EP2205832B1 - Machine à pistons - Google Patents

Machine à pistons Download PDF

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Publication number
EP2205832B1
EP2205832B1 EP08844218.1A EP08844218A EP2205832B1 EP 2205832 B1 EP2205832 B1 EP 2205832B1 EP 08844218 A EP08844218 A EP 08844218A EP 2205832 B1 EP2205832 B1 EP 2205832B1
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EP
European Patent Office
Prior art keywords
piston
axis
pistons
revolution
housing
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.)
Not-in-force
Application number
EP08844218.1A
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German (de)
English (en)
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EP2205832A1 (fr
Inventor
Herbert Hüttlin
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.)
Huettlin Herbert
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Huettlin Herbert
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Publication of EP2205832A1 publication Critical patent/EP2205832A1/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
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/002—Oscillating-piston machines or engines the piston oscillating around a fixed axis
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines

Definitions

  • the invention relates to a piston engine according to the preamble of claim 1.
  • a piston engine according to the present invention can be used in particular as an internal combustion engine.
  • the use of the reciprocating engine as an internal combustion engine is shown as the preferred use.
  • other applications of a piston engine according to the present invention are possible, for example the use of the piston engine as a compressor.
  • a known piston engine is a rotary piston machine.
  • a total of four pistons are arranged, which rotate together about a housing-fixed axis of rotation.
  • the four pistons perform reciprocating motions, with two pistons forming a pair of pistons making reciprocal reciprocal reciprocations to alternately displace a working chamber defined between the end surfaces of the two pistons of the piston pair zoom in and out.
  • the known rotary piston machine on two working chambers, wherein the working chambers in the same direction to reduce and enlarge.
  • the four pistons are slidably mounted in a piston cage, which rotates together with the piston about the axis of rotation.
  • the reciprocating movements of the individual pistons are thereby derived from the rotation of the pistons about the axis of rotation by the pistons each having a guide member which runs in a control cam of a housing-fixed cam member, wherein the control cam has a corresponding wavy contouring to the out - And forthcoming movements of the piston from the rotation of the piston to derive about the axis of rotation.
  • the rotation of the piston cage can be transmitted to an output shaft, for example, to drive a vehicle.
  • rotary piston machines of comparable type are for example from the documents DE 10 2005 024 751 A1 or off WO 03/067033 A1 known.
  • the cam member is integrated directly into the inner wall of the housing, as in the case of WO 03/067033 A1 known rotary piston machine.
  • an internal combustion engine in which the reciprocating motion of one or more pistons is generated by a rotation of a cam having a cam and engaged by a pin connected to the respective piston.
  • a gas inlet and a gas outlet is present in the housing with respect to the axis of rotation at the front side, in which a tulip valve is arranged, whose control is derived via a cam via the rotation of the curved piece.
  • US 2 425 813 discloses a compressor for use on an internal combustion engine.
  • the compressor has a hollow rotatable shaft driven by a fan belt.
  • the shaft carries a sleeve in which the shaft rotates, the sleeve carrying disc-shaped pistons which are non-rotatable with respect to the sleeve, but can perform reciprocating movements along the axis thereof.
  • a radial piston high-pressure pump in particular as a fuel pump for injection systems of internal combustion engines, known.
  • This high-pressure pump has radially movable pump pistons in a pump head, whose reciprocating motions are generated by a rotatable cam ring surrounding the pump pistons, which has a correspondingly contoured cam track.
  • the invention has the object to improve a piston engine of the type mentioned.
  • the piston engine according to the invention is detached from the concept of rotary piston engines in that the reciprocating movements of the piston or pistons are not derived from a rotational movement of the piston or pistons about the axis of rotation, but from a rotation of the cam member about the axis of rotation the piston or pistons do not rotate with respect to the axis of rotation. Centrifugal forces with respect to the axis of rotation on the piston or pistons are thus excluded.
