EP1745206B1 - Schallleistungsübertragungseinheit für thermoakustische systeme - Google Patents

Schallleistungsübertragungseinheit für thermoakustische systeme Download PDF

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Publication number
EP1745206B1
EP1745206B1 EP05759766A EP05759766A EP1745206B1 EP 1745206 B1 EP1745206 B1 EP 1745206B1 EP 05759766 A EP05759766 A EP 05759766A EP 05759766 A EP05759766 A EP 05759766A EP 1745206 B1 EP1745206 B1 EP 1745206B1
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EP
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Prior art keywords
acoustic
power transmission
transmission unit
thermoacoustic
unit according
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EP05759766A
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French (fr)
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EP1745206A1 (de
Inventor
Emmanuel Bretagne
Maurice-Xavier Francois
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Centre National de la Recherche Scientifique CNRS
Universite Pierre et Marie Curie Paris 6
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Centre National de la Recherche Scientifique CNRS
Universite Pierre et Marie Curie Paris 6
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/0435—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines the engine being of the free piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1402—Pulse-tube cycles with acoustic driver
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/14—Compression machines, plants or systems characterised by the cycle used 
    • F25B2309/1423—Pulse tubes with basic schematic including an inertance tube
    • 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

Definitions

  • This invention relates to thermal machines, motors and refrigerators employing a thermoacoustic energy conversion process.
  • thermoacoustic machines of all types including wave generators and thermoacoustic refrigerators, but also the family of Stirling and Ericsson machines and the family of pulsed gas tubes.
  • thermoacoustic machine Any thermal machine requires at least the presence of two heat sources at different temperatures, a mechanical work transmission system and an energy conversion agent describing a thermodynamic cycle.
  • the mechanical work takes the form of an acoustic work, expressed more commonly per unit of time in terms of acoustic workflow or acoustic power and corresponding to the average time of the product of the acoustic pressure by the volume flow rate. acoustic.
  • thermodynamic cycle and therefore of energy conversion is the basis of the operation of any thermal machine.
  • heat engines a quantity of heat is converted into acoustic work and in refrigerators a quantity of work is consumed to transfer heat from a so-called "low” temperature medium to another medium at higher temperature.
  • the power of the thermal machines is directly related to the "opening" of the thermodynamic cycle, i.e. the area formed by this cycle.
  • the conversion agent that describes the thermodynamic cycle is a fluid. This fluid is called “refrigerant”, and is circulated in a closed circuit where it vaporizes and condenses.
  • thermoacoustic machines the conversion agent is generally a gas, typically helium, and the thermodynamic cycle is implemented by an acoustic wave on a smaller scale corresponding to that of the displacement of a particle of fluid which oscillates. It is the cooperation of all the local thermodynamic cycles, cooperation naturally synchronized by the wave itself, which allows a conversion of energy at the global scale of the engine (also called wave generator) or the thermoacoustic refrigerator.
  • thermodynamic cycle takes place only in the contact zone, or acoustic thermal limit layer, between the fluid subjected to compression-expansion phases by the acoustic wave and a solid medium that produces the necessary heat sources. at the "opening" of the thermodynamic cycle.
  • This fluid / solid interaction in the boundary layer which results in heat exchanges between the fluid and the solid, results from temperature oscillations that accompany any acoustic propagation.
  • This fluid / solid interaction involves the dilatability of the fluid.
  • thermodynamic cycles performed can, depending on the type of acoustic field, be more like Brayton cycles or rather cycles of Ericsson and Stirling.
  • a first type of so-called "Brayton” operation is obtained when the acoustic wave is similar to a rather stationary wave, that is to say having a phase shift between acoustic pressure and particle displacement close to 180 °, and a second type of operation called 'Ericsson or Stirling' when the wave is rather progressive, that is to say has a phase shift between acoustic pressure and particle displacement close to 90 °.
  • thermodynamic cycle requires that thermodynamic transformations follow one another in a coordinated way in time.
  • heat input is such that the fluid of a thermoacoustic wave generator locally performs a thermal expansion (expansion) when its pressure is maximum and a thermal contraction when its pressure is minimal.
  • thermodynamic transformations which translates an 'arrangement' between the phases of displacement, compression-expansion and extension-contraction of the fluid is carried out by the acoustic wave.
  • the solid medium is a more or less dense and relatively uniform matrix allowing a good propagation of acoustic waves insofar as the typical dimensions are much smaller than the wavelength corresponding to the acoustic field.
  • This solid medium consists of a set of pores or channels, placed in parallel, allowing the passage of a fluid from one end to the other of the matrix. These channels can have very different shapes, and are not necessarily identical.
