EP1134381B1 - Kolbenmaschine - Google Patents

Kolbenmaschine Download PDF

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Publication number
EP1134381B1
EP1134381B1 EP00810219A EP00810219A EP1134381B1 EP 1134381 B1 EP1134381 B1 EP 1134381B1 EP 00810219 A EP00810219 A EP 00810219A EP 00810219 A EP00810219 A EP 00810219A EP 1134381 B1 EP1134381 B1 EP 1134381B1
Authority
EP
European Patent Office
Prior art keywords
shaft
lever
sealing plate
rollers
cylinder
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
EP00810219A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1134381A1 (de
Inventor
Gerhard Lehofer
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
Priority to EP00810219A priority Critical patent/EP1134381B1/de
Application filed by Individual filed Critical Individual
Priority to ES00810219T priority patent/ES2222886T3/es
Priority to DE50007126T priority patent/DE50007126D1/de
Priority to AT00810219T priority patent/ATE271650T1/de
Priority to CA002403178A priority patent/CA2403178C/en
Priority to AU2001229957A priority patent/AU2001229957B2/en
Priority to US10/221,100 priority patent/US6926248B2/en
Priority to JP2001567918A priority patent/JP3820371B2/ja
Priority to PCT/CH2001/000102 priority patent/WO2001069063A1/de
Priority to RU2002127593/06A priority patent/RU2254488C2/ru
Priority to CNB018065937A priority patent/CN1298976C/zh
Priority to AU2995701A priority patent/AU2995701A/xx
Publication of EP1134381A1 publication Critical patent/EP1134381A1/de
Application granted granted Critical
Publication of EP1134381B1 publication Critical patent/EP1134381B1/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
    • 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
    • F01B3/045—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 two or more curved surfaces, e.g. for two or more pistons in one cylinder
    • 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
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0005—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or 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
    • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis

