EP0218554B1 - Machine stirling - Google Patents

Machine stirling Download PDF

Info

Publication number
EP0218554B1
EP0218554B1 EP86810429A EP86810429A EP0218554B1 EP 0218554 B1 EP0218554 B1 EP 0218554B1 EP 86810429 A EP86810429 A EP 86810429A EP 86810429 A EP86810429 A EP 86810429A EP 0218554 B1 EP0218554 B1 EP 0218554B1
Authority
EP
European Patent Office
Prior art keywords
piston
engine
heat pump
stirling
resonance tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP86810429A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0218554A1 (fr
Inventor
Jean-Pierre Budliger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Budliger Jean-Pierre
Original Assignee
Budliger Jean-Pierre
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Budliger Jean-Pierre filed Critical Budliger Jean-Pierre
Priority to AT86810429T priority Critical patent/ATE40738T1/de
Publication of EP0218554A1 publication Critical patent/EP0218554A1/fr
Application granted granted Critical
Publication of EP0218554B1 publication Critical patent/EP0218554B1/fr
Expired legal-status Critical Current

Links

Images

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
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F02G1/0445—Engine plants with combined cycles, e.g. Vuilleumier
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F25B9/145—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle pulse-tube cycle
    • 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
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • 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
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • F02G2243/04—Crank-connecting-rod drives
    • F02G2243/08—External regenerators, e.g. "Rankine Napier" 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
    • F02G2243/02—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder
    • F02G2243/22—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having pistons and displacers in the same cylinder with oscillating cylinders
    • 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
    • F02G2250/00—Special cycles or special engines
    • F02G2250/18—Vuilleumier cycles
    • 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
    • F02G2250/00—Special cycles or special engines
    • F02G2250/27—Martini Stirling engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2270/00—Constructional features
    • F02G2270/50—Crosshead guiding pistons
    • 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
    • F02G2270/80—Engines without crankshafts

