EP2273093B1 - Moteur thermique - Google Patents

Moteur thermique Download PDF

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Publication number
EP2273093B1
EP2273093B1 EP10164742.8A EP10164742A EP2273093B1 EP 2273093 B1 EP2273093 B1 EP 2273093B1 EP 10164742 A EP10164742 A EP 10164742A EP 2273093 B1 EP2273093 B1 EP 2273093B1
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EP
European Patent Office
Prior art keywords
piston
working
heat transmission
heat
chamber
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
EP10164742.8A
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German (de)
English (en)
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EP2273093A1 (fr
Inventor
Alexander Ivanovich Samarin
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Mona Intellectual Property Establishment
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Mona Intellectual Property Establishment
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Priority claimed from CH9062009A external-priority patent/CH701246A2/de
Application filed by Mona Intellectual Property Establishment filed Critical Mona Intellectual Property Establishment
Publication of EP2273093A1 publication Critical patent/EP2273093A1/fr
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Publication of EP2273093B1 publication Critical patent/EP2273093B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
    • F02G2243/30—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders
    • F02G2243/34—Regenerative displacers having their cylinders at right angle, e.g. "Robinson" engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2270/00—Constructional features
    • F02G2270/30—Displacer assemblies

Definitions

  • the present invention describes a heat transfer piston for a heat engine with a first working piston, and a heat engine with a driven flywheel or a crankshaft with a closed total interior, which can be filled with a working fluid and pressure sealed, comprising at least a first working chamber with a linearly movable first working piston at least one first heat transfer chamber having a linearly movable first heat transferring piston having a piston head and a piston pin, a first heat exchanger connected to the first working chamber and the first heat transfer chamber, and a first cooling device, wherein the first working piston and the first heat transferring piston are mechanically coupled together ,
  • Heat engines such as Stirling engines have long been known and offer a way to convert thermal energy into mechanical work, with a fairly high efficiency and long maintenance-free operating times are possible due to the design.
  • the document EP0850353 discloses heat engines in the form of a Stirling engine, wherein the working medium undergoes a cyclic process in which heat energy is partially converted into mechanical work.
  • the improvement of the operation of the heat engine EP0850353 was achieved by means for adjusting the piston stroke and the swashplate angle. These means are carried out electrically and cause the heat engine must be equipped with a motor and other components. Such heat engines are so complex and executed by a variety of components, making them more cumbersome to use and error prone.
  • the working medium passed through a plurality of thin tubes with a large total surface outside the chambers, wherein the heat energy was transferred.
  • the operating pressure had to be increased accordingly, resulting in a mechanical load of the plurality of tubes.
  • a reciprocating engine which has a piston with piston head having a plurality of ribs.
  • the ribs protrude in a linear up and down movement of the piston head in the working space, wherein the ribs protrude without contact between the wedges shaped walls of the working space.
  • the working medium is located between the wedge-shaped ribs of the piston head and the working space, wherein the heat flow between the ribs results by heat conduction.
  • the working piston described ensures during the lifting movement for a heat transmission, wherein the heat transmission is achieved by heat conduction during the lifting movement.
  • the ribs must be brought as close to each other as possible, resulting in narrow gaps and undesirable turbulence of the working medium. Also, it is according to the US4271669 so far only possible to use helium or argon gas as the working medium.
  • the present invention provides a novel way to exchange heat energy with low dead volume. Due to the reduced use of a plurality of thin tubes for heat exchange, the resulting torques on the pistons are smaller than in prior art motors.
  • the present invention has for its object to provide a mechanical heat engine in the manner of a Stirling engine, which allows use of air as the working medium, with a sufficiently high efficiency can be achieved, being dispensed with additional electrical controls and consumers.
  • the flywheel 21 may be connected, for example, to a device for utilizing the mechanical output energy or to an electrical generator for conversion into electrical energy.
  • a first heat transfer chamber 1, a second heat transfer chamber 2, a first working chamber 5 and a second working chamber 6 are arranged.
  • the particular hollow cylindrical shaped chambers 1, 2, 5, 6 each form an internal displacement.
  • the first heat transfer chamber 1 is connected outside the base flange 100 via a first heat exchanger 9 to the first working chamber 5.
