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WO1990011447A1 - Dispositif d'utilisation de chaleur par conversion en energie mecanique, notamment dispositif de refroidissement - Google Patents

Dispositif d'utilisation de chaleur par conversion en energie mecanique, notamment dispositif de refroidissement Download PDF

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Publication number
WO1990011447A1
WO1990011447A1 PCT/NL1989/000012 NL8900012W WO9011447A1 WO 1990011447 A1 WO1990011447 A1 WO 1990011447A1 NL 8900012 W NL8900012 W NL 8900012W WO 9011447 A1 WO9011447 A1 WO 9011447A1
Authority
WO
WIPO (PCT)
Prior art keywords
channel
heat
regenerator
fluid
wave
Prior art date
Application number
PCT/NL1989/000012
Other languages
English (en)
Inventor
Cornelis Maria De Blok
Nicolaas Adrianus Henrikus Jozef Van Rijt
Original Assignee
Cornelis Maria De Blok
Rijt Nicolaas Adrianus Henriku
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 Cornelis Maria De Blok, Rijt Nicolaas Adrianus Henriku filed Critical Cornelis Maria De Blok
Priority to PCT/NL1989/000012 priority Critical patent/WO1990011447A1/fr
Publication of WO1990011447A1 publication Critical patent/WO1990011447A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/002—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using the energy of vibration of fluid columns
    • 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
    • F02G2243/30—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 
    • F25B2309/1403—Pulse-tube cycles with heat input into 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 
    • F25B2309/1405—Pulse-tube cycles with travelling waves