Definitions

  • the present invention relates to a piston engine according to the preamble of claim 1.
  • Such piston machines are known.
  • reciprocating engines are known by the Otto or Diesel process, in which the linear reciprocation of the pistons via connecting rods, which with a Interacting crankshaft can be converted into a rotational movement.
  • the movement of the pistons is thus sinusoidal, the sequence of movements the piston cannot be influenced, an optimization of the combustion process, for example with regard to internal combustion engines Low pollutant combustion cannot be achieved.
  • a mechanism is shown by means of which the linear reciprocation of the piston over a cam is converted into a rotational movement of a shaft.
  • a cam disc can show the movement characteristics of the piston the desired process can be adjusted and optimized by the one shown here
  • the arrangement is subject to changing forces, in particular transverse forces, on the walls of the piston, which negatively affects the frictional relationships affects and thus increases the wear of the corresponding friction surfaces becomes.
  • the cam disc has a large difference between largest radius and smallest radius, whereby the rolling on it Roll when the shaft is essentially a constant angular velocity during one revolution of the shaft from a maximum speed slowed down a minimum speed and back to maximum speed is accelerated. It happens because of high-speed engines the inertia of the mass of the roll for sliding movements between the roll surface and cam surface, which also causes wear here becomes relatively large.
  • WO 88/05858 is an internal combustion engine removable, in which the pistons interact in pairs are arranged, and their linear back and forth movement on the piston attached rollers is transferred to a curve that has the shape of an annular surface has, which is provided with ridges and depressions, and with the Shaft is firmly connected.
  • the Speed fluctuation of the rollers in the use described above of cams is very large, significantly reduced.
  • cambered cylindrical rollers which means that the load capacity is very high drops sharply, and thereby the drilling movement that occur with cylindrical rollers would, can be avoided, remains an axial shift of the rollers in the slopes of the cam still exist, making a relative major wear and tear cannot be prevented.
  • a reaction force via the piston to the cylinder wall, which also creates a lot of friction here.
  • the object of the present invention is now one Piston engine to design so that the conversion of the linear reciprocation the piston get into a rotary motion of the shaft and vice versa can be that the friction and wear are as low as possible can be held. Furthermore, the structure of what is required for this Mechanism to be simple and inexpensive.
  • the path on which the rolls roll runs in one Hollow spherical shell the center of which is at the intersection of the pivot axis of the Swivel lever lies with the axis of rotation of the shaft.
  • the area of the web is in directed radially towards the center, the two roles have the Shape of a truncated cone, the tip of which is defined by the truncated cone defined cone is also in the center defined above.
  • Another advantageous embodiment of the invention consists in that the respective coupling rod is firmly connected to the corresponding piston and in the area in which it is articulated on the swivel lever in a linear guide is guided, which is aligned parallel to the cylinder axis is. This ensures optimal guidance of the pistons in the cylinder Friction between piston and cylinder is very low, which means that Wear and the efficiency is improved accordingly.
  • pivot lever is formed from a frame between the two parallel legs the shaft runs and the two legs each with are equipped with a trunnion through which the pivot axis is formed is and the trunnions are each stored in a bearing, which bearings each are held in a tab, which tabs are fixed to the housing are connected.
  • the bearings in the tabs with the Housing are firmly connected, adjustable, which makes the pivot lever becomes adjustable and the two rollers interact optimally with the web can.
  • the shaft is advantageously provided with means for transmitting the Rotational movement equipped on other transmission elements, for example to control the valves and to drive other units.
  • Another object of the invention is a valve device for opening and closing inlet and outlet openings in one Cylinder of a piston machine of the type described above create that is easy to set up and has little wear.
  • this object is achieved by the Claim 7 features listed.
  • a sealing plate which is hinged to a pivotable lever, and which in the closed state the respective opening in the cylinder covers, an optimal seal achieved without complex surfaces being ground on each other have to.
  • the sealing surface of the sealing plate is flat, the corresponding area of the cylinder surface that the respective opening surrounds can also be flat, these surfaces can in easily obtained.
  • valve device in that the sealing plate with respect to the pivot axis of the pivotable Lever is held so that the sealing surface of the sealing plate adjusts itself automatically with respect to the area surrounding the respective opening. This ensures optimal tightness.
  • valve device in that a counterweight is attached to the sealing plate, which is arranged such that during the opening and closing movement of the sealing plate this is essentially stationary with respect to the pivot lever. There there is practically no movement between the sealing plate and the swivel lever, it is not necessary to provide lubrication, which makes the structure is significantly simplified.
  • Another advantageous embodiment of the invention consists in that at least the sealing plate is made of a ceramic material is. This provides the required temperature resistance without cooling, a distortion and thermal stress in the sealing plate caused by the cooling could result, are therefore eliminated.
