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EP1165955B1 - Method and device for transmitting mechanical energy between a stirling engine and a generator or an electric motor - Google Patents

Method and device for transmitting mechanical energy between a stirling engine and a generator or an electric motor Download PDF

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Publication number
EP1165955B1
EP1165955B1 EP00912325A EP00912325A EP1165955B1 EP 1165955 B1 EP1165955 B1 EP 1165955B1 EP 00912325 A EP00912325 A EP 00912325A EP 00912325 A EP00912325 A EP 00912325A EP 1165955 B1 EP1165955 B1 EP 1165955B1
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EP
European Patent Office
Prior art keywords
piston
volume
transfer
transfer piston
resonator
Prior art date
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EP00912325A
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German (de)
French (fr)
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EP1165955A1 (en
Inventor
Jean-Pierre Budliger
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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
    • F02G1/0435—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 transmit mechanical energy between a transfer piston of a Stirling machine and a moving part of a generator or an electric motor, the transfer piston being mounted in a cylinder, which moves periodically using said transfer piston a working gas between an expansion chamber and a compression chamber associated respectively with two working faces of said piston transfer by passing said gas through a heat exchanger, alternately cold, connected to a source of heat, a regenerator and a cooling exchanger connected to a heat sink and one exerts a force elastic return on this transfer piston.
  • EP-A-0 218 554 has proposed a machine for free piston comprising a transfer piston mounted in a engine compartment, a seal separating expansion volumes and compression, which itself is delimited by a second piston surrounded by a joint. An axial passage crosses this second piston and allows a rod secured to the piston transfer to access a crankshaft also connected to the second piston, to supply mechanical energy to a machine press.
  • a resonance tube is connected to the volume compression and increases the pressure ratio between expansion and compression volumes to increase the yield.
  • the purpose of the present invention is to remedy the less in part to the aforementioned disadvantages.
  • the object of this invention is firstly a method for transmitting mechanical energy between a transfer piston of a Stirling machine and a movable member a generator or an electric motor as defined by claim 1.
  • This invention also object a device for implementing this method, according to claim 10.
  • the device illustrated in Figure 1 comprises an elongated housing 1 formed of two cylindrical compartments 2, 3, assembled on an intermediate element 4, acting as a frame.
  • the cylindrical compartment 2 comprises a cylindrical housing 5, constituting a working volume of a Stirling engine, in which a two-part transfer piston 6, 6a is mounted, free to move in the longitudinal axis of the cylindrical housing 5.
  • the volume located between the portion 6 of the transfer piston 6, 6a and the outer end of the housing 5 is the one that is in contact with a hot heat exchanger 7 connected to a hot source (not shown) and constitutes the chamber hot or expansion volume V E Stirling engine, while at the other end of this cylindrical housing 5, there is a volume in contact with a cold heat exchanger 8 connected to a cold source (not shown), which is the cold room or compression volume V C of the Stirling engine.
  • a regenerator 9 is disposed between the heat exchanger 7 and cold 8.
  • the portion 6a of the transfer piston 6, 6a adjacent to the compression chamber V C is engaged in a closed volume filled with working gas, which constitutes an elastic return means of the transfer piston 6, 6a.
  • the cylindrical compartment 3 encloses a volume in which a movable element of an electric generator, here the inductor 11 constituted by a cylindrical element carrying permanent magnets, is attached to the periphery of a annular member 12, whose inner edge is integral with a elastic suspension member 14, constituted by springs annular plates whose peripheral edges are fixed to the frame 4 and whose inner edges are secured a rod 17 whose end is fixed to the part 6a of transfer piston 6, 6a.
  • the inner edge of a second organ of elastic suspension 15 similar to the organ 14, is attached to the other end of the rod 17, while its periphery is attached to a support 13 secured to the frame 4.
  • the armature of the generator is formed by windings 16.
  • the portion 6a of the transfer piston 6, 6a and the rod 17 cross the bottom of the closed volume 10 formed in the element intermediate 4 with a clearance of between 30 and 50 ⁇ m.
  • Such game is perfectly acceptable as well from the point of view manufacturing tolerances that the influence of leaks of working gas on energy efficiency and on the return force of the compressed gas in the closed volume 10.
  • This resonator has the role of replacing the second piston, which according to the method of the invention is no longer used to produce energy, all the energy being produced by the transfer piston 6, 6a as will be explained. below, but serves to amplify the pressure wave and to ensure an appropriate phase shift between the displacement of the transfer piston 6, 6a and the pressure variations p in the working volume.
  • this tubular resonator 18 ends advantageously in a Helmholtz volume 19.
  • the of this resonator found in the Helmholtz volume ends with a flare 18a.
  • the transfer piston 6, 6a then plays the double role of transferring the working gas between the expansion chamber V ⁇ and the compression chamber Vc and producing all the motive energy transmitted to the inductor 11, provided that that certain conditions, of which we will speak now, are fulfilled.
  • the operation of the motor is possible only if the surface ratio at C / a E is greater than this limit, that is to say the displacement of the transfer piston 6, 6a must induce a pressure component p x (FIG. 4) which must be opposed to the displacement X of this piston 6, 6a.
  • the displacement of the transfer piston 6, 6a is positive if it moves towards the volume V E.
  • the variation of the amount of working gas WG in the working volume of the Stirling engine gives rise to a pressure variation p w , which is in phase with the variation of the quantity WG of working gas.
  • the variation of the pressure p in the working volume of the Stirling engine corresponds to the vector sum of the two partial pressures p x and p w .
  • Figure 5 shows the variation of the X position of the transfer piston 6, 6a and the variation of the pressure in function of time (or angle ⁇ ). This representation schematically corresponds to that of Figure 4.
  • the pressure decreases, the working gas is in large party in the room warm or relaxing; when increases, the working gas is essentially in the cold room or compression. To produce energy, it is necessary that the displacement X of the piston 6 precedes the pressure variation p.
  • Figure 6 shows the variation of the quantity WG of working gas in the Stirling work volume and the pressure p in this volume.
  • the quantity WG of gas decreases, the pressure is greater than during his return where the quantity WG of gas increases. So there is a transport of energy from the Stirling volume to the tube, which offsets the friction losses in this tubular resonator 18.
  • Fig. 4 shows that p x must be opposite to X. If p x becomes null, or oriented in the direction of X, no energy is transmitted. to the tubular resonator 18 to compensate for friction losses. As a result, the pressure wave can not be maintained and the machine stops working.
  • the ratio of the sections to C / a E must be between 0.4 and 0.6, preferably between 0.45 and 0.55.
  • FIG. 7 gives an example of efficiency of the cycle ⁇ C calculated as a function of the work supplied by cycle E, with the wall temperature T H of the expansion chamber V E and the amplitude X of the transfer piston 6, 6a as parameter.
  • the temperature of the cold exchanger T, close to the temperature T C is approximately at 50 ° C.
  • the net efficiency of the generator can be obtained by multiplying the efficiency of the cycle by the efficiency of the heating means and that of the alternator.
  • the Stirling engine should always operate at expansion chamber temperatures between 600 ° and 700 ° C. In this range, the temperature T H of the expansion 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 transfer piston 6, 6a is provided by flat springs 14, 15 of the type of those described in "Recent developments in cryocoolers” Ray Radebaugh 19 TH International Congress of Refrigeration 1995 Proceedings Volume IIIb, allows it to oscillate perfectly along the longitudinal axis of the cylindrical housing 5, so that it is not necessary to use pneumatic bearings to center it.
  • the transfer piston 6, 6a can be centered with great precision. Due to the pneumatic suspension of this transfer piston and consequently the low forces required for the elastic suspension elements constituted by the annular flat springs 14 and 15, the amplitude of the transfer piston 6, 6a of 25 can be increased. % to 50% compared 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 achieved.
  • the use of a single mobile piston simplifies the initial setting, starting and power control of significantly compared to conventional Stirling systems free piston.
  • the rigidity of the suspension of transfer piston 6, 6a and therefore the angle of phase can be adjusted by adjusting the gas pressure of work in the work volume of the Stirling engine.
  • the natural frequency of the tubular resonator 18 can be adjusted by varying the composition of the working gas, i.e. its molecular mass.
  • Starting the engine is then performed by first raising the temperature of the working gas in the expansion chamber V E to a value T H at which the working gas pressure becomes independent of the position of the transfer piston.
  • the Stirling engine load is thus reduced to a minimum (losses by internal friction of the motor and by the periodic flow through the exchangers and the regenerator).
  • the temperature T H will be adjusted to the optimum working temperature.
  • the amplitude of the transfer piston 6, 6a and consequently the power of the Stirling engine is adjusted by adjusting the braking force exerted by the electric generator to a determined value.
  • the output power varies proportionally to the amplitude of the transfer piston 6, 6a.
  • the heating power of the burner (not shown) for heating the working gas of the expansion chamber V E is continuously adjusted to maintain the desired temperature T H in this expansion chamber V E.
  • the amplitude of the transfer piston can therefore be precisely controlled. It is therefore not necessary to provide additional dead volume to avoid shocks in case of overshoot accidental amplitude of the transfer piston. It is only necessary to prevent the transfer piston from exceeding a maximum amplitude in the event of a failure in the electrical network associated with the electrical generator.
  • the natural frequency of the tubular resonator 18 depends only on the average temperature of the working gas therein. This temperature can be accurately set to the desired value by means of an additional heat exchanger 20 disposed in the Helmholtz volume 19 and controlling the thermal energy extracted. This makes it possible to adjust the phase angle of the resonator with respect to the other variables of the system.
  • the extraction of heat from the tubular resonator 18 makes it possible to reduce the cooling of the working gas situated in the compression chamber 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 object of the present invention.
  • the tubular resonator 18 may have a total length including the Helmholtz volume 19, of about 1.6 m, and a temperature T of 40 ° C.
  • the average pressure p o of the gas is 4 MPa and the resonant frequency of this resonator is 50 Hz.
  • a working gas whose molecular weight is higher than that of helium such as a mixture of helium and argon or carbon dioxide with a molecular weight M of gas of 14 kg / kmol.
  • the minimum section S min of the tubular resonator 18 is, in this example, 4.75 cm 2 .
  • the working gas volume V s of the Stirling 2 engine is 1000 cm 3
  • that of the Helmholtz 19 volume is 6000 cm 3 .
  • the tubular resonator can be prolonged inside the volume Helmholtz 19. Given that this portion of the tube is only exposed to differences limited pressure, its wall can be thin and can easily be put in conical form 18a preventing the formation of steep pressure waves.
  • FIG. 8 An example of distribution of the section along the tube 18 of the resonator is shown in the diagram of the figure 8.
  • the left end of the diagram corresponds to the end of the tube 18 in communication with the Stirling compartment 2, while the right end corresponds to the one that communicates with the volume Helmholtz 19.
  • the diagram in Figure 9 represents nine values at regular intervals of the gas flow velocity of working in tube 18 related to the speed of sound (so the Mach number) according to the position in the tube 18 during a cycle, while the diagram in Figure 10 shows the distribution of the pressure of the working gas relative to the average pressure during the same cycle.
  • the pressure diagram clearly shows that with a appropriate sizing of the tube, no shock occurs to the resonance conditions of the tube 18.
  • the pressure in the Stirling volume 2 varies in a sinusoidal way.
  • the pressure and velocity are orthogonal functions, that is to say that if the pressure takes an extreme value, the speed of the gas of work is null and vice versa.
  • the range indicated takes into account that, on the one hand, the coefficient of friction of the unsteady working gas may differ from that of an established regime, on the other hand that the roughness of the tubes is known only approximately.
  • the volumes of displaced working gas are of the order of a hundred cm 3 .
  • the cylindrical parts of the tube typically have diameters of 2.5 to 4 cm. It can easily be bent or rolled so that the entire device occupies as small a volume as possible.
  • the device illustrated in FIG. 3 can have a height of 90 cm, a width of 60 cm and a depth of 40 cm.
  • FIG. 11 Such a variant is illustrated in FIG. 11 on which is found the end of the free transfer piston 6a 'and that of the resonance tube 18' communicating with the cold chamber or compression volume Vc .
  • a rod 21 is slidably mounted in a cylindrical guide 22 by linear bearings 31.
  • a connecting rod 23 is articulated at one end to the rod 21 and at its other end to a crankshaft 24 secured to the axis of a rotary electric generator. for example, mounted in an enclosure 25.
  • tubular resonator 18 may be constituted by two identical tubular elements arranged in opposition diametrically with respect to said transfer piston 6, 6a in order to balance the lateral forces that are exercised on this transfer piston.
  • the tubular resonator 18 may be connected to the expansion volume V E or hot compartment of the Stirling engine, provided that the entire tube is kept warm and does not constitute a heat sink.
  • FIG. 12 illustrates a variant in which the Helmholtz volume 19 is placed in a heating chamber 26, heated by gaseous, liquid or solid fuels, while the tube 18 is surrounded by a 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 replace part or all of the hot exchanger 7 of the Stirling engine.
  • the tubular resonator 18, 19 has a considerable exchange surface and thanks to the periodic flow that is established in it, the internal heat transfer is favorable. Due to the standing wave regime that 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 placed in a helical form, 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, which has been shown the transfer piston 6 and the regenerator 9.
  • FIG. 14 very schematically illustrates the combination of four Stirling engines whose respective compression volumes V CA , V CB , V CC , V CD have been shown to be alternately the respective expansion volumes V EA , V EB , V EC , V ED , connected by four tubular resonators, of symmetrical shapes T 1 , T 2 , T 3 and T 4 .
  • the assembly forms a closed loop, each volume V being connected to two other neighboring volumes, the whole forming a square whose resonance tubes T 1 to T 4 constitute the sides, the volumes V CA to V CD , alternatively 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.
  • FIG. 15 simply shows two pairs of Stirling engines whose compression volumes V CA , V CB , respectively V CC , V CD , alternatively the expansion volumes V ⁇ A , 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, alternatively the volumes of expansion V EA and V EC on the one hand and expansion volumes V EB and V ED , on the other hand, are connected to each other by T C1 and T C2 connecting tubes whose role is to ensure that the pressures of compression volumes, alternatively 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 motors as illustrated by FIGS. 14 to 16, disposed in a heating chamber 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 resonance tube used Since in this mode of operation, the resonance tube used is entirely passive, it can only work if it is supplied with energy by the Stirling cycle. This implies that for a cryogenic machine, the section a E of the transfer piston 6, 6a delimiting the expansion volume V E is smaller than the section a C of the transfer piston 6, 6a delimiting the compression volume V C .
  • the ratio of these two sections to E / a C determines the lowest temperature level that can theoretically be reached.