Definitions

  • the present invention relates to a Stirling machine comprising a transfer piston mounted in a cylinder delimiting two compartments with variable volumes, of compression, respectively of expansion of a gaseous working fluid enclosed in this machine, the compression compartment communicating with the expansion compartment via a conduit containing a heat exchanger intended to be associated with a hot source, a regenerator and a heat exchanger intended to be associated with a heat sink and an oscillating member synchronized with said transfer piston.
  • the W. Beale patent, US-4183 214 describes an assembly in which a Stirling engine drives a Stirling heat pump in the early 1970s. It is a single piston free piston machine. This configuration requires the storage of energy in the form of a mobile mass whose role is to absorb the energy produced during the cycle period when the engine provides work and to return it to the heat pump cycle.
  • This work was the subject of an experimental construction of 100 W (see WT Beale, CF Rankine, D. Gedeon, C. Kinzelman: Duplex stirling heating-only gas-fired heat pump feasibility study - NTIS PB 81- 181323 / GRI 79/0047).
  • This heat pump essentially comprises three mobile elements arranged in the same cylinder.
  • a heavy central engine piston divides the working volume into an engine compartment and a heat pump compartment, each compartment having a light transfer piston.
  • the movement of the central engine piston causes the periodic variation of the gas pressure in the engine compartment and a similar variation in phase opposition in the heat pump compartment.
  • the transfer piston By the movements of the transfer piston, the gas periodically moves back and forth between the expansion chamber and the compression chamber, through a hot exchanger, a hot regenerator and a cold engine exchanger, respectively through an exchanger associated with a cold source, a cold regenerator and an exchanger intended to transfer the heat pumped from the cold source.
  • the movements of the two transfer pistons precede the movement of the central engine piston so that the expansion of the gas occurs when most of the gas is contained in the hot expansion chamber of the engine compartment, respectively in the expansion chamber heat pump cold.
  • gas compression occurs in each compartment, when most of the gas is contained at temperatures close to ambient temperature in the compression chambers.
  • the periodic and synchronous movement of the three pistons can be maintained by the single pressure of the working gas acting on the different surfaces of the respective pistons.
  • the engine piston is suspended by the gas cushions formed by the engine compartment on one side and the heat pump compartment on the other side and oscillates under resonance conditions.
  • the transfer pistons are kept in oscillation by the action of other gas cushions supplied by the piston rods or return springs which act either between the transfer pistons and the driving piston on the one hand, and the respective ends of the cylinder, on the other hand.
  • the Benson patents US-3,928,974 and 4,044,558 describe another Stirling engine assembly Stirling heat pump comprising an engine transfer piston, connected to the heat pump transfer piston by a rod and two opposite free pistons, balanced dynamically compressing and expanding the common working gas in a closed circuit.
  • the engine and heat pump cycles are classic sinusoidal Stirling cycles with constant volume heat exchange and isothermal variable volume chambers. In practice, however, there is a substantial deviation which is all the more significant as the temperature difference is small between the hot exchanger and the cold exchanger and the pressure ratio of the cycle is large. These deviations are therefore far less significant for a Stirling engine with a temperature difference of 600 ° C between the hot and cold exchangers than for a heat pump with a relatively small temperature difference between heat source and sink.
  • the gas is brought in and removed periodically from the transfer part of the engine and from the heat pump by means of oscillating engine pistons, arranged separately.
  • engine pistons are used to periodically accumulate gas and to store mechanical energy, which is then brought back to the transfer volumes.
  • the process is arranged so that the pressure decreases at the maximum expansion volume at high temperature of the engine and at the maximum expansion volume at low temperature of the heat pump. Conversely, the pressure increases when the two compression volumes are large.
  • cycle-VM (from the name of its inventor Vuilleumier) which does not require any engine piston.
  • This solution only comprises two free transfer pistons oscillating with a phase shift between the two pistons. Their movement subjects the entire volume of work to a common pressure which varies periodically. The gas in the high temperature expansion chamber and in the cold expansion chamber undergoes an engine cycle providing work, while the work is absorbed in the common compression chamber. The only significant pressure differences exist only at the seals of the relatively small volumes of the air bags serving as return springs.
