WO2012019656A1 - Schrägscheibenmotor - Google Patents
Schrägscheibenmotor Download PDFInfo
- Publication number
- WO2012019656A1 WO2012019656A1 PCT/EP2010/070751 EP2010070751W WO2012019656A1 WO 2012019656 A1 WO2012019656 A1 WO 2012019656A1 EP 2010070751 W EP2010070751 W EP 2010070751W WO 2012019656 A1 WO2012019656 A1 WO 2012019656A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- swash plate
- piston
- piston rods
- output shaft
- swashplate
- Prior art date
Links
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
- F01B3/0002—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
- 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
- F01B3/0017—Component parts, details, e.g. sealings, lubrication
- F01B3/0023—Actuating or actuated elements
-
- 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
- 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 invention relates to a swash plate motor according to the preamble of patent claim 1.
- the invention relates to the field of engine construction and, in particular
- This engine has, among other things
- valve-shaped or valves having gas distribution or gas exchange mechanism
- a reciprocating mechanism that includes:
- cylindrical housing are arranged, an output shaft with bearings within the cylindrical motor housing,
- the aim of the invention is to provide a powerful, economical piston engine simplified construction with high reliability of the reciprocating mechanism.
- the motor according to the invention has at least one, preferably two cylinder groups, which are formed on one or opposite sides of a swash plate (rotor).
- the cylinder groups are arranged on the outside of the circumference on the end faces of the cylindrical motor housing parallel to the axis of the output shaft.
- Shaft bearings of the output shaft are mounted in the central areas of the end faces and designed as connected radial and thrust bearings.
- the swash plate Due to the oblique arrangement of the swash plate within the cylindrical housing, the swash plate has an elliptical shape.
- the raceways are shaped so as to ensure the best possible loading by the provided at the ends of the connecting rods or piston rods bearing. At least in places, at least to the
- Main crest elliptical swash plate the raceways are shaped such that the ends of the piston rods act vertically.
- the main vertexes are in conventional swash plate engines dead centers in which Forces produced by axially acting piston rods on the swash plate make no contribution to the rotation of the swash plate. These forces act in conventional swash plates at an angle or at an angle to the axis of rotation of the swash plate. Such forces are a particularly great burden for the bearings of the swash plate and the individual piston rods. According to the present invention, these forces act in the main vertices perpendicular to the raceway of the swash plate, and thus parallel to the axis of rotation of the swash plate.
- each of the raceways helically extends around the axis of rotation to ensure that as far as possible areas a vertical action by the bearings at the ends of the piston rods is possible.
- each track consists of two helical, each extending over 180 ° Operalaufbahnen, with one part runway in the clockwise direction and the other part runway runs counterclockwise.
- the raceways in the main apexes may be formed so as to ensure a perpendicular loading at these points through the ends of the piston rods which engage in the main apexes.
- the bearings are designed as rolling bearings, wherein the corresponding rolling bearing balls interact with the raceways of the swash plate.
- the raceways are preferably formed so that they from the piston rods over as large as possible Dreh Jardin be attacked or acted upon substantially vertically.
- the raceways have this, in addition to their helical shape in
- a trough-shaped cross-section which may be formed partially circular or elliptical in particular in adaptation to the roller bearing ball.
- the engine is intended for use in energy engineering as a piston engine.
- the two-stroke engine includes two sets of coaxial cylinders, one left and one right, disposed circumferentially on corresponding faces of the cylindrical motor housing, parallel to the axis of the output shaft located at the center of the housing, and through the elliptical race swash plate is provided, which are perpendicular to the piston rods, which are connected via sliding sleeves with the end faces of the cylindrical motor housing.
- the shaft bearings are arranged in the center of the round end faces of the housing; the pistons of the left and right cylinder groups are connected to each other by piston rods via joints and reciprocating clutches having rolling bearings that interact with the swash plate's elliptical races.