  • the second heat transfer chamber 2 is connected outside the base flange 100 via a second heat exchanger 10 to the second working chamber 6.
  • a first cooling device 11 and a second cooling device 12 run. While the first heat transfer chamber 1 is connected to the second working chamber 6 via the first cooling device 11, the second heat transfer chamber 2 is connected to the first working chamber 5 via the second cooling device 12.
  • the heat transfer chambers 1, 2, the heat exchangers 9, 10, and the working chambers 5, 6 and the cooling devices 11, 12 form a coherent closed and gas-tight overall interior, which is filled with a working fluid.
  • the inventive heat engine 0 can be used with the use of air, but also of pure nitrogen or oxygen as the working medium.
  • the heat exchangers 9, 10 outside the base flange 100 and the cooling devices 11, 12 are designed in the form of a plurality of tubes. While the cooling devices 11, 12 within the base flange 100 are in thermal contact with a coolant, the heat exchangers 9, 10 are in thermal contact with an external heat source.
  • the heat exchangers 9, 10 are connected to a heat source during operation of the heat engine 0, so that the working medium located within the heat exchangers 9, 10 is heated.
  • the heat energy supplied from outside through the heat source heats the side of the heat engine 0, on which the heat exchangers 9, 10 are located, to a temperature T 2 > T 1 .
  • the type of heat source plays no role for the inventive heat engine and can be selected depending on the location of the heat engine and accessibility.
  • the cooling devices 11, 12 arranged inside the base flange 100 are cooled by means of a coolant to the temperature T 1 , so that the working medium circulating inside the cooling devices 11, 12 is cooled accordingly.
  • the coolant for example water, can be introduced into the base flange 100 through a coolant inlet 22 and a coolant outlet 23 and correspondingly exchanged.
  • the heat exchangers 9, 10 opposite side of the base flange 100 along the longitudinal axis L is a guide slot 101 attached.
  • the flywheel 21 is rotatably mounted.
  • a joint attachment 20 which carries a universal joint 19, releasably secured.
  • a swash plate 18 in the form of a cross with the universal joint 19 is cooperatively connected and tiltably mounted on the universal joint 19.
  • a receptacle for a coupling rod 25 is arranged in each case. The coupling rod 25 is thus pivotally connected to the swash plate 18 on a first side.
  • the four coupling rods 25 are connected on the base flange 100 facing the second side in each case with a first heat transfer piston 3, a second heat transfer piston 4, a first piston 7 and a second working piston 8.
  • the pistons 3,4,7,8 each have a piston pin and a piston head, wherein the piston pin is cooperatively connected to a coupling rod 25.
  • the first heat transferring piston 3 moves linearly into and out of the first heat transferring chamber 1 in turn.
  • the stationary swash plate 18 is tilted differently.
  • An attached to the swash plate 18 or integrally formed shaft 17 is mounted in an eccentric bore 240 in an eccentric disc 24.
  • the bearing of the shaft 17 takes place in a shaft bearing 241 within the eccentric bore 240.
  • the eccentric 24 is carried by deflection of the shaft 17 and set in rotation.
  • An integrally formed on the eccentric 24 drive shaft 103 is ball-bearing performed by the guide slot 101.
  • the bearing of the drive shaft 103 in the guide slot 101 takes place in a bearing 102, preferably a ball bearing 102.
  • the flywheel 21 mounted on the drive shaft 103 is correspondingly set in rotation by the piston movement. The deflection of the pistons 3,4,7,8 thus leads to a tilting movement of the swash plate 18, which leads by means of eccentric disc 24 in a rotational movement of the drive shaft 103 and the flywheel 21 attached thereto.
  • the shaft longitudinal axis 170 during the reciprocal strokes of the pistons 3,4,7,8 makes a precession about the longitudinal axis L and thus to the universal joint 19, wherein the flywheel 21 is rotated by the storage of the shaft 17.
  • the kinetic energy of the flywheel 21 leads to a continuous operation, wherein the tilting movement and the precession movements of the shaft 17 by mechanically performed work due to the temperature difference, is constantly maintained by means of the heat supply of the first and second heat exchanger 9, 10.
  • the inventive heat engine 0 has heat transfer chambers 1, 2 with significantly greater lengths and / or diameters and thus larger displacements, as the corresponding first and second working chambers 5, 6. Accordingly, the diameter and cross-sectional areas of the piston heads of the heat transfer pistons 3, 4 are greater than that Diameter and cross-sectional areas of the piston heads of the working piston 7, 8.
  • the piston head of the segmented and slotted first and second heat transfer pistons 3, 4 has a slightly smaller diameter than the inside diameter of the corresponding first and second heat transfer chambers 1, 2, so that a radial distance between heat transfer pistons 3, 4 and respective heat transfer chamber 1, 2 guaranteed is.
  • thermodynamic cycle Due to the arrangement described above, pressure and temperature of the working medium hardly change during the movement of the first and second working pistons 5, 6. Due to the size difference between the heat transfer chamber and the working chamber, the working medium does not pass through a classically known continuous thermodynamic cycle.