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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 Electric Motors In General (AREA)
  • Control Of Multiple Motors (AREA)

Abstract

The method of power transmission from a Stirling engine has a drive piston (6) in a cylinder. The piston rod (6A) has a sect (AP) with a ratio to that of the piston which produces a total transmission to an output (11). A pneumatic resonator (18) is connected to the hot (Ve) and cold (Vc) chambers and adjusted so that the pressure wave is de-phased with respect to the transfe piston.

Description

La présente invention se rapporte à un procédé pour transmettre de l'énergie mécanique entre un piston de transfert d'une machine Stirling et un organe mobile d'un générateur ou d'un moteur électrique, le piston de transfert étant monté dans un cylindre, selon lequel on déplace périodiquement à l'aide dudit piston de transfert un gaz de travail entre une chambre d'expansion et une chambre de compression associées respectivement à deux faces de travail dudit piston de transfert en faisant passer ledit gaz à travers un échangeur chaud, alternativement froid, relié à une source de chaleur, un régénérateur et un échangeur de refroidissement relié à un puits de chaleur et on exerce une force élastique de rappel sur ce piston de transfert.The present invention relates to a method for transmit mechanical energy between a transfer piston of a Stirling machine and a moving part of a generator or an electric motor, the transfer piston being mounted in a cylinder, which moves periodically using said transfer piston a working gas between an expansion chamber and a compression chamber associated respectively with two working faces of said piston transfer by passing said gas through a heat exchanger, alternately cold, connected to a source of heat, a regenerator and a cooling exchanger connected to a heat sink and one exerts a force elastic return on this transfer piston.

Les machines Stirling à piston libre ont été considérés depuis longtemps comme une solution idéale pour des unités de couplage chaleur-force servant à la production d'énergie thermique et mécanique pour des habitations. La possibilité d'augmenter le degré d'utilisation du combustible fossile, la propreté du processus de combustion externe et le fonctionnement silencieux du dispositif constituent les arguments principaux en faveur de l'application de cette technologie aux habitations. Cependant jusqu'ici, la complexité et le prix élevé de telles unités ont empêché son emploi.Stirling free piston machines were considered for a long time as an ideal solution for units of heat-force coupling for energy production thermal and mechanical for homes. The possibility to increase the degree of use of fossil fuel, the cleanliness of the external combustion process and the operation silent the device constitute the arguments key to the application of this technology to homes. So far, however, the complexity and the high price of such units prevented his employment.

On a proposé dans le EP-A-0 218 554 une machine à piston libre comprenant un piston de transfert monté dans un compartiment moteur, un joint séparant les volumes d'expansion et de compression, lequel est lui-même délimité par un second piston entouré par un joint. Un passage axial traverse ce second piston et permet à une tige solidaire du piston de transfert d'accéder à un vilebrequin également relié au second piston, pour fournir de l'énergie mécanique à une machine rotative. Un tube de résonance est connecté au volume de compression et permet d'augmenter le rapport de pression entre les volumes d'expansion et de compression pour accroítre le rendement.EP-A-0 218 554 has proposed a machine for free piston comprising a transfer piston mounted in a engine compartment, a seal separating expansion volumes and compression, which itself is delimited by a second piston surrounded by a joint. An axial passage crosses this second piston and allows a rod secured to the piston transfer to access a crankshaft also connected to the second piston, to supply mechanical energy to a machine press. A resonance tube is connected to the volume compression and increases the pressure ratio between expansion and compression volumes to increase the yield.

L'inconvénient de cette solution est de nécessiter deux pistons coaxiaux avec les problèmes de guidage et d'étanchéité que cela implique, tant en matière de coût que de fiabilité.The disadvantage of this solution is to require two coaxial pistons with guiding and sealing problems that implies, both in terms of cost and reliability.