Definitions

  • the invention relates to a device for utilizing heat via conversion into mechanical energy having a travelling wave heat motor comprising a self-enclosed conduit which defines internally an endless channel filled with a compres- sible fluid, a regenerator arranged in a portion of the chan ⁇ nel and comprising a heat exchanging medium through which the fluid can flow, heat supply and heat discharge means coupled in the lengthwise direction of the channel at a mutual inter ⁇ val to the heat exchanging medium, which means can generate a temperature gradient in the regenerator during operation, whereby the length of the channel is dimensioned in accordance with a design wave length of a travelling wave with a desired frequency to be generated in the channel during operation, and with energy extraction means absorbing mechanical energy from the travelling wave.
  • Such a device is known from the American patent specification 4.114.380. It has been found in practice that this known device functions either not at all or hardly at all.
  • the invention therefore has for its object to pro ⁇ vide a device of the type specified in the preamble which can operate with a good yield.
  • This is achieved in the device according to the invention in that connecting onto the channel portion containing the regenerator on the side of the heat supply means is a channel portion which has at least the same diameter as the channel portion in which the regenerator is accommodated and which is provided with means for neutrali ⁇ zing wave phenomena in the fluid reflected in the direction towards the side of the regenerator coupled to the heat supply means.
  • the wave phenomena in the fluid correspond in very good approximation to those of a travelling wave. That is, the momentary speed of movement and pressure in the fluid are at least virtually in phase with one another during operation.
  • the invention is therefore based on the insight that, for the purpose of obtaining a good yield from the thermodynamic processes generated in the fluid by the wave phenomena in a device of the present type, it is important that the cyclic pressure and speed changes must occur with the correct mutual phase and that it is of importance for this purpose that disturbances of the correct phase relation- ship occurring in practice be neutralized.
  • a travelling wave heat motor it is of particular importance for a good yield that, as already noted, the phase difference between the pressure and gas speed is minimal.
  • the gas pressure and gas displacement have to be in phase with one another, or the gas pressure and the gas speed must have a phase difference of 90 when operation is performed with sine-like wave phenomena.
  • a favourable embodiment of the device according to the invention can be seen in claim 2.
  • the compensation formed by the widening neutralizes the reflected wave phenomena in the fluid so that no disturbing wave phenomena can occur in the regenerator.
  • the energy extracting means may consist of means absorbing alternating pressure energy and connected to the channel.
  • Use can be made particularly of a piezoelectric, electromagnetic or mechanical disengaging member.
  • the desired wave phenomena can however also be generated in liquid fluids such as for instance liquid alkali metal such as sodium. In such an em- bodiment the wave energy can be converted directly into elec ⁇ tricity by means of the magnetohydrodynamic principle.
  • the energy extracting means may however also comprise a conduit piece which is joined in open communication with the main channel and which forms a resonator and is provided with heat absorbing means and heat dissipating means on the side of the heat absorbing means facing away from the open connection, and whereby the main channel is provided with means for neutralizing reflected wave phenomena introduced into the fluid in the channel as a result of wave phenomena in the fluid in the side channel.
  • the correct phase relationship in the wave phenomena is of great importance for a good operation of a device of the present type.
  • Generated in the fluid in the conduit piece forming the resonator is a standing wave that is driven by the travelling wave in the main channel.
  • the embodiment as characterized in claim 6 is par ⁇ ticularly favourable.
  • the disturbances introduced through the one side channel are in precisely opposite phase to those caused by the other side channel, so that these disturbances neutralize one another.
  • a number of such pairs of side channels neutralizing the disturbances on either side can be employed in the device according to the invention.
  • the channels lying closest to one another can thereby be combined into a larger side channel.
  • the disturbances caused in the main channel by the combined side channel are again compensated by both the other side channels.
  • Claims 8 and 9 characterize a favourable application of the device according to the invention as a refrigerator or cooling box.
  • the great advantage of the device according to the invention embodied as a cooling device is that it has a very simple construction without moving parts and that the active fluid can be normal air, or in any case an innocuous gas.
  • the device does not therefore contain the harmful active fluids such as chlorofluorocarbons employed in the usual cooling devices.
  • Figures 1-3 show schematically three embodiments of the device according to the invention.
  • Figures 4 and 5 show corresponding schematic repre ⁇ sentations of the device according to the invention in the form of a cooling device.
  • Figure 6 shows in partially perspective view with dismantled parts a portion of an actual embodiment of a cool ⁇ ing device according to the invention.
  • Figure 7 is a cross section of such a cooling de- vice.
  • Figure 8 shows perspectively another embodiment of the heat absorbing means as employed in an embodiment of a cooling device according to the invention.
  • the device 1 shown schematically in figure 1 com- prises a self-enclosed conduit 2 internally defining an end ⁇ less channel 12 filled with a compressible fluid.
  • a regenerator 3 comprising a heat exchanging medium 7 through which the fluid can flow and which can for instance take the form of steel wool.