  • FIG. 6 is a central connecting line B, which runs along the centers of the first and second heat transfer chamber 1, 2, as well as through the longitudinal axis L.
  • Another connecting line C runs along the centers of the first and second working chamber 5, 6 and traverses the longitudinal axis L.
  • an angle ⁇ is clamped between the central connecting line B and the further connecting line C.
  • heat engines 0 can be adapted to specific requirements.
  • the arrangement of the pistons can be adjusted to achieve maximum performance or maximum efficiency.
  • thermodynamic cycle of the inventive heat engine 0 explained in four cycles. Due to the alternating arrangement of the working pistons 7, 8 and heat transfer pistons 3, 4 described above, during operation of the heat engine 0, either the working pistons 7, 8 or the heat transfer pistons are simultaneously deflected linearly in opposite directions.
  • FIGS. 8a to 7d show a section through all four chambers 1, 2, 5, 6 along the line D, which is shown folded into the plane of the paper.
  • the displacement, which are filled with working fluid under highest pressure, are marked with "+” - sign.
  • displacements are marked with "-" signs, in which the pressure is minimal.
  • Figure 7a shows the movement of the first working piston 7 and the second working piston 8, during the rotation of the eccentric disc 24 from 0 ° to 90 °.
  • the working medium in the first heat transfer chamber 1, in the first heat exchanger 9, in the upper hot region of the first working chamber 5 and in the lower cold region of the second working chamber 6 is under high pressure. Due to the segmentation of the first heat transferring piston 3, which was previously heated, the working medium could be additionally heated.
  • the first heat transferring piston 3 is at the cooled lower stop of the first heat transfer chamber 1, while the first working piston 7 is centrally deflected within the first working chamber 5.
  • the working medium can flow through the longitudinal slots 13 from the hot side of the heat transferring piston 3 in the direction of the first cooling device 11 into the lower cold region of the second
  • the second segmented heat transfer piston 4 is located at the beginning of the upper hot stop the second heat transfer chamber 2.
  • the working fluid can under low pressure from the working chamber 6 through the second heat exchanger 10 through the longitudinal slots 13 in the cold region of second heat transfer chamber 2 and the second cooling device 12 to flow into the cold region of the first working chamber 5.
  • the first working piston 7 is deflected to the lower cold stop and the second working piston 8 to the upper hot stop, wherein a relaxation of the working medium takes place.
  • first and second heat transfer pistons 3, 4 are moved linearly opposite. While the first heat transferring piston 3 is in an upward movement toward the first heat exchanger 9, the second heat transferring piston 4 moves toward the cold lower stopper of the second heat transferring chamber 2.
  • a low pressure prevails in the first heat transfer chamber 1, the first heat exchanger 9 and in the upper region of the first working chamber 5.
  • a high pressure of the working medium prevails accordingly in the second heat transfer chamber 2, the second heat exchanger 10 and the second working chamber 6. Due to these pressure differences, the first working piston is deflected in the direction of the first heat exchanger 9 and the second working piston in the direction of the second heat exchanger 10, wherein mechanical work is again performed.
  • a further deflection of the swash plate 18 from 270 ° to 360 ° leads the first heat transfer piston 3 in the direction of the cold stop and the second heat transfer piston 4 in the direction the hot stop, with the first working piston 7 at the hot stop and the second working piston 8 is at the cold stop.
  • the heat transfer pistons 3, 4 are able to absorb a lot of heat energy and deliver it to the working medium during the process, whereby precooling or preheating of the working medium takes place.
  • the amount of heat energy that can be absorbed by the heat transfer pistons 3, 4 is significantly greater than the work performed in the thermodynamic cycle.
  • FIG. 8 shows a pV diagram of the known ideal clockwise Stirling process, wherein 3 ⁇ 4 an isothermal expansion with the addition of heat 4 ⁇ 1 isochronous cooling 1 ⁇ 2 an isothermal compression with supplied volume change and 2 ⁇ 3 isochoric heating is a closed loop process and the convertible mechanical work represents the area under the cycles.
  • the pressure occurring in the first working chamber 5 and the second working chamber 6 during the compression of the working medium is about 6 to 7 MPa. Due to the use of air as the working medium, the requirements for the seal of the entire interior of the heat engine 0 are not particularly high.
  • the chambers 1, 2.5, 6 and pistons 3, 4, 7, 8 stainless steel is used, wherein solder joints are connected to a solder containing copper and magnesium.
  • the hollow design of the first and second working piston 7, 8. The necessary stability is given and due to minimized weight optimum power transmission is possible.