- the invention ensures the simplicity, reliability, compactness and economy of the engine.
- characterizing internal combustion engine are:
- a reciprocating mechanism including: a middle part of the cylindrical motor housing,
- a swashplate comprising:
- Piston rods are arranged
- the raceways are formed in the transverse direction with a curved profile, in particular a part-circular profile. This allows, with appropriate adaptation of the radii of curvature of the radii used bearing balls at the ends of the connecting rod or piston rods, a linear support of
- Rolling bearing balls are ensured on the raceways, whereby the wear is minimized.
- each cylinder piston assembly on a first side of the swashplate is associated with a cylinder-piston assembly on the second side of the swashplate, piston rods connected to the respective pistons engaging the swashplate being coupled together by means of a coupling mechanism spanning the swashplate , As a result, for example, with appropriate timing of the ignitions, be ensured that the swash plate is applied uniformly from both sides.
- each raceway along the circumference of the swash plate is modeled sinusoidally, so that the course of said central axial lines of the elliptical raceways differs sinusoidally from a helical shape. That is, the (usually constant) pitch of the screw is modeled sinusoidal.
- each of the partial tracks is expediently modeled in accordance with a half sine period.
- the coupling mechanism has a swashplate cross-housing, in which engage the respective piston rods, wherein at the ends of the Piston rods each bearing, in particular rolling bearings are provided by means of which the piston rods act on the swash plate.
- a spring mechanism between a bearing or ball bearing and the piston rod associated with this bearing is provided at least on one side of the coupling mechanism (in particular in the swashplate cross-housing).
- the respective clutch mechanisms are reciprocable within guides in the housing of the engine. With this measure, occurring lateral forces can be effectively absorbed.
- pistons are connected via joints with the respective pistons. This also makes it possible to optimally absorb any transverse forces which may occur.
- a particularly preferred embodiment is the subject of claim 10. It should be noted that the bearings of the output shaft are not necessarily disposed within the block.
- the piston rods in particular their ends formed with ball bearings, act on the elliptical raceways of the swash plate.
- the raceways of the swashplate have the same distance from the longitudinal axis of the shaft over their entire length, and / or the profile of the raceways corresponds to the profile of the bearings of the couplings and / or the longitudinal section extend the raceways perpendicular to the shaft and to the piston rods ,
- the respective cylinder groups are externally attached to the circumference of the circumference on a respective end face of the (cylindrical) engine. Furthermore, it proves to be particularly advantageous to use metal balls as the rolling bearing balls of the reciprocating coupling.
- Fig. 1 the transmission diagram of the longitudinal section of a preferred embodiment of the engine according to the invention is shown.
- FIG. 2 the view A of Figure 1 is shown.
- Fig. 3 the longitudinal section of the reciprocating mechanism is shown.
- Cylinder group shown in three projections.
- Fig. 9 the assembled piston rod of the left cylinder group is shown in three projections.
- Fig. 10 the compensator spring of the left piston rod is shown.
- Fig. 12 the firing order of the left cylinder group is shown.
- Fig. 13 the firing order of the right cylinder group is shown.
- FIG. 14 shows a view corresponding to FIG. 1 of a preferred embodiment of a swash plate motor according to the invention.
- FIG. 15 shows three projections or views of a preferred embodiment of a swashplate usable in accordance with the invention.
- Fig. 16 is a longitudinal section of a preferred embodiment of a swash plate used in the invention shown in longitudinal section, in this view particularly well the sinusoidal or helical shape of the raceways and their curved, here semicircular profile is visible.
- Fig. 17 (bottom) is a schematic side
- FIG. 18 shows a side view of a further preferred embodiment of a swash plate which can be used according to the invention.
- FIG. 19 shows an oblique view of one side of the swashplate according to FIG.
- the piston combustion engine engine consists of a reciprocating and a gas distribution mechanism as well as a cooling, lubricating, feeding and ignition system.