On a récemment proposé d'associer un piston moteur à un piston de transfert d'une machine Stirling et de-fixer les aimants inducteurs d'un alternateur électrique à ce piston moteur pour les déplacer par rapport aux enroulements de l'induit de cet alternateur. Ce concept prometteur présente cependant l'inconvénient de nécessiter deux pistons coaxiaux, mobiles l'un par rapport à l'autre, qui doivent être guidés avec une grande précision. En effet, la tige du piston de transfert est montée coulissante dans un volume fermé rempli de gaz du piston moteur, qui couple pneumatiquement ces deux pistons. Ce système nécessite également un asservissement de manière à régler le déphasage entre ces pistons. Un tel système est développé par la firme américaine Sunpower Inc. Athens, Ohio, et a fait notamment l'objet d'un article intitulé « Development of a 3kW free-piston Stirling engine with the displacer gas-spring partially sprung to the power piston » G. Chen et J. McEntee, Proceedings of the 26th Intersociety Energy Conversion Engineering Conference, vol. 5, p. 233-238. Un fort couplage élastique entre les deux pistons indique qu'une fraction substantielle de l'énergie motrice induite est engendrée par les forces du gaz agissant sur le piston de transfert et transférée par l'accouplement élastique au piston moteur. Les auteurs de l'article affirment que 2/3 de l'énergie totale est produite par le piston de transfert du moteur Stirling. Dans ce moteur, ce piston sert donc non seulement à transférer le gaz entre les volumes chaud et froid situés aux deux extrémités du cylindre dans lequel se déplace ce piston, mais aussi à engendrer une partie de l'énergie motrice.It has recently been proposed to associate a motor piston with a Transfer piston of a Stirling machine and de-set the inductive magnets of an electric alternator to this piston motor to move them relative to the windings of the armature of this alternator. This promising concept presents however the disadvantage of requiring two coaxial pistons, moving relative to each other, which must be guided with great precision. Indeed, the stem of transfer piston is slidably mounted in one volume closed filled with gas from the engine piston, which couples pneumatically these two pistons. This system also requires a slaving so as to adjust the phase difference between these pistons. Such a system is developed by the American firm Sunpower Inc. Athens, Ohio, and has been the subject of an article entitled "Development of a 3kW free-piston Stirling engine with displacer gas-spring partially sprung to the piston power "G. Chen and J. McEntee, Proceedings of the 26th Intersociety Energy Conversion Engineering Conference, vol. 5, p. 233-238. Strong elastic coupling between the two pistons indicates that a substantial fraction induced motor energy is generated by the gas forces acting on the transfer piston and transferred by the elastic coupling to the engine piston. Authors of the article claim that 2/3 of the total energy is produced by the Stirling engine transfer piston. In this engine, this piston therefore serves not only to transfer the gas between the hot and cold volumes located at both ends of the cylinder in which this piston moves but also to generate a part of the motive energy.

On pourrait certes se demander légitimement, dès lors, si il ne serait pas possible de produire la totalité de l'énergie motrice à l'aide du piston de transfert et d'associer la partie mobile du générateur électrique à celui-ci. Une telle hypothèse à elle seule ne résoudrait cependant pas les problèmes susmentionnés. En effet, le déphasage nécessaire entre les deux pistons coaxiaux devant subsister pour permettre la production d'énergie et son transfert, les problèmes de guidage et d'asservissement resteraient inchangés.One could certainly legitimately ask, therefore, if it would not be possible to produce all the energy motor using the transfer piston and to associate the moving part of the electrical generator to this one. A such a hypothesis alone would not, however, resolve the above mentioned problems. Indeed, the necessary phase shift between the two coaxial pistons to survive to allow energy production and its transfer, the problems guidance and servo control would remain unchanged.

Le but de la présente invention est de remédier au moins en partie aux inconvénients susmentionnés. The purpose of the present invention is to remedy the less in part to the aforementioned disadvantages.

A cet effet, cette invention a tout d'abord pour objet un procédé pour transmettre de l'énergie mécanique entre un piston de transfert d'une machine Stirling et un organe mobile d'un générateur ou d'un moteur électrique tel que défini par la revendication 1. Cette invention a également pour objet un dispositif pour la mise en oeuvre de ce procédé, selon la revendication 10.For this purpose, the object of this invention is firstly a method for transmitting mechanical energy between a transfer piston of a Stirling machine and a movable member a generator or an electric motor as defined by claim 1. This invention also object a device for implementing this method, according to claim 10.

Le remplacement du piston moteur par un résonateur pneumatique entièrement statique permet non seulement de simplifier considérablement le dispositif, comme ceci est évident, puisque ce procédé permet de supprimer le piston moteur, mais aussi de faciliter l'asservissement comme on l'expliquera par la suite. Ceci signifie que non seulement l'invention permet de simplifier sensiblement le dispositif et d'en réduire les coûts de production, mais aussi que la fiabilité du dispositif s'en trouve accrue. Or pour qu'un tel dispositif présente un intérêt économique, il faut non seulement qu'il puisse être produit à un prix compétitif, mais qu'il soit capable de fonctionner aussi de nombreuses années sans nécessiter aucun entretien ni réglage.Replacing the engine piston with a resonator fully static tire allows not only greatly simplify the device, as this is obvious, since this process allows to remove the piston motor, but also to facilitate servoing as one will explain it later. This means that not only the invention makes it possible to substantially simplify the device and to reduce production costs, but also that reliability of the device is increased. So that such a device is of economic interest, it is necessary only that it can be produced at a competitive price, but that he is able to function also many years without requiring any maintenance or adjustment.

D'autres particularités et avantages du procédé et du dispositif objets de l'invention apparaítront à la lecture de la description qui suit, ainsi que du dessin annexé, qui illustre, schématiquement et à titre d'exemple, deux formes d'exécution et diverses variantes de ce dispositif.

  • La figure 1 est une vue en coupe diamétrale de cette forme d'exécution;
  • la figure 2 est une vue d'une variante de la figure 1;
  • la figure 3 est une vue en élévation du dispositif selon les figures 1 ou 2;
  • la figure 4 est un diagramme vectoriel, les figures 5 et 6 sont des diagrammes explicatifs relatifs au procédé;
  • la figure 7 est un diagramme relatif au rendement du cycle par rapport au travail par cycle;
  • les figures 8 à 10 sont des diagrammes relatifs au dimensionnement et au comportement du résonateur;
  • la figure 11 est une vue en élévation, partiellement en coupe de la seconde forme d'exécution;
  • les figures 12 et 13 illustrent partiellement deux variantes pour le chauffage d'un moteur Stirling;
  • les figures 14 à 16 illustrent trois variantes dans lesquels des moteurs Stirling sont accouplés par des tubes de résonance;
  • la figure 17 illustre un mode de chauffage applicable aux variantes des figures 14 à 16.
    • Other features and advantages of the method and device that are the subject of the invention will become apparent on reading the description which follows, as well as the attached drawing, which illustrates, schematically and by way of example, two embodiments and various embodiments. variants of this device.
  • Figure 1 is a diametral sectional view of this embodiment;
  • Figure 2 is a view of a variant of Figure 1;
  • Figure 3 is an elevational view of the device according to Figures 1 or 2;
  • Fig. 4 is a vector diagram; Figs. 5 and 6 are explanatory diagrams relating to the method;
  • Fig. 7 is a diagram relating to cycle efficiency versus work per cycle;
  • Figures 8 to 10 are diagrams relating to the design and behavior of the resonator;
  • Figure 11 is an elevational view, partly in section of the second embodiment;
  • Figures 12 and 13 partially illustrate two variants for heating a Stirling engine;
  • Figures 14 to 16 illustrate three variants in which Stirling motors are coupled by resonance tubes;
  • Figure 17 illustrates a heating mode applicable to the variants of Figures 14 to 16.

    • Le dispositif illustré par la figure 1 comporte un carter allongé 1 formé de deux compartiments cylindriques 2, 3, assemblés sur un élément intermédiaire 4, jouant le rôle de bâti. Le compartiment cylindrique 2 comporte un logement cylindrique 5, constituant un volume de travail d'un moteur Stirling, dans lequel un piston de transfert en deux parties 6, 6a est monté, libre de se déplacer dans l'axe longitudinal du logement cylindrique 5. A une extrémité, le volume situé entre la partie 6 du piston de transfert 6, 6a et l'extrémité externe du logement 5 est celui qui est en contact avec un échangeur chaud 7 relié à une source chaude (non représentée) et constitue la chambre chaude ou volume d'expansion VE du-moteur Stirling, tandis qu'à l'autre extrémité de ce logement cylindrique 5, on trouve un volume en contact avec un échangeur froid 8 relié à une source froide (non représentée), qui constitue la chambre froide ou volume de compression VC du moteur Stirling. Un régénérateur 9 est disposé entre les échangeurs chaud 7 et froid 8.The device illustrated in Figure 1 comprises an elongated housing 1 formed of two cylindrical compartments 2, 3, assembled on an intermediate element 4, acting as a frame. The cylindrical compartment 2 comprises a cylindrical housing 5, constituting a working volume of a Stirling engine, in which a two-part transfer piston 6, 6a is mounted, free to move in the longitudinal axis of the cylindrical housing 5. At one end, the volume located between the portion 6 of the transfer piston 6, 6a and the outer end of the housing 5 is the one that is in contact with a hot heat exchanger 7 connected to a hot source (not shown) and constitutes the chamber hot or expansion volume V E Stirling engine, while at the other end of this cylindrical housing 5, there is a volume in contact with a cold heat exchanger 8 connected to a cold source (not shown), which is the cold room or compression volume V C of the Stirling engine. A regenerator 9 is disposed between the heat exchanger 7 and cold 8.

    La partie 6a du piston de transfert 6, 6a adjacente à la chambre de compression VC est engagée dans un volume fermé 10 rempli de gaz de travail, qui constitue un moyen de rappel élastique du piston de transfert 6,6a. The portion 6a of the transfer piston 6, 6a adjacent to the compression chamber V C is engaged in a closed volume filled with working gas, which constitutes an elastic return means of the transfer piston 6, 6a.