  • the object of the present invention is to at least partially remedy the drawbacks of the above-mentioned solutions.
  • the subject of this invention is a Stirling machine according to claim 1.
  • the oscillating pressure wave in the resonance tube makes it possible to reach pressure variations Pmax / Pmin from 1.5 to 2.0, even with relatively large dead volumes in the engine and heat pump compartments. This allows the cross section of the flow passages through the heat exchangers to be increased to some extent, thereby reducing losses due to flow resistances.
  • the dead volumes in the transfer piston chambers can also be increased, which improves the reliability of the operation of the free piston mechanisms.
  • the assembly illustrated in FIG. 1 comprises an engine compartment 1 formed by a cylinder which encloses a transfer piston 2 which delimits in this cylinder an expansion volume V E and a compression volume Vci. These two volumes communicate with each other by a heat exchanger 3 associated with a hot source (not shown), a regenerator 4 and a heat exchanger 5 associated with a circuit. heating (not shown).
  • This assembly also includes a second compartment 6 formed by a cylinder coaxial with that of the engine compartment 1 and which constitutes a heat pump.
  • the second compartment 6 contains a transfer piston 7 linked to the transfer piston 2 by a rod 8 of section SV associated with a seal 9. This piston 7 delimits in the compartment 6 a compression volume Vc 2 and a volume d 'expansion V K.
  • This transfer piston 7 is also provided with a rod 13 slidingly mounted in a chamber 14 of section SW closed hermetically by a seal 15.
  • This chamber 14 constitutes a pneumatic return spring.
  • the two compartments 1 and 6 which are hermetically separated by the rod 8 associated with the seal 9 are connected by a resonance tube 16, the two ends of which terminate in the two compression volumes V C1 respectively Vc 2 .
  • This resonance tube plays the role of an engine piston, transmitting the work from the engine compartment 1 to that of the heat pump 6.
  • the expansion volume V E is at high temperature, while the compression volume V C1 is at low temperature, here close to ambient temperature. These two volumes vary cyclically following the alternating movement of the transfer piston 2. Since the gas column of the resonance tube 16 is subjected to a pressure wave which causes it to oscillate at the frequency of the transfer piston 2, this tube resonance plays the role of an engine piston which periodically compresses and expands the gas contained in the engine compartment 1 and, in phase opposition, in the heat pump compartment 6.
  • the diagram in fig. 2 illustrates the variations in volume and pressure in each of the two compartments.
  • the bottom of the diagram relates to the heat pump compartment 6 and the top to that of the engine compartment 1.
  • the transfer piston (continuous line) precedes the pressure wave (broken lines) so that the gas in the engine compartment will always expand when the hot expansion volume is large and conversely, compression occurs when the compression volume is large.
  • the pressure rise also occurs at a large compression volume and the expansion at a large expansion volume.
  • the cyclic pressure change in the engine compartment is produced by a periodic change in the mass of gas it contains, instead of being consecutive to the displacement of a piston. It is assumed, in order to avoid an excessive heat flow produced by the engine compartment, that the mass flow enters and leaves the compression volume of the engine under roughly isothermal conditions.
  • the propagation of waves in a constant section tube faces the problem of the formation and propagation of shock waves. To avoid this phenomenon, it is necessary to vary the section of the tube. When this section is convergent with respect to the direction of propagation of the waves, they are gradually reflected. This is the reason why the resonance tube 16 connecting the compartments 1 and 6 of FIG. 1 will preferably have two conical sections 16a respectively 16b, each converging towards the compartments 1 and 6 to which their ends are connected, these conical sections being connected to one another by a cylindrical section.
  • This method takes into account the friction of the gas on the walls, the heat exchange through them as well as changes in section of the resonance tube.
  • the conditions of the gas in the engine and / or Stirling heat pump part of the assembly are also established by a succession of time increments as a function of the displacement of the pistons and of the gas exchange with the resonance tube.