  • the piston engine designed as a heat engine as shown in FIG. 1 is shown schematically, comprises two groups 1 and 2 of four cylinders each 3, 4, 5 and 6. In each cylinder 3, 4, 5 and 6 there is a piston 7, 8, 9 or 10 arranged linearly. Each cylinder 3 to 6 is with one Valve device 11 equipped with which the inlet and outlet openings of the respective cylinder 3 to 6 can be opened and closed, which valve devices 11 will be described in detail later.
  • a coupling rod 12 is attached to each of the pistons 7, 8, 9 and 10.
  • the coupling rod 12, which is connected to the piston 7, which is in the cylinder 3 moves, is hinged to an end portion of a pivot lever 13.
  • the coupling rod 12 of the piston 8, which moves in the cylinder 4, is on the other end portion of the pivot lever 13 articulated.
  • the pivot lever 13 is pivotable centrally about a pivot axis 14, which is in the housing of the piston machine is held, as will be described later.
  • roller 15 arranged, the axes of rotation of which are perpendicular to each Stand pivot axis 14 of the pivot lever 13.
  • the rollers 15 roll on one Track 16, which is fixedly connected to a centrally arranged shaft 17, and which is provided with elevations and depressions, as described later becomes.
  • the coupling rod 12 of the piston 9 is in the cylinder 5 is movable back and forth at one end area of another Pivoted lever 18 articulated, while the coupling rod 12 of the piston 10, which can be moved back and forth in the cylinder 6, further at the other end region Swivel lever 18 is articulated.
  • This further pivot lever 18 is also Equipped with rollers 19 in the same way as the pivot lever 13.
  • the further pivot lever 18 is pivotable about the pivot axis 20, the axes of rotation the rollers 19 are also perpendicular to this pivot axis 20, which is also held on the housing.
  • the rollers 19 also roll on a track 24 that is fixed to the Wave 17 is connected.
  • this heat engine By rotating the shaft 17 is alternately by the Pistons 7 and 8, respectively, via the coupling rods 12 and the pivot lever 13 in the cylinders 3 and 4 can be moved back and forth via an intake duct 21 a gaseous medium is sucked in and compressed, the valve device 11 opens and closes the inlet and outlet openings in a controlled manner. The compressed gas is expelled into a high pressure chamber 22.
  • heat is supplied to the compressed gas, what, for example, by burning an appropriate fuel can take place in the high pressure chamber 22, represented by reference numerals 23.
  • the heat can also be supplied by a heat exchanger, which can be operated, for example, by an external heat source. This external heat source can be operated practically as desired.
  • This supply of heat expands the combustion gas and flows over it Valve device 11 into cylinders 5 and 6.
  • the gas expands, the pistons 9 and 10 alternate back and drive over the coupling rod 12, the other pivot lever 18, the rollers 19 and the web 24 Wave 17 on.
  • the expanded gas leaves cylinders 5 and 6 through the valve device 11 controlled outlet openings.
  • the combustion gas is again filled by slow Overflow and thus with little energy loss.
  • the valve devices 11 are in a known manner on the shaft 17 with the corresponding Drive mechanism controlled.
  • the gas in the high pressure chamber at a pressure of approx. 15 to 20 bar to a temperature of around 1500 Kelvin.
  • the stroke volume of the cylinders the heated gas is about 2.5 times the stroke volume the cylinders that suck in and compress the gas.
  • the temperature of the escaping gas is then about 470 Kelvin.
  • throttle disks 56 known per se (FIG. 2) can be used.
  • Appropriate Throttle disks are also in the area of the valve devices 11 the cylinders 5 and 6 used. This allows the filling of cylinders 3 and 4, which suck in and compress the gas. With not When completely filled, the compression pressure becomes smaller, resulting in a smaller one Pressure in the combustion chamber. So much is in the combustion chamber Heat is supplied in connection with the removal of the heated gas a constant pressure is set in cylinders 5 and 6. This pressure can measured and regulated by the supply of heat. With the appropriate Throttle disks can prevent gas from entering cylinders 5 and 6 can flow back.
  • FIG. 2 in which a group 1 of those described in Fig. 1 Piston engine is shown, it can be seen how the cylinders 3, 4, 5 and 6 and the shaft 17 are arranged in the housing 25. Also on the housing 25 is the pivot axis, not shown, mounted, as will be described later, around which the pivot lever 13 is pivotable. As already mentioned, they are Rollers 15 are each rotatably mounted on an end region of the pivot lever 13 and roll on the web 16.
  • This track 16 is designed as a kind of ring surface, which is formed by a hollow spherical shell 26.
  • This hollow spherical shell 26 has a flattened part 27 on which, for example, a gear 28 is fixed, and which is fixed to the shaft 17.
  • the center the hollow spherical shell 26 is located at the intersection of the pivot axis 14 of the pivot lever 13 with the axis of rotation 29 of the shaft 17. This has the in the hollow spherical shell 26 extending track 16, the elevations and depressions always the same distance from the center mentioned above.
  • the surface of the web 16 is always against that in the radial direction Center directed.
  • the rollers 15, which roll on the web 16, have the shape of a truncated cone, the tip of which is defined by the truncated cone Kegels is also in the center.
  • rollers 15 on the whole Length of the web 16 always optimal rolling conditions, it is thus created no drilling movement of the roll with respect to the web, an axial shift the roll is avoided, the wear is therefore very low.
  • steady Line contact between roller 15 and track 16 is also the load capacity large.