  • the at least one first piston performs its reciprocating movements in a fixed plane of rotation with respect to the axis of rotation, while in the known rotary piston machines, the plane of movement of the reciprocating movements of the individual pistons also rotates about the axis of rotation.
  • the piston engine according to the invention also manages with substantially fewer rotating parts than the known rotary piston machines, because the rotation of the piston or pistons is dispensed with, and only the lower-mass cam member executes a rotational movement in order to produce the reciprocating movements of the piston or pistons ,
  • the concept of the piston engine according to the invention is advantageously applied in an embodiment in which the at least one first piston faces a second piston which performs opposite reciprocating motions when the cam member is rotated relative to the first piston, the second piston having a second end surface. which faces the first end surface of the first piston, and the working chamber in which a working gas, in particular a fuel-air mixture, compressed, ignited and expanded, is located between the end surfaces.
  • This boxer principle known per se, for example, from the document mentioned above, in which the two pistons work against one another, has the advantage that, with a comparatively small stroke of the two pistons, a large breathing volume of the working chamber is achieved.
  • a gas inlet and a gas outlet are present, the gas inlet and the gas outlet by means of a rotary valve having an opening is released and closed, which rotates about the axis of rotation at the same speed as the cam member.
  • the piston engine according to the invention advantageously makes it possible for the gas inlet and the gas outlet to be provided in the immediate vicinity of the axis of rotation in the frontal part of the housing without the gas inlet and the gas outlet colliding with, for example, a rotating part.
  • an inlet and outlet valve is provided in a structurally advantageous particularly simple manner to a gas, such as a fuel-air mixture to admit into the working chamber, and a gas, such as combusted fuel air Mixture, to be discharged from the working chamber, wherein synchronized by the same rotational speed of the rotary valve as the rotational speed of the cam member, the timing of the gas inlet and the gas outlet with the reciprocating movement of the at least one first piston.
  • the second piston on a guide member which is in engagement with the control cam of the cam member.
  • the reciprocating movements of the two opposing pistons are independently derived from the rotation of the cam member about the axis of rotation. This has the advantage that no mechanical coupling between the two pistons has to be provided to produce the reciprocating movements of the second piston. In addition, only one control cam in the cam member is required for the first and second pistons.
  • the axis of rotation runs centrally through the working chamber.
  • This measure has the advantage that, in the case of using the piston engine according to the invention as an internal combustion engine, an ignition device for igniting the fuel-air mixture in the working chamber can be arranged on the front side in the housing and on the axis of rotation.
  • an arrangement of the ignition device on the axis of rotation for example, in the known rotary piston machine according to WO 2006/122658 A1 provided, however, there is the disadvantage that the ignition device is performed through a hole in the rotating piston cage, which can lead to sealing problems between the ignition device and the rotating piston cage.
  • the ignition device can be performed by the housing and thus by a fixed part and easily sealed.
  • the at least one first piston is slidably mounted in a piston cage, which is fixed relative to the housing.
  • the inclusion of the at least one first piston in a piston cage has the advantage that the piston may have a cylindrical shape, so that the first end surface the at least one first piston can be made circular, and the piston can be slidably mounted in a circular bore in the piston cage.
  • the piston may have a cylindrical shape, so that the first end surface the at least one first piston can be made circular, and the piston can be slidably mounted in a circular bore in the piston cage.
  • a shaft is in operative connection with the cam member, such that the rotation of the cam member is converted into a rotation of the shaft.