  • the displacement of the pistons is firstly fixed according to a determined kinematics. Once the calculation result approaches the desired periodic conditions, it is possible to determine the movement of the free pistons according to the set of forces which act on them. In the event of stability of the assembly, the periodicity is maintained both for the movements of the transfer pistons and for the movement of the gas.
  • the dimension of the smallest section which is adjacent to the engine and / or heat pump part, must be fixed according to the volume flow rate of gas to be displaced and depends first of all on the oscillation pressure ratio to be established and the dead volume of the Stirling part to consider. This last point is of capital interest for the whole system, because by choosing a resonance tube of appropriate section, it is possible to consider Stirling systems having relatively high dead volumes. These resonance tube systems are therefore less sensitive to the dead volume of the Stirling part than in other free piston systems. As a result, the heat exchange surfaces can be dimensioned more comfortably than in other known systems, which makes it possible to increase the overall performance factors.
  • the dimensions of the engine part of the assembly correspond to those of the engine used by W.R. Martini director of Martini Engineering 2303 Harris, Richland, Washington 99352, in "A simple method of calculating Stirling engines for engine design optimization".
  • the various data relating to this engine, heat exchange, efficiency, etc. are known.
  • sections Sv and Sw depend essentially on the permissible mass m of the transfer pistons 2 and 7 and on the friction forces acting on these pistons. These essentially depend on the width of the seals 9 and 15 (fig. 1) subjected to high pressures and therefore on the diameter of the sections Sv and Sw. These friction forces obviously also depend on the nature of the seals used.
  • the assembly described only works with two seals working with cylinders of relatively small diameters. The removal of an engine cylinder from large diameter constitutes from this point of view an important improvement on the technological level while making it possible to reduce the losses by friction.
  • the assembly consisting of a free double piston and only one air spring volume, seems particularly well suited for adapting energy regulation.
  • One possibility is to use a linear alternator to control the phase angle of the movement of the free piston relative to the pressure wave. This phase angle can also be adjusted by a slight variation in the volume of the dead space of the air spring.
  • Another possibility would be to vary the average pressure of the working gas which, combined with one of the other two solutions, would make it possible to control the energy produced under a wide range of operating conditions.
  • FIG. 5 shows a configuration which is indistinguishable from that of FIG. 1 only by the fact that the two transfer pistons 2 'and 7' are independent of each other, each therefore having a rod Sv, Sw working with a volume of gas 14a, 14b acting as a spring pneumatic.
  • the variant of fig. 6 only has one engine compartment 1 "and a transfer piston 2".
  • the resonance tube 16 "leads to a dead volume 17 and it is this tube itself which plays the role of heat pump, as explained by the diagram in FIG. 8.
  • One end of this tube is connected to the compression volume V C1 of the engine compartment 1 ", itself associated with a heat exchanger 5" distilled to cool it.
  • a scale of length L is shown on the abscissa ordered a temperature scale T.
  • the dashed line represents the temperature of the wall of the resonance tube
  • the solid lines show the flow of the gas, this being at low pressure when it flows towards the engine compartment (arrow F i ) and at high pressure when it flows towards the dead volume 17 (arrow F 2 ).
  • Line Tc represents the temperature of the cooling water of the compression volume and line T K la temperature of the heat pump cold source.
  • fig. 7 illustrates a variant which comprises a combination of a heat pump motor assembly with two free and independent transfer pistons 2 * and 7 * , each associated with a seal 18 * respectively 19 * and suspended elastically by two springs 14a * respectively 14b * , comprising a resonance tube 16 * connected to the compression volumes V C1 , Vc 2 of the two engine compartments 1 * , respectively heat pump 6 * themselves in communication with one another.
  • the expansion volume compartment V E of the engine compartment 1 * is connected to compartment V C1 by a heat exchanger 3 * associated with a hot source (not shown), a regenerator 4 * and a heat exchanger 5 * associated with a cold source.
  • the major drawback of the known VM system lies mainly in pressure ratios which remain too low, so that the energy pumping efficiency is low.
  • the pressure variation is not directly linked to the dead volumes of the Stirling part, but essentially depends on the quality of the resonator.
  • each piston is held in a fixed equilibrium position and oscillates around this position. No centering system is therefore necessary to compensate for a possible drift of the piston.