  • mineral fibers in particular basalt fibers, are introduced into the interior of the working pistons 7, 8.
  • the basalt fibers are in amorphous form and have a heat-protective effect, a mechanical reinforcing effect.
  • piston guides are formed, through which the piston pin guided by a bore stabilized guided linearly in the corresponding chambers are moved alternately.
  • the linear movement of the pistons 3,4,7,8 is converted into rotational movement of the swash plate 18, the eccentric disc 24 and ultimately the flywheel 21. Due to the type of coupling shown here, the pistons 3,4,7,8 can also be deflected by rotation of the flywheel 21.
  • the inventive heat engine 0 form. Accordingly, further heat transfer pistons and working piston would have to be provided, which are movably mounted in the additional chambers.
  • the mechanism for decoupling the linear piston movement and conversion into a rotational movement for driving the flywheel 21 must be matched to the number of pistons used in each case.
  • this first heat transferring piston 3 was installed in known commercial Stirling engines and heat engines according to a Stirling engine and experimented with it. In this case, known heat engines with only a first heat transfer chamber 1 were used. The efficiency of such Heat engines are not particularly high when using pistons according to the prior art. After installation of a segmented heat transfer piston 3 in a heat transfer chamber 1 and the use of air as a working medium good results could be achieved with a similar high efficiency, such as in standard operation, for example with helium gas.
  • crank drive 40 For transmitting the linear translational movement of the pistons 3, 4, 7, 8 into a rotational movement, the crank drive 40 explained below can be used. In addition to the drive of a flywheel 21 so that the drive of a crankshaft 400 is possible.
  • the crank mechanism 40 allows a good power transmission during operation of the heat engine 0, which by design is a simple juxtaposition of several heat engines 0 or more pairs of working piston 7, 8 and heat transfer pistons 3, 4 is possible.
  • the crank mechanism 40 includes the crankshaft 400, which is rotatably arranged in a stationary manner in a crank drive housing 41 on at least one crankshaft bearing 401.
  • At least one lifting element 403 is connected to the crankshaft 400 via a crankpin 4010, which is mounted eccentrically to the axis of rotation of the crankshaft 400 on the crankshaft 400 and thus can put the crankshaft 400 in a rotary motion.
  • the lifting element 403 has a transverse bar 4031, at the ends of which in each case a working piston 7 and a heat transferring piston 3 are arranged.
  • By means of joints 405 two double-jointed rods 404 are rotatably mounted via rolling bearings 407 at the ends of the crossbar 4031.
  • the pistons 3, 4, 7, 8 in turn mounted by roller bearings by means of fork couplings 406 movably attached to the double joint rods 404.
  • a pivot lever 402 is pivotally mounted in a pivot lever bearing 4022 on the crank drive housing 41 and movable on the projecting into the crank drive housing 41 side with a pivot rod 4021, preferably supported by roller bearings, connected to the lifting element 403.
  • the lifting elements 403 according to arrow mark A in FIG. 9b pivoted depending on the deflection of the adjacent suspended piston and out due to the eccentric attachment to the crank pin 4010 of the crankshaft 400 in the direction perpendicular to the crankshaft axis up and down.
  • the distance of the suspension of the piston 7 and the piston 3 an optimal power transmission to the crankshaft 400 due to the phase shift of the pistons can be achieved.
  • the pistons 3, 7 and the pistons 4, 8 are each fastened to the crankshaft 400 at different crank pins, so that a necessary phase shift of the piston pairs relative to each other can be achieved.
  • the pivot lever 402 By the coupling of the pivot rod 4021 on the lifting element 403, the pivot lever 402 is carried along with the up and down movement and pivoted about the pivot lever bearing 4022 accordingly.
  • the Pivot lever 402 is forked here, wherein each one of the piston or piston rods is guided by the forked portion of the pivot lever 402 feasible.
  • the phase shift of the movable piston can be adjusted.
  • the pivotal movement of the front pivot lever 402 is defined by the arrow mark D and the pivotal movement of the rear pivot lever 402 'is defined by the arrow mark E.
  • heat engines 0 can be linearly coupled to one another via the crank mechanism 40 on a crankshaft 400, so that as in FIG. 10a
  • two heat engines 0 may be coupled in a crankcase 41, as known from V-engines.
  • pistons 3, 7 of a first heat engine 0 and pistons 3 ', 7' of a second heat engine 0 are aligned differently via two adjacent transverse beams 4031 and 4031 ', but arranged on the same crank pin 4010.
  • the pistons 4, 8 and 4 ', 8' are arranged indirectly adjacent to the crankshaft 400 directly.
  • the lifting elements 403 must be arranged on the crankshaft 400 in accordance with the prevailing phase shift of the piston movement. Again, the lifting elements 403 each perform a combined pivoting movement and a movement perpendicular to the crankshaft axis.
  • crank mechanisms 40 each two heat engines 0, 0 'and 0 ", 0"' in each case a crankcase 41st are arranged.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (11)