  • rollers 19 roll on the further pivot lever 18 are attached, on a correspondingly shaped track 24, whereby the pistons 9 and 10 (FIG. 1) are moved back and forth in the cylinders 5 and 6, so that a detailed description can be dispensed with. Also here is an optimal rolling process of the rollers 19 on the corresponding Lane 24 reached.
  • the coupling rods 12 are with the pistons 7 and 8, as shown in FIG. 2 is shown, firmly connected.
  • the coupling rods are in the same way 12 firmly connected to the pistons 9 and 10, which are in the cylinders 5 and 6 to move back and fourth. Therefore, in the area of the respective pivot lever 13 or 18, the coupling rod 12 each guided in a linear guide 30.
  • the connection between coupling rod 12 and pivot lever 13 or 18 is designed that the articulation point essentially against the pivot axis 14 or 20 of the pivot lever 13 or 18 to and from it is mounted so that the arc movement of the pivot lever 13 or 18 and the linear movement of the coupling rod 12 without an additional intermediate member can be compensated. This ensures that pistons 7, 8, 9 and 10 reached in the respective cylinders 3, 4, 5 and 6.
  • the shaft 17 can still drive further units, as shown in the lower part of FIG. 2, such as the control of the valve devices 11.
  • the piston surfaces the pistons 7, 8, 9 and 10 are provided with a heat-insulating layer 57 his. Accordingly, the high pressure chamber 22 (Fig. 1) with heat insulating Material lined.
  • the pivot lever 13 and the other Swivel lever 18 has the shape of a frame 31.
  • This frame 31 is formed from two legs 32 and 33, between which the shaft 17 extends.
  • a bearing journal 34 is fastened to each of the two legs 32 and 33, which engages in a bearing 35, which is each held in a tab 36, which tab 36 is attached to the housing. Through these two journals 34 thus the pivot axis 14 and 20 is formed.
  • the bearings 35, in which the journals of the pivot lever are mounted in a known manner be adjustable, for example by means of adjusting screws.
  • the two legs 32 and 33 are at the end area with a connecting web 37 connected to each other.
  • this connecting web 37 is a Bearing pin 38 attached, on which the roller 15 and 19 rotatable and against axial displacement is stored securely.
  • There are two on the bearing pin 38 Fastened webs 39 and 40, each provided with a longitudinal slot 41 are.
  • a bearing bush 42 is inserted into these longitudinal slots 41 so as to be longitudinally displaceable, in which an axle piece 43 is held.
  • This axis piece 43 is on both sides guided in the linear guides 30. Is held on the bearing bush 42 each the corresponding end of the coupling rod 12. Through this storage is the arcuate pivoting movement of the pivot lever 13 or 18 to the Linear movement of the coupling rod 12 can be compensated.
  • valve device 44 with which one Inlet or outlet opening 45 opened in a cylinder of a piston engine and can be locked.
  • This valve device 44 consists of a pivot axis 46 to which a lever 47 is attached.
  • the pivot axis 46 is pivotable and stationary with respect to the corresponding cylinder stored.
  • the pivotable lever 47 has a slot-shaped recess 48 provided, in which a web 49 comes to rest, which on the sealing plate 50th is attached.
  • the pivotable lever 47 and the web 49 are continuous Provide bore in which an axle piece 51 is inserted. in the the central region, the axle piece 51 has a spherical shape, on which the web 49 is mounted.
  • the sealing plate 50 which in the closed state the inlet or Closes outlet opening, is supported with its flat sealing surface 52 on the surface 53 of the cylinder surface surrounding the respective opening 45. Due to the possibility of pivoting the web 49 with respect to the axle piece 51, the sealing surface 52 of the sealing plate 50 adapts to the surface 53. This makes the seal optimal, the processing of the sealing surfaces is corresponding simple. This configuration also allows thermal expansion of the corresponding material.
  • the drive mechanism can one have known structure, the use of a pivot lever would also be conceivable with a roll that rolls on a track as it moves the Piston is used in the previously described piston machine.
  • a counterweight 54 is arranged on the web 49 on the sealing plate 50 opposite side.
  • This Counterweight 54 is arranged and designed so that when opening and Closing movement of the valve device, the sealing plate 50, the web 49 and the counterweight 54 practical because of the inertia with respect to the axle piece 51 not moved. It is therefore also not necessary for a lubrication device is provided with which the bearing of the sealing plate is lubricated should be. This simplifies the construction of this valve device.
  • the material of the Sealing plate 50, the web 49 and the counterweight 54 selected accordingly be, for example, it is advantageous to make this part from a ceramic To manufacture material.
  • valve device 44 which has essentially the same structure as the previously described but with the axle pin 51 no longer having a spherical shape Middle piece is provided and thus the sealing plate 50 with respect to this axis piece 51 is only pivotable about an axis and that the pivotability around the axis perpendicular to the axle piece 51 by a further bolt 55 is reached, around which the pivotable lever 47 about the pivot axis 46 is slightly pivotable.
  • This also optimally achieves that the flat sealing surface 52 of the sealing plate 50 adapts to the surface 53.
  • the counterweight 54 it is achieved that the sealing plate 50, the web 49 and the counterweight 54 with respect to the axes of rotation move as little as possible, so that there is no lubrication here either can be.
  • This valve device 44 can be used for piston machines of any kind are used, for example, heat engines, as previously described heat pumps, but also compressors etc.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Sealing Devices (AREA)
EP00810219A 2000-03-15 2000-03-15 Kolbenmaschine Expired - Lifetime EP1134381B1 (de)