  • the oscillation frequency of the pistons, as well as that of the resonance tube, becomes independent of the gas pressure. Therefore, it is possible to vary the heating power by varying the average system pressure.
  • the overall performance or the gain factor of the entire heat pump will therefore remain substantially independent of the load or seasonal variations in heating demand.
  • the first of these configurations comprises a tube whose section varies according to a parabolic law (corresponding substantially to a cone) of 1.8 m in length, the smallest section of which is 2.5 cm2 and the largest of which is 15.2 cm 2 .
  • the small section is connected to a cylinder in which is mounted a piston actuated in a sinusoidal movement by a connecting rod mechanism.
  • the dead volume of the cylinder can vary from 150 to 300 cm3 and the displacement volume of the piston can vary from 19 to 38 cm3.
  • the large section of the conical tube is connected to a cylindrical tube whose section corresponds to the large section of the conical tube and whose length is 1.2 m and ends in a dead volume of approximately 5 I.
  • the second configuration differs from the first only by the fact that the dead volume of 5 is replaced by a second conical tube of 1.2 m in length, the largest section of which corresponds to that of the cylindrical tube, namely 15.2 cm 2 and of which the smallest section is 5 cm 2 .
  • the gas used was nitrogen at an average pressure of between 1. 105 to 2. 105 Pa.
  • the variation of the frequency of the piston driven by a DC motor makes it possible to determine the resonance conditions of the gas column.
  • the dead volume of the cylinder simulates that of the Stirling system.
  • the diagram in fig. 10 also recorded during the tests, shows, on the one hand, a curve A corresponding to the displacement of the piston in the cylinder and, on the other hand, a curve B corresponding to the corresponding pressure variation in the resonance tube.
  • This recording shows that this variation in pressure as a function of time is effectively close to a sinusoidal variation as desired in a heat pump of the VM type with free pistons.
  • the COP corresponds to the ratio between the useful heating power and the heating power supplied to the hot source of the engine compartment of the engine-heat pump assembly.
  • the achievable energy gain is between 30 and 45%.
  • expansion volumes V E and of compression Vc are connected by a heat exchanger 3a intended to absorb heat, a regenerator 4a and a heat exchanger 5a intended to yield heat.
  • a resonance tube 16.1 is connected to the compression volume Vc.
  • This resonance tube is closed at one end like that illustrated in FIG. 7 and comprises a portion 16.1 a of progressively increasing section, a portion 16.1 of constant section and a portion 16.1 of decreasing section.
  • the end of the portion 16.1 a which is connected to the compression volume Vc is connected to this volume by a portion 16.1 which flares slightly, so that the smallest section of this portion 16.1a is located in the part 16.1s which is slightly behind the compression volume Vc.
  • This configuration which is applicable to all the previous embodiments, aims to better recover the dynamic energy of the gas during its reciprocating movement and thus to reduce the losses of this resonance tube.
  • This resonance tube 16.1 in this application makes it possible to increase the pressure ratio between the volumes V E and Vc and consequently to obtain for the same size of machine, better efficiency.
  • FIG. 12 shows two motor heat pump M assemblies HP similar to those of FIGS. 1 or 7 for example, connected to each other by a resonance tube 16.2.
  • FIG. 13 shows another variant in which part of the pressure energy of the resonance tube 16.3 is used to move a piston carrying permanent magnets 24 housed in the resonance tube, opposite a coil 25 in which a voltage is induced.
  • This solution can be useful in the case of an installation located in a remote place without an electrical line, giving in addition a source of electrical energy which can replace a small generator for relatively low powers and used for the control of the machine and the drive of the auxiliary parts of the Stirling machine (fans of the air burner and water pumps).
  • the pressure waves from the resonance tube generate lateral forces on the pistons of the Stirling MS machine (fig. 14).
  • the resonance tube 16.4 divides into two branches 16.4g and 16.4d which come together to form a single tube.
  • it can take the form of a hairpin 16.4e to balance the forces which act along the tube.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Polarising Elements (AREA)
  • Noodles (AREA)
  • Holo Graphy (AREA)
EP86810429A 1985-10-07 1986-09-30 Machine stirling Expired EP0218554B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86810429T ATE40738T1 (de) 1985-10-07 1986-09-30 Stirling-maschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH4325/85A CH664799A5 (fr) 1985-10-07 1985-10-07 Ensemble moteur-pompe a chaleur stirling a piston libre.
CH4325/85 1985-10-07