  • the tap of the rotational movement for example for driving a vehicle, is advantageously carried out here by the rotating cam member, so that the rotation of the cam member can be transmitted directly into a rotation of the shaft, which avoids complicated conversion gear.
  • the shaft is connected via a worm toothing with the cam member.
  • the shaft may advantageously be directly in engagement with the outside of the cam member, thereby saving further moving parts between the cam member and the shaft.
  • the shaft is preferably arranged perpendicular to the axis of rotation.
  • the rotation of the rotary valve from the rotation of the cam member via a transmission with a ratio of the speed of 1: 1 is derived.
  • Such a transmission can in turn be formed by a worm gear between the outer side of the cam member and a drive shaft for the rotary valve as in the case of the above-mentioned shaft.
  • a total of four pistons are arranged in the housing, of which the at least first and a second piston, a first piston pair and a third and a fourth piston form a second piston pair, wherein the second piston pair defines a second working chamber, which with the Working chamber defined by the first piston pair lies in a plane, wherein the reciprocating movements of the first and third piston are rectified, and wherein the reciprocating movements of the second and fourth pistons are rectified.
  • the piston engine according to the invention although this also has four pistons and two working chambers as the known rotary piston machine, however, increase and decrease the two working chambers in the piston engine according to the invention in contrast to the known rotary piston machine in opposite directions, ie if the one working chamber has its minimum volume , the other working chamber has its maximum volume, and vice versa.
  • the advantage here is, in particular in connection with the inventive concept that the pistons in the housing no longer rotate about the axis of rotation, in that on the one hand on the piston; As already mentioned above, no centrifugal forces act, and on the other hand, two pistons adjacent to one another via their rear surfaces opposite the end surfaces, ie the first and third or the second and fourth pistons, reciprocate together in the same direction. As a result, vibrations of the piston engine are reduced during operation.
  • the third and the fourth piston each have a guide member, wherein the two guide members engage in a further control cam of the cam member.
  • first and third pistons are connected to each other on their sides facing each other, and the second and fourth pistons are also connected to each other on their sides facing each other.
  • Fig. 1 to 5 is a provided with the general reference numeral 10 piston engine shown. Further details of the piston engine are in the 6 and 7 shown.
  • the piston engine 10 serves in the present embodiment as an internal combustion engine, for example for use in a motor vehicle.
  • the piston engine 10 has a housing 12, which is composed of a plurality of housing segments.
  • the housing 12 has a substantially spherical symmetry, but is not limited thereto.
  • the housing 12 has a first end-side housing segment 16 and this opposite a second end-side housing segment 18 and in the circumferential direction about the rotation axis 14 one or more housing segments 20 as the main components of the housing 12.
  • a total of four pistons are arranged, namely a first piston 22, a second piston 24, a third piston 26 and a fourth piston 28th
  • All four pistons 22 to 28 are arranged in a common plane, as in particular from Fig. 2 to 4 evident.
  • the first piston 22 has a first end surface 30, the second piston 24 has a second end surface 32, the third piston 26 has a third end surface 34 and the fourth piston 28 has a fourth end surface 36.
  • the first piston 22 and the second piston 24 define between their respective end surfaces 30 and 32 a first working chamber 38, and the third piston 26 and the fourth piston 28 define between their end surfaces 34 and 36 a second working chamber 40.
  • the pistons 22 to 28 carry out reciprocating movements in the housing 12, whereby these reciprocating movements take place here as pivoting movements about a pivot axis 41, which runs perpendicular to the abovementioned axis of rotation 14 and is stationary relative to the housing 12.
  • the pistons 22 to 28 are here correspondingly curved cylindrical. It is understood that the pistons 22 to 28 can perform in a modified embodiment, instead of pivoting movements and linear reciprocating movements perpendicular or oblique to the axis of rotation and then need not be correspondingly curved.
