EP1043491A1 - Verfahren und Vorrichtung zur Erzeugung und Durchgabe von mechanischer Arbeit einer Stirlingmaschine zu einem Verbraucherorgan - Google Patents

Verfahren und Vorrichtung zur Erzeugung und Durchgabe von mechanischer Arbeit einer Stirlingmaschine zu einem Verbraucherorgan Download PDF

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Publication number
EP1043491A1
EP1043491A1 EP99810286A EP99810286A EP1043491A1 EP 1043491 A1 EP1043491 A1 EP 1043491A1 EP 99810286 A EP99810286 A EP 99810286A EP 99810286 A EP99810286 A EP 99810286A EP 1043491 A1 EP1043491 A1 EP 1043491A1
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EP
European Patent Office
Prior art keywords
piston
energy
resonator
hot
volume
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.)
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Application number
EP99810286A
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English (en)
French (fr)
Inventor
Jean-Pierre Budliger
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Individual
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Individual
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Priority to EP99810286A priority Critical patent/EP1043491A1/de
Priority to AT00912325T priority patent/ATE301773T1/de
Priority to DE60021863T priority patent/DE60021863T2/de
Priority to PCT/CH2000/000199 priority patent/WO2000061936A1/fr
Priority to EP00912325A priority patent/EP1165955B1/de
Publication of EP1043491A1 publication Critical patent/EP1043491A1/de
Priority to US09/972,263 priority patent/US6510689B2/en
Withdrawn legal-status Critical Current

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    • 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
    • F02G1/0435—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 the engine being of the free piston type
    • 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
    • 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
    • F02G2243/40—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders with free displacers
    • 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
    • F02G2243/50—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes
    • 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
    • F02G2243/50—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes
    • F02G2243/52—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes acoustic
    • 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
    • F02G2243/50—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes
    • F02G2243/54—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders having resonance tubes thermo-acoustic
    • 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
    • F02G2270/45—Piston rods
    • 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
    • F02G2280/00—Output delivery
    • F02G2280/10—Linear generators