  • This active solid matrix in which the fluid oscillates, necessarily has a different appearance characteristic ⁇ ⁇ / R h to allow the realization of the two types of operation described above.
  • R h denotes the mean hydraulic radius of the solid matrix taken in the sense of the porous media.
  • ⁇ ⁇ is of the order of R h and the solid matrix is then commonly called a "stack".
  • ⁇ ⁇ is much greater than R h and the solid matrix is then called a "regenerator", with reference to the Stirling regeneration machines.
  • phase difference between the acoustic pressure and the acoustic velocity is close to zero or has an area where the phase shift is zero. On the contrary, in the case of the stack, this phase shift is still significant and close to 90 °.
  • Both the regenerator and the stack are stationary temperature distribution devices, despite the oscillating displacement of the fluid, because they are placed between two "heat sources". There is therefore a spatial distribution of heat sources with temperatures intermediate to those of the two external heat sources.
  • both of a stack and of a regenerator requires that they be each placed between two heat exchangers held at constant and different temperatures in order to constitute a thermal machine.
  • the terms "stack unit” or “regenerator unit” are then used to denote a stack or regenerator placed between two heat exchangers.
  • the temperature distribution both in a generator and in a stack is imposed in the case of a motor operation, by the supply of heat to one of the heat exchangers of the regenerator unit or the stack unit.
  • the heat input can be obtained from electrical energy, nuclear or solar, by combustion, or by recovery of any thermal rejection at appropriate temperature.
  • the temperature distribution in the regenerator is generated by the acoustic wave.
  • the stack units can be used in engine operation to generate thermoacoustic power in a thermoacoustic machine, thereby producing the same effect as an acousto-mechanical engine but with the advantage of not including any moving mechanical parts.
  • the regenerator units can be used to amplify the acoustic power flow generated by the motors or the stack units in an acoustic resonator.
  • the rate of amplification of the acoustic power in a regenerator is equal to the ratio of the temperature of the heat exchanger where the heat supply takes place to the one where the unconverted heat is extracted, the temperatures being expressed in Kelvin .
  • the amplification of the acoustic power flow is effected in the direction corresponding to positive temperature gradients.
  • the stack and regenerator units are used interchangeably to allow extraction of heat from a medium to be cooled. This heat is transferred to a higher temperature heat exchanger for disposal.
  • the highest temperature can be variably selected, which is an advantage over many refrigeration technologies such as condensing-vaporization refrigeration for example. It is thus not necessarily close to 293K and may for example be less than 200K for cryogenic applications or greater than 500K for applications in a high temperature environment.
  • a refrigeration unit in the form of a stack or regenerator unit directly influences the coefficient of performance of the unit, also called the energy conversion coefficient, which is defined as the ratio of the quantity of heat extracted. the amount of acoustic work consumed, and the temperature differential between the lowest temperature heat exchanger and the highest temperature heat exchanger.
  • a stack unit generally does not provide a coefficient of performance as high as that of a regenerator unit.
  • a regenerator unit is generally better suited to large temperature differentials than a stack unit.
  • regenerator unit or “extended regenerator unit” a regenerator associated with its two exchangers to which is joined a tube section and a third heat exchanger.
  • the tube section constitutes a volume of buffer gas for thermally isolating the hottest exchanger in the case of an acoustic power amplification unit or the coldest in the case of a refrigeration unit.
  • the third exchanger placed at one end participates in the control of the temperature distribution in the tube section.
  • the regenerator unit is called a "pulsed gas tube unit".
  • the vertically extended regenerator unit is preferably placed, the exchanger at the highest temperature among the second and third exchangers being placed at the altitude the highest.
  • thermoacoustic machine thus consists of active thermoacoustic units placed in an acoustic resonator.
  • the resonator has among others a role of waveguide. It can be used at its resonant frequency or not. For example, in the case of an acoustic energy source consisting of a loudspeaker, it is preferable to choose an operating frequency that is different from the resonant frequency.
  • the acoustic machine comprises an acoustic wave generator
  • the resonator geometry closely determines the operating frequency f POOR PERFORMANCE of the device.
  • the impedance Z is defined as being the ratio between the acoustic pressure P 1 and the acoustic velocity u 1 .
  • Each of these two parameters P 1 and u 1 can be measured locally and can access the impedance Z at each point.
  • the index 1 of each parameter specifies that it is an acoustic quantity, infinitely small of the first order.
  • the dimensionless impedance is the ratio
  • thermoacoustic units function properly only in areas where the amplitude of fluid particle displacements is reasonably low and the amplitude of the sound pressure is large.
  • thermoacoustic units This amounts to placing the thermoacoustic units in a zone of high dimensionless impedance.
  • An object of this invention is to allow an improvement in the overall performance of a thermoacoustic machine thermodynamically.