- the reciprocating mechanism is designed to convert the reciprocating motion of the pistons into rotary motion of the output shaft. It consists of movable and immovable components. To the immovable components belongs (see Figures 1, 2, 3, 4) of the engine block 2, to the moving components, the pistons 4, the joints 35 to articulated connections of the piston with their connecting rod or piston rods 6,7, the Piston rings 5, the piston rods 6.7 of the piston 4, the reciprocating clutches 8 each mutually associated piston rods 6, 7, the bearing 9 of the clutches 8, the output shaft 10 with the here sinusoidal modeled swash plate 11th
- the engine block is designed as a frame or housing (see Fig. 1, 2, 3, 4). In its interior, the assemblies and components of the reciprocating mechanism are mounted. In the housing guide grooves 41 are formed for the clutches 8.
- the housing is formed overall as a cylindrical housing 2, which has at the end faces caps 1, 3, on or on which outside the circumference of the left (12) and the right (13) cylinder group are arranged, and at the edges of the motor bearings 37 and 38.
- the caps of the housing or engine block are the bearings 19, 20 of the output shaft 10 and the sleeves 39th , 40 of the piston rods 6, 7.
- various mechanisms and devices are mounted on the block housing and in its interior.
- the piston rods 6, 7 serve to connect the pistons of the opposite cylinder groups 12, 13, which are arranged on the circumference outside of the end faces 1, 3 of the cylindrical housing 2, and they also ensure the transmission of forces from the pistons 4 via the joints 35 , the clutches 8 and the bearings 9 on the elliptical tracks 15, 16 of the sinusoidal modeled swash plate 11th
- the output shaft 10 (see Fig. 5, 1, 3) with the sinusoidal modeled swash plate 11 receives the forces from the elliptical tracks 15, 16 of the swash plate and transmits the torque generated thereon to the transmission of the transport and vice versa. It is arranged inside the cylindrical housing 2 of the engine.
- the reciprocating clutches 8 (see Fig. 11,
- the clutches 8 are arranged in the cylindrical housing 2 of the engine and kinematically connected to it by guide grooves 41 for the purpose of preventing the spinning of the clutches about the axes of the piston rods 6, 7.
- the bearings 9 (see Fig.
- the springs 42 are in particular between the detachable parts 43, 44 of the piston rods 7, 45 of the left Cylinder group 12 arranged.
- the joints 35 ensure a flexible or flexible connection of the piston 4 with the piston rods 6, 7. They exclude the possibility of a firm running of the cylinder walls by the pistons 4 in the course of starting and operating the engine and are as ball or cross connections of the Piston rods 6, 7 executed with the piston 4.
- the connected ball bearings 19, 20 are used as bearings of the output shaft 10, which in the end faces or end caps 1, 3 of the cylindrical housing 2 of the engine are arranged.
- the radial bearing 20 is provided for receiving the radial loads, and the thrust bearing 19 for receiving the axial loads.
- the gas distribution mechanism serves to draw the working mixture (fuel-air mixture with residual gases) into the cylinders of the engine and exhaust the exhaust gases from the cylinders and includes the output shaft 10 (see Fig. 5, 7, 1, 3) with the same Pressed sinusoidal modeled (swash plate) swash plate 11, the bearings 9 of the reciprocating clutch 8, the piston rods 6, 7, the joints 35, the pistons 4, the inlet slots 21, 32 and the outlet slots 22, 23, the are arranged in the cylinder sleeves, as well as the transfer channels 23, 31 of the fuel-air mixture.
- the ignition system (see Figures 1, 12, 13) is intended to ensure the pairwise ignition of the fuel-air mixture in the cylinders according to the firing order and mode of operation of the engine: lz, lz * - 2z, 2z * - 3z, 3z * - 4z, 4z *.
- the lubrication system of the piston groups is preferably realized according to the principle of two-stroke engines by a mixture of oil and gasoline in the ratio 1:25.
