halves 32, 34 has an approximately triangular outline in a plane perpendicular to the cylinder axis, the combustion chamber halves 32, 34 on their inner long sides and the combustion chamber half 34 also on their one axial end face to the working displacement 8 are open.
  • An ignition device in the form of a spark plug 35 is assigned to the combustion chamber half 32 formed in the cylinder 2. The mode of operation of the combustion chamber 30 is explained in more detail below.
  • an inlet channel 36 with an inlet opening 38 opening into the displacement 8 is formed for supplying fuel gas, cf. 3, 3a and 4. Furthermore, an outlet channel 40 is formed in the end wall 6a with an outlet opening 42 connected to the displacement 8 for discharging exhaust gas.
  • a valve device is provided, which in the exemplary embodiment shown is designed as a valve flange 48a provided on the drive shaft 16a with a valve slot 54a penetrating the valve flange 48a (cf. in particular FIGS. 1, 3, 3a and 6, 7).
  • the valve flange 48a which is rotatably mounted in a recess in the end wall 6a, performs the same rotary movement because of the drive connection between the drive shaft 16a and the piston 10 like the piston 10, so that the valve slot 54a alternately coincides with the inlet opening 38 and the outlet opening 42, in order to open and close the inlet opening 38 and the outlet opening 42 in accordance with the four work cycles of the four-stroke engine.
  • a sealing washer 50a is axially slidably mounted in a recess of the valve flange 48a.
  • the sealing disk 50a is provided with a valve slot 52a penetrating the sealing disk, the shape of which corresponds to the valve slot 54a and is slidably guided on an axial shoulder surrounding the valve slot 54a of the valve flange 48a, cf. 6 and 7.
  • the sealing washer 50a is pressed against the end face of the end wall 6a by several (for example three) curved leaf springs 56a, which are supported on the valve flange 48a, so that the sealing washer 50a can perform its sealing function to avoid leakage losses.
  • the fuel gas can consist of a fuel-air mixture if the mixture is formed in a carburetor (not shown). However, it can also consist of pure air if the mixture is only formed in the displacement 8 by means of fuel injection (not shown).
  • the piston Upon its further rotation by 90 °, the piston executes a lifting movement into its (in FIG. 1) left end position, as a result of which the fuel gas located in the displacement 8 and in the combustion chamber halves 32, 34 is compressed.
  • the piston 10 assumes the angular position indicated by dashed lines in FIG. 3a, in which the combustion chamber halves 32 and 34 complement each other to form the combustion chamber 30 and in which the maximum compression is achieved.
  • essentially all of the fuel gas is in the combustion chamber 30 and is now ignited by the spark plug 35.
  • the combustion chamber 30 has an approximately rectangular shape, the combustion chamber half 34 of the piston 10 having a drive surface 34 'substantially perpendicular to the circumferential direction and the combustion chamber half 32 formed in the cylinder having a reaction surface 32' substantially parallel thereto. Due to this combustion chamber design, the expanding fuel gas exerts a rotating force on the piston 10, which acts on the outer circumference of the piston 10 and thus generates a correspondingly large torque.
  • the piston 10 is thus driven by the fuel gas in the direction of rotation, while at the same time exerting an expansion stroke (to the right in FIG. 1).
  • the rotary movement of the piston 10 is directly on the drive shaft via the shaft 14a 16a transmit, which ensures a high efficiency of the internal combustion engine.
  • the piston After a quarter of a turn, the piston has completed its work stroke (expansion stroke), whereupon the work cycle begins to expel the exhaust gas.
  • the piston 10 is again moved to the left (in FIG. 1) by the positive guide 20, while the valve slots 52a, 54a sweep over the outlet opening 42. The exhaust gas is thus expelled from the piston 10 into the exhaust gas duct 40.
  • the piston 10 At the end of the ejection stroke, the piston 10 again assumes the angular position indicated by the dashed line in FIG. 3, in which the valve slots 52a, 54a are located between the outlet opening 42 and the inlet opening 38.
  • the piston 10 has thus carried out the four working cycles of suction - compression - working (expanding) - ejecting which are characteristic of a four-stroke engine, with each working cycle corresponding to a piston rotation by 90 ° and an axial stroke movement. During a work cycle with the four work cycles, the piston 10 thus makes a rotation through 360 ° and four axial stroke movements.
  • a return line 60 or 62 is branched off, which are connected via openings 64 and 66 to the rear displacement 9.
  • an arrangement of valve flange 48b, sealing washer 50b, valve slots 52b, 54b and springs 56b corresponding to the working side is provided on the back, which in principle is the same as the corresponding arrangement on the working side works.
  • the proportion of the gas branched off to the return side can be dimensioned by appropriately dimensioning the return lines 60, 62. It goes without saying that the metering can also be carried out by a correspondingly controlled valve device (not shown). The latter possibility has the advantage that the return of the exhaust gas to operating states with a heat deficit such as the cold start can be limited.
  • a recess (not shown) can be provided in the piston 10, which increases the volume of the rear displacement 9.
  • drive shafts of further cylinders can be coupled to the drive shafts 16a, 16b - either directly or via gears.
  • coolant channels 68 for cooling the cylinder are indicated. Further details of the internal combustion engine that are not necessary for understanding the invention, such as e.g. the lubricant supply has been omitted for the sake of simplicity.
  • longitudinal lubricant bores in the screws 26 provide precise lubrication of the positive guide 20, i.e. the balls 24 and the groove 22 and the piston 10 can take place.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP94111859A 1993-08-06 1994-07-29 Moteur à combustion interne à quatre temps Expired - Lifetime EP0637677B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4326463A DE4326463A1 (de) 1993-08-06 1993-08-06 Viertakt-Verbrennungsmotor
DE4326463 1993-08-06