  • a cam member 42 is further arranged in the housing 12.
  • the cam member 42 is formed as circumferentially circumferentially closed around the rotation axis 14 and formed, and is located with respect to the pistons 22 to 28 viewed from the rotation axis 14 radially outward of the pistons 22 to 28 and approximately centrally between the front housing segments 16 and 18 and approximately in the center of the housing 12th
  • the cam member 42 is rotatably supported in the housing 12 about the rotation axis 14 by means of two ring bearings 44, 46.
  • the cam member 42 can thus rotate about the axis of rotation 14 to be understood as a geometric axis in the housing 12, wherein the rotation of the cam member 42 serves to generate the reciprocating movements of the pistons 22 to 28.
  • the cam member 42 has a first control cam 48 and a second control cam 50, wherein the two control cams 48, 50 are arranged axially adjacent to each other with respect to the axis of rotation and each extend fully around the axis of rotation 14.
  • control cam 48 With the control cam 48 is a guide member 52 which is connected to the first piston 22, and a guide member 54 which is connected to the second piston 24 in engagement.
  • control cam 50 With the control cam 50 is a guide member 56 which is connected to the third piston 26, and a guide member 58 which is connected to the fourth piston 28, in engagement.
  • the guide members 52 to 58 are formed as rollers and arranged on the respective end faces 30 to 36 facing away from the back of the piston 22 to 28.
  • the guide members 52 to 58 may be formed instead of by rollers as in the embodiment shown also by ball cups in the pistons 22 to 28 mounted balls, or by sliding shoes or other shaped rollers.
  • the pistons 22 to 28 are also slidably mounted in a piston cage 62, which is fixed with respect to the axis of rotation 14 in the housing 12, so is rotatably connected to the housing 12.
  • the piston cage 62 has for the first piston 22 and the second piston 24 has a circular bore 64 here, as well as for the third piston 26 and the fourth piston 28 is also a circular bore 66, so that the piston 22 and 24 in the bore 64 and the pistons 26 and 28 are slidably mounted in the bore 66.
  • the pistons 22 to 28, which are preferably circular in cross-section, can thus via circular seals (for example, seals 68 of the piston 22 in FIG Fig. 3 ) sealed in the holes 64 and 66, respectively, so that the working chambers 38 and 40 are sealed.
  • the peripheral walls of the bores 64 and 66 bound together with the end surfaces 30, 32 and 34, 36, the working chambers 38 and 40, so that the working chambers 38 and 40 have substantially the shape of a cylinder.
  • Each of the pistons 22 to 28 carries out its reciprocating movements between two end positions, wherein the movement of the pistons 22 to 28 always takes place in the same plane of motion, which for the four pistons 22 to 28 in Fig. 2 to 4 the drawing plane is.
  • the pistons 22 to 28 thus do not run around the axis of rotation 14 as in the known rotary piston machines.
  • the pistons 22 to 28, however, are always in a substantially central plane in the housing 12th
  • the first piston 22 and the second piston 24 perform mutually opposite movements, and the third piston 26 and the fourth piston 28 also perform mutually opposite movements.
  • the reciprocating movements of the first piston 22 are rectified to those of the third piston 26, and the reciprocating movements of the second piston 24 are rectified with those of the fourth piston 28.
  • Fig. 2 the first piston 22 and the second piston 24 are shown in their end position, which is referred to as top dead center (TDC), in which the pistons 22 and 24 have moved maximally toward one another and the working chamber 38 correspondingly has a minimum volume.
  • TDC top dead center
  • the pistons 26 and 28 are in an end position, referred to as bottom dead center (UT), in which the pistons 26 and 28 are maximally spaced apart and the working chamber 40 has correspondingly maximum volume.
  • UT bottom dead center
  • Fig. 3 shows an intermediate position of the pistons 22 and 24 or 26 and 28, in which the pistons 22 to 28 from their respective end position in Fig. 2 have moved by half in each case toward the other end position.
  • the transition from Fig. 2 to Fig. 3 is a 90 ° rotation of the cam member 42 around the rotation axis 14 based.
  • Fig. 4 shows after another 90 ° turn starting from Fig. 3 the too Fig. 2 reverse situation in which the pistons 22 and 24 have reached their UT position, while the pistons 26 and 28 have reached their TDC position.