  • this invention is of interest for the realization of a thermoacoustic machine associating one or more units of pulsed gas tubes with a thermoacoustic wave generator composed of stack and regenerator units.
  • thermoacoustic machine comprising more than one thermoacoustic unit
  • the acoustic power transmission between two units of stack, regenerator or pulsed gas tube must, of course, be maximum in order to conserve the machine a significant energy efficiency.
  • thermoacoustic units Given the material size of the thermoacoustic units, an optimal operation of each of them can not be perfectly satisfied in the same area of high dimensionless impedance from more than 3 thermoacoustic units. It is then necessary to use an extension device of the same area of high dimensionless impedance ( Swift et al., US-6,658,862 ). However this extension device is inevitably consumer of acoustic power.
  • this first arrangement has few independent adjustment parameters. As a result, the malfunction of a single element of the cascade can be very detrimental to the operation of the whole.
  • thermoacoustic units in the same zone of high dimensionless impedance With the necessary coordination of the thermoacoustic units in the same zone of high dimensionless impedance and therefore their adjustment becomes more and more complex when the number of thermoacoustic units increases. Furthermore, an additional brake on the accumulation of thermoacoustic units in the same area of high dimensionless impedance is the difficulty of guaranteeing the stability of such a system during operation in variable conditions (for example, in a zone geographical area with high temperature differences between day and night).
  • An object of the present invention is therefore to propose a simple device in its design and in its operating mode allowing a significant transmission of acoustic power between each stack or regenerator unit, or pulsed gas tube while limiting the energy losses. by viscous dissipation mechanisms or by allowing to group in a space reduces several consecutive units without damaging their individual performance.
  • thermoacoustic unit at areas of high dimensionless impedance and to place several of them at zones of high dimensionless impedance, each of these zones being separated by a zone of low dimensional impedance.
  • Another object of the invention is to allow the establishment of acoustic parameters in accordance with an optimized operation of each thermoacoustic unit, this essentially independently of the operation of adjacent thermoacoustic units. This possibility of adjustment and control introduced by the invention is particularly advantageous when the units are grouped.
  • the invention also advantageously makes it possible to reduce the dimensions of such a machine and therefore its bulk.
  • shrinkage is meant an area in which the diameter is decreased relative to the largest tube diameter of the area of high dimensionless impedance.
  • the power transmission unit for thermoacoustic systems is an integral part of an acoustic resonator comprising a main tube of any geometry and generally of uniform diameter D.
  • This resonator in combination with the other elements of the device, defines the system frequency and the corresponding wavelength.
  • the main tube comprises according to the invention a first 1 and a second 2 element which are connected by a tube section 5 of reduced diameter d.
  • the ends of the first and second elements 1, 2, connected by said section of each tube 6, 7 comprises a cavity 8, 9 representing a closed volume connected to a conduit 10, 11, acting on the acoustic characteristics, and in particular on the acoustic volume flow, of the main tube ( figure 1 ).
  • Thermoacoustic cells or units 3, 4 are arranged in the resonator, in areas of high dimensionless impedance, two successive non-dimensional impedance zones being separated by a zone of low impedance.
  • branches 6, 7 make it possible to modify the acoustic parameters and in particular the volume flow rate at the inlet (or the outlet) of the reduced diameter tube section 5.
  • the invention therefore makes it possible to obtain an optimal transmission of the acoustic power between each thermoacoustic unit 3, 4 while maintaining a small overall size of the system.
  • the reduced diameter section 5 may consist of a succession of reductions and increases in diameter.
  • the evolution of the flow rate in the reduced diameter section can be controlled by acting on the local temperature gradient ( figure 10 ).
  • regenerator units have a better energy conversion efficiency than stack units and it is therefore recommended to use as many regenerator units as possible to compose a thermoacoustic machine.
  • the regenerator units however require the injection of an acoustic power at their end at 'ambient' temperature, that is to say at the end from which heat is rejected to the outside of the machine. , and can not be used exclusively in the composition of a thermoacoustic machine with the exception of any source of acoustic power such as a stack unit for example.
  • a preferred embodiment is to associate cascaded units to form a machine and thereby provide a large amplification of a small power initially created by a small stack unit or a mechanical acoustic source.
  • the low efficiency of the stack in comparison with the regenerators thus takes a negligible part in the efficiency total, especially since the amount of power dissipated in the transmission between units remains low.
  • the Figure 2 shows such a power transmission and amplification unit for thermoacoustic systems in a second embodiment of the invention.
  • the resonator includes a stack unit 12 for generating acoustic power, which will be amplified by cascaded regenerator units 13-14 and used by the "pulsed gas tube" units 15-16.