Publications (2)

Publication Number Publication Date
EP0637677A1 true EP0637677A1 (fr) 1995-02-08
EP0637677B1 EP0637677B1 (fr) 1997-10-08

Family

ID=6494617

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94111859A Expired - Lifetime EP0637677B1 (fr) 1993-08-06 1994-07-29 Moteur à combustion interne à quatre temps

Country Status (4)

Country Link
EP (1) EP0637677B1 (fr)
JP (1) JP3677058B2 (fr)
KR (1) KR100313162B1 (fr)
DE (2) DE4326463A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2246008C1 (ru) * 2003-08-04 2005-02-10 Южно-Уральский государственный университет Поршневая машина
RU2263801C1 (ru) * 2004-04-26 2005-11-10 Южно-Уральский государственный университет Бескривошипный двигатель внутреннего сгорания
WO2016201529A1 (fr) * 2015-11-16 2016-12-22 Ksimetro -Tatiana Nikolova Ltd Dispositif pour convertir un mouvement de alternatif en un mouvement rotatif et inversement, dans des systèmes mécaniques à pistons axiaux
WO2018016973A1 (fr) * 2016-07-18 2018-01-25 Shepherd Inventor Limited Moteurs et compresseurs alternatifs

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19920564C2 (de) * 1999-05-05 2003-06-05 Bernd Pfalz Drehkolben-Verbrennungsmotor
RU2156871C1 (ru) * 1999-05-18 2000-09-27 Южно-Уральский государственный университет Бескривошипный двигатель внутреннего сгорания
DE10121036B4 (de) * 2001-04-28 2007-08-02 Pfalz, Thomas, Dipl.-Ing. Verdichtungsraum für einen Drehkolbenmotor
US20120192830A1 (en) * 2008-09-01 2012-08-02 Are Engines Limited Internal combustion rotary piston engine
AU2009287355B2 (en) * 2009-09-01 2015-03-26 Are Engines Limited Internal combustion rotary piston engine
RU2551717C1 (ru) * 2014-06-10 2015-05-27 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Южно-Уральский государственный университет" (национальный исследовательский университет) (ФГБОУ ВПО "ЮУрГУ" (НИУ)) Двухтактная бескривошипная поршневая тепловая машина-двигатель

