WO2003102403A1 - Procede et dispositif pour transformer de l'energie thermique en energie cinetique - Google Patents

Procede et dispositif pour transformer de l'energie thermique en energie cinetique Download PDF

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Publication number
WO2003102403A1
WO2003102403A1 PCT/AT2003/000160 AT0300160W WO03102403A1 WO 2003102403 A1 WO2003102403 A1 WO 2003102403A1 AT 0300160 W AT0300160 W AT 0300160W WO 03102403 A1 WO03102403 A1 WO 03102403A1
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WO
WIPO (PCT)
Prior art keywords
space
work
working
regenerator
compression
Prior art date
Application number
PCT/AT2003/000160
Other languages
German (de)
English (en)
Inventor
Camillo Holecek
Klaus Engelhart
Original Assignee
Donauwind Erneuerbare Energiegewinnung Und Beteiligungs Gmbh & Co Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AT8432002A external-priority patent/AT500640B1/de
Application filed by Donauwind Erneuerbare Energiegewinnung Und Beteiligungs Gmbh & Co Kg filed Critical Donauwind Erneuerbare Energiegewinnung Und Beteiligungs Gmbh & Co Kg
Priority to MXPA04012100A priority Critical patent/MXPA04012100A/es
Priority to CA002488241A priority patent/CA2488241A1/fr
Priority to JP2004509264A priority patent/JP2005531708A/ja
Priority to EP03735135A priority patent/EP1509690B1/fr
Priority to AU2003237553A priority patent/AU2003237553A1/en
Priority to DE50301321T priority patent/DE50301321D1/de
Priority to AT03735135T priority patent/ATE306016T1/de
Publication of WO2003102403A1 publication Critical patent/WO2003102403A1/fr
Priority to US11/000,972 priority patent/US20050172624A1/en

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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