    Le compartiment cylindrique 3 renferme un volume dans lequel un élément mobile d'un générateur électrique, ici l'inducteur 11 constitué par un élément cylindrique portant des aimants permanents, est solidaire de la périphérie d'un organe annulaire 12, dont le bord interne est solidaire d'un organe de suspension élastique 14, constitué par des ressorts plats annulaires, dont les bords périphériques sont fixés au bâti 4 et dont les bords internes sont solidaires d'une tige 17 dont une extrémité est fixée à la partie 6a du piston de transfert 6, 6a. Le bord interne d'un second organe de suspension élastique 15 semblable à l'organe 14, est fixé à l'autre extrémité de la tige 17, tandis que sa périphérie est fixée à un support 13 solidaire du bâti 4. L'induit du générateur est formé par des enroulements 16.The cylindrical compartment 3 encloses a volume in which a movable element of an electric generator, here the inductor 11 constituted by a cylindrical element carrying permanent magnets, is attached to the periphery of a annular member 12, whose inner edge is integral with a elastic suspension member 14, constituted by springs annular plates whose peripheral edges are fixed to the frame 4 and whose inner edges are secured a rod 17 whose end is fixed to the part 6a of transfer piston 6, 6a. The inner edge of a second organ of elastic suspension 15 similar to the organ 14, is attached to the other end of the rod 17, while its periphery is attached to a support 13 secured to the frame 4. The armature of the generator is formed by windings 16.

    La partie 6a du piston de transfert 6,6a et la tige 17 traversent le fond du volume fermé 10 ménagé dans l'élément intermédiaire 4 avec un jeu compris entre 30 et 50µm. Un tel jeu est parfaitement acceptable aussi bien du point de vue des tolérances de fabrication que de l'influence des fuites du gaz de travail sur le rendement énergétique et sur la force de rappel du gaz comprimé dans le volume fermé 10.The portion 6a of the transfer piston 6, 6a and the rod 17 cross the bottom of the closed volume 10 formed in the element intermediate 4 with a clearance of between 30 and 50 μm. Such game is perfectly acceptable as well from the point of view manufacturing tolerances that the influence of leaks of working gas on energy efficiency and on the return force of the compressed gas in the closed volume 10.

    Un résonateur tubulaire 18, dont seule l'extrémité solidaire du compartiment cylindrique 2 est représentée sur la figure 1, communique avec le volume de compression ou chambre froide VC du moteur Stirling. Ce résonateur a pour rôle de remplacer le second piston, qui selon le procédé objet de l'invention, ne sert plus à produire de l'énergie, toute l'énergie étant produite par le piston de transfert 6, 6a comme on l'expliquera ci-après, mais sert à amplifier l'onde de pression et à assurer un déphasage approprié entre le déplacement du piston de transfert 6, 6a et les variations de pression p dans le volume de travail.A tubular resonator 18, of which only the end integral with the cylindrical compartment 2 is shown in FIG. 1, communicates with the compression volume or cold chamber V C of the Stirling engine. This resonator has the role of replacing the second piston, which according to the method of the invention is no longer used to produce energy, all the energy being produced by the transfer piston 6, 6a as will be explained. below, but serves to amplify the pressure wave and to ensure an appropriate phase shift between the displacement of the transfer piston 6, 6a and the pressure variations p in the working volume.

    Comme illustré par la figure 3, l'autre extrémité de ce résonateur tubulaire 18 se termine avantageusement dans un volume de Helmholtz 19. Dans ce cas, de préférence, la partie de ce résonateur qui se trouve dans le volume Helmholtz se termine par un évasement 18a.As illustrated in Figure 3, the other end of this tubular resonator 18 ends advantageously in a Helmholtz volume 19. In this case, preferably, the of this resonator found in the Helmholtz volume ends with a flare 18a.

    Le piston de transfert 6, 6a joue alors le double rôle de transfert du gaz de travail entre la chambre d'expansion Vε et la chambre de compression Vc et de production de toute l'énergie motrice transmise à l'inducteur 11, pour autant que certaines conditions, dont nous allons parler maintenant, soient remplies.The transfer piston 6, 6a then plays the double role of transferring the working gas between the expansion chamber V ε and the compression chamber Vc and producing all the motive energy transmitted to the inductor 11, provided that that certain conditions, of which we will speak now, are fulfilled.

    Pour atteindre cet objectif, il est nécessaire de déterminer le rapport entre la surface aC du piston de transfert 6, 6a délimitant la chambre de compression et celle aE de ce même piston, délimitant la chambre d'expansion.To achieve this objective, it is necessary to determine the ratio between the surface a C of the transfer piston 6, 6a delimiting the compression chamber and that a E of the same piston, defining the expansion chamber.

    L'analyse du cycle isothermique montre que la pression du gaz de travail dans le volume de travail devient indépendante de la position du piston de transfert 6, 6a si: a C a E = T C T H The analysis of the isothermal cycle shows that the pressure of the working gas in the working volume becomes independent of the position of the transfer piston 6, 6a if: at VS at E = T VS T H

    ExempleExample

  • Température TH du volume chaud VE, TH = 923°K = 650°CTemperature T H of the hot volume V E , T H = 923 ° K = 650 ° C
  • Température TC du volume froid VC, TC = 323°K = 50°C a C /a E ≥0,35 Temperature T C of the cold volume V C , T C = 323 ° K = 50 ° C. at VS / at E ≥0,35

    • Le fonctionnement du moteur est possible seulement si le rapport de surface aC/aE est supérieur à cette limite, c'est-à-dire que le déplacement du piston de transfert 6, 6a doit induire une composante de pression px (fig. 4) qui doit être opposée au déplacement X de ce piston 6, 6a. Le déplacement du piston de transfert 6, 6a est positif si celui-ci se déplace en direction du volume VE. La variation de la quantité WG de gaz de travail dans le volume de travail du moteur Stirling donne lieu à une variation de pression pw, qui est en phase avec la variation de la quantité WG de gaz de travail. La variation de la pression p dans le volume de travail du moteur Stirling correspond à la somme vectorielle des deux pressions partielles px et pw.The operation of the motor is possible only if the surface ratio at C / a E is greater than this limit, that is to say the displacement of the transfer piston 6, 6a must induce a pressure component p x (FIG. 4) which must be opposed to the displacement X of this piston 6, 6a. The displacement of the transfer piston 6, 6a is positive if it moves towards the volume V E. The variation of the amount of working gas WG in the working volume of the Stirling engine gives rise to a pressure variation p w , which is in phase with the variation of the quantity WG of working gas. The variation of the pressure p in the working volume of the Stirling engine corresponds to the vector sum of the two partial pressures p x and p w .

    La figure 5 montre la variation de la position X du piston de transfert 6, 6a et la variation de la pression en fonction du temps (ou de l'angle Φ). Cette représentation correspond schématiquement à celle de la figure 4. Lorsque la pression diminue, le gaz de travail se trouve en grande partie dans la chambre chaude ou de détente; lorsqu'elle augmente, le gaz de travail se trouve essentiellement dans la chambre froide ou de compression. Pour produire de l'énergie, il faut que le déplacement X du piston 6 précède la variation de pression p.Figure 5 shows the variation of the X position of the transfer piston 6, 6a and the variation of the pressure in function of time (or angle Φ). This representation schematically corresponds to that of Figure 4. When the pressure decreases, the working gas is in large party in the room warm or relaxing; when increases, the working gas is essentially in the cold room or compression. To produce energy, it is necessary that the displacement X of the piston 6 precedes the pressure variation p.

    La figure 6 représente la variation de la quantité WG de gaz de travail dans le volume de travail Stirling et la pression p dans ce volume. Lorsque le gaz de travail s'écoule vers le résonateur tubulaire 18, la quantité WG de gaz diminue, la pression est plus grande que durant son retour où la quantité WG de gaz augmente. Il y a donc un transport d'énergie du volume Stirling vers le tube, qui compense les pertes par frottement dans ce résonateur tubulaire 18.Figure 6 shows the variation of the quantity WG of working gas in the Stirling work volume and the pressure p in this volume. When the working gas flows to the tubular resonator 18, the quantity WG of gas decreases, the pressure is greater than during his return where the quantity WG of gas increases. So there is a transport of energy from the Stirling volume to the tube, which offsets the friction losses in this tubular resonator 18.

    Afin que p soit en retard sur la variation de la quantité WG de gaz de travail, la figure 4 montre que px doit être opposé à X. Si px devient nul, ou orienté en direction de X, aucune énergie n'est transmise vers le résonateur tubulaire 18 pour compenser les pertes par frottement. Par conséquent, l'onde de pression ne peut pas être maintenue et la machine cesse de fonctionner.In order for p to lag behind the variation of the quantity WG of working gas, Fig. 4 shows that p x must be opposite to X. If p x becomes null, or oriented in the direction of X, no energy is transmitted. to the tubular resonator 18 to compensate for friction losses. As a result, the pressure wave can not be maintained and the machine stops working.

    Suite à une étude d'optimisation effectuée à l'aide d'un programme informatique spécialement adapté pour le calcul des cycles Stirling selon la présente invention, les résultats ont montré que pour les générateurs Stirling, le rapport des sections aC/aE doit se situer entre 0,4 et 0,6, de préférence entre 0,45 et 0,55. Following an optimization study carried out using a computer program specially adapted for calculating Stirling cycles according to the present invention, the results showed that for Stirling generators, the ratio of the sections to C / a E must be between 0.4 and 0.6, preferably between 0.45 and 0.55.

    La figure 7 donne un exemple de rendement du cycle ηC calculé en fonction du travail fourni par cycle E, avec la température de paroi TH de la chambre d'expansion VE et l'amplitude X du piston de transfert 6, 6a comme paramètre. La température de l'échangeur froid T, proche de la température TC est environ à 50°C. Le rendement net du générateur peut être obtenu en multipliant le rendement du cycle par le rendement des moyens de chauffage et celui de l'alternateur.FIG. 7 gives an example of efficiency of the cycle η C calculated as a function of the work supplied by cycle E, with the wall temperature T H of the expansion chamber V E and the amplitude X of the transfer piston 6, 6a as parameter. The temperature of the cold exchanger T, close to the temperature T C is approximately at 50 ° C. The net efficiency of the generator can be obtained by multiplying the efficiency of the cycle by the efficiency of the heating means and that of the alternator.