Priority Applications (12)

Application Number Priority Date Filing Date Title
ES00810219T ES2222886T3 (es) 2000-03-15 2000-03-15 Maquina alternativa.
DE50007126T DE50007126D1 (de) 2000-03-15 2000-03-15 Kolbenmaschine
AT00810219T ATE271650T1 (de) 2000-03-15 2000-03-15 Kolbenmaschine
EP00810219A EP1134381B1 (de) 2000-03-15 2000-03-15 Kolbenmaschine
AU2001229957A AU2001229957B2 (en) 2000-03-15 2001-02-15 Piston engine
US10/221,100 US6926248B2 (en) 2000-03-15 2001-02-15 Piston engine
CA002403178A CA2403178C (en) 2000-03-15 2001-02-15 Piston engine
JP2001567918A JP3820371B2 (ja) 2000-03-15 2001-02-15 ピストン機関
PCT/CH2001/000102 WO2001069063A1 (de) 2000-03-15 2001-02-15 Kolbenmaschine
RU2002127593/06A RU2254488C2 (ru) 2000-03-15 2001-02-15 Поршневая машина
CNB018065937A CN1298976C (zh) 2000-03-15 2001-02-15 活塞式机械
AU2995701A AU2995701A (en) 2000-03-15 2001-02-15 Piston engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00810219A EP1134381B1 (de) 2000-03-15 2000-03-15 Kolbenmaschine

Publications (2)

Publication Number Publication Date
EP1134381A1 EP1134381A1 (de) 2001-09-19
EP1134381B1 true EP1134381B1 (de) 2004-07-21

Family

ID=8174601

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810219A Expired - Lifetime EP1134381B1 (de) 2000-03-15 2000-03-15 Kolbenmaschine

Country Status (11)