  • These thermoacoustic units 12-16 are each arranged in a zone of high dimensionless impedance in the resonator and are separated from the adjacent unit by a zone of low dimensional impedance.
  • the pass section for the acoustic wave is retained.
  • the diameter of the resonator may be larger to contain the thermal insulation (ceramic fiber) and the actual diameter can be matched to the inner diameter of a coaxial tube, itself thin to limit the effects of conductions thermal.
  • a pipe element 30 comprising a section of reduced diameter tube 21 and two branches 24, 25 it has a length equivalent to the acoustic plane at ⁇ / 2, where ⁇ denotes the length of wave of the preferred acoustic wave.
  • ⁇ denotes the length of wave of the preferred acoustic wave.
  • acoustically equivalent lengthwise conductor element at ⁇ / 2 it is meant that the resonator element is between two zones of high dimensionless impedance and incorporates a zero impedance section for the preferred acoustic wave.
  • the resonator comprises a first 17 and a second 18 elements connected at one of their ends by a first section of tube 21 of reduced diameter d ( Fig. 2 ).
  • the ends of the first 17 and second 18 elements each comprise a derived cavity 24, 25 comprising a duct 31, 32.
  • the device makes it possible to maintain a Reynolds number Re much lower than the critical Reynolds number. R ecritic beyond which the phenomenon of acoustic turbulence appears. This makes it possible both to reduce the linear energy dissipation, to keep the system laminar acoustic behavior, as well as to favor linear modeling.
  • the critical Reynolds acoustic, R ecritique typically has a value between 10 5 to 10 6 [ SM Hino et al. ; Journal of Fluid Mechanics 75 (1976) 193-207 ].
  • the Figure 11 shows a typical variation of the volume flow in the reduced tube 21 and the effect of the derived cavities 24, 25 on the reduction of the flow rate in the tube.
  • the first curve 33 shows the evolution of the volume flow
  • the second curve 34 shows the evolution of the acoustic pressure in the reduced diameter tube section 21 of the unit of transmission 30 of the figure 2 .
  • the reduction in flow in the tube will be adapted to the diameter reduction that reduces the developed length of the device.
  • FIG. Figure 2 A second possible embodiment of the pipe element 35 comprising a reduced diameter section and two branches is shown in FIG. Figure 2 , through a second tube 22 of reduced diameter d 2 connecting the other end of the second element 18 to a third element 19 of the main tube.
  • the length equivalent to the acoustic plane of this element of driving is much less than ⁇ / 4, for example it is typically equal to 15% of ⁇ / 4.
  • driving element of equivalent length much less than ⁇ / 4 acoustically means in the context of the invention that the resonator element is between two high impedance areas and incorporates low impedance sections but never zero for the preferred acoustic wave.
  • Each of the ends of the second 18 and third 19 main tube elements are connected via a conduit 36, 37 to a corresponding cavity placed in bypass 38, 39.
  • These cavities 38, 39 and 36, 37 are different ducts because it is thus allowed to independently adjust the operating conditions (ie the amplitude and the phase between pressure and acoustic speed) of each regeneration unit 13-16 to recreate at the input of each of these units operating conditions which are optimal.
  • this reduced diameter tube 22 makes it possible to create a zone of low dimensionless impedance over a length of weak tube, which thus makes it possible to make the power transmission unit compact.
  • the other end of the third main tube member 19 is connected through a third section 23 of reduced diameter tube d 3 to one end of a fourth tube member 20.
  • This third section 23 of reduced diameter tube d 3 and the associated branches 28, 29 form a driving element of length equivalent to ⁇ / 2 acoustically.
  • the fourth tube member 20 that completes the main tube is the refrigerator part of the thermoacoustic system.
  • This consists of two parallel-orifice pulsed gas tubes [Bretagne et al. ; "In progress of CEC-ICMC'03 - Anchorage”.
  • the paralleling is obtained by separating the main tube 20 at its other end into two secondary tube elements of reduced section.
  • the tubes are bent at 180 °.
  • the preferred acoustic wave can be either imposed when using a non-thermal acoustic power source, or correspond to a preferred acoustic mode of the resonator.
  • a source of thermal acoustic power it is mainly the strong resistance to the passage of the fluid imposed by the stack or regenerator units which determines its acoustic mode of operation by imposing the presence of speed nodes (position where the speed vanishes) in the close vicinity of the regenerator units. Consecutively the regenerator units will impose the presence of high impedance zones.
  • the acoustic mode of the resonator is modified by the absence or the presence of the second 13 and third 14 regenerator units ( Figure 2 ).
  • the presence of these two regenerator units generally has the effect of doubling the pulsation of the preferred acoustic wave.
  • FIG. 12A illustrates how the volumetric flow rate (first solid line and dotted line 40) and the sound pressure level (second continuous line curve 41) vary in an acoustic power transmission unit comprising a pipe element according to the second embodiment, ie having an equivalent length much less than ⁇ / 4 acoustically.
  • the Figure 12B explicit in a different and more detailed representation (Fresnel diagram) of the evolution of the phases and amplitudes of the pressure and volume flow between the ends C and A 2 of the acoustic power transmission unit and shows that the conditions ensuring optimal operation of each of the regenerator units are ensured.