Publications (2)

Publication Number Publication Date
EP0218554A1 EP0218554A1 (fr) 1987-04-15
EP0218554B1 true EP0218554B1 (fr) 1989-02-08

Family

ID=4273969

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86810429A Expired EP0218554B1 (fr) 1985-10-07 1986-09-30 Machine stirling

Country Status (6)

Country Link
US (1) US4717405A (ja)
EP (1) EP0218554B1 (ja)
JP (1) JPH07116986B2 (ja)
AT (1) ATE40738T1 (ja)
CH (1) CH664799A5 (ja)
DE (1) DE3662071D1 (ja)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0660770B2 (ja) * 1986-03-25 1994-08-10 川崎重工業株式会社 熱駆動ヒ−トポンプ
US4894995A (en) * 1989-05-22 1990-01-23 Lawrence LaSota Combined internal combustion and hot gas engine
JP2902159B2 (ja) * 1991-06-26 1999-06-07 アイシン精機株式会社 パルス管式冷凍機
DE4234678C2 (de) * 1991-10-15 2003-04-24 Aisin Seiki Reversible Schwingrohr-Wärmekraftmaschine
CN1098192A (zh) * 1993-05-16 1995-02-01 朱绍伟 回转式脉管制冷机
GB2279139B (en) * 1993-06-18 1997-12-17 Mitsubishi Electric Corp Vuilleumier heat pump
JPH10148411A (ja) * 1996-11-15 1998-06-02 Sanyo Electric Co Ltd スターリング冷凍装置
TW347464B (en) * 1996-11-15 1998-12-11 Sanyo Electric Co Stirling cycle machine
EP1043491A1 (fr) * 1999-04-07 2000-10-11 Jean-Pierre Budliger Procédé pour générer et transmettre une énergie mécanique d'un moteur stirling à un organe consommateur d'énergie et dispositif pour la mise en oeuvre de ce procédé
US6564552B1 (en) 2001-04-27 2003-05-20 The Regents Of The University Of California Drift stabilizer for reciprocating free-piston devices
FR2831598A1 (fr) * 2001-10-25 2003-05-02 Mdi Motor Dev Internat Groupe motocompresseur-motoalternateur a injection d'air comprime additionnel fonctionnant en mono et pluri energies
US6711905B2 (en) 2002-04-05 2004-03-30 Lockheed Martin Corporation Acoustically isolated heat exchanger for thermoacoustic engine
JP4193970B2 (ja) * 2002-06-19 2008-12-10 独立行政法人 宇宙航空研究開発機構 圧力振動発生装置
JP4796393B2 (ja) * 2006-01-17 2011-10-19 株式会社日立製作所 超電導電磁石
CH702965A2 (fr) 2010-04-06 2011-10-14 Jean-Pierre Budliger Machine stirling.
GB2498378A (en) * 2012-01-12 2013-07-17 Isis Innovation Linear Stirling machine with expansion and compression pistons coupled by gas spring
CN106679231A (zh) * 2017-01-04 2017-05-17 上海理工大学 利用渔船发动机尾气余热驱动的维勒米尔制冷装置
US10724470B1 (en) 2019-05-21 2020-07-28 General Electric Company System and apparatus for energy conversion
US10598125B1 (en) 2019-05-21 2020-03-24 General Electric Company Engine apparatus and method for operation
US10711733B1 (en) 2019-05-21 2020-07-14 General Electric Company Closed cycle engine with bottoming-cycle system
WO2020236863A1 (en) 2019-05-21 2020-11-26 General Electric Company Monolithic heater bodies
CN110118450B (zh) * 2019-05-23 2024-06-28 江苏热声机电科技有限公司 一种热声制冷机

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1534734A (fr) * 1966-04-14 1968-08-02 Philips Nv Dispositif pour convertir de l'énergie mécanique en énergie calorique ou inversement
GB1412935A (en) * 1971-10-05 1975-11-05 Stobart A F Fluid heating systems
US4044558A (en) * 1974-08-09 1977-08-30 New Process Industries, Inc. Thermal oscillator
US3971230A (en) * 1975-05-05 1976-07-27 Nasa Stirling cycle engine and refrigeration systems
US4044538A (en) * 1977-01-24 1977-08-30 Teijin Seiki Company Limited Arrangement of strand twisting apparatuses
US4114380A (en) * 1977-03-03 1978-09-19 Peter Hutson Ceperley Traveling wave heat engine
US4183214A (en) * 1977-05-05 1980-01-15 Sunpower, Inc. Spring and resonant system for free-piston Stirling engines
US4458495A (en) * 1981-12-16 1984-07-10 Sunpower, Inc. Pressure modulation system for load matching and stroke limitation of Stirling cycle apparatus
US4458489A (en) * 1982-07-27 1984-07-10 Mechanical Technology Incorporated Resonant free-piston Stirling engine having virtual rod displacer and linear electrodynamic machine control of displacer drive/damping
US4498296A (en) * 1983-07-01 1985-02-12 U.S. Philips Corporation Thermodynamic oscillator with average pressure control
US4610143A (en) * 1984-12-18 1986-09-09 North American Philips Corporation Long life vibration canceller having a gas spring