  • the first piston 22 and the third piston 26 are connected to each other on their rear surfaces facing away from the end surfaces 30 and 34, preferably elastically, for example via a tension spring 68, and the second piston 24 and the fourth piston 28 are also preferably connected elastically, For example, via a tension spring 70.
  • the connection between the first piston 22 and the third piston 26 and the connection between the second piston 24 and the fourth piston 28 causes a mutual drag or entrainment effect between the first piston 22 and the third piston 26 or between the second piston 24 and the fourth piston 28, whereby the guide members 52 to 58 are securely held in contact with the control cam 48 and 50 of the cam member 42.
  • the elastic connection between the pistons 22 and 26 or 24 and 28 allows a slight elastic distance clearance between these pistons.
  • the cam member 42 In order to use the rotation of the cam member 42 in the operation of the piston engine 10 as a driving force, the cam member 42 is provided with a shaft 72 (FIG. Fig. 1 ) in operative connection. In Fig. 2 to 4 End portions 74, 76 of the shaft 72 are shown, to the For example, the drive train of a vehicle or units can be connected.
  • the cam member 42 has according to 6 and 7 on the outside a worm gear 78, and the shaft 72 has a corresponding external toothing, which meshes with the worm gear 78 of the cam member 42, such that upon rotation of the cam member 42 about the rotation axis 14, the shaft 72 is rotated about its longitudinal center axis.
  • the shaft 72 extends in this particularly simple embodiment, which requires only a toothing on these two parts and no other parts of a transmission for rotational transmission between the cam member 42 and the shaft 72, perpendicular to the axis of rotation 14th
  • the first working chamber 38 is associated with a gas inlet 80 and a gas outlet 82, wherein the gas inlet 80 and the gas outlet 82 are arranged in the immediate vicinity of the rotational axis 14 in the front-side housing segment 16.
  • the working chamber 40 is correspondingly associated with a gas inlet 84 and a gas outlet 86 in the housing segment 86.
  • a mixture of fresh air and fuel which is supplied via the fuel supply device 88, for example an injection nozzle, into the working chamber 38 can be introduced through the gas inlet 80.
  • the fuel can also be injected just before reaching the UT position.
  • the pistons then move back to the TDC position, then the mixture is compressed.
  • the piston 22, 24 can then ignite the mixture by means of an igniter 92, such as a spark plug, whereupon the pistons 22 and 24 are moved apart explosively, that is, the expansion stroke takes place.
  • the burnt mixture is then expelled via the gas outlet 82, as is known in a four-stroke engine.
  • a corresponding ignition device 94 is provided for the working chamber 40.
  • a rotary valve 96 is disposed in the housing 12, and for closing the gas inlet 84 and the gas outlet 86, a rotary valve 98 is disposed in the housing 12.
  • the two rotary valves 96 and 98 each have only one circumferentially limited about the axis of rotation 14 opening, wherein in Fig. 1 an opening 100 of the rotary valve 98 can be seen.
  • Both rotary valves 96 and 98 are rotatably mounted about the axis of rotation 14 in the housing 12, wherein the rotary valves 96 and 98 rotate at the same speed as the cam member 42 about the axis of rotation 14.
  • the rotation of the rotary valve 96 and 98 is derived from the rotation of the cam member 42 which is connected to the rotary valves 96 and 98 via a gear 102, which transmits the rotational speed of the cam member 42 1: 1 in the rotational speed of the rotary valve 96 and 98.
  • the gearbox 102 has a shaft 104 which meshes with the external toothing 78 of the cam member 42 via a toothed wheel 106 in order to set the shaft 104 in rotation about its longitudinal axis, the shaft 104 bearing end gears 108, 110 which mesh with gears 112, 114, which in turn mesh with external teeth on the rotary valves 96, 98.
  • the starting point of the description is the TDC position of the pistons 22 and 24 and, consequently, the UT position of the pistons 26 and 28.
  • the working chamber 38 thus has a minimum volume and the working chamber 40 has a maximum volume.
  • the first piston engine 10 are phase-shifted by 90 ° to each other, can be a total of a piston machine realize in each revolution of the then two cam members by 90 ° a working cycle of working (expanding) takes place, so that in this way a complete sequence of four Cycles of working (expanding) in a revolution of 360 ° as an 8-cylinder engine takes place.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Transmission Devices (AREA)