Definitions

  • the invention relates to a method for converting thermal energy into kinetic energy, wherein a working medium in at least one work space separated by a displacer undergoes the following state changes in the process:
  • Heat dissipation preferably isochoric heat dissipation, in the regenerator when pushed back into the compression space.
  • the invention also relates to a device for carrying out the method.
  • Energy cannot be "created” in the sense of newly created. Energy is available in the most varied forms in nature, but not every existing form of energy can be used equally well for human needs. For example, the energy in wood can be used very well 5 for heating purposes , but relatively poorly generate light or cold for the refrigerator etc.
  • the efficiency is also not better in other conversion processes, such as the conversion of chemical energy in petroleum to kinetic energy for driving cars, ships, trains or even airplanes, although the conversion chain is shorter.
  • the conversion process is implemented in the Stirling engine.
  • the Stirling engine can convert thermal energy directly into kinetic energy without the "detour" via steam.
  • the Stirling engine is the second oldest after the steam engine
  • Heat source increasingly interested. However, he has a lot of catching up to do in research and development to do a similar one "Maturity", such as today's steam engines or the petrol engine in a car.
  • thermodynamically favorable process control very high efficiencies are to be expected in principle - also in
  • Stirring motors Three different types are currently distinguished from the embodiment: the ⁇ type, the ⁇ type and the ⁇ type. These Stirling engine types differ primarily in the functional principle and the constructive implementation.
  • the ideal Stirling process corresponds to a Carnot process and therefore has a very high efficiency. In practice, however, an exact implementation, i.e. an exact replication of the ideal or better the theoretical process, is not possible. A number of design-related deviations have to be accepted with machines that have a negative impact on efficiency and power density.
  • crank drives with flywheels so that there is a reversal of movement at the dead centers, but not a brief standstill, as is the case with theory
  • the ⁇ machine uses two pistons in separate cylinders, one piston being located in the hot expansion space and the other piston in the cold compression space. Depending on the work step or crankshaft angle, both pistons are either working pistons and then displacers again.
  • the ß machine uses a piston and a displacer, whereby both the piston and the displacer are housed in the same cylinder.
  • Gearbox eg Rhomboid gear required.
  • the main disadvantage of the ß machines is, similar to that of the ⁇ motors, the dry running seals. Furthermore, the sequence of movements of the piston and displacer, which acts like a crank mechanism despite the complex gearbox and therefore has dead centers with reversal of movement but no real standstill. In the case of the ß - type too, the efficiency of the Stirling engines that are actually implemented is far from the efficiency of the ideal Stirling process.
  • double-acting stirring machines were also developed and manufactured, in particular of the ⁇ type.
  • the Franchot Stirling engine is known, for example. With this engine, a Stirling process takes place in the space above the two pistons, but also below the pistons, i.e. the two cylinders always carry out two different work cycles of two different Stirling processes with the top and bottom of the piston at the same time.
  • the two pistons and the associated cylinders limit four variable volumes, which can be viewed in pairs as two separate ⁇ machines.
  • the expansion piston and the compression piston must have a phase shift of approx. 90 °.
  • the efficiency of double-acting machines, such as the Franchot Stirling engine is no better than that of single-acting machines. The serious disadvantages and problems remain the same. Only the volume performance can be improved by the compactness.
  • Siemens Stirling engine which, with any number of cylinders, is the standard configuration of most powerful Stirling engines, such as the 4-95 ' mechanical from United Stirling with an output of approx. 52 kW.
  • Several designs have also been developed for this version, such as the arrangement of the cylinders in series, as "U”, as "V, in a square or in a circle.
  • U the arrangement of the cylinders in series
  • V the arrangement of the heater, regenerator and cooler was chosen in this way for the Siemens Stirling engine If the piston is sealed in the housing wall in the cold part, the main disadvantages of the machines remain.
  • the object of the invention is to provide a method of the type mentioned at the outset which on the one hand avoids the above disadvantages and on the other hand makes it possible for the first time to design a Stirling engine in such a way that its mode of operation can be brought much closer to the ideal Stirling process than before.
  • the object is achieved by the invention.
  • the method according to the invention is characterized in that the working medium flows back and forth between at least two closed working rooms, the working medium being passed between the working rooms via a working machine for the purpose of delivering useful work, the heat being taken up in front of the working machine and the heat being removed after the working machine and that the working medium is compressed in the work space after the heat has been dissipated and that the displacer then flows from one side through the regenerator to the other side of the displacer, the flow of the working medium being controlled by control elements, in particular valves, and each displacer being moved by a drive becomes.
  • control elements in particular valves
  • the higher efficiency is primarily due to the better approximation of the work process carried out to the theoretical cycle, which is achieved with the method according to the invention. Due to the temperature difference of the working medium in the two coupled work rooms and the resulting pressure differences, it flows into the cold work room and does work on a work machine. The state of equilibrium that arises is due to the fact that the majority of the working medium is located in the cold work area. In the subsequent isochoric regenerator cycle, with the addition of heat, the pressure difference builds up in a mirror image between the work rooms and is converted back into work via the work machine. This behavior is analogous to a resonant circuit and, with the Carnot efficiency remaining the same, enables a higher power density based on the amount of working medium than in the theoretical ideal Stirling process.