Definitions

  • the present invention relates to a method for generate and transmit mechanical energy from a piston transfer of a Stirling engine to a consumer body energy, the transfer piston being mounted in a cylinder, that gas is periodically moved between a hot room and a cold room at the ends respective of this cylinder by passing it through a hot exchanger connected to a hot source, a regenerator and a cold exchanger connected to a cold source and we exercise an elastic restoring force on this transfer piston.
  • This invention also relates to a device for the implementation of this process.
  • the object of the present invention is to remedy the less in part to the aforementioned drawbacks.
  • this invention firstly relates to a process for producing and transmitting mechanical energy a transfer piston from a Stirling engine to an organ energy consumer as defined in claim 1.
  • the subject of this invention is also a device for the implementation of this method, according to claim 9.
  • the device illustrated in FIG. 1 comprises an elongated casing 1 formed by two cylindrical compartments 2, 3, assembled on an intermediate element 4, playing the role of frame.
  • the cylindrical compartment 2 comprises a cylindrical housing 5, constituting a working volume, in which a transfer piston 6 is mounted free to move in the longitudinal axis of the cylindrical housing 5.
  • the volume located between the piston 6 and the outer end of the housing 5 is that which is in contact with a hot exchanger 7 connected to a hot source (not shown) and constitutes the hot chamber or expansion volume V E of the Stirling engine, while at the at the other end of this cylindrical housing 5, there is a volume in contact with a cold exchanger 8 connected to a cold source (not shown), which constitutes the cold room or compression volume V C of the Stirling engine.
  • a regenerator 9 is placed between the hot 7 and cold 8 exchangers.
  • the end of the piston 6 adjacent to the cold room V C comprises a piston rod 6a, engaged in a closed volume 10 filled with gas and which constitutes an elastic return member of the transfer piston 6.
  • the cylindrical compartment 3 contains a volume in which a moving element of an alternator, in this example, inductor 11 consisting of a cylindrical element carrying permanent magnets, is attached to the periphery of a annular member 12, the internal edge of which is integral with a elastic suspension member 14, constituted by springs annular plates, the peripheral edges of which are fixed to the frame 4 and whose internal edges are integral a rod 17, one end of which is fixed to the rod 6a of the piston 6.
  • the internal edge of a second suspension member elastic 15 similar to member 14, is attached to the other end of rod 17, while its periphery is fixed to a support 13 secured to the frame 4.
  • the armature of the alternator is formed by windings 16.
  • Rods 6a and 17 cross the bottom of the closed volume 10 formed in the intermediate element 4 with a clearance included between 30 and 50 ⁇ m. Such a game is perfectly acceptable both in terms of manufacturing tolerances and the influence of gas leaks on energy efficiency and on the restoring force of the compressed gas in the volume closed 10.
  • This resonator has the role of replacing the second piston, which according to the process which is the subject of the invention, no longer serves to produce energy, all the energy being produced by the transfer piston 6, as will be explained below. -afterwards, but serves to amplify the pressure wave and to ensure an appropriate phase shift between the displacement of the transfer piston 6 and the pressure variations p in the working volume.
  • this tubular resonator 18 advantageously ends in a volume of Helmholtz 19.
  • the part of this resonator which is in the Helmholtz volume ends with a flare 18a.
  • the transfer piston 6 then plays the double role of transferring the gas between the hot room V E and the cold room V C and of producing all the driving energy transmitted to the inductor 11, provided that certain conditions, including let's go talk now, be met.
  • Figure 5 shows the variation of the X position of the piston 6 and the variation of pressure as a function of time (or angle ⁇ ). This representation corresponds schematically to that of figure 4.
  • the pressure decreases, gas is largely in the chamber hot or relaxing; when it increases, the gas is found mainly in the cold or compression room.
  • the displacement X of the piston 6 precedes the pressure variation p.
  • Figure 6 shows the variation in the amount of WG gas in Stirling working volume and pressure p in this volume.
  • FIG. 4 shows that p X must be opposite to X. If p X becomes zero, or oriented in the direction of X, no energy is transmitted to the tubular resonator 18 to compensate for the losses by friction. Therefore, the pressure wave cannot be maintained and the machine stops working.
  • the ratio of the sections a P / a must be between 0.4 and 0.6, preferably between 0.45 and 0.55.
  • FIG. 7 gives an example of the efficiency of the cycle ⁇ C calculated as a function of the work provided by cycle E, with the wall temperature T H of the hot chamber V E and the amplitude X of the piston 6 as a parameter.
  • the temperature of the cold exchanger T is equal to 50 ° C.
  • the net efficiency of the engine can be obtained by multiplying the efficiency of the cycle by the efficiency of the heating means and that of the alternator.
  • the engine should always operate at hot chamber temperatures between 600 ° and 700 ° C.
  • the temperature T H of the hot chamber V E mainly influences the power, to a lesser extent the efficiency. But by lowering the temperature to 400-500 ° C, the efficiency and power decrease sharply, mainly because, under these conditions, the pressure variation p X induced by the movement of the piston becomes small and finally disappears completely.
  • the lateral rigidity of the mechanical suspension of the piston 6 is ensured by flat springs 14, 15 of the type described in “Recent developments in cryocoolers” Ray Radebaugh 19 TH International Congress of Réfrigeration 1995 Proceedings Volume IIIb, allows it to oscillate perfectly along the longitudinal axis of the cylindrical housing 5, so that the pneumatic bearings to center it are not necessary.
  • the piston 6 can be centered with great precision. Due to the pneumatic suspension of this piston 6 and therefore the low forces required for the elastic suspension elements constituted by the annular flat springs 14 and 15, the amplitude of the piston 6 can be increased from 25% to 50% by relation to the device described in “Free-piston Stirling design features” Neill W. Lane et al. 8 TH International Stirling Engine Conference and Exhibition May 27-30, 1997 Ancona. This increase in amplitude leading to an increase in linear speeds, makes it possible to reduce the dimensions of the alternator. Under unchanged operating conditions, similar amounts of energy can be reached.
  • the rigidity of the suspension of the piston 6 and by Therefore, the phase angle can be adjusted by adjusting gas pressure in the working volume of the Stirling.
  • the natural frequency of tubular resonator 18 can be adjusted by varying the composition of the gas, i.e. its molecular weight.
  • the engine is then started by first bringing the temperature of the gas in the hot chamber V E to a value T H at which the pressure of the working gas becomes independent of the position of the piston.
  • the engine load is thus reduced to a minimum (losses by internal friction of the engine and by periodic flow through the exchangers and the regenerator).
  • the temperature T H will be adjusted to the optimum working temperature.
  • Power control is very easy.
  • the amplitude of the piston 6 and therefore the power of the engine is adjusted, by adjusting the braking force exerted by the alternator to a determined value.
  • the output power varies in proportion to the amplitude of the piston 6.
  • the heating power of the burner (not shown) intended to heat the gas in the chamber hot V E is continuously adjusted to maintain the desired temperature T H in this hot or expansion chamber V E.
  • the amplitude of the piston can therefore be precisely controlled. It is therefore not necessary to provide additional dead volume to avoid shocks in the event of accidental overshoot of the piston. It is only necessary to prevent the piston from exceeding a maximum amplitude in the event of a breakdown in the electrical network with which the alternator is associated.