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR372580A (fr) * 1906-12-15 1907-04-11 Ludwig Maurer Moteur à combustion rotatif
DE3320363A1 (de) * 1983-06-06 1984-12-06 Schweikert, Otfried, 8575 Kirchenthumbach Kurbelwellenlose viertaktverbrennungskraftmaschine
DE4027533A1 (de) * 1990-08-31 1992-03-05 Karl Sprenger Verbrennungsmotor mit zwangsweise drehendem kolben

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DE1143057B (de) * 1961-02-27 1963-01-31 Heinrich Franke Kolbenmaschine mit hin- und hergehendem und sich drehendem Kolben
DE1169195B (de) * 1962-03-22 1964-04-30 Heinrich Franke Kolbenmaschine mit hin- und hergehendem und sich drehendem Kolben
GB1146589A (en) * 1965-05-17 1969-03-26 Blackstone & Co Ltd Improvements in or relating to a fuel injection internal combustion piston engine
GB1204434A (en) * 1967-10-16 1970-09-09 Ustav Pro Vyzkum Motorovych Vo Improvements in or relating to otto engines having a combustion space of rotary or substantially rotary shape
US4026250A (en) * 1973-11-30 1977-05-31 Angelo Funiciello Explosion internal-combustion engines
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JPS52107419A (en) * 1976-03-06 1977-09-09 Shigeyuki Segi Four cycle low speed rolling piston engine
DD132990A1 (de) * 1977-08-12 1978-11-22 Egon Schlosser Drehhubkolben-brennkraftmotor
JPS5537531A (en) * 1978-09-06 1980-03-15 Isao Yamaguchi Internal combustion engine for piston to rotate without crankshaft
DE3326714A1 (de) * 1983-07-25 1985-02-07 John 8011 Zorneding Völker Verbrennungsmaschine
JPS62135618A (ja) * 1984-07-02 1987-06-18 Shigeyoshi Karasawa 同軸型内燃機関
DE3710824A1 (de) * 1987-04-01 1988-12-15 Erich Ortmeier Steuerscheibe zum steuern des gaswechsels bei kolben-motoren und -pumpen
GB2213549A (en) * 1987-12-10 1989-08-16 Kevin Wilcox Improvements in or relating to mechanisms for translating reciprocating motion into rotary motion and vice versa
DE3931702A1 (de) * 1989-09-22 1991-04-04 Rabbe Dr Med Nordstroem Brennkraftmaschine
DE4129804C2 (de) * 1991-09-07 2002-11-28 Porsche Ag Brennraum eines Hubkolbenmotors

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR372580A (fr) * 1906-12-15 1907-04-11 Ludwig Maurer Moteur à combustion rotatif
DE3320363A1 (de) * 1983-06-06 1984-12-06 Schweikert, Otfried, 8575 Kirchenthumbach Kurbelwellenlose viertaktverbrennungskraftmaschine
DE4027533A1 (de) * 1990-08-31 1992-03-05 Karl Sprenger Verbrennungsmotor mit zwangsweise drehendem kolben

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2246008C1 (ru) * 2003-08-04 2005-02-10 Южно-Уральский государственный университет Поршневая машина
RU2263801C1 (ru) * 2004-04-26 2005-11-10 Южно-Уральский государственный университет Бескривошипный двигатель внутреннего сгорания
WO2016201529A1 (fr) * 2015-11-16 2016-12-22 Ksimetro -Tatiana Nikolova Ltd Dispositif pour convertir un mouvement de alternatif en un mouvement rotatif et inversement, dans des systèmes mécaniques à pistons axiaux
WO2018016973A1 (fr) * 2016-07-18 2018-01-25 Shepherd Inventor Limited Moteurs et compresseurs alternatifs

Also Published As

Publication number Publication date
DE4326463A1 (de) 1995-02-09
DE59404261D1 (de) 1997-11-13
KR950006214A (ko) 1995-03-20
JP3677058B2 (ja) 2005-07-27
EP0637677B1 (fr) 1997-10-08
JPH07158464A (ja) 1995-06-20
KR100313162B1 (ko) 2001-12-28

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