  1. Moteur thermique (0) comportant un volant entraîné (21) ou un vilebrequin (400) avec un espace intérieur total fermé, qui peut être rempli par un milieu de travail et obturé de manière étanche à la pression, comprenant
    au moins une première chambre de travail (5) avec un premier piston de travail (7) mobile linéaire,
    au moins une première chambre de transmission de chaleur (1) avec un premier piston de transmission de chaleur (3) mobile linéaire, qui présente une tête de piston,
    un premier échangeur thermique (9) relié à la première chambre de travail (5) et à la première chambre de transmission de chaleur (1),
    ainsi qu'un premier dispositif de refroidissement (11),
    dans lequel le premier piston de travail (7) et le premier piston de transmission de chaleur (3) sont couplés mécaniquement l'un à l'autre,
    caractérisé en ce que
    le premier piston de transmission de chaleur (3) présente une tête de piston à configuration segmentée et/ou fendue avec une surface de contact agrandie par rapport au premier piston de travail (7) entre le premier piston de transmission de chaleur (3) et le milieu de travail qui l'entoure, moyennant quoi l'énergie thermique peut être libérée par le premier piston de transmission de chaleur (3) sur le milieu de travail, dans lequel l'air peut être employé comme milieu de travail.
  2. Moteur thermique (0) selon la revendication 1, caractérisé en ce que la tête de piston du premier piston de transmission de chaleur (3) présente une pluralité de fentes longitudinales (13), moyennant quoi un écoulement du milieu de travail à travers la tête de piston peut être obtenu au niveau du premier échangeur thermique (9) dans la direction d'un boulon de piston.
  3. Moteur thermique (0) selon la revendication 1, caractérisé en ce que la tête de piston du premier piston de transmission de chaleur (3) présente une pluralité de fentes transversales (14), qui complique la conduction thermique à travers le premier piston de transmission de chaleur (3) segmenté entre une partie chauffée (15) et une partie refroidie (16) de la première chambre de transmission de chaleur (1).
  4. Moteur thermique (0) selon la revendication 1, caractérisé en ce que les surfaces de section transversale de la première chambre de transmission de chaleur (1) ainsi que du premier piston de transmission de chaleur (3) sont plus grandes que les surfaces de section transversale de la première chambre de travail (5) ainsi que du premier piston de travail (7).
  5. Moteur thermique (0) selon une des revendications précédentes, caractérisé en ce que l'espace intérieur total fermé présente en outre au moins une deuxième chambre de travail (6) avec un deuxième piston de travail (8) mobile linéaire et au moins une deuxième chambre de transmission de chaleur (2) avec un deuxième piston de transmission de chaleur (4) mobile linéaire, dans lequel
    la première chambre de travail (5) et la deuxième chambre de transmission de chaleur (1) sont reliées de manière couplée par l'intermédiaire du premier échangeur thermique (9), ainsi que la deuxième chambre de travail (6) et la deuxième chambre de transmission de chaleur (2) par l'intermédiaire d'un deuxième échangeur thermique (10),
    le premier dispositif de refroidissement (11) est disposé entre la deuxième chambre de travail (6) et la première chambre de transmission de chaleur (1) et un deuxième dispositif de refroidissement (12) est disposé entre la première chambre de travail (5) et la deuxième chambre de transmission de chaleur (2),
    et les quatre pistons (3, 4, 7, 8) sont couplés mécaniquement les uns aux autres au moyen d'une plaque oscillante (18) et le deuxième piston de transmission de chaleur (4) présente une tête de piston à configuration segmentée et/ou fendue avec une surface de contact agrandie par rapport au deuxième piston de travail (8) entre le piston de transmission de chaleur (4) et le milieu de travail qui l'entoure, dès que l'énergie thermique peut être libérée du piston de transmission de chaleur (3, 4) au milieu de travail.