    Ce diagramme montre que dans une gamme relativement grande d'amplitudes du piston de transfert, on peut obtenir de bons rendements, les valeurs les plus élevées étant atteintes à charge partielle. Ces rendements sont légèrement inférieurs à ceux du dispositif de l'état de la technique susmentionné, mais cette très légère baisse est largement compensée par la simplification apportée au dispositif.This diagram shows that in a relatively large amplitude of the transfer piston, it is possible to obtain good yields, the highest values being impaired partial load. These returns are slightly lower than those of the device of the state of the art above mentioned, but this very slight decrease is largely compensated by the simplification provided to the device.

    Le moteur Stirling devrait toujours fonctionner à des températures de la chambre d'expansion comprises entre 600° et 700°C. Dans cette gamme, la température TH de la chambre d'expansion VE influence principalement la puissance, dans une moindre mesure le rendement. Mais en abaissant la température à 400-500°C, le rendement et la puissance diminuent fortement, essentiellement parce que, dans ces conditions, la variation de pression px induite par le mouvement du piston devient petite et finalement disparaít complètement.The Stirling engine should always operate at expansion chamber temperatures between 600 ° and 700 ° C. In this range, the temperature T H of the expansion 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.

    La rigidité latérale de la suspension mécanique du piston de transfert 6, 6a est assurée par des ressorts plats 14, 15 du type de ceux décrits dans « Recent developments in cryocoolers » Ray Radebaugh 19TH International Congress of Refrigeration 1995 Proceedings Volume IIIb, lui permet d'osciller parfaitement selon l'axe longitudinal du logement cylindrique 5, de sorte qu'il n'est pas nécessaire d'utiliser des paliers pneumatiques pour le centrer. Lors de l'assemblage initial, le piston de transfert 6, 6a peut être centré avec une grande précision. En raison de la suspension pneumatique de ce piston de transfert et par conséquent, des faibles forces nécessaires pour les éléments de suspension élastiques constitués par les ressorts plats annulaires 14 et 15, on peut augmenter l'amplitude du piston de transfert 6, 6a de 25% à 50% par rapport au dispositif décrit dans « Free-piston Stirling design features » Neill W. Lane et al. 8TH International Stirling Engine Conference and Exhibition May 27-30, 1997 Ancona. Cette augmentation d'amplitude conduisant à une augmentation des vitesses linéaires, permet de réduire les dimensions de l'alternateur. Dans des conditions de fonctionnement inchangées, on peut atteindre des quantités d'énergie similaires.The lateral rigidity of the mechanical suspension of the transfer piston 6, 6a is provided by flat springs 14, 15 of the type of those described in "Recent developments in cryocoolers" Ray Radebaugh 19 TH International Congress of Refrigeration 1995 Proceedings Volume IIIb, allows it to oscillate perfectly along the longitudinal axis of the cylindrical housing 5, so that it is not necessary to use pneumatic bearings to center it. During the initial assembly, the transfer piston 6, 6a can be centered with great precision. Due to the pneumatic suspension of this transfer piston and consequently the low forces required for the elastic suspension elements constituted by the annular flat springs 14 and 15, the amplitude of the transfer piston 6, 6a of 25 can be increased. % to 50% compared 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 achieved.

    L'utilisation d'un seul piston mobile simplifie le réglage initial, le démarrage et le contrôle de puissance de manière significative par rapport aux systèmes Stirling conventionnels à piston libre. La rigidité de la suspension du piston de transfert 6, 6a et par conséquent, l'angle de phase peuvent être ajustés en réglant la pression du gaz de travail dans le volume de travail du moteur Stirling. La fréquence naturelle du résonateur tubulaire 18 peut être ajustée en variant la composition du gaz de travail, c'est-à-dire sa masse moléculaire.The use of a single mobile piston simplifies the initial setting, starting and power control of significantly compared to conventional Stirling systems free piston. The rigidity of the suspension of transfer piston 6, 6a and therefore the angle of phase can be adjusted by adjusting the gas pressure of work in the work volume of the Stirling engine. The natural frequency of the tubular resonator 18 can be adjusted by varying the composition of the working gas, i.e. its molecular mass.

    Le démarrage du moteur est ensuite exécuté en portant tout d'abord la température du gaz de travail dans la chambre d'expansion VE à une valeur TH à laquelle la pression du gaz de travail devient indépendante de la position du piston de transfert. La charge du moteur Stirling est ainsi réduite à un minimum (pertes par frottement interne du moteur et par l'écoulement périodique à travers les échangeurs et le régénérateur). Après le démarrage, la température TH sera ajustée à la température de travail optimum.Starting the engine is then performed by first raising the temperature of the working gas in the expansion chamber V E to a value T H at which the working gas pressure becomes independent of the position of the transfer piston. The Stirling engine load is thus reduced to a minimum (losses by internal friction of the motor and by the periodic flow through the exchangers and the regenerator). After starting, the temperature T H will be adjusted to the optimum working temperature.

    Le contrôle de la puissance s'effectue très facilement. On règle l'amplitude du piston de transfert 6, 6a et par conséquent la puissance du moteur Stirling, en ajustant la force de freinage exercée par le générateur électrique à une valeur déterminée. Pour des températures données du gaz TH, TC dans les chambres d'expansion, respectivement de compression, la puissance de sortie varie proportionnellement à l'amplitude du piston de transfert 6, 6a. La puissance de chauffage du brûleur (non représenté) destiné à chauffer le gaz de travail de la chambre d'expansion VE est ajustée en continu pour maintenir la température TH désirée dans cette chambre d'expansion VE. Dans des conditions normales, l'amplitude du piston de transfert peut donc être contrôlée avec précision. Il n'est donc pas nécessaire de prévoir de volume mort supplémentaire pour éviter des chocs en cas de dépassement d'amplitude accidentel du piston de transfert. Il est seulement nécessaire d'empêcher que le piston de transfert ne dépasse une amplitude maximum en cas de panne dans le réseau électrique auquel est associé au générateur électrique.Power control is very easy. The amplitude of the transfer piston 6, 6a and consequently the power of the Stirling engine is adjusted by adjusting the braking force exerted by the electric generator to a determined value. For given temperatures of gas T H , T C in the expansion chambers, respectively of compression, the output power varies proportionally to the amplitude of the transfer piston 6, 6a. The heating power of the burner (not shown) for heating the working gas of the expansion chamber V E is continuously adjusted to maintain the desired temperature T H in this expansion chamber V E. Under normal conditions, the amplitude of the transfer piston can therefore be precisely controlled. It is therefore not necessary to provide additional dead volume to avoid shocks in case of overshoot accidental amplitude of the transfer piston. It is only necessary to prevent the transfer piston from exceeding a maximum amplitude in the event of a failure in the electrical network associated with the electrical generator.

    Toute non linéarité de la rigidité de la suspension du piston de transfert 6, 6a a un effet marginal sur sa phase étant donné qu'il est couplé à une charge et se comporte comme un oscillateur fortement amorti.Any non-linearity of the rigidity of the suspension of transfer piston 6, 6a has a marginal effect on its phase since it is coupled to a load and behaves like a highly damped oscillator.

    Une fois que l'ensemble du dispositif est scellé, la fréquence naturelle du résonateur tubulaire 18 dépend seulement de la température moyenne du gaz de travail qui s'y trouve. Cette température peut être réglée avec précision à la valeur désirée au moyen d'un échangeur de chaleur supplémentaire 20 disposé dans le volume Helmholtz 19 et en contrôlant l'énergie thermique extraite. Ceci permet d'ajuster l'angle de phase du résonateur par rapport aux autres variables du système. L'extraction de chaleur du résonateur tubulaire 18 permet de diminuer le refroidissement du gaz de travail situé dans la chambre de compression VC, ce qui permet de simplifier l'échangeur froid du moteur Stirling. Son volume mort et/ou ses pertes par frottement pneumatique peuvent être réduits, apportant un avantage supplémentaire au dispositif objet de la présente invention.Once the entire device is sealed, the natural frequency of the tubular resonator 18 depends only on the average temperature of the working gas therein. This temperature can be accurately set to the desired value by means of an additional heat exchanger 20 disposed in the Helmholtz volume 19 and controlling the thermal energy extracted. This makes it possible to adjust the phase angle of the resonator with respect to the other variables of the system. The extraction of heat from the tubular resonator 18 makes it possible to reduce the cooling of the working gas situated in the compression chamber 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 object of the present invention.

    La pression du gaz de travail dans le volume Stirling varie de manière cyclique en fonction de l'oscillation de l'onde de pression dans le résonateur tubulaire 18. En faisant varier de façon appropriée la section du tube, comme on l'expliquera ci-après, on peut obtenir des variations de pression presque parfaitement sinusoïdales. La dissipation d'énergie est alors exclusivement due aux pertes par frottement du fluide et restent modérées, au moins pour les variations de pression considérées dans cette application. Les paramètres du résonateur tubulaire 18, dont un exemple suit, doivent être ajustés à ceux du processus Stirling pour garantir que ces composants interagissent de manière convenable, c'est-à-dire que l'onde est entraínée par le cycle Stirling et que les variations de pression résultantes maintiennent la périodicité du cycle Stirling.Work gas pressure in the Stirling volume varies cyclically depending on the oscillation of the pressure wave in the tubular resonator 18. In doing suitably vary the section of the tube, as will explain below, we can obtain variations of pressure almost perfectly sinusoidal. Dissipation of energy is then exclusively due to friction losses fluid and remain moderate, at least for the variations of pressure considered in this application. The parameters of the tubular resonator 18, an example of which follows, have to be adjusted to those of the Stirling process for 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.