  • heat supply means 4 are represen ⁇ ted schematically here by a thermally conducting plate which is heated by a burner 5.
  • heat discharge means 6 designated schematically and having a likewise ther ⁇ mally conducting plate provided with cooling ribs.
  • the seal 7 is itself of heat conducting material and thermally connected at both ends to the heat supply means 4 and the heat discharge means 6 so that during operation a temperature gradient will be established in the seal 7.
  • the regenerator 3 is embodied such that there resul- ts a very good transfer of the fluid onto the seal material.
  • the above mentioned steel wool or metal wool in general ful ⁇ fills this requirement well.
  • the device comprises for this purpose energy extracting means 9 which, as noted ear- lier, can extract for instance piezoelectric, electromagnetic or purely mechanical energy. In preference however, as will be elucidated later, the energy extracting means 9 are em ⁇ bodied as a heat pump.
  • the channel portion connecting directly onto the regenerator 3 is widened over a length at least virtually equal to a quarter of the design wave length.
  • This widened portion 8 has a diameter at least virtually equal to the product of the diameter of the remaining part of channel 12 and the square root of the quotient of the operating tem ⁇ peratures in Kelvin of the regenerator 3 close to the heat supply means 4 and the heat discharge means 6.
  • FIG. 2 Another embodiment of the means for neutralizing reflected wave phenomena is shown in figure 2.
  • the channel portion containing the regenerator hereby has the same dia ⁇ meter as the chann'el portion connecting on the side of the heat supply means 4.
  • a heating element 10 Arranged about this channel portion directly adjoining the regenerator 3 is a heating element 10 which extends over a length at least practically equal to a quarter of the design wave length.
  • the fluid in the relevant channel portion obtains the same tem ⁇ perature. Since the fluid has this higher temperature along the stated length of at least one quarter of the design wave length, the unadulterated travelling wave in the regenerator 3 is not disturbed by reflected wave phenomena.
  • design wave length is meant the wave length of the travelling wave occurring in the fluid. In the simplest approximation this wave length is equal to the length of the channel 12. However, as a result of par ⁇ ticular steps, which will not be further mentioned, a travel ⁇ ling wave with a higher frequency can also be generated. The length of the channel is then a whole number of times the wave length. It is further the case that the energy extraction means 9 introduce a certain damping into the system which has the effect that the frequency of the travelling wave becomes lower. These influences on the wave length can be computed in the design stage of the device and, if determined dimensions of the conduit are assumed, the computed wave length, or if this is taken as starting point, the selected wave length is designated in this description as the design wave length.
  • the means for neutralizing the reflected wave phenomena are likewise formed by a widened channel por ⁇ tion 11.
  • the widened channel portion 11 is ar ⁇ ranged at a distance of 0.09 to 0.14 times the design wave length from the side of the regenerator 3 coupled to the heat supply means 4.
  • the length of the widened portion 11 is 0.02 to 0.05 times the design wave length, while the diameter is equal to 1.14 to 4.0 times the diameter of the remaining part of the channel.
  • the channel portion containing regenerator 3 has the same diameter as the channel portion connecting there- to on the side of the heat supply means 4.
  • FIG 4 shows a device according to the invention whereby the energy extracting means are formed by a standing wave-heat pump 21.
  • the travelling wave heat motor 16 cor ⁇ responds In principle with the embodiment of figure 3.
  • Shown on the heat supply side of the regenerator in the embodiment shown here is a burner 17.
  • the hot combustion gases of burner 17 are collected in a burner housing 18 which guides the hot gases via a heat exchanger, wherein heat is extracted and passed to the seal of the regenerator, to a gas discharge 19.
  • the means for neutralizing reflected wave phenomena are formed here by a widened portion 20 arranged in the channel at an interval from the regenerator.
  • the standing wave-heat pump 21 is formed by a con ⁇ duit portion 22 having a closed end 23 and an open end 24.
  • the open end is in open communication with the main channel of the travelling wave-heat motor 16.
  • the side channel defined in the conduit piece 22 has a length of a quarter times the design wave length and thus forms a resonator.
  • This disturbance can be seen as a reflected wave phenomenon introduced in the fluid in the main channel.
  • a compensation 25 is now arranged in the main channel which neutralizes the introduced, reflected wave phenomena.
  • This compensation 25 is formed by a widened conduit portion. The dimensioning thereof can again be computed using per se known wave line theory.
  • each fluid volume particle Due to the standing wave in the conduit portion 22 each fluid volume particle is subjected to a varying compres- sion and expansion. Since in a standing wave the pressure and displacement are in phase with one another, each volume par ⁇ ticle is displaced during the compression towards the closed end 23. Because the temperature thereby thus increases, the volume particle can give off heat, for example to the wall of the conduit portion. During expansion the fluid volume par ⁇ ticle cools off again, and at the minimal pressure the volume particle undergoes maximum displacement in the direction towards the open end 24. As a result of the cooling caused by the expansion the volume particle can take up heat, for exam- pie from the wall of the conduit portion. Occurring thus in this manner is a heat pump cycle.
  • Heat is taken up at a deter ⁇ mined position in the conduit portion 22 and can be given off again at a position lying further towards the closed end 23. As noted, it is thus of importance hereby for the achieving of a maximum yield that the pressure and displacement lie as closely as possible in phase.