Country Link
US (1) US6926248B2 (es)
EP (1) EP1134381B1 (es)
JP (1) JP3820371B2 (es)
CN (1) CN1298976C (es)
AT (1) ATE271650T1 (es)
AU (2) AU2001229957B2 (es)
CA (1) CA2403178C (es)
DE (1) DE50007126D1 (es)
ES (1) ES2222886T3 (es)
RU (1) RU2254488C2 (es)
WO (1) WO2001069063A1 (es)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2905728B1 (fr) * 2006-09-11 2012-11-16 Frederic Thevenod Moteur hybride a recuperation de la chaleur d'echappement
EP2456955A2 (de) * 2009-07-24 2012-05-30 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Axialkolbenmotor, verfahren zum betrieb eines axialkolbenmotors sowie verfahren zur herstellung eines wärmeübertragers eines axialkolbenmotors
EP2462319A2 (de) * 2009-07-24 2012-06-13 GETAS Gesellschaft für thermodynamische Antriebssysteme mbH Axialkolbenmotor, verfahren zum betrieb eines axialkolbenmotors sowie verfahren zur herstellung eines wärmeübertragers eines axialkolbenmotors
RU2474770C2 (ru) * 2011-03-30 2013-02-10 Государственное научное учреждение Всероссийский научно-исследовательский технологический институт ремонта и эксплуатации машинно-тракторного парка Российской академии сельскохозяйственных наук (ГНУ ГОСНИТИ РОССЕЛЬХОЗАКАДЕМИИ) Теплообменная система, использующая тепловые насосы (варианты)
CN110886843A (zh) * 2019-12-04 2020-03-17 湖南湘钢工程技术有限公司 一种中、低压活塞式机械密封装置

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB106472A (en) * 1916-04-03 1918-03-20 Gnome Et Rhone Moteurs Improvements in Valve Actuating Mechanism for Internal Combustion Engines.
US1738512A (en) * 1927-12-09 1929-12-10 Andrews Albert Mechanical movement
US1810017A (en) * 1928-11-20 1931-06-16 Herbert W Houston Variable stroke cam-engine
US1770311A (en) * 1929-03-22 1930-07-08 Keith Motor Company Engine
US1777580A (en) * 1929-04-10 1930-10-07 Vapor Car Heating Co Inc End train-pipe valve
US1772531A (en) * 1929-06-29 1930-08-12 Calvin C Williams Mechanical movement
DE937742C (de) * 1952-12-16 1956-01-12 Theodor Niggemann Umlaufbrennkraftmaschine
US4103556A (en) * 1976-05-12 1978-08-01 Louis L. Niday Mechanical movement mechanism
US4185508A (en) * 1977-06-08 1980-01-29 Hardt Peter J Motion change transmission
SE451616B (sv) 1985-11-28 1987-10-19 Folke Mannerstedt Forbrenningsmotor av typ junkers, att arbeta i kombination med turbokompressor
IT1272806B (it) 1994-09-13 1997-06-30 Pomezia Srl "sistema di manovellismo per la trasformazione del moto rettilineo alternato in moto rotatorio, in particolare adatto per motori endotermici alternativi".
US5743220A (en) 1996-07-29 1998-04-28 Guarner-Lans; Enrique Eduardo Internal combustion engine with central chamber
DE29817540U1 (de) * 1998-10-01 1999-01-21 BALZAT Werkzeugmaschinenfabrik GmbH, 50170 Kerpen Kurvenmechanik für Hubkolbenmaschine

Also Published As

Publication number Publication date
US20030106506A1 (en) 2003-06-12
JP2003528242A (ja) 2003-09-24
RU2254488C2 (ru) 2005-06-20
WO2001069063A1 (de) 2001-09-20
JP3820371B2 (ja) 2006-09-13
CA2403178C (en) 2008-09-16
ATE271650T1 (de) 2004-08-15
ES2222886T3 (es) 2005-02-16
CN1298976C (zh) 2007-02-07
AU2995701A (en) 2001-09-24
CN1418285A (zh) 2003-05-14
AU2001229957B2 (en) 2004-07-08
DE50007126D1 (de) 2004-08-26
US6926248B2 (en) 2005-08-09
CA2403178A1 (en) 2001-09-20
EP1134381A1 (de) 2001-09-19

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