  • the natural frequency of the tubular resonator 18 only depends on the average temperature of the working gas therein. This temperature can be precisely adjusted to the desired value by means of an additional heat exchanger 20 arranged in the Helmholtz volume 19 and by controlling the thermal energy extracted. This allows the phase angle of the resonator to be adjusted relative to the other variables of the system.
  • the heat extraction from the tubular resonator 18 makes it possible to reduce the cooling of the gas located in the cold room V C , which makes it possible to simplify the cold exchanger of the Stirling engine. Its dead volume and / or its losses by pneumatic friction can be reduced, bringing an additional advantage to the device which is the subject of the present invention.
  • the working gas pressure in the Stirling volume varies cyclically depending on the oscillation of the pressure wave in the tubular resonator 18.
  • the parameters of the tubular resonator 18, an example of which follows, must be adjusted to those of the Stirling process to ensure that these components interact properly, that is to say that the wave is driven by the cycle Stirling and that the resulting pressure variations maintain the periodicity of the Stirling cycle.
  • the tubular resonator 18 can have a total length including the Helmholtz volume 19, of approximately 1.6 m, and a temperature T of 40 ° C.
  • the average pressure p 0 of the gas is 4 MPa and the resonant frequency of this resonator is 50 Hz.
  • a gas heavier than helium is advantageously used, such as a mixture of helium and argon or carbon dioxide with a molecular mass M of the gas of 14 kg / kmol.
  • the minimum section S min of the tubular resonator 18 is, in this example, 4.75 cm 2 .
  • the volume of gas V S of the Stirling 2 engine is 1000 cm 3
  • that of the volume of Helmholtz 19 is 6000 cm 3 .
  • the tubular resonator can be extended inside the Helmholtz volume 19. Given that this portion of the tube is only exposed to limited pressure differences, wall may be thin and can thus easily be put in conical form 18a preventing the formation of steep front pressure waves.
  • FIG. 8 An example of sectional distribution along the tube 18 of the resonator is represented on the diagram of the figure 8.
  • the left end of the diagram corresponds to the end of tube 18 in communication with the Stirling compartment 2, while the right end corresponds to that which communicates with the volume Helmholtz 19.
  • the diagram in Figure 9 shows nine values to regular intervals of the gas flow velocity in the tube 18, related to the speed of sound (therefore to the number of Mach) depending on the position in the tube 18 during a cycle, while the diagram in Figure 10 shows the distribution of gas pressure relative to pressure average during the same cycle.
  • the pressure diagram clearly shows that with a appropriate sizing of the tube, no shock occurs at the resonance conditions of the tube 18.
  • the pressure in the Stirling 2 volume varies sinusoidally.
  • the pressure and speed are orthogonal functions, that is to say that if the pressure takes an extreme value, the gas speed is null and vice versa.
  • the range indicated takes account of the fact that, on the one hand, the coefficient of friction of the gas in unsteady state can differ from that of an established regime, on the other hand that the roughness of the tubes is known only approximately.
  • the volumes of gas displaced are of the order of a hundred cm 3 .
  • the cylindrical parts of the tube typically have diameters of 2.5 to 4cm. It can easily be curved or rolled up so that the entire device occupies as small a volume as possible.
  • the device illustrated in FIG. 3 can have a height of 90cm, a width of 60cm and a depth of 40cm.
  • FIG. 11 Such a variant is illustrated by FIG. 11 in which we find the end of the free piston 6a 'and that of the resonance tube 18' communicating with the cold room or compression volume V C.
  • a rod 21 is slidably mounted in a cylindrical guide 22 by linear bearings 31.
  • a connecting rod 23 is articulated by one end to the rod 21 and by its other end, to a crankshaft 24 integral with the axis of a rotary electric generator for example, mounted in an enclosure 25.
  • the tubular resonator 18 can be constituted by two identical tubular elements arranged in opposition diametral with respect to said transfer piston 6, of so as to balance the lateral forces exerted on this piston 6.
  • the tubular resonator 18 can be connected to the expansion volume V E or hot compartment of the Stirling engine, provided that the whole of this tube is kept warm and does not constitute a heat sink.
  • FIG. 12 illustrates a variant in which the Helmhotz volume 19 is placed in a heating enclosure 26, heated by gaseous, liquid or solid fuels, while the tube 18 is surrounded by thermal insulation 27. It is thus possible to increase the temperature of the working gas contained in the tubular resonator 18 above the temperature T H of this gas in the expansion volume V E. The tubular resonator 18, 19 can then partially or entirely replace the hot exchanger 7 of the Stirling engine.
  • the tubular resonator 18, 19 has a considerable exchange surface and thanks to the periodic flow which is established therein, the internal heat transfer is favorable. Due to the standing wave regime which is established in this resonator, its internal volume is not part of the dead volume of the Stirling engine.
  • FIG. 13 shows a configuration in which the tubular resonator 18 is integrated in a high temperature solar collector.
  • the tube 18 of the resonator is put in the form of a helix, placed inside a cylindrical or conical cavity 28.
  • One end of this tubular resonator 18 opens in a volume of Helmholtz 19, while that the other end communicates with the expansion volume V E of the Stirling engine, of which the transfer piston 6 and the regenerator 9 have been shown.
  • FIG. 14 very schematically illustrates the combination of four Stirling engines of which it has been shown that the respective compression volumes V CA , V CB , V CC , V CD , alternatively the respective expansion volumes V EA , V EB , V EC , V ED , connected by four tubular resonators T 1 , T 2 , T 3 and T 4 .
  • the whole forms a closed loop, each volume V being connected to two other neighboring volumes, the whole forming a square of which the resonance tubes T 1 to T 4 constitute the sides, the volumes V CA to V CD , alternately V EA to V ED being arranged at the corners.
  • This configuration makes it possible to increase the thermal power by associating machines with each other according to a modular design.
  • the section variations given to the tubes T 1 to T 4 also make it possible to balance the dynamic forces of the movement of the working gas in these tubes.
  • FIG. 15 simply shows two pairs of motors whose compression volumes V CA , V CB , respectively V CC , V CD , alternatively the expansion volumes V EA , V EB , respectively V EC , V ED , are connected by two tubular resonators T 1 , respectively T 2 , while the compression volumes V CA and V CC on the one hand, and the compression volumes V CB and V CD , on the other hand, alternately the expansion volumes V EA and V EC on the one hand and the expansion volumes V EB and V ED , on the other hand, are connected to each other by connecting tubes T C1 and T C2 whose role is to ensure that the pressures of the compression volumes, alternately of expansion, thus connected are the same since the motors arranged diagonally are in phase.
  • FIG. 16 shows two Stirling engines illustrated by their only compression volumes V CI , V CII , alternatively their expansion volumes V EI , V EII connected by a tubular resonator 18.
  • FIG. 17 shows the heating of a tubular resonator 18 connecting two Stirling engines as illustrated by FIGS. 14 to 16, arranged in a heating enclosure 26.
  • the respective ends of the tube 18 of this resonator communicate with the expansion volumes V EI , V EII of two Stirling engines.
  • V EI , V EII expansion volumes
  • the tube 18 of the resonator common to these two motors also constitutes a heating element common to these two motors. It would also be possible to use several resonance tubes 18 in parallel in order to increase the exchange surface and improve the heat transfer.