  • the working space is separated into a double-acting working space by the displacer.
  • the process can run faster since there are no overflow sections.
  • any seals against an otherwise necessary buffer space are not required.
  • each displacer is moved by its own drive.
  • a linear drive is used, which can be controlled independently of other movements, so that any number and any long downtimes can be achieved, for example, with the displacers.
  • the displacers of the coupled work spaces are moved via a rigid connection via a drive.
  • a simple structure for example, two hot or cold work spaces being coupled to one another. This allows a full immersion of the hot-hot
  • the work space is divided by the displacer into an expansion and a compression space, the working medium used for the useful work after leaving the expansion space via the regenerator assigned to this work space for the delivery of useful work via the
  • This version is the so-called "cold" motor.
  • the working machine can be simply constructed since it is not exposed to high temperature stresses.
  • the expansion of the cold working medium cooled by the regenerator can generate cold, which may possibly be introduced into the cold one
  • the efficiency and the power density are higher than with a ⁇ -type Stirling engine that flanged the working piston on the cold side.
  • the work space is divided by the displacer into an expansion and a compression space, the working medium used for the useful work after leaving the expansion space for the delivery of useful work, possibly via a heater, flowing over the work machine and then over the regenerator and optionally via a compressor, optionally via a further cooler, flows into the compression space of the coupled work space and then flows through the movement of the displacer from the compression side through the regenerator assigned to this work space into the expansion space of the same work space.
  • This version is the so-called "hot" engine.
  • the theoretical efficiency of this type is approximately that of the Carnot efficiency, the theoretical power density based on the amount of working medium is higher than that of the ideal Stirling process.
  • the work space is divided by the displacer into two expansion or two compression spaces, the working medium used for useful work flowing out of an expansion space via the regenerator assigned to this work space for delivering useful work via the work machine and after the machine flows into the compression space of the coupled work space and then flows through the movement of the displacer from the compression side through the regenerator assigned to this work space into the other expansion space of the work space.
  • this "low temperature" motor enables the use of low temperature for the generation of electricity as well as the generation of cold.
  • the heat is absorbed isobarically, in particular directly in front of the machine.
  • the main advantage can be seen in the fact that the temperature in the displacers is limited to the maximum regenerator temperature, the regenerator temperature being below the heater temperature.
  • the compression takes place by means of pressure compensation and / or by a compressor. If the compression is done solely by means of pressure equalization, a rotating machine, i.e. the compressor, is not required. The process will certainly be easier. With the integration of a compressor, an even higher efficiency is achieved.
  • the device according to the invention for carrying out the method is characterized in that at least two closed work spaces are provided, each work space being movable by a drive
  • Displacer is divided into two sections, one section having a heater and the other section having a cooler and each working space having a regenerator assigned to it, both sections being connected to the same Regenerator are connected and that at least one section of each work space is connected to a work machine, the section used for the subsequent delivery of the useful work is connected to the corresponding section of the other work space and that control elements, in particular valves, are provided for controlling the working medium.
  • a higher power density is achieved with the device according to the invention.
  • Another advantage of the device according to the invention is that the machine can be operated at a low clock frequency.
  • the workrooms do not have real piston seals and thus avoid the sealing problem that occurs particularly with larger piston volumes.
  • large-volume work rooms can be used that can be operated with a low clock frequency and discontinuously. This brings the ideal Stirling process closer.
  • the dead space is the volume that does not participate in the thermodynamic process and thus has a detrimental effect on the efficiency. It is created virtually by sinusoidal movement of the working pistons, and in real terms by the volume of the regenerator, the heating pipes, etc. flowed through by the working medium, etc.
  • Working machine, regenerator, heater and cooler results in a favorable ratio of dead space to working space and is many times lower than the machines currently being built.
  • the minimization of the driving forces is also advantageous. They are made up of the flow resistance of the isochoric pushing of the working medium inside the work area, the actuation of the valves and, if necessary, the compression of the working medium by a compressor.
  • One of the main components, the friction of the dry running piston seals together with the friction of the crank drive are eliminated.
  • At least one control element in particular a valve, is provided in the connections between the working machine and the individual sections. These serve to decouple the working and regenerator cycle.
  • a slot control could also be used instead of control via valves.
  • the working machine is a turbine, in particular an axial, radial or Tesla turbine.
  • a turbine in particular an axial, radial or Tesla turbine.
  • the working machine is a piston engine.
  • This version has the advantage that it is cheap and can be carried out with standard components.
  • the work machine is a screw motor.
  • the screw motor offers the advantage of eliminating the seals.
  • the drive for the displacer is a linear drive.