  • a seal 26 is arranged in the conduit por ⁇ tion 22 in which the standing wave occurs. This seal consists of thermally insulating material and is embodied such that the best possible laminar flow of the fluid can take place therein.
  • the seal 26 comprises for instance a large number of parallel channels with smooth walls. For a good yield it is important that the smallest possible heat flow occurs in lengthwise direction of these channels.
  • the fluid must on the other hand have a good heat exchange with the walls of the channels so that during operation a temperature gradient occurs in the seal.
  • Thermally insulating materials suffice In practice.
  • An improvement of the heat exchanging with fluid in gas form can be achieved by providing the walls of the chan ⁇ nels with a thin metal layer. At higher levels of pressure a seal can be employed that is manufactured entirely of metal foil. The lengthwise conduction is hereby small in relation to the amount of heat displaced.
  • a circuit connects to both the "hot” and the "cold" side of the seal 26.
  • the circuit on the cold side is designated with 27 and contains a heat exchanger 29.
  • the fluid on the underside of the seal 26 as seen in figure 4 is cooled and that in the upper part is heated. That is, if the fluid is in gas form a cold gas cloud is created on the cold side of seal 26 and a hot gas cloud on the hot side.
  • the cold fluid is taken up into the circuit 27 and can absorb heat in the heat exchanger 29.
  • the thus re-heated fluid is carried back to the cold side of seal 26, where heat can once again be extracted therefrom and the circuit cycle can be repeated.
  • FIG. 5 shows a further developed embodiment of the principle shown in figure 4.
  • the travelling wave heat motor corresponds to that shown in figure 4 and has the same reference numeral 16.
  • a second heat pump 35 is arranged similar to the heat pump 21.
  • the two heat pumps 21, 35 are connected onto the main channel at a mutual distance of substantially a quarter of the design wave length.
  • the standing wave occurring in heat pump 35 during operation has a resulting phase shift of 90 relative to that in the heat pump 21.
  • the disturbances introduced in the travelling wave as a consequence of both standing waves thus result in a phase shift of 180 and there ⁇ fore cancel each other out.
  • heat is taken up in the combined heat exchanger 36 and given off again in the heat exchangers 37 and 38. There thus occurs heat transport from the space of heat exchanger 36 to that of the heat exchangers 37 and 38.
  • the heat pumps shown here each have the form of a conduit portion closed at one end with a length of substantially a quarter times the design wave length
  • other embodiments can also be employed, such as a Helmholtz resona ⁇ tor or a conduit part connected at its ends to the main chan ⁇ nel at locations where the wave phenomena have a like phase and in which for example two heat exchangers can be accom ⁇ modated. All that is important is that the conduit part is embodied such that a standing wave occurs therein.
  • FIG. 6 shows perspectively with broken away parts the portion of the cooling device comprising the travelling wave motor.
  • the main channel 41 of the travelling wave motor is recessed into the rear wall 40 of the device.
  • This rear wall 40 consists of a central part in which the channel 51 is recessed and two side plates 42, 43.
  • the regenerator 44 takes the form of a cassette pushed into the rear wall 40 and fixed in position therein with known means.
  • the regenerator com ⁇ prises the above described seal 45 of metal wool, a heat discharge plate 46 and a heating element 48.
  • This element 48 is here an electrical heating element consisting of a "honey ⁇ comb" formed from corrugated stainless steel foil.
  • the heat discharge 46 is in thermal communication with the cooling ribs 47 which, as figure 7 shows, are freely accessible for cooling surrounding air.
  • a widening 49 in accordance with the principle of figure 3 is arranged in the channel 41 in order to neutralize the wave phenomena reflected to the regenerator. Air is used as the active fluid.
  • the direction of the travelling wave occurring in the device during operation is indicated with the double arrows 50.
  • a heat pump Arranged on two locations in the plate 43 of the rear wall are cut away portions 51, 52. Measured along the main channel 41 these two openings 51, 52 are situated at an interval of practically one quarter of the design wave length. Connected onto each of these openings 51, 52 is a heat pump, only one of which is shown partially in figure 6.
  • the heat pump 53 is hereby embodied as a Helmholtz resonator.
  • the seal 54 can be seen which provides the laminar flow guiding of the fluid in the heat pump.
  • a cooling fin 55 Arranged on the cold side of seal 54 is a cooling fin 55.
  • the heat pump 56 located opposite.
  • the cooling fins 55, 57 of the heat pumps 53, 56 protrude into the internal space 60, which is enclosed by a door 61 as well as by insulated walls 62.
  • the heat pumps 53, 56 are arranged in the insulated wall 62.
  • Arranged on the hot side of each heat pump 53, 56 are cooling ribs 58 and 59 respectively which protrude into the outer surroundings.
  • the heat transported by the heat pumps 53, 56 from the heat absorbing means in the form of the cooling fins 55, 57 to the heat dissipating means in the form of the cool ⁇ ing ribs 58, 59 is given off there to the outer air. Heat is thus extracted from the internal space 60 of the refrigerator.
  • FIG 8 shows another embodiment of the heat absorbing means in a cooling device according to the invention. Shown with dashed lines is the resonance channel 65 in which the standing wave is generated.
  • a number of tubes of heat conducting material such as metal. Air can flow through these tubes 66.
  • guide channels are formed which guide air towards the openings of the tubes 66, as indicated with the arrows 68.
  • the air in the tubes 66 cools and, as a result of convectional flow, the cooled air flows outside on the underside and is replenished by hot air from above. Created in this way is a constant air flow in the direction of the arrow 68, resulting in heat being extracted from the air in the interior of the cooling device.