- the piston rods 6, 7, the bearings of the reciprocating clutches 8 and the bearings 19, 20 of the output shaft 10 are lubricated by partial immersion of the swash plate 11 in oil.
- the air cooling system (see Fig. 1, 2) is realized by means of impellers 24, 25 which are arranged on the output shaft 10 of the engine.
- the two-cycle engine of cylindrical shape operates as follows: "Suction-Compress" cycle
- the bearings 9 of the clutches 8 start on the elliptical tracks 15, 16 of the sinusoidal modeled swash plate 11 to move the reciprocating clutches 8 along the output shaft 10 together with the pistons 4 of the left (12) and the right cylinder group 13, wherein in the movement of the piston 4 of the first cylinder lz the right group 13 to top dead center ( 1, 12, 13), the first piston 4 of the first cylinder lz * of the left group 12 will move to the top dead center, and under the pistons 4 of the cylinders lz and lz *, a discharge takes place, whereby air passes through the suction cups 28, 29 and the inlet slots 21, 32 passes into the lower parts of the cylinder, simultaneously with the fuel supply by the injector system Movement of the piston to the top dead center in the cylinders lz, lz * takes place via the piston compression of the working mixture,
- FIG. 14 essentially corresponds to the view of FIG. 1, individual components being shown in greater detail.
- the raceways 15, 16 have the same distance Ri to the axis of rotation or central axis of the output shaft 10 in the projection perpendicular to the axis of rotation of the output shaft 10 over the entire length or over 360 °.
- the profile of the raceways corresponds exactly or substantially to the profile of the ball bearings 9 of the reciprocating clutches 8. This can also be seen in particular in FIG. 16.
- the illustrated construction of the swash plate makes it possible to considerably reduce the radial loads on the piston rods 6, 7, the sleeves or supports 39, 40 of the piston rods, the reciprocating couplings 8 and the guide grooves 41 (see in particular FIG. 14 ), as well as to minimize the specific pressure of the ball bearings on the raceways 15, 16 of the swash plate, this being accomplished by an enlargement of the contact surface of the ball bearing 9 with the profiled raceways 15, 16.
- This makes it possible, particularly with the simultaneous use of the supports 39, 40 of the piston rods 6, 7 and the guide grooves 41 of the reciprocating clutches 8, lateral or oblique loads on the piston of the engine essentially to exclude, and a simple, reliable and to create a sturdy building reciprocating mechanism.
- the preferred design of the raceways 15, 16 of the swashplate according to the invention will be explained again with reference to FIGS. 14 to 16 and 18 and 19.
- the main vertexes or main vertex areas of the cylindrical raceways 15, 16 are designated 15a, 15b and 16a, 16b in FIG.
- main vertex 16a has moved up, and main vertex 15b has traveled down.
- the two other major vertices are not designated in detail in this figure.
- the piston rods act on the raceways 15, 16 along parallels x to the center axis of the output shaft 10.
- the effective loading surfaces of the raceways are perpendicular to this.
- the effective urging surface is the tangent T which passes through the apex of the raceway 16.
- raceways are also formed between the main crests so that obliquely outward forces are minimized or avoided altogether.
- the raceways are shaped so that even in the areas between the main crests, the forces are directed substantially only along the raceway.
- raceways 15, 16 according to the embodiment of Fig. 18 a straight profile. Such a profile is particularly suitable for being acted upon by cylindrical bearings at the end of the respective piston rods.
- a possible (exemplary) construction of a suitable track 15 or 16 may be constructed on the basis of two ellipses with slightly different major axes and minor axes, respectively. This will be explained with reference to FIG. 19, reference being also made to FIG. 14.
- the raceway 15 has an inner boundary line 15 'and an outer boundary 15''on.
- the outer boundary 15 '' describes an ellipse having a major diameter 15 '''and a minor diameter 15''''.
- the inner boundary 15' has a major diameter 15 '''''and a minor diameter 15''''''.