  • the effect is capacitive in the acoustic sense, and the flow rate varies according to the first curve 40, and the sound pressure is generally conserved.
  • a flow quantity is taken from the first branch 42 to bring the acoustic volume flow to the inlet of the reduced diameter section 43 in advance with respect to the sound pressure.
  • the effect is inductive in the acoustic sense and the sound pressure varies according to the second curve 41 and the flow rate is maintained.
  • the acoustic flow rate being in advance of the sound pressure at H 1 , this has the effect of increasing the amplitude of the sound pressure along the tube.
  • the second derivative 44 will this time restore the flow and allow to adjust the phase and amplitude of the flow A2.
  • the favorable inlet conditions at the end of the second regenerator are satisfied, that is, the acoustic volume flow is in advance of the acoustic pressure at A2 and the amplitude of the acoustic pressure at A2. is greater than that at C, in order to recover a sufficient dimensionless impedance.
  • the invention has the additional advantage of making it possible to adjust the phase of the volume flow rate at the end (A2) of the second regenerator independently of its amplitude.
  • a penalizing case identified may be, for example, the cascading of too many regenerator units.
  • the present invention induces the correlation of the position of the thermoacoustic units and the transmission units which are interposed between the thermoacoustic units with the characteristic magnitude Z of the acoustic field in the resonator.
  • zone of high impedance adimensional when it is higher by an order of magnitude to 1 and zone of low dimensionless impedance in the opposite case.
  • stack and regenerator units must be arranged in areas of high dimensionless impedance and typically values close to 5 for one stack unit and 30 for one regenerator unit are retained.
  • a resonator section corresponding to a zero dimensionless impedance can be identified by local measurement of the acoustic pressure and determination of the section where it cancels.
  • An area of high dimensionless impedance corresponds to the resonator part where the value of the sound pressure amplitude in absolute value is maximum ( Figure 11 ).
  • Two main tube elements can also be connected not by a single reduced diameter tube d but by a plurality of reduced diameter tubes d 0 or different diameters d 1 , d 2 , ... producing the same effect with respect to power transmission ( Figure 3 ).
  • the section change between the main tube and the reduced diameter tube or section can be both discontinuous and continuous. In the first case, it may be a step, in the second, it may take the form of a cone.
  • the Figure 3 shows two main tube elements 1, 2 respectively comprising either a stack unit 3 and a regenerator unit 4, or two units of regenerator 3, 4. These thermoacoustic units 3, 4 are arranged in areas of high dimensional impedance adjacent, which are separated by a zone of low dimensional impedance.
  • the two main tube elements 1, 2 are each connected at one of their ends by a plurality of tubes 5 of reduced diameter of parallel to each other and to a branch 6, 7 comprising a connected cavity 8, 9 to a straight conduit of circular section 10, 11.
  • This embodiment is advantageous when the acoustic powers to be transmitted are very important and it is necessary to reduce both the speeds in each of the tubes but also the diameters of each tube to avoid the large wall thicknesses that are imposed by regulation in relation to the holding of the device at the maximum operating pressure.
  • the conduit leading to the cavity may comprise one or more resistive elements placed in series and acting positively on the phase of the flow at the inlet of the bypass. These elements are chosen from the group comprising a diaphragm ( Fig. 4 ), a compressible porous medium ( Fig. 5 ) and a resistive valve ( Fig. 6 ) Or other.
  • the duct is temperature controlled either by heating or cooling.
  • the pipe in a thermostatic bath whose temperature is adjusted either by heating said bath by an electric heating resistor or by cooling by means of an auxiliary cooling unit.
  • Electronic temperature control means adjust the temperature according to a setpoint ( Fig. 7 ). Control of the duct temperature advantageously allows a non-intrusive adjustment of the acoustic characteristics.
  • the Figure 8 shows a branch comprising a conduit 45 and a derived cavity 46.
  • This cavity 46 comprises an acoustically active element 47, for example, a stack unit or a loudspeaker mainly allowing an active adjustment of the acoustic characteristics at the input of the branch, but also to counterbalance the losses due to dissipation, this essentially in the derivation.
  • lV Art ⁇ ⁇ 2 is preferably greater than 5.
  • this length is much smaller than ⁇ / 4 acoustically, it is preferable to choose lV Art ⁇ ⁇ 2 close to 2 but not equal or close to 1, this to avoid dissipating all the acoustic power of the main tube in the derivation.
  • the Figure 9 is a sectional view of a resonator having multiple branches in the same section according to one embodiment of the invention.
  • the main tube member 48 At the main tube member 48 is connected four leads 49-52 each comprising a rectilinear conduit 53-56 and a derived cavity 57-60.
  • leads 49-52 each comprising a rectilinear conduit 53-56 and a derived cavity 57-60.
  • a preferred embodiment is to arrange the leads 49-52 in pairs in directly opposite directions.
  • thermoacoustic machines are varied and focused on refrigeration applications.
  • the preferred fields of application of thermoacoustic refrigeration machines using heat as a source of energy are, among others, the liquefaction of industrial or medical gases and industrial refrigeration.