  • the linear drive ensures precisely controllable acceleration and deceleration of the displacer. As a result, discontinuous movement, which corresponds to the ideal thermodynamic process, is possible with little loss. All bushings and thus seals for the linkage or crank mechanism can be omitted. A possible quick power regulation is by changing the
  • Displacement clock frequency is possible immediately and does not have to be induced by changing the upper temperature. This enables very good control in the partial load range.
  • a heater is optionally connected upstream and / or downstream of the regenerator.
  • the heater supplies energy to the working medium, thus increasing the total receiving area in the hot area.
  • a special embodiment variant of the invention is characterized in that the work space is divided by the displacer into an expansion and a compression space, that the expansion space with the regenerator assigned to this work space and the regenerator with the Work machine is connected that the outflow side of the work machine is connected to the compression space of the coupled other work space and this compression space is connected via the regenerator assigned to this work space to the expansion space of the same work space, with a respective one between the regenerator and the inflow side of the work machine and the outflow side of the work machine and compression space Control element, in particular a valve, is provided.
  • a further special embodiment of the invention is characterized in that the working space is divided by the displacer into an expansion and a compression space, that the expansion space with the upstream side of the work machine and the work machine with its outflow side via the regenerator and possibly via a compressor with the Compression space of the coupled other work space is connected and this compression space is connected to the expansion space of the same work space via the regenerator assigned to this work space, a control element, in particular a valve, being provided between the expansion space and the inflow side of the working machine and the outlet side of the regenerator and compression space.
  • Another alternative embodiment of the invention is characterized in that the working space is divided into two expansion or two compression spaces by the displacer, that each expansion space has one
  • Regenerator is connected to the upstream side of the working machine and the downstream side of the working machine is connected to the compression space of the coupled other working space and this compression space is connected via a regenerator to the expansion space of the other working space, the regenerator connected downstream of the expansion space and the upstream side of the working machine and the outlet side the working machine and compression chamber each have a control element, in particular a valve, is provided.
  • the hot gases could also be expanded, analogously to the working principle of the hot engine.
  • a further embodiment of the invention is characterized in that a heater is arranged in the flow direction after the section which is connected to the working machine. As a result, higher temperatures are reached in front of the working machine, which leads to a better power yield.
  • the heater is arranged separately from the section, for example in the combustion chamber of a boiler.
  • the equipment parts used as a heater are loaded with the highest temperature, so that only these parts have to be dimensioned accordingly.
  • Fig. 4 shows an embodiment of the device with locally separate heaters
  • Fig. 5 is a diagram of the operation of a device.
  • the same parts or states are provided with the same reference symbols or the same component designations, the disclosures contained in the entire description being able to be applied analogously to the same parts or states with the same reference symbols or the same component designations.
  • the device using a working medium for converting thermal energy into kinetic energy has two closed working spaces 1, 2, each working space 1, 2 by a movable displacer 3, 4 in two sections, namely in an expansion and a compression space is divided.
  • Each displacer 3, 4 can be moved via a drive, in particular via a linear drive 5.
  • Each working space 1, 2 has a regenerator 6, 7 assigned to it. Both sections of the work space 1 and 2 are connected to this regenerator 6 and 7 via lines 8, 9 and 10, 11, respectively.
  • a section - in the illustrated case the expansion space - of each work space 1 or 2 is connected to a work machine 12.
  • the expansion space of the work space 1 used to deliver the useful work is connected after the work machine 12 to the corresponding section - that is to say the compression space - of the work space 2.
  • control elements in particular valves 13, are provided, which are arranged between the working machine 12 and the individual sections of the working space 1 or 2.
  • valves 13 instead of the valves 13, a slot control could also be used.
  • a turbine in particular an axial or radial turbine, can be used as the working machine 12.
  • a work machine 12 too a piston or screw motor possible.
  • the work machine 12 is connected to the generator 18 via a shaft 17.
  • the working medium flows back and forth between the two double-acting, closed working spaces 1, 2.
  • the working medium is guided between work rooms 1, 2 via a work machine 12.
  • the working medium then flows in the double-acting working space 1, 2 by means of the displacer 3 or 4 from one side through the regenerator 6 or 7 to the other side of the displacer 3 or 4, the flow of the working medium being controlled via the valves 13 and each displacer 3, 4 is moved via a drive 5.
  • the device also referred to as a 4-quadrant turbine, is shown as a "hot" motor according to FIG. 1, since the working medium in its highest temperature state is guided over the working machine 12.
  • the expansion space is on the upstream side of the Working machine 12 and working machine 12 are connected with their outflow side via the regenerator 6 or 7 and via a compressor 19 to the compression space of the coupled other working space 2. This compression space is above the latter
  • Regenerator 7 assigned to work space 2 is connected to the expansion space of the same work space 2, being between the expansion space and the inflow side
  • a valve 13 is provided for each of the work machine 12 and the outlet side of the regenerator 7 and the compression chamber.
  • the regenerator 6 or 7 consists of a heater 14, a coupling regenerator 15 and a cooler 16, the expansion space being connected to the heater 14 and the compression space being connected to the cooler 16.