- the major diameter and minor diameter of the inner boundary are each slightly smaller than the major diameter or minor diameter of the perimeter.,
- the respective ellipses described by outer perimeter 15 '' and inner perimeter 15 ', respectively have a slightly different angle with respect to This can be seen, for example, in FIG.
- FIG. 17 serves to illustrate a particularly advantageous embodiment of the swash plate according to the invention. If the swash plate were formed with a constant thickness, i. H. without the preferred sinusoidal modeled or curved raceways 15, 16, two opposing piston rods would be different in different angular positions
- the tracks are z. B. at the locations of the minor peaks so formed that the axial distance of the contact points or lines is always substantially equal.
- the example dimensions in Fig. 17 illustrate this.
- the points of contact of the two balls with respect to their axial distance from each other both in the main apex (12 o'clock position and 6 o'clock position) and in the secondary vertex (3 o'clock position or 9 o'clock position) the same (axial) distances to each other.
- the respective pitch of the two partial tracks which extend helically from the 12 o'clock position to the 6 o'clock position over a range of 180 degrees once clockwise and once counterclockwise, is not (as usual with a screw ) constant, but fluctuated sinusoidally (preferably over a sine half period) by one value.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010005809T DE112010005809A5 (de) | 2010-08-13 | 2010-12-27 | Schrägscheibenmotor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10172769 | 2010-08-13 | ||
EP10172769.1 | 2010-08-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2012019656A1 true WO2012019656A1 (de) | 2012-02-16 |
Family
ID=44041545
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2010/070751 WO2012019656A1 (de) | 2010-08-13 | 2010-12-27 | Schrägscheibenmotor |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112010005809A5 (de) |
WO (1) | WO2012019656A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012217045B3 (de) * | 2012-09-21 | 2014-06-12 | Formtech Technologies Gmbh | Zweitakt-Schrägscheibenmotor |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2076334A (en) * | 1934-04-16 | 1937-04-06 | Earl A Burns | Diesel engine |
DE2618556A1 (de) | 1976-04-28 | 1977-11-10 | Wilhelm Schmid | Hubscheibenbrennkraftmaschine |
US4149498A (en) * | 1976-11-19 | 1979-04-17 | Ferrell Arthur T | Internal combustion engine |
US4516536A (en) * | 1981-05-06 | 1985-05-14 | Williams Gerald J | Three cycle internal combustion engine |
AU629238B2 (en) * | 1988-08-29 | 1992-10-01 | Brian Leslie Powell | Crankless reciprocating two stroke internal combustion engin e |
US5799629A (en) * | 1993-08-27 | 1998-09-01 | Lowi, Jr.; Alvin | Adiabatic, two-stroke cycle engine having external piston rod alignment |
WO1998049437A1 (en) * | 1997-04-25 | 1998-11-05 | Sinus Holding As | Arrangement in a two cycle combustion engine with internal combustion |
WO2002023040A1 (en) * | 2000-09-15 | 2002-03-21 | National Oilwell Norway As | Arrangement at a piston engine and method of controlling the pistons |
GB2367328A (en) * | 2000-09-15 | 2002-04-03 | William Fairney | I.c. engine with opposed pistons and cam surfaces to transmit the piston movements |
US20090145377A1 (en) * | 2005-06-09 | 2009-06-11 | Thomas Engine Company, Llc | Piston Assembly For Barrel Engine |
-
2010
- 2010-12-27 WO PCT/EP2010/070751 patent/WO2012019656A1/de active Application Filing
- 2010-12-27 DE DE112010005809T patent/DE112010005809A5/de not_active Withdrawn