Also Published As

Publication number Publication date
CH664799A5 (fr) 1988-03-31
EP0218554A1 (fr) 1987-04-15
JPS6293477A (ja) 1987-04-28
JPH07116986B2 (ja) 1995-12-18
DE3662071D1 (en) 1989-03-16
ATE40738T1 (de) 1989-02-15
US4717405A (en) 1988-01-05

Similar Documents

Publication Publication Date Title
EP0218554B1 (fr) Machine stirling
US4044558A (en) Thermal oscillator
CN105066500B (zh) 一种热驱动脉冲管制冷机系统
EP0070780A1 (fr) Convertisseur d'énergie thermique en énergie électrique à moteur Stirling et générateur électrique intégré
US4489553A (en) Intrinsically irreversible heat engine
US4058382A (en) Hot-gas reciprocating machine with self-centered free piston
US3928974A (en) Thermal oscillator
US4458489A (en) Resonant free-piston Stirling engine having virtual rod displacer and linear electrodynamic machine control of displacer drive/damping
JP5852095B2 (ja) スターリング機関
US20050028535A1 (en) Compliant enclosure for thermoacoustic device
WO2003087680A1 (en) Thermoacoustic device
EP1165955B1 (fr) Procede et dispositif pour transmettre une energie mecanique entre une machine stirling et un generateur ou un moteur electrique
US7685818B2 (en) Connection of a free-piston stirling machine and a load or prime mover permitting differing amplitudes of reciprocation
AU2010269058A1 (en) Stirling cycle transducer for converting between thermal energy and mechanical energy
WO2005108879A1 (en) Cryocooler system with frequency modulating mechanical resonator
US5414997A (en) Thermal lag machine
JP2009281614A (ja) フリーピストン型のスターリングサイクル機械
Arafa et al. Developments and recent patents on Thermoacoustic devices
KR20000012903A (ko) 맥동관 냉동기의 구동 모터 방열장치
Boukhanouf et al. Diaphragm Stirling engine design
JPH07198218A (ja) フリ−ピストン式熱ガス機関
FR2536788A2 (fr) Moteur thermique intrinsequement irreversible
JPS59131753A (ja) 熱ガス機関
JPH05626B2 (ja)
Pattapu A novel approach to design and fabrication of thermo-acoustic refrigerator using high amplitude sound waves

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19870806

17Q First examination report despatched

Effective date: 19880225

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BUDLIGER, JEAN-PIERRE

RIN1 Information on inventor provided before grant (corrected)

Inventor name: BUDLIGER, JEAN-PIERRE

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19890208

Ref country code: AT

Effective date: 19890208

REF Corresponds to:

Ref document number: 40738

Country of ref document: AT

Date of ref document: 19890215

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3662071

Country of ref document: DE

Date of ref document: 19890316

ITF It: translation for a ep patent filed

Owner name: MODIANO & ASSOCIATI S.R.L.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19890930

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19930920

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19930922

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Effective date: 19940930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19941001

EAL Se: european patent in force in sweden

Ref document number: 86810429.0

BERE Be: lapsed

Owner name: BUDLIGER JEAN-PIERRE

Effective date: 19940930

EUG Se: european patent has lapsed

Ref document number: 86810429.0

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19960925

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19960930

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19970930

Ref country code: FR

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19970930

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19970930

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19980930

Year of fee payment: 13

Ref country code: CH

Payment date: 19980930

Year of fee payment: 13

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990930

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050930