    A titre d'exemple, le résonateur tubulaire 18 peut avoir une longueur totale y compris le volume Helmholtz 19, d'environ 1,6m, et une température T de 40°C. La pression moyenne po du gaz est de 4MPa et la fréquence de résonance de ce résonateur est de 50Hz. Pour limiter la longueur du tube on utilisera avantageusement un gaz de travail dont la masse moléculaire est plus élevée que celle de l'hélium, tel qu'un mélange d'hélium et d'argon ou de dioxyde de carbone avec une masse moléculaire M du gaz de 14 kg/kmol. La section minimale Smin du résonateur tubulaire 18 est, dans cet exemple, de 4, 75cm2. Le volume de gaz de travail Vs du moteur Stirling 2 est de 1000cm3, tandis que celle du volume de Helmholtz 19 est de 6000cm3.By way of example, the tubular resonator 18 may have a total length including the Helmholtz volume 19, of about 1.6 m, and a temperature T of 40 ° C. The average pressure p o of the gas is 4 MPa and the resonant frequency of this resonator is 50 Hz. To limit the length of the tube is advantageously used a working gas whose molecular weight is higher than that of helium, such as a mixture of helium and argon or carbon dioxide with a molecular weight M of gas of 14 kg / kmol. The minimum section S min of the tubular resonator 18 is, in this example, 4.75 cm 2 . The working gas volume V s of the Stirling 2 engine is 1000 cm 3 , while that of the Helmholtz 19 volume is 6000 cm 3 .

    Avantageusement, le résonateur tubulaire peut être prolongé à l'intérieur du volume Helmholtz 19. Etant donné que cette portion du tube est seulement exposée à des différences de pression limitées, sa paroi peut être mince et peut ainsi facilement être mise sous forme conique 18a empêchant la formation d'ondes de pression à front raide.Advantageously, the tubular resonator can be prolonged inside the volume Helmholtz 19. Given that this portion of the tube is only exposed to differences limited pressure, its wall can be thin and can easily be put in conical form 18a preventing the formation of steep pressure waves.

    Un exemple de répartition de la section le long du tube 18 du résonateur est représenté sur le diagramme de la figure 8. L'extrémité gauche du diagramme correspond à l'extrémité du tube 18 en communication avec le compartiment Stirling 2, tandis que l'extrémité droite correspond à celle qui communique avec le volume Helmholtz 19.An example of distribution of the section along the tube 18 of the resonator is shown in the diagram of the figure 8. The left end of the diagram corresponds to the end of the tube 18 in communication with the Stirling compartment 2, while the right end corresponds to the one that communicates with the volume Helmholtz 19.

    Le diagramme de la figure 9 représente neuf valeurs à intervalles réguliers de la vitesse d'écoulement du gaz de travail dans le tube 18 rapportée à la vitesse du son (donc le nombre de Mach) en fonction de la position dans le tube 18 durant un cycle, tandis que le diagramme de la figure 10 montre la répartition de la pression du gaz de travail rapportée à la pression moyenne durant le même cycle.The diagram in Figure 9 represents nine values at regular intervals of the gas flow velocity of working in tube 18 related to the speed of sound (so the Mach number) according to the position in the tube 18 during a cycle, while the diagram in Figure 10 shows the distribution of the pressure of the working gas relative to the average pressure during the same cycle.

    Le diagramme des pressions montre clairement qu'avec un dimensionnement approprié du tube, aucun choc ne se produit aux conditions de résonance du tube 18. La pression dans le volume Stirling 2 varie de façon sinusoïdale. La pression et la vitesse sont des fonctions orthogonales, c'est-à-dire que si la pression prend une valeur extrême, la vitesse du gaz de travail est nulle et réciproquement.The pressure diagram clearly shows that with a appropriate sizing of the tube, no shock occurs to the resonance conditions of the tube 18. The pressure in the Stirling volume 2 varies in a sinusoidal way. The pressure and velocity are orthogonal functions, that is to say that if the pressure takes an extreme value, the speed of the gas of work is null and vice versa.

    Le facteur de qualité calculé du tube 18 se situe entre 25 et 40 pour un rapport de pression dans le volume Stirling πC = pmax/pmin = 1, 1, respectivement entre 15 et 25 pour πC = 1,2. La fourchette indiquée tient compte du fait que, d'une part, le coefficient de frottement du gaz de travail en régime instationnaire peut différer de celui d'un régime établi, d'autre part que la rugosité des tubes n'est connue qu'approximativement.The calculated quality factor of the tube 18 is between 25 and 40 for a pressure ratio in the Stirling volume π C = p max / p min = 1.1, respectively between 15 and 25 for π C = 1.2. The range indicated takes into account that, on the one hand, the coefficient of friction of the unsteady working gas may differ from that of an established regime, on the other hand that the roughness of the tubes is known only approximately.

    Dans le cas du moteur Stirling à faible puissance étudié dans cet exemple, typiquement de l'ordre 2kW à 5kW, les volumes de gaz de travail déplacés sont de l'ordre d'une centaine de cm3. Les parties cylindriques du tube ont typiquement des diamètres de 2,5 à 4cm. Il peut facilement être courbé ou enroulé de manière à ce que l'ensemble du dispositif occupe un volume aussi réduit que possible. A titre d'exemple, le dispositif illustré par la figure 3 peut avoir une hauteur de 90cm, une largeur de 60cm et une profondeur de 40cm.In the case of the low power Stirling engine studied in this example, typically of the order 2kW to 5kW, the volumes of displaced working gas are of the order of a hundred cm 3 . The cylindrical parts of the tube typically have diameters of 2.5 to 4 cm. It can easily be bent or rolled so that the entire device occupies as small a volume as possible. By way of example, the device illustrated in FIG. 3 can have a height of 90 cm, a width of 60 cm and a depth of 40 cm.

    La variante illustrée par la figure 2 ne diffère de la forme d'exécution de la figure 1 que par le fait que l'organe de rappel élastique du piston de transfert 6, 6a n'est plus constitué par le volume fermé 10, mais directement par le compartiment cylindrique 3 renfermant l'alternateur. En effet, ce compartiment est également un volume fermé et peut donc aussi servir d'organe élastique de rappel et remplacer ainsi le volume 10 de la forme d'exécution de la figure 1.The variant illustrated in Figure 2 differs from the embodiment of Figure 1 only by the fact that the organ of elastic return of the transfer piston 6, 6a is plus constituted by the closed volume 10, but directly by the cylindrical compartment 3 enclosing the alternator. In indeed, this compartment is also a closed volume and can therefore also serve as a springback and replace and the volume 10 of the embodiment of Figure 1.

    Jusqu'ici nous n'avons décrit qu'une forme d'exécution dans laquelle l'énergie mécanique produite est transmise à un organe à mouvement alternatif comme celui du piston de transfert libre 6, 6a du moteur Stirling. En variante, il serait également possible de transformer ce mouvement alternatif en un mouvement rotatif comme ceci est bien connu dans le cas des moteurs à explosion ou des moteurs à vapeur.So far we have only described one form of execution in which the mechanical energy produced is transmitted to a reciprocating member such as that of the piston of free transfer 6, 6a of the Stirling engine. In a variant, would also be possible to transform this reciprocating motion in a rotary motion like this is well known in the case of internal combustion engines or steam engines.

    Une telle variante est illustrée par la figure 11 sur laquelle on retrouve l'extrémité du piston de transfert libre 6a' et celle du tube de résonance 18' communiquant avec la chambre froide ou volume de compression Vc. Une tige 21 est montée coulissante dans un guidage cylindrique 22 par des roulements linéaires 31. Une bielle 23 est articulée par une extrémité à la tige 21 et par son autre extrémité, à un vilebrequin 24 solidaire de l'axe d'un générateur électrique rotatif par exemple, monté dans une enceinte 25.Such a variant is illustrated in FIG. 11 on which is found the end of the free transfer piston 6a 'and that of the resonance tube 18' communicating with the cold chamber or compression volume Vc . A rod 21 is slidably mounted in a cylindrical guide 22 by linear bearings 31. A connecting rod 23 is articulated at one end to the rod 21 and at its other end to a crankshaft 24 secured to the axis of a rotary electric generator. for example, mounted in an enclosure 25.

    Dans une variante non représentée des figures 1 à 3 notamment, le résonateur tubulaire 18 peut être constitué par deux éléments tubulaires identiques disposés en opposition diamétrale par rapport audit piston de transfert 6, 6a de manière à équilibrer les forces latérales qui s'exercent sur ce piston de transfert.In a not shown variant of Figures 1 to 3 in particular, the tubular resonator 18 may be constituted by two identical tubular elements arranged in opposition diametrically with respect to said transfer piston 6, 6a in order to balance the lateral forces that are exercised on this transfer piston.