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  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Electrostatic, Electromagnetic, Magneto- Strictive, And Variable-Resistance Transducers (AREA)
  • Transducers For Ultrasonic Waves (AREA)
  • Measurement Of Velocity Or Position Using Acoustic Or Ultrasonic Waves (AREA)
  • Transmitters (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
  • Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
  • Arrangements For Transmission Of Measured Signals (AREA)

Claims (12)

  1. Leistungsübertragungseinheit für thermoakustische Systeme, die mindestens eine Stufe aufweisen, Folgendes aufweisend:
    - mindestens zwei thermoakustische Einheiten, die jeweils einen Regenerator oder einen Stack aufweisen, und zwei Wärmeaustauscher,
    - einen akustischen Resonator, der eine Röhre aufweist und ein Fluid enthält, und in dem sich ein akustisches Feld erstellt, das Zonen mit starker dimensionsloser Impedanz und Zonen mit schwacher dimensionsloser Impedanz aufweist,
    - wobei bestimmte thermoakustische Einheiten (3, 4, 12-16) in Zonen mit starker dimensionsloser Impedanz platziert sind,
    dadurch gekennzeichnet, dass
    - jede Zone mit starker dimensionsloser Impedanz maximal eine thermoakustische Einheit aufweist,
    - zwei aufeinander folgende thermoakustische Einheiten (3, 4, 12-16) immer von einer Zone mit schwacher dimensionsloser Impedanz getrennt sind,
    - der Resonator einen Querschnitt mit verringertem Durchmesser (5, 21-23) zwischen jedem der Paare aus aufeinander folgenden thermoakustischen Einheiten aufweist,
    und dass jede Querschnittsverjüngung (5, 21-23) mit mindestens einer Abzweigung (6, 7) verbunden ist, die einen Hohlraum (8, 9) aufweist, wobei es die Abzweigung (6, 7) erlaubt, mindestens einen Teil der Durchflussmenge des Rohrs umzulenken.
  2. Leistungsübertragungseinheit nach Anspruch 1, dadurch gekennzeichnet, dass jede Querschnittsverjüngung mit zwei Abzweigungen (6, 7) verbunden ist, die jeweils an jedem Ende der Verjüngung platziert sind.
  3. Leistungsübertragungseinheit nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Querschnittsverjüngung kontinuierlich ist.
  4. Leistungsübertragungseinheit nach Anspruch 3, dadurch gekennzeichnet, dass die Querschnittsverjüngung die Form eines Kegels annimmt.
  5. Leistungsübertragungseinheit nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Querschnittsverjüngung unterbrochen ist.
  6. Leistungsübertragungseinheit nach Anspruch 5, dadurch gekennzeichnet, dass die Querschnittsverjüngung die Form einer Stufe annimmt.
  7. Leistungsübertragungseinheit nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass jede Abzweigung (6, 7) eine Leitung (10, 11) umfasst, die den Hohlraum (8, 9) mit dem Rohr verbindet.
  8. Leistungsübertragungseinheit nach Anspruch 7, dadurch gekennzeichnet, dass jede Abzweigung ferner Wärmeregulierungsmittel (6, 7) aufweist, die es erlauben, den Durchfluss in der Abzweigung zu steuern.
  9. Leistungsübertragungseinheit nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass Widerstandssysteme mit mindestens einer der Leitungen verbunden sind.
  10. Leistungsübertragungseinheit nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass sie mindestens ein akustisch aktives Element (47) aufweist, das das Anpassen der Betriebsbedingungen der thermoakustischen Einheiten (3, 4, 12-16) erlaubt.
  11. Leistungsübertragungseinheit nach Anspruch 10, dadurch gekennzeichnet, dass das akustisch aktive Element (47) eine Stackeinheit ist, die in dem abgezweigten Hohlraum platziert ist.
  12. Leistungsübertragungseinheit nach Anspruch 10, dadurch gekennzeichnet, dass das akustisch aktive Element (47) ein Lautsprecher ist, der in dem abgezweigten Hohlraum platziert ist.
EP05759766A 2004-05-04 2005-05-03 Schallleistungsübertragungseinheit für thermoakustische systeme Not-in-force EP1745206B1 (de)