  6. Moteur thermique (0) selon la revendication 5, caractérisé en ce que les chambres (1, 2, 5, 6) et le premier et le deuxième dispositifs de refroidissement (11, 12) sont disposés dans une bride de base (100) et les dispositifs de refroidissement (11, 12) sont en contact thermique avec un milieu de refroidissement à l'intérieur de la bride de base (100).
  7. Moteur thermique (0) selon la revendication 5, caractérisé en ce que
    un angle α dans la plage de 90° à 140° est défini entre
    une ligne de liaison centrale (B), qui s'étend le long des centres de la première et la deuxième chambres de transmission de chaleur (1, 2) et à travers l'axe longitudinal (L) et
    une autre ligne de liaison (C), qui s'étend le long des centres de la première et la deuxième chambres de travail (5, 6) et à travers l'axe longitudinal (L).
  8. Moteur thermique (0) selon une des revendications précédentes, caractérisé en ce que respectivement une paire de premiers pistons de transmission de chaleur (3) et un premier piston de travail (7) sont fixés sur deux côtés opposés d'un élément de levage (403), dans lequel le vilebrequin (400) peut être déplacé en rotation en disposant l'élément de levage (403) sur un maneton (4010).
  9. Moteur thermique (0) selon la revendication 8, caractérisé en ce que l'élément de levage (403) est déplaçable de haut en bas au moyen d'un levier pivotant (402) autour d'un palier de levier pivotant (4022) sur le logement de vilebrequin (41) de manière basculante perpendiculairement à l'axe de vilebrequin.
  10. Moteur thermique (0) selon une des revendications précédentes, caractérisé en ce que le moteur thermique comprend au moins deux paires de chambres de transmission de chaleur (1, 2) et chambres de travail (5, 6) avec les pistons de transmission de chaleur (3, 4) et pistons de travail (7, 8) correspondants, dans lequel les pistons de transmission de chaleur présentent respectivement des têtes de piston segmentées.
  11. Moteur thermique (0) selon les revendications 9 et 10, caractérisé en ce que l'autre paire de deuxièmes pistons de transmission de chaleur (4) et deuxièmes pistons de travail (8) sont fixées sur deux côtés opposés d'un deuxième élément de levage (403'), dans lequel les deux éléments de levage (403, 403') sont disposés de manière basculante sur le vilebrequin (400) avec décalage de phase par les quatre pistons.
EP10164742.8A 2009-06-11 2010-06-02 Moteur thermique Not-in-force EP2273093B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH9062009A CH701246A2 (de) 2009-06-11 2009-06-11 Wärmekraftmaschine.
CH01608/09A CH701391B1 (de) 2009-06-11 2009-10-21 Wärmeübertragungskolben sowie Wärmekraftmaschine mit Wärmeübertragungskolben.

Publications (2)

Publication Number Publication Date
EP2273093A1 EP2273093A1 (fr) 2011-01-12
EP2273093B1 true EP2273093B1 (fr) 2013-08-28

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EP10164742.8A Not-in-force EP2273093B1 (fr) 2009-06-11 2010-06-02 Moteur thermique

Country Status (5)

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US (1) US8418454B2 (fr)
EP (1) EP2273093B1 (fr)
CH (1) CH701391B1 (fr)
EA (1) EA201000806A1 (fr)
HK (1) HK1152982A1 (fr)

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US20130031900A1 (en) * 2011-08-05 2013-02-07 Peter Andrew Nelson High Efficiency Heat Exchanger and Thermal Engine Pump
AT514226B1 (de) 2013-04-16 2015-02-15 Alfred Spiesberger Kolbenmaschine und Verfahren zu deren Betrieb
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EA201000806A1 (ru) 2011-02-28
EP2273093A1 (fr) 2011-01-12
US8418454B2 (en) 2013-04-16
CH701391B1 (de) 2011-01-14
HK1152982A1 (en) 2012-03-16
US20100313559A1 (en) 2010-12-16

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