  • the regenerator 6 or 7 is divided into individual sectors in the vertical direction. These sectors are sealed off from each other accordingly. In the inner sectors, the working medium flows from the working machine 12 to the compressor 19 and the outer sectors serve for the regenerator cycle of the working medium.
  • the expansion space is connected to the heater 14 of the regenerator 6 assigned to this work space 1 and the regenerator 6 to the work machine 12.
  • the outflow side of the work machine 12 is connected via the cooler 16 to the compression space of the coupled other work space 2 and this compression space is connected to the expansion space of the same work space 2 via the regenerator 7 assigned to this work space 2.
  • a valve 13 is provided between the regenerator 6 or 7 and the upstream side of the working machine 12 and the downstream side of the working machine 12 or compressor 19 and the compression chamber.
  • the 4-quadrant turbine is shown as a "cold" motor.
  • the working space 1, 2 is again divided into an expansion and a compression space by the displacer 3, 4.
  • the working medium used for the useful work flows after leaving the expansion space via the regenerator 6 assigned to this work space 1 for delivering useful work via the working machine 12 and after the working machine 12 into the compression space of the coupled one
  • the working medium then flows through the movement of the displacer 4 from the compression side through the regenerator 7 assigned to this working space 2 into the expansion space of the same working space 2.
  • the device is shown as a low-temperature motor.
  • the displacers 3, 4 are moved via a rigid connection 20 via a drive 5.
  • the work space 1, 2 is divided by the displacer 3, 4 into two expansion and two compression spaces.
  • Each expansion space of the work space 1 is connected via a regenerator 6, 7 to the inflow side of the work machine 12 and the outflow side of the work machine 12 to the compression space of the coupled other work space 2.
  • This compression space is connected via the regenerators 6 and 7 to the expansion space of the other work space 1, a valve 13 being provided between the regenerator 6 or 7 connected downstream of the expansion space and the inflow side of the work machine 12 and the outlet side of the work machine 12 and compression space ,
  • the working medium used for the useful work flows through the regenerator 6 or 7 assigned to this work space 1 for delivering useful work via the work machine 12 and after the work machine 12 into the compression space of the coupled work space 2. Then flows through the movement of the displacer 3 or 4 the working medium from the compression side through the regenerator 6 or 7 assigned to this working space 2 into the other expansion space of the working space 1.
  • the work space 2 it can be arranged in the ground, for example.
  • displacers 3 and 4 can also be designed as coupled membranes.
  • each work space 1, 2 is divided into an expansion space and a compression space by the displacer 3, 4.
  • Each displacer 3, 4 can be moved via a drive, in particular via a linear drive 5.
  • each displacer 3, 4 is mounted in a guide 22.
  • Each work space 1, 2 has one assigned to it Regenerator 6, 7 on. Both sections of the work space 1 and 2 are connected to this regenerator 6 and 7 via lines.
  • the expansion space is equipped with a reheater 21.
  • This intermediate heater 21 can be designed as a layered intermediate heater 21 or can be constructed in the form of plate packs.
  • the compression space is provided with a cooler 16.
  • the expansion space is optionally connected to a locally separated heater 14 via the reheater 21.
  • the heater 14 could be located in a boiler. Isobaric heating takes place in the heater 14.
  • the working medium flows from the heater 14 via the working machine 12.
  • the working machine 12, preferably a Tesla turbine, is coupled to a generator 18 by a direct shaft 17.
  • the working medium flows from the working machine 12 via the regenerator 7 and the cooler 16 into the compression space of the working space 2 and is isothermally compressed by the afterflow or a compressor.
  • the heat of compression is emitted in the cooler 16 of the work space 2. Due to the movement of the displacer 4 in the work space 2, the compressed working medium is transferred via the regenerator 7 and the reheater 21 into the expansion space of the work space 2. After leaving the expansion space of the working space 2, the working medium flows via the external heater 14, in which isobaric heat absorption takes place, to the working machine 12.
  • the working medium flows analogously from the working machine 12 into the compression space of the working space 1.
  • the working medium runs through a figure eight loop, with the working machine 12 being provided in the center.
  • the individual process steps are controlled by the corresponding valves (not shown).
  • the operation of the device with the valve control is described using a real example.
  • the working medium has a temperature To of 530 ° C. and a pressure Po of 30 bar.
  • the working space 2 with the displacer 4 there is a temperature Pu of 30 ° C. and a pressure Pu of 10 bar.
  • Valve 23 and 24 open in the forward direction due to the pressure difference between working chamber 1 and 2 generated in the displacement cycle.
  • the 530 ° C hot working medium now flows from the working space 1 via the valve 23 into the heater 14, where it is overheated to 630 ° C and then brought back to 530 ° C in the working machine 12 by the polytropic relaxation.
  • the working medium then passes through valve 24, the regenerator 7, where it is cooled to 60 ° C., the cooler 16, where it is cooled to 30 ° C., into the working space 2.
  • the valves 25 and 26 are in the blocking direction to the pressure difference and only open after the following regenerator cycle, ie at the next work cycle.
  • the regenerator cycle begins after the work cycle has equalized pressure between the two work rooms 1, 2; ie the same pressure prevails in the entire system (medium pressure).
  • the displacers 3, 4 now move to the opposite dead center positions and thereby shift the working medium through the regenerator-cooler unit to the other side of the displacer 3, 4.
  • the isochoric which is running off Heating or cooling of the working medium causes a change in pressure in the respective working space 1, 2; ie when pushing from cold to hot, pressure increases; when pushing from hot to cold, pressure decreases.
  • the regenerator cycle is hereby ended and the pressure difference is used for the subsequent work cycle.