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  • 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)
  • Physical Or Chemical Processes And Apparatus (AREA)

Abstract

Dispositif d'utilisation de chaleur par conversion en énergie mécanique, comportant un moteur thermique (1) à ondes progressives comprenant un conduit auto-fermé (2), lequel définit intérieurement un canal sans fin rempli d'un fluide compressible, un régénérateur (3) agencé dans une partie dudit canal et comprenant un milieu d'échange thermique (7) par lequel ledit fluide peut s'écouler, des moyens d'amenée (4) et d'évacuation de chaleur (6) couplés dans le sens de la longueur dudit canal, à un intervalle mutuel, audit milieu d'échange thermique, lesquels moyens peuvent produire un gradient de température dans ledit régénérateur lors du fonctionnement. La longueur du canal est dimensionnée en fonction d'une longueur d'onde type, en fonction d'une fréquence désirée à émettre dans ledit canal lors du fonctionnement, et en fonction d'un moyen (9) d'extraction d'énergie absorbant l'énergie mécanique provenant de ladite onde progressive. Une partie de canal reliée à ladite partie de canal contenant ledit régénérateur, du côté dudit moyen d'amenée de chaleur, présente au moins le même diamètre que ladite partie de canal dans laquelle est logé ledit régénérateur, et comporte un moyen de neutralisation des phénomènes d'ondes se produisant dans le fluide réfléchi dans la direction du côté dudit régénérateur couplé audit moyen d'amenée de chaleur.
PCT/NL1989/000012 1989-03-17 1989-03-17 Dispositif d'utilisation de chaleur par conversion en energie mecanique, notamment dispositif de refroidissement WO1990011447A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/NL1989/000012 WO1990011447A1 (fr) 1989-03-17 1989-03-17 Dispositif d'utilisation de chaleur par conversion en energie mecanique, notamment dispositif de refroidissement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/NL1989/000012 WO1990011447A1 (fr) 1989-03-17 1989-03-17 Dispositif d'utilisation de chaleur par conversion en energie mecanique, notamment dispositif de refroidissement

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WO1990011447A1 true WO1990011447A1 (fr) 1990-10-04

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010037358A1 (fr) * 2008-09-30 2010-04-08 Institut Für Luft- Und Kältetechnik Gemeinnützige Gmbh Système d'échappement pour véhicules automobiles comprenant un moteur thermique intégré
CN104214062A (zh) * 2014-08-04 2014-12-17 浙江大学 旋转动力驱动的热声发电系统
JP2015535901A (ja) * 2012-09-19 2015-12-17 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
US11371431B1 (en) 2015-11-06 2022-06-28 United States Of America As Represented By The Administrator Of Nasa Thermal management system

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2549464A (en) * 1947-10-29 1951-04-17 Bell Telephone Labor Inc Electric power source
US4114380A (en) * 1977-03-03 1978-09-19 Peter Hutson Ceperley Traveling wave heat engine
US4355517A (en) * 1980-11-04 1982-10-26 Ceperley Peter H Resonant travelling wave heat engine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2549464A (en) * 1947-10-29 1951-04-17 Bell Telephone Labor Inc Electric power source
US4114380A (en) * 1977-03-03 1978-09-19 Peter Hutson Ceperley Traveling wave heat engine
US4355517A (en) * 1980-11-04 1982-10-26 Ceperley Peter H Resonant travelling wave heat engine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JOURNAL OF THE ACOUSTICAL SOCIETY OF AMERICA. vol. 77, no. 3, 01 March 1985, NEW YORK US pages 1239 - 1244; P.H. CEPERLEY: "Gain and efficiency of a short wave heat engine " see page 1239 the first 10 lines of the abstract see page 1240, left-hand column the last 2 lines see page 1240, right-hand column, the first 3 lines, figure 1 SA 27547 030see page 1242; figure 5 see page 1243 chapter VII *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010037358A1 (fr) * 2008-09-30 2010-04-08 Institut Für Luft- Und Kältetechnik Gemeinnützige Gmbh Système d'échappement pour véhicules automobiles comprenant un moteur thermique intégré
JP2015535901A (ja) * 2012-09-19 2015-12-17 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
US9664181B2 (en) 2012-09-19 2017-05-30 Etalim Inc. Thermoacoustic transducer apparatus including a transmission duct
CN104214062A (zh) * 2014-08-04 2014-12-17 浙江大学 旋转动力驱动的热声发电系统
US11371431B1 (en) 2015-11-06 2022-06-28 United States Of America As Represented By The Administrator Of Nasa Thermal management system

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