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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)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Control Of Multiple Motors (AREA)
  • Control Of Electric Motors In General (AREA)
EP99810286A 1999-04-07 1999-04-07 Verfahren und Vorrichtung zur Erzeugung und Durchgabe von mechanischer Arbeit einer Stirlingmaschine zu einem Verbraucherorgan Withdrawn EP1043491A1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP99810286A EP1043491A1 (de) 1999-04-07 1999-04-07 Verfahren und Vorrichtung zur Erzeugung und Durchgabe von mechanischer Arbeit einer Stirlingmaschine zu einem Verbraucherorgan
AT00912325T ATE301773T1 (de) 1999-04-07 2000-04-05 Verfahren und vorrichtung zum übersetzen einer mechanischen energie zwischen einer stirlingmachine und einem generator oder einem elektromotor
DE60021863T DE60021863T2 (de) 1999-04-07 2000-04-05 Verfahren und vorrichtung zum übersetzen einer mechanischen energie zwischen einer stirlingmachine und einem generator oder einem elektromotor
PCT/CH2000/000199 WO2000061936A1 (fr) 1999-04-07 2000-04-05 Procede et dispositif pour transmettre une energie mecanique entre une machine stirling et un generateur ou un moteur electrique
EP00912325A EP1165955B1 (de) 1999-04-07 2000-04-05 Verfahren und vorrichtung zum übersetzen einer mechanischen energie zwischen einer stirlingmachine und einem generator oder einem elektromotor
US09/972,263 US6510689B2 (en) 1999-04-07 2001-10-05 Method and device for transmitting mechanical energy between a stirling machine and a generator or an electric motor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP99810286A EP1043491A1 (de) 1999-04-07 1999-04-07 Verfahren und Vorrichtung zur Erzeugung und Durchgabe von mechanischer Arbeit einer Stirlingmaschine zu einem Verbraucherorgan