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2076334A (en) * | 1934-04-16 | 1937-04-06 | Earl A Burns | Diesel engine |
DE2618556A1 (de) | 1976-04-28 | 1977-11-10 | Wilhelm Schmid | Hubscheibenbrennkraftmaschine |
US4149498A (en) * | 1976-11-19 | 1979-04-17 | Ferrell Arthur T | Internal combustion engine |
US4516536A (en) * | 1981-05-06 | 1985-05-14 | Williams Gerald J | Three cycle internal combustion engine |
AU629238B2 (en) * | 1988-08-29 | 1992-10-01 | Brian Leslie Powell | Crankless reciprocating two stroke internal combustion engin e |
US5799629A (en) * | 1993-08-27 | 1998-09-01 | Lowi, Jr.; Alvin | Adiabatic, two-stroke cycle engine having external piston rod alignment |
WO1998049437A1 (en) * | 1997-04-25 | 1998-11-05 | Sinus Holding As | Arrangement in a two cycle combustion engine with internal combustion |
WO2002023040A1 (en) * | 2000-09-15 | 2002-03-21 | National Oilwell Norway As | Arrangement at a piston engine and method of controlling the pistons |
GB2367328A (en) * | 2000-09-15 | 2002-04-03 | William Fairney | I.c. engine with opposed pistons and cam surfaces to transmit the piston movements |
US20090145377A1 (en) * | 2005-06-09 | 2009-06-11 | Thomas Engine Company, Llc | Piston Assembly For Barrel Engine |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012217045B3 (de) * | 2012-09-21 | 2014-06-12 | Formtech Technologies Gmbh | Zweitakt-Schrägscheibenmotor |
Also Published As
Publication number | Publication date |
---|---|
DE112010005809A5 (de) | 2013-06-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE10145478B4 (de) | Hubkolbenmaschine mit umlaufendem Zylinder | |
DE3224482C2 (de) | Kolbenmaschine | |
DE102005010775B3 (de) | Schwenkkolbenmaschine | |
DE69019357T2 (de) | Drehkolbenmotor, -pumpe oder -kompressor, mit dreieckigem Zylinder. | |
DE3331636C2 (de) | Aggregat bestehend aus einer Hubkolbenmaschine und einem Getriebe | |
WO2012019656A1 (de) | Schrägscheibenmotor | |
DE19500854C2 (de) | Hubkolbenmaschine | |
DE2613992A1 (de) | Als verdichter fuer gase oder als brennkraftmaschine arbeitende maschine | |
DE202013009627U1 (de) | Koaxialkolben-Motor mit einem oder mehrerer Zylinder, mit einem jeweilig doppelt wirkenden Kolben | |
DE19812800A1 (de) | Gegenkolben-Brennkraftmaschine | |
DE10054523C2 (de) | Brennkraftmaschine | |
DE202012100865U1 (de) | Freikolben-Motorgenerator mit entgegengesetzt angeordneten Zylindern | |
DE3920620A1 (de) | Rotationsmaschine | |
EP2205832A1 (de) | Kolbenmaschine | |
DE102015101592B3 (de) | Motor mit an einer Doppelnocken-Kurvenscheibe geführtem Kolben | |
DE102010060814A1 (de) | Kolbenkraftmaschine | |
DE4118938C2 (de) | Rotationsschwingkolbenmotor | |
DE102009048648B4 (de) | Wechselhubmotor, Heißgasmotor | |
DE102012217045B3 (de) | Zweitakt-Schrägscheibenmotor | |
DE102016119720B4 (de) | Kurbelschlaufen-Motor | |
DE19923021B4 (de) | Kurbeltrieb und Kurbeltriebanordnung | |
EP0214255A1 (de) | Brennkraftmaschine. | |
DE10004759B4 (de) | Rotationsschwingkolbenmotor | |
EP2500515A1 (de) | Verbrennungsmotor | |
EP3904637A1 (de) | Motor mit kurbeltriebmechanismus |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 10805789 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120100058091 Country of ref document: DE Ref document number: 112010005809 Country of ref document: DE |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: R225 Ref document number: 112010005809 Country of ref document: DE Effective date: 20130606 |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 10805789 Country of ref document: EP Kind code of ref document: A1 |