    En variante, le résonateur tubulaire 18 peut être relié au volume d'expansion VE ou compartiment chaud du moteur Stirling, à condition que l'ensemble de ce tube soit maintenu chaud et ne constitue pas un puits de chaleur. La figure 12 illustre une variante dans laquelle le volume Helmholtz 19 est placé dans une enceinte de chauffage 26, chauffée par des combustibles gazeux, liquides ou solides, alors que le tube 18 est entouré par une isolation thermique 27. On peut ainsi augmenter la température du gaz de travail contenu dans le résonateur tubulaire 18 au-dessus de la température TH de ce gaz dans le volume d'expansion VE. Le résonateur tubulaire 18, 19 peut alors se substituer en partie ou entièrement à l'échangeur chaud 7 du moteur Stirling. Il en résulte ainsi l'économie partielle ou totale d'un échangeur compliqué, coûteux et difficile à optimiser (surface d'échange suffisante avec un volume mort réduit et de faibles pertes de charge). Le résonateur tubulaire 18, 19 présente une surface d'échange considérable et grâce à l'écoulement périodique qui s'établit dans celui-ci, le transfert interne de chaleur est favorable. En raison du régime d'ondes stationnaires qui s'établit dans ce résonateur, son volume interne ne fait pas partie du volume mort du moteur Stirling.Alternatively, the tubular resonator 18 may be connected to the expansion volume V E or hot compartment of the Stirling engine, provided that the entire tube is kept warm and does not constitute a heat sink. FIG. 12 illustrates a variant in which the Helmholtz volume 19 is placed in a heating chamber 26, heated by gaseous, liquid or solid fuels, while the tube 18 is surrounded by a 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 replace part or all of the hot exchanger 7 of the Stirling engine. This results in the partial or total economy of a complicated exchanger, expensive and difficult to optimize (sufficient exchange surface with a reduced dead volume and low pressure losses). The tubular resonator 18, 19 has a considerable exchange surface and thanks to the periodic flow that is established in it, the internal heat transfer is favorable. Due to the standing wave regime that is established in this resonator, its internal volume is not part of the dead volume of the Stirling engine.

    Le principe de fonctionnement du cycle Stirling reste le même que celui expliqué à l'aide des figures 4 à 6.The operating principle of the Stirling cycle remains the same as that explained in Figures 4 to 6.

    Pour favoriser l'échange de chaleur on peut augmenter la surface d'échange à l'aide d'ailettes 30 à l'intérieur et/ou à l'extérieur du volume Helmholtz 19. Etant donné que le diamètre du tube 18 est déjà de l'ordre de 2 à 4 fois supérieur à celui de l'échangeur de chaleur 7 et que le diamètre du volume Helmholtz est encore lui-même 2 à 4 fois supérieur à celui du tube 18, l'écartement entre les ailettes peut être sensiblement augmenté. Par conséquent, un tel échangeur est beaucoup moins sensible à l'encrassement par des suies ou autres résidus de combustion que les échangeurs Stirling conventionnels de faible taille. Si nécessaire, il peut facilement être nettoyé et est donc particulièrement bien adapté à des systèmes fonctionnant avec des combustibles solides ou de la biomasse.To promote the exchange of heat one can increase the exchange surface with fins 30 inside and / or outside the Helmholtz volume 19. Since the diameter of the tube 18 is already of the order of 2 to 4 times greater to that of the heat exchanger 7 and that the diameter of volume Helmholtz is still itself 2 to 4 times higher to that of the tube 18, the spacing between the fins can be significantly increased. Therefore, such a exchanger is much less sensitive to fouling by soot or other combustion residues as the exchangers Stirling conventional small size. If necessary, can easily be cleaned and is therefore particularly well suited to systems operating with fuels solids or biomass.

    La variante illustrée par la figure 13 montre une configuration dans laquelle le résonateur tubulaire 18 est intégré dans un collecteur solaire à haute température. A cet effet, le tube 18 du résonateur est mis sous une forme d'hélice, placée à l'intérieur d'une cavité cylindrique ou conique 28. Une extrémité de ce résonateur tubulaire 18 s'ouvre dans un volume de Helmholtz 19, tandis que l'autre extrémité communique avec le volume d'expansion VE du moteur Stirling, dont on a représenté le piston de transfert 6 et le régénérateur 9. Un miroir parabolique 29 disposé sous l'ouverture de la cavité 28, concentre le rayonnement solaire à l'intérieur de celle-ci.The variant illustrated in FIG. 13 shows a configuration in which the tubular resonator 18 is integrated in a high temperature solar collector. For this purpose, the tube 18 of the resonator is placed in a helical form, 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, which has been shown the transfer piston 6 and the regenerator 9. A parabolic mirror 29 disposed under the opening of the cavity 28, concentrates the solar radiation inside of it.

    Un des avantages de cette solution réside dans le fait qu'un tel collecteur est relativement peu sensible à la répartition exacte du rayonnement solaire incident, étant donné que le mouvement périodique du gaz de travail dans le tube 18 du résonateur assure une répartition uniforme de la température dans celui-ci. Un autre avantage résulte du fait que lors de l'apparition du soleil, au moment où un niveau de température TH du gaz de travail dans la chambre d'expansion VE est atteint, le moteur Stirling se met facilement en marche; le risque d'une surchauffe instantanée du collecteur est ainsi diminué.One of the advantages of this solution lies in the fact that such a collector is relatively insensitive to the exact distribution of the incident solar radiation, since the periodic movement of the working gas in the tube 18 of the resonator ensures a uniform distribution of the temperature in it. Another advantage results from the fact that when the sun appears, when a temperature level T H of the working gas in the expansion chamber V E is reached, the Stirling engine starts easily; the risk of instantaneous overheating of the collector is thus reduced.

    Une autre variante (figure 14) illustre très schématiquement la combinaison de quatre moteurs Stirling dont on a montré que les volumes de compression respectifs VCA, VCB, VCC, VCD, alternativement les volumes d'expansion respectifs VEA, VEB, VEC, VED, reliés par quatre résonateurs tubulaires, de formes symétriques T1, T2, T3 et T4. L'ensemble forme une boucle fermée, chaque volume V étant relié à deux autres volumes voisins, le tout formant un carré dont les tubes de résonance T1 à T4 constituent les côtés, les volumes VCA à VCD, alternativement VEA à VED étant disposés aux angles. Cette configuration permet d'augmenter la puissance thermique en associant entre elles des machines selon une conception modulaire.Another variant (FIG. 14) very schematically illustrates the combination of four Stirling engines whose respective compression volumes V CA , V CB , V CC , V CD have been shown to be alternately the respective expansion volumes V EA , V EB , V EC , V ED , connected by four tubular resonators, of symmetrical shapes T 1 , T 2 , T 3 and T 4 . The assembly forms a closed loop, each volume V being connected to two other neighboring volumes, the whole forming a square whose resonance tubes T 1 to T 4 constitute the sides, the volumes V CA to V CD , alternatively 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.

    Lorsque deux moteurs Stirling sont couplés par l'intermédiaire d'un résonateur tubulaire dans une configuration symétrique, ils travaillent en opposition de phase. Lorsque l'on a quatre moteurs Stirling disposés aux sommets d'un carré comme dans la figure 14, les moteurs qui sont sur une même diagonale sont en phase et sont déphasés de 180° par rapport aux deux autres moteurs disposés sur l'autre diagonale. Les forces transmises à l'extérieur par cet ensemble sont entièrement compensées, ce qui permet de réduire les vibrations transmises à l'extérieur.When two Stirling engines are coupled via of a tubular resonator in a configuration symmetrical, they work in opposition of phase. When we have four Stirling engines arranged at the tops of a square as in Figure 14, the engines that are on a same diagonal are in phase and are 180 ° out of phase by compared to the other two engines arranged on the other diagonal. Forces transmitted to the outside by this set are fully compensated, which reduces vibrations transmitted to the outside.

    La variante de la figure 15 montre simplement deux paires de moteurs Stirling dont les volumes de compression VCA, VCB, respectivement VCC, VCD, alternativement les volumes d'expansion VεA, VEB, respectivement VEC, VED, sont reliés par deux résonateurs tubulaires T1, respectivement T2, alors que les volumes de compression VCA et VCC d'une part, et les volumes de compression VCB et VCD, d'autre part, alternativement les volumes d'expansion VEA et VEC d'une part et les volumes d'expansion VEB et VED, d'autre part, sont reliés les uns aux autres par des tubes de liaison TC1 et TC2 dont le rôle est d'assurer que les pressions des volumes de compression, alternativement d'expansion, ainsi reliés sont les mêmes étant donné que les moteurs disposés en diagonales sont en phase.The variant of FIG. 15 simply shows two pairs of Stirling engines whose compression volumes V CA , V CB , respectively V CC , V CD , alternatively the expansion volumes V εA , 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, alternatively the volumes of expansion V EA and V EC on the one hand and expansion volumes V EB and V ED , on the other hand, are connected to each other by T C1 and T C2 connecting tubes whose role is to ensure that the pressures of compression volumes, alternatively expansion, thus connected are the same since the motors arranged diagonally are in phase.

    La figure 16 montre deux moteurs Stirling illustrés par leurs seuls volumes de compression VCI, VCII, alternativement leurs volumes d'expansion VEI, VEII reliés par un résonateur tubulaire 18.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.

    La figure 17 montre le chauffage d'un résonateur tubulaire 18 reliant deux moteurs Stirling comme illustré par les figures 14 à 16, disposé dans une enceinte de chauffage 26. Les extrémités respectives du tube 18 de ce résonateur communiquent avec les volumes d'expansion VEI, VEII de deux moteurs Stirling. Ainsi le tube 18 du résonateur commun à ces deux moteurs constitue également un élément de chauffage commun à ces deux moteurs. Il serait également envisageable d'utiliser plusieurs tubes de résonance 18 en parallèle afin d'augmenter la surface d'échange et d'améliorer le transfert de chaleur.FIG. 17 shows the heating of a tubular resonator 18 connecting two Stirling motors as illustrated by FIGS. 14 to 16, disposed in a heating chamber 26. The respective ends of the tube 18 of this resonator communicate with the expansion volumes V EI , V EII of two Stirling engines. Thus the tube 18 of the resonator common to these two motors is also 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.

    Tous les exemples qui précèdent montrent une machine Stirling fonctionnant en tant que moteur d'entraínement d'un générateur électrique. Or il est bien connu que les machines Stirling peuvent aussi fonctionner en mode inversé: au lieu de chauffer le gaz de travail circulant à travers la chambre d'expansion pour produire de l'énergie mécanique, il est aussi possible, en entraínant mécaniquement le piston de transfert, de produire du froid par la détente du gaz dans cette chambre d'expansion.All the above examples show a machine Stirling functioning as a drive motor of a electric generator. Now it is well known that machines Stirling can also work in reverse mode: instead to heat the working gas flowing through the chamber of expansion to produce mechanical energy, it is also possible, by mechanically driving the piston of transfer, to produce cold by relaxing the gas in this expansion chamber.