Claims (10)

  1. Machine à pistons, comprenant un boîtier (12), dans lequel est disposé au moins un premier piston (22), qui peut effectuer des mouvements de va-et-vient entre deux positions de fin de course, afin d'agrandir et de réduire de manière périodique une chambre de travail (38) adjacente à une première face d'extrémité (30) du premier piston (22) au moins au nombre de un, sachant que le premier piston (22) au moins au nombre de un présente au moins un organe de guidage (52), qui se trouve en prise avec une came de commande (48) réalisée au niveau d'un organe de came (42) disposé dans le boîtier (12), sachant que l'organe de came (42) s'étend de manière concentrique dans le boîtier (12) et en totalité tout autour d'un axe de rotation (14) solidaire du boîtier et est disposé de manière radiale à l'extérieur du piston (22) par rapport à l'axe de rotation (14), sachant qu'un deuxième piston (24) fait face au premier piston (22) au moins au nombre de un, lequel exécute des mouvements de va-et-vient opposés à ceux du premier piston (22), sachant que le deuxième piston (24) présente une deuxième face d'extrémité (32), qui est tournée vers la première face d'extrémité (30) du premier piston (22) et que la chambre de travail (38) se trouve entre les faces d'extrémité (30, 32), sachant que l'organe de came (42) est monté dans le boîtier (12) de manière à pouvoir tourner autour de l'axe de rotation (14), tandis que le premier piston (22) au moins au nombre de un et le deuxième piston (24) ne peuvent pas tourner autour de l'axe de rotation (14) de sorte que le premier piston (22) au moins au nombre de un et le deuxième piston (24) exécutent, lors de la rotation de l'organe de came (42) autour de l'axe de rotation (14), des mouvements de va-et-vient dans un plan de déplacement fixe par rapport à l'axe de rotation (14), caractérisée en ce qu'une entrée de gaz (80) et une sortie de gaz (82) sont présentes côté frontal dans le boîtier (12) par rapport à l'axe de rotation (14), sachant que l'entrée de gaz (80) et la sortie de gaz (82) sont ouvertes et fermées au moyen d'un coulisseau rotatif (96), qui présente une ouverture, lequel tourne autour de l'axe de rotation (14) à une vitesse de rotation identique à celle de l'organe de came (42).
  2. Machine à pistons selon la revendication 1, caractérisée en ce que le deuxième piston (24) présente un organe de guidage (54), qui se trouve en prise avec la came de commande (48) de l'organe de came (42).
  3. Machine à pistons selon la revendication 1 ou 2, caractérisée en ce que l'axe de rotation (14) s'étend au centre à travers la chambre de travail (38).
  4. Machine à pistons selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le premier piston (22) au moins au nombre de un est monté de manière à pouvoir glisser dans une cage à pistons (62), qui est immobile par rapport au boîtier (12).
  5. Machine à pistons selon l'une quelconque des revendications 1 à 4, caractérisée en ce qu'un arbre (72) est en liaison fonctionnelle avec l'organe de came (42) de telle manière que la rotation de l'organe de came (42) est convertie en une rotation de l'arbre (72).
  6. Machine à pistons selon la revendication 5, caractérisée en ce que l'arbre (72) est relié à l'organe de came (42) par l'intermédiaire d'une denture de vis sans fin (78).
  7. Machine à pistons selon l'une quelconque des revendications 1 à 6, caractérisée en ce que la rotation du coulisseau rotatif (96) est issue de la rotation de l'organe de came (42) par l'intermédiaire d'un engrenage (102) selon un rapport de multiplication de la vitesse de rotation de 1:1.
  8. Machine à pistons selon l'une quelconque des revendications 1 à 7, caractérisée en ce qu'au total quatre pistons (22, 24, 26, 28) sont disposés dans le boîtier (12), dont le premier et un deuxième piston (22, 24) forment une première paire de pistons et un troisième et quatrième piston (26, 28) forment une deuxième paire de pistons, sachant que la deuxième paire de pistons définit une deuxième chambre de travail (40), qui se trouve dans un plan avec la chambre de travail (38) définie par la première paire de pistons, et en ce que les mouvements de va-et-vient du premier piston et du troisième piston (22, 26) sont orientés dans le même sens et les mouvements de va-et-vient du deuxième piston et du quatrième piston (24, 28) sont orientés dans le même sens.
  9. Machine à pistons selon la revendication 8, caractérisée en ce que le troisième piston et le quatrième piston (26, 28) présentent respectivement un organe de guidage (56, 58), sachant que les deux organes de guidage (56, 58) viennent en prise avec une autre came de commande (58) de l'organe de came (42).
  10. Machine à pistons selon la revendication 8 ou 9, caractérisée en ce que le premier piston (22) et le troisième piston (26) sont reliés entre eux sur leur côté tourné l'un vers l'autre, et en ce que le deuxième piston (24) et le quatrième piston (28) sont reliés entre eux sur leur côté tourné l'un vers l'autre.
EP08844218.1A 2007-10-31 2008-10-29 Machine à pistons Not-in-force EP2205832B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007054321A DE102007054321A1 (de) 2007-10-31 2007-10-31 Kolbenmaschine
PCT/EP2008/009132 WO2009056295A1 (fr) 2007-10-31 2008-10-29 Machine à pistons