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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)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

La présente invention concerne un procédé et un dispositif pour transformer de l'énergie thermique en énergie cinétique. Selon cette invention, un fluide moteur connaît des changements d'état dans au moins une chambre de travail divisée par un système de déplacement. Ce fluide moteur circule en va-et-vient entre au moins deux chambres de travail fermées (1, 2). Afin de fournir du travail utile, le fluide moteur est conduit entre les chambres de travail (1, 2) par une machine. Le fluide moteur circule ensuite dans une chambre de travail (1, 2), au moyen du système de déplacement (3, 4), d'un côté du système de déplacement (3, 4) à l'autre en traversant le régénérateur (6, 7). Le flux de fluide moteur est commandé par un organe de commande, notamment par des soupapes (13, 23, 24, 25, 26), et chaque système de déplacement est déplacé par un mécanisme de commande (5).
PCT/AT2003/000160 2002-06-03 2003-06-02 Procede et dispositif pour transformer de l'energie thermique en energie cinetique WO2003102403A1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
MXPA04012100A MXPA04012100A (es) 2002-06-03 2003-06-02 Metodo y dispositivo para la transformacion de energia termica en energia cinetica.
CA002488241A CA2488241A1 (fr) 2002-06-03 2003-06-02 Procede et dispositif pour transformer de l'energie thermique en energie cinetique
JP2004509264A JP2005531708A (ja) 2002-06-03 2003-06-02 熱エネルギーを運動エネルギーに変換する方法及び装置
EP03735135A EP1509690B1 (fr) 2002-06-03 2003-06-02 Procede et dispositif pour transformer de l'energie thermique en energie cinetique
AU2003237553A AU2003237553A1 (en) 2002-06-03 2003-06-02 Method and device for converting thermal energy into kinetic energy
DE50301321T DE50301321D1 (de) 2002-06-03 2003-06-02 Verfahren und einrichtung zur umwandlung von wärmeenergie in kinetische energie
AT03735135T ATE306016T1 (de) 2002-06-03 2003-06-02 Verfahren und einrichtung zur umwandlung von wärmeenergie in kinetische energie
US11/000,972 US20050172624A1 (en) 2002-06-03 2004-12-02 Method and device for converting thermal energy into kinetic energy