Applications Claiming Priority (2)

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FR0404773A FR2869945B1 (fr) 2004-05-04 2004-05-04 Unite de transmission de puissance pour systemes thermoacoustiques
PCT/FR2005/050299 WO2005108768A1 (fr) 2004-05-04 2005-05-03 Unite de transmission de puissance acoustique pour systemes thermoacoustiques

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EP1745206B1 true EP1745206B1 (de) 2010-08-18

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CN100593678C (zh) * 2006-12-31 2010-03-10 中国科学院理化技术研究所 一种串列式热声系统
DE102008018000B4 (de) * 2008-04-09 2010-04-01 Siemens Aktiengesellschaft Verfahren und Vorrichtung zur CO2-Verflüssigung
JP6207611B2 (ja) 2012-09-19 2017-10-04 エタリム インコーポレイテッド 伝達ダクトを含む熱音響トランスデューサ装置
US10024950B1 (en) * 2012-10-19 2018-07-17 Tad Hogg Acoustic field coupling with micro-devices
US8787115B1 (en) * 2012-10-19 2014-07-22 Tad Hogg Acoustics for power and communication in small devices
JP6233835B2 (ja) * 2013-09-13 2017-11-22 学校法人東海大学 熱音響機関及びその製造方法
CN103485931A (zh) * 2013-09-21 2014-01-01 冯智勇 一种热声驱动的斯特林发动机
JP6313106B2 (ja) * 2014-04-22 2018-04-18 京セラ株式会社 ハイブリッドシステム

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DK1745206T3 (da) 2010-12-06
CA2565573A1 (fr) 2005-11-17
US20080276625A1 (en) 2008-11-13
CA2565573C (fr) 2013-01-08
CN1981127A (zh) 2007-06-13
FR2869945B1 (fr) 2006-08-04
DE602005023004D1 (de) 2010-09-30
ATE478250T1 (de) 2010-09-15
US8640467B2 (en) 2014-02-04
WO2005108768A1 (fr) 2005-11-17
EP1745206A1 (de) 2007-01-24
FR2869945A1 (fr) 2005-11-11

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