Publications (2)

Publication Number Publication Date
EP2205832A1 EP2205832A1 (fr) 2010-07-14
EP2205832B1 true EP2205832B1 (fr) 2015-05-27

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EP08844218.1A Not-in-force EP2205832B1 (fr) 2007-10-31 2008-10-29 Machine à pistons

Country Status (6)

Country Link
US (1) US8141475B2 (fr)
EP (1) EP2205832B1 (fr)
JP (1) JP5010742B2 (fr)
CN (1) CN101842554B (fr)
DE (1) DE102007054321A1 (fr)
WO (1) WO2009056295A1 (fr)

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DE102010022012A1 (de) * 2010-05-25 2011-12-01 Herbert Hüttlin Aggregat, insbesondere Hybridmotor, Stromgenerator oder Kompressor
DE102012111812B3 (de) * 2012-12-05 2013-12-12 Herbert Hüttlin Aggregat, insbesondere Verbrennungsmotor oder Kompressor
DE102015103734A1 (de) * 2015-03-13 2016-09-15 Innowatt GmbH Schwenkkolbenmaschine

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US5404849A (en) * 1991-12-11 1995-04-11 Fenton; John W. Spherical engine
AT402320B (de) * 1992-06-16 1997-04-25 Geiger Johann Ing Schwenkkolbenmotor
DE10115167C1 (de) * 2001-03-27 2002-12-12 Orange Gmbh Radialkolben-Hochdruckpumpe, insbesondere für Einspritzsysteme von Brennkraftmaschinen
CA2474449C (fr) 2002-02-06 2009-06-09 Herbert Huettlin Moteur a pistons oscillants
EP1856375B1 (fr) * 2005-02-25 2010-05-19 Herbert Hüttlin Moteur à pistons oscillants
DE102005024751B4 (de) 2005-02-25 2015-10-22 Herbert Hüttlin Schwenkkolbenmaschine
DE102005023721B3 (de) * 2005-05-17 2006-08-17 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine

Also Published As

Publication number Publication date
CN101842554A (zh) 2010-09-22
DE102007054321A1 (de) 2009-05-07
WO2009056295A1 (fr) 2009-05-07
US20100269688A1 (en) 2010-10-28
JP2011501032A (ja) 2011-01-06
US8141475B2 (en) 2012-03-27
CN101842554B (zh) 2013-01-30
EP2205832A1 (fr) 2010-07-14
JP5010742B2 (ja) 2012-08-29

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