    Etant donné que dans ce mode de fonctionnement, le tube de résonance utilisé est entièrement passif, celui-ci ne peut fonctionner que si il est alimenté en énergie par le cycle Stirling. Ceci implique que pour une machine cryogénique, la section aE du piston de transfert 6, 6a délimitant le volume d'expansion VE soit plus faible que la section aC de ce piston de transfert 6, 6a délimitant le volume de compression VC. Le rapport de ces deux section aE/aC détermine le niveau de température le plus bas qui peut théoriquement être atteint.Since in this mode of operation, the resonance tube used is entirely passive, it can only work if it is supplied with energy by the Stirling cycle. This implies that for a cryogenic machine, the section a E of the transfer piston 6, 6a delimiting the expansion volume V E is smaller than the section a C of the transfer piston 6, 6a delimiting the compression volume V C . The ratio of these two sections to E / a C determines the lowest temperature level that can theoretically be reached.

    Claims (17)

    1. A method for transmitting mechanical energy between a transfer piston (6, 6a) of a Stirling machine and a moveable induction member (11) of a generator or of an electric motor, the transfer piston (6, 6a) being mounted in a cylinder (2), according to which a working gas is periodically displaced between an expansion chamber (VE) and a compression chamber (VC) constituting the working volume of said Stirling machine, with the aid of said transfer piston (6, 6a), said chambers being associated respectively with two working faces of said transfer piston (6, 6a), by making the gas pass through a hot (7), alternatively cold exchanger, linked to a heat source, a regenerator (9) and a cooling exchanger (8) linked to a heat sink and an elastic restoring force is exerted on this transfer piston (6, 6a), characterised by disposing in said cylinder (2) the only transfer piston (6, 6a), one of the compression (VC), expansion (VE) chambers being linked to a pneumatic resonator (18), the frequency of said resonator is adjusted to make it act as a second piston amplifying the pressure wave and to create a phase shift between the movement of the transfer piston (6, 6a) along an X-axis oriented towards the expansion chamber (VE) and the pressure variation of said gas contained in said working volume, a component px of said pressure variation being opposed to the movement of said transfer piston (6, 6a) by which the flow friction forces exerted in the tubular resonator (18) become compensated, in providing the piston at the compression volume side with elastic suspension means (10; 3) creating a restoring force, a section ratio (a C /a E )≥0.35 is created between the piston working faces associated respectively to the compression volume (VC) and to the expansion volume (VE) in such a way as to maintain said transfer piston (6, 6a) in a periodic movement at a controlled amplitude in adjusting the braking forces exerted upon the said piston (6, 6a) and to transmit from said piston (6, 6a) to said moveable induction member (11) all of said mechanical energy produced .
    2. The method as claimed in claim 1, wherein to transmit said mechanical energy from said transfer piston (6, 6a) to said moveable induction member (11) of an electric generator, the ratio (aC/aE) created between the section (aC) of that working face of this transfer piston which is associated with said compression volume (Vc) and the section (aE) of this transfer piston which is associated with that expansion volume (VE) lies between 40 and 60%.
    3. The method as claimed in one of the preceding claims, wherein an end (6a) of said piston (6, 6a) is made to exit said cylinder (2) in a leak-tight manner so as to place said end in communication with a closed volume (3) in which said electric generator is disposed and said elastic restoring force is exerted with the aid of the pressure variations of the working gas contained in said closed volume (3), consecutively upon the displacement of said piston (6, 6a).
    4. The method as claimed in one of the preceding claims, wherein to avoid the formation of steep-fronted waves, the section of a tubular duct intended to form said pneumatic resonator (18) is varied.
    5. The method as claimed in claim 4, wherein a Helmholtz volume (19) is disposed at the opposite end of said tubular duct (18) from that which is linked to one of said compression (VC), expansion (VE) chambers of said Stirling machine.
    6. The method as claimed in claims 4 or 5, wherein a part (18a) of the tubular duct with variable section is disposed inside the Helmholtz volume (19).
    7. The method as claimed in claims 5 or 6, wherein the working gas contained in said Helmholtz volume (19) is cooled, respectively heated, in a controlled manner.
    8. The method as claimed in one of the preceding claims, wherein the natural frequency of said resonator (18) is adjusted by forming said working gas by mixing gases of various molecular masses in a specified proportion.
    9. The method as claimed in claim 1, wherein to transmit said mechanical energy of said moveable induction member (11) of an electric motor to said transfer piston, the section (aE) of that end of the transfer piston which is associated with said expansion chamber (VE) is dimensioned smaller than the section (aC) of that end of the transfer piston (6, 6a) which is associated with the compression chamber (VC).
    10. A device for implementing the method as claimed in claim 1, wherein said piston is kinematically secured to said moveable induction member (11).
    11. The device as claimed in claim 10, wherein said elastic restoring force exerted on said piston (6, 6a) is produced by a closed space (10; 3) containing gas of a specified volume determined as a function of the desired natural frequency of said piston (6, 6a) and one of the walls of which consists of a face of said piston (6, 6a) whose surface area corresponds to the difference in area of said working surfaces.
    12. The device as claimed in one of the preceding claims, wherein said moveable member is a rotary member, linked to said piston (6'a, 21) by a connecting-rod assembly (23, 24), linear means of guidance (31) being associated with said piston (6'a, 21).
    13. The device as claimed in one of the preceding claims, wherein said resonator consists of two identical tubular elements (T1, T2) disposed in diametral opposition with respect to said transfer piston (6, 6a).
    14. The device as claimed in one of the preceding claims, wherein said tubular resonator (18) is linked to the expansion chamber (VE) of the Stirling machine and that it is associated with heating means constituting the hot source of said Stirling machine.
    15. The device as claimed in one of the claims 10, 11 and 14, wherein four Stirling devices are linked together by means of four tubular resonators (T1 - T4), the transfer pistons of two non-adjacent Stirling devices working in phase and the other two in phase opposition.
    16. The device as claimed in one of the claims 10, 11, 12 and 14, wherein each end of the tubular resonator (18) is linked to one of the cold (VC), hot (VE) chambers of a Stirling machine.
    17. The device as claimed in one of the preceding claims, wherein said heating means exhibit the form of a solar radiation collector (28, 29).
    EP00912325A 1999-04-07 2000-04-05 Method and device for transmitting mechanical energy between a stirling engine and a generator or an electric motor Expired - Lifetime EP1165955B1 (en)

    Priority Applications (1)

    Application Number Priority Date Filing Date Title
    EP00912325A EP1165955B1 (en) 1999-04-07 2000-04-05 Method and device for transmitting mechanical energy between a stirling engine and a generator or an electric motor

    Applications Claiming Priority (4)

    Application Number Priority Date Filing Date Title
    EP99810286A EP1043491A1 (en) 1999-04-07 1999-04-07 Process and device for generating and transferring mechanical energy from a Stirling engine to an energy consuming element
    EP99810286 1999-04-07
    PCT/CH2000/000199 WO2000061936A1 (en) 1999-04-07 2000-04-05 Method and device for transmitting mechanical energy between a stirling engine and a generator or an electric motor
    EP00912325A EP1165955B1 (en) 1999-04-07 2000-04-05 Method and device for transmitting mechanical energy between a stirling engine and a generator or an electric motor

    Publications (2)

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    EP1165955A1 EP1165955A1 (en) 2002-01-02
    EP1165955B1 true EP1165955B1 (en) 2005-08-10

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    EP99810286A Withdrawn EP1043491A1 (en) 1999-04-07 1999-04-07 Process and device for generating and transferring mechanical energy from a Stirling engine to an energy consuming element
    EP00912325A Expired - Lifetime EP1165955B1 (en) 1999-04-07 2000-04-05 Method and device for transmitting mechanical energy between a stirling engine and a generator or an electric motor

    Family Applications Before (1)

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    EP99810286A Withdrawn EP1043491A1 (en) 1999-04-07 1999-04-07 Process and device for generating and transferring mechanical energy from a Stirling engine to an energy consuming element

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    EP (2) EP1043491A1 (en)
    AT (1) ATE301773T1 (en)
    DE (1) DE60021863T2 (en)
    WO (1) WO2000061936A1 (en)

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    AU2003239866A1 (en) * 2002-05-24 2003-12-12 Stm Power Inc. Multiple cylinder stiriling engine for electrical power generation
    JP3769751B2 (en) * 2003-02-19 2006-04-26 ツインバード工業株式会社 Stirling cycle engine
    US7017344B2 (en) * 2003-09-19 2006-03-28 Pellizzari Roberto O Machine spring displacer for Stirling cycle machines
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    WO2009070771A1 (en) * 2007-11-28 2009-06-04 Tiax Llc Free piston stirling engine
    ITLI20080007A1 (en) * 2008-07-08 2010-01-08 Fabio Prosperi ELECTRIC GENERATOR POWERED BY HEAT SOURCES
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    US8096118B2 (en) * 2009-01-30 2012-01-17 Williams Jonathan H Engine for utilizing thermal energy to generate electricity
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    US6510689B2 (en) 2003-01-28
    DE60021863T2 (en) 2006-05-24
    WO2000061936A1 (en) 2000-10-19
    EP1165955A1 (en) 2002-01-02
    US20020096884A1 (en) 2002-07-25
    ATE301773T1 (en) 2005-08-15
    DE60021863D1 (en) 2005-09-15
    EP1043491A1 (en) 2000-10-11

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