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT8432002A AT500640B1 (de) 2002-06-03 2002-06-03 Verfahren und einrichtung zur umwandlung von wärmeenergie in kinetische energie
ATA843/02 2002-06-03
ATA767/03 2003-05-19
AT7672003A AT500641B8 (de) 2002-06-03 2003-05-19 Verfahren und einrichtung zur umwandlung von wärmeenergie in kinetische energie

Related Child Applications (1)

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US11/000,972 Continuation US20050172624A1 (en) 2002-06-03 2004-12-02 Method and device for converting thermal energy into kinetic energy

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WO2003102403A1 true WO2003102403A1 (fr) 2003-12-11

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EP (1) EP1509690B1 (fr)
JP (1) JP2005531708A (fr)
CN (1) CN1659371A (fr)
AT (1) AT500641B8 (fr)
AU (1) AU2003237553A1 (fr)
CA (1) CA2488241A1 (fr)
DE (1) DE50301321D1 (fr)
DK (1) DK1509690T3 (fr)
MX (1) MXPA04012100A (fr)
WO (1) WO2003102403A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004088114A1 (fr) * 2003-04-01 2004-10-14 Tolarova, Simona Procede et dispositif pour transformer de l'energie thermique en energie mecanique
DE102007039517A1 (de) 2007-08-21 2009-02-26 Waechter-Spittler, Freiherr von, Hartmut Rotierende Hubkolbenmaschine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5317942B2 (ja) * 2009-12-07 2013-10-16 横浜製機株式会社 外燃式クローズドサイクル熱機関
JP5525371B2 (ja) * 2010-08-02 2014-06-18 横浜製機株式会社 外燃式クローズドサイクル熱機関
JP2014031726A (ja) * 2012-08-01 2014-02-20 Hidemi Kurita スターリングエンジンの駆動制御方法

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US3248870A (en) * 1960-07-29 1966-05-03 Morgenroth Henri Stirling cycle engine divided into a pressure generating unit and energy converting unit
US3678686A (en) * 1970-02-20 1972-07-25 Atomic Energy Commission Modified stirling cycle engine-compressor having a freely reciprocable displacer piston
US4012910A (en) * 1975-07-03 1977-03-22 Mark Schuman Thermally driven piston apparatus having an angled cylinder bypass directing fluid into a thermal lag heating chamber beyond the bypass

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Publication number Priority date Publication date Assignee Title
WO2004088114A1 (fr) * 2003-04-01 2004-10-14 Tolarova, Simona Procede et dispositif pour transformer de l'energie thermique en energie mecanique
EA010122B1 (ru) * 2003-04-01 2008-06-30 Эдуард Зележни Способ и устройство для преобразования тепловой энергии в механическую
KR100871734B1 (ko) * 2003-04-01 2008-12-03 에드워드 젤레즈니 열 에너지를 기계 에너지로 변환하는 방법 및 장치
AU2004225862B2 (en) * 2003-04-01 2010-04-22 Tolarova, Simona Method and device for converting heat energy into mechanical energy
NO337189B1 (no) * 2003-04-01 2016-02-08 Eduard Zelezny Metode og fremgangsmåte for omforming av varmeenergi til mekanisk energi
DE102007039517A1 (de) 2007-08-21 2009-02-26 Waechter-Spittler, Freiherr von, Hartmut Rotierende Hubkolbenmaschine
DE102007039517B4 (de) * 2007-08-21 2010-04-29 Waechter-Spittler, Freiherr von, Hartmut Rotierende Hubkolbenmaschine

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EP1509690B1 (fr) 2005-10-05
EP1509690A1 (fr) 2005-03-02
MXPA04012100A (es) 2005-09-21
JP2005531708A (ja) 2005-10-20
DK1509690T3 (da) 2006-01-30
AT500641B1 (de) 2006-08-15
AU2003237553A1 (en) 2003-12-19
AT500641B8 (de) 2007-02-15
AT500641A1 (de) 2006-02-15
DE50301321D1 (de) 2005-11-10
CA2488241A1 (fr) 2003-12-11
CN1659371A (zh) 2005-08-24

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