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EP1043491A1 true EP1043491A1 (de) 2000-10-11

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EP99810286A Withdrawn EP1043491A1 (de) 1999-04-07 1999-04-07 Verfahren und Vorrichtung zur Erzeugung und Durchgabe von mechanischer Arbeit einer Stirlingmaschine zu einem Verbraucherorgan
EP00912325A Expired - Lifetime EP1165955B1 (de) 1999-04-07 2000-04-05 Verfahren und vorrichtung zum übersetzen einer mechanischen energie zwischen einer stirlingmachine und einem generator oder einem elektromotor

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EP00912325A Expired - Lifetime EP1165955B1 (de) 1999-04-07 2000-04-05 Verfahren und vorrichtung zum übersetzen einer mechanischen energie zwischen einer stirlingmachine und einem generator oder einem elektromotor

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US (1) US6510689B2 (de)
EP (2) EP1043491A1 (de)
AT (1) ATE301773T1 (de)
DE (1) DE60021863T2 (de)
WO (1) WO2000061936A1 (de)

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WO2003100240A1 (en) * 2002-05-24 2003-12-04 Stm Power Inc. Multiple cylinder stiriling engine for electrical power generation
CN104500262A (zh) * 2014-12-19 2015-04-08 中国科学院理化技术研究所 自由活塞斯特林发电机

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US6701708B2 (en) 2001-05-03 2004-03-09 Pasadena Power Moveable regenerator for stirling engines
GB0130380D0 (en) * 2001-12-19 2002-02-06 Bg Intellectual Pty Ltd A heat appliance
JP3769751B2 (ja) * 2003-02-19 2006-04-26 ツインバード工業株式会社 スターリングサイクル機関
US7017344B2 (en) * 2003-09-19 2006-03-28 Pellizzari Roberto O Machine spring displacer for Stirling cycle machines
US7677039B1 (en) 2005-12-20 2010-03-16 Fleck Technologies, Inc. Stirling engine and associated methods
US7417331B2 (en) * 2006-05-08 2008-08-26 Towertech Research Group, Inc. Combustion engine driven electric generator apparatus
US8011183B2 (en) * 2007-08-09 2011-09-06 Global Cooling Bv Resonant stator balancing of free piston machine coupled to linear motor or alternator
WO2009070771A1 (en) * 2007-11-28 2009-06-04 Tiax Llc Free piston stirling engine
ITLI20080007A1 (it) * 2008-07-08 2010-01-08 Fabio Prosperi Generatore elettrico alimentato mediante fonti di calore
US8590300B2 (en) * 2008-10-20 2013-11-26 Sunpower, Inc. Balanced multiple groupings of beta stirling machines
US8096118B2 (en) * 2009-01-30 2012-01-17 Williams Jonathan H Engine for utilizing thermal energy to generate electricity
US8967136B2 (en) * 2009-10-14 2015-03-03 Jeffrey Lee Solar collector system
CH702965A2 (fr) * 2010-04-06 2011-10-14 Jean-Pierre Budliger Machine stirling.
DE102011107802B4 (de) * 2011-07-11 2013-05-02 Rhp Gmbh Wärmekraftmaschine mit äußerer Verbrennung oder der Nutzung von Solarenergie

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ATE301773T1 (de) 2005-08-15
US20020096884A1 (en) 2002-07-25
EP1165955B1 (de) 2005-08-10
WO2000061936A1 (fr) 2000-10-19
EP1165955A1 (de) 2002-01-02
DE60021863D1 (de) 2005-09-15
US6510689B2 (en) 2003-01-28

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