US3702533A - Hot-gas machine comprising a heat transfer device - Google Patents

Hot-gas machine comprising a heat transfer device Download PDF

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US3702533A
US3702533A US93104A US3702533DA US3702533A US 3702533 A US3702533 A US 3702533A US 93104 A US93104 A US 93104A US 3702533D A US3702533D A US 3702533DA US 3702533 A US3702533 A US 3702533A
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Prior art keywords
heat
reservoir
liquid
medium
space
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US93104A
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English (en)
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Adrianus Petrus Dirne
George Albert Apoloni Asselman
Herman Henricus Maria Van D Aa
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US Philips Corp
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US Philips Corp
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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
    • F02G1/053—Component parts or details
    • 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
    • F02G1/045—Controlling
    • F02G1/047—Controlling by varying the heating or cooling
    • 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
    • F02G1/053—Component parts or details
    • F02G1/055—Heaters or coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/06—Control arrangements therefor
    • 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
    • F02G2254/00—Heat inputs
    • F02G2254/20—Heat inputs using heat transfer tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2258/00—Materials used
    • F02G2258/10—Materials used ceramic

Definitions

  • a hot-gas machine in which a gaseous medium performs a closed thermodynamic cycle includes a heat conveying device which is. capable of conveying heat by means of an evaporation condensation process from a heat source to the heater of the machine.
  • This device comprises at least two closed spaces containing conveying-medium and arranged one after the other in the direction of heat conveyance, the distal ends of these spaces being provided with heat transferring walls across which heat can be conducted from the heat source to the conveying medium, or the conveying medium can give off heat to the heater; the proximal ends of these spaces comprises further heat-transferring walls, between which a switching element is provided for the establishment of a thermal and variable contact between these further walls.
  • the invention relates to a hot-gas machine, for example, a hot-gas reciprocating engine or a hot-gas turbine, in which a gaseous medium performs a closed thermodynamic cycle.
  • the machine includes a heater in which the cyclic medium receives heat from the outside from a source of heat; particularly a heat accumulator, a heat transfer device is provided between the heat source and the heater, said device containing a heat transporting medium which absorbs heat from the heat source while changing over from the liquid phase to the vapor phase, and giving off heat to the heater while changing-over from the vapor phase into the liquid phase.
  • a prior art machine of this kind is known from Dutch Pat. Specification No. 58,355.
  • the heat transfer device may serve various purposes. lt may be advantageous for reasons of space to arrange the heat source at a distance from the heater; for example, in vehicles may be equipped with a thermodynamic engine, in which the heat is furnished by a re-chargeable heat accumulator arranged elsewhere in the vehicle.
  • the nature of the heat source may involve the desirability or necessity to dispose the machine at a distance from said source, for example, when the heat is supplied from a nuclear reactor, and when the machine has to be protected from the dangers .of the radiation released by the nuclear reactions and the like. It may furthermore be advantageous to use that transfer device for establishing a thermal contact between the heaters of a number of thermodynamic machines or the various heaters of a multi-cylinder thermodynamic engine and one and the same common heat source.
  • the heat transfer device usually forms part of the machine, so that interruption of the heat transport by removal of the heat transfer device would require a time-consuming dismounting operation, the more difficult on account of the high heater temperatures, which may exceed 700 C in thermodynamic engines. Finally also turning away and/or displacing of the heat transfer device in conjunction or not in conjunction with the machine with respect to the heat source are attended by great practical inconveniences.
  • the present invention has for its object to provide a hot-gas machine comprising a heat transfer device, in which the heat transport from the heat source to the heater can be interrupted in a simple, rapid manner.
  • the hot-gas machine in accordance with the invention is characterized in that the heat transfer device comprises at least two closed spaces containing a heat transporting medium and arranged one after the other in the direction of heat transport; the distal ends of these spaces are provided with heat-passing walls through which heat from the heat source can be conducted to the transporting medium, or the latter can give off heat to the heater, the proximal ends of said spaces having further heat-passing walls between which a switching element is provided for establishing a thermal contact between said further walls.
  • each space of an advantageous embodiment of the machine in accordance with the invention may comprise a porous mass of material which connects the heat passing wall with the further heat-passing wall. By the capillary action of this mass of material, the reflow of condensate may then also take place without contribution of the force of gravity and even against the force of gravity. This means a great independence of position of the machine comprising a heat transfer device.
  • the switching element is formed by a reservoir having two heat-passing reservoir walls, which are each in contact with a further heat-passing wall or are also formed by a further heat-passing wall, the reservoir containing a heat transporting medium of variable pressure and/or quantity.
  • the heat transporting medium in the reservoir may be formed by a liquid which always remains in the same state of aggregation. A decrease of the quantity of liquid in the reservoir results in a decrease of the flow of heat between the two heat-passing walls of the reservoir. The heat transfer is blocked, when the whole quantity of liquid is removed from the reservoir.
  • a further advantageous machine embodying the invention is characterized in that the heat transportingmedium in the reservoir conducts heat from a hot heatpassing wall to a cold one of the reservoir while the liquid changes over to the vapor phase when heat is absorbed from the hot heat-passing wall and the vapor changes over to the liquid phase when heat is given off to the cold heat-passing wall; there is provided an auxiliary reservoir having portions serving as a liquid space and as a vapor space respectively and being in open communication with the reservoir through a vapor duct connected with the vapor space; the auxiliary reservoir is capable of absorbing cold from a cold source for condensing and/or solidifying the transportingmedium in the liquid space and of absorbing heat from a heat source for melting and/or evaporating the transportingmedium in said liquid space.
  • the aforesaid auxiliary reservoir may be in open communication with the reservoir also through a liquid duct connected with the liquid space of the auxiliary reservoir for passing transporting-medium from the auxiliary reservoir to the reservoir; this liquid duct includes a liquid trap adapted to be cooled, in which liquid transporting medium can be solidified for closing the liquid duct.
  • the liquid trap is formed by at least a portion of the liquid duct comprising a porous filling mass.
  • a further advantageous machine embodying the invention is characterized in that the reservoir comprises a porous mass of material, which interconnects the heat passing walls of the reservoir. If the heat transport in the reservoir is carried out by an evaporation-condensation process between the two heat passing walls of the reservoir, the transporting medium condensed on the colder wall can readily be conducted back to the hotter wall without the action of gravity or against gravity by the capillary action of the suitably chosen porous mass of material.
  • the reservoir may accommodate radiation screens for preventing heat transfer by radiation between the heat passing walls of the reservoir.
  • the invention furthermore relates to a heat transfer device of the kind set forth.
  • the transfer device is particularly suitable for use in thermodynamic engines, its use is not restricted thereto.
  • the invention will be described more fully with reference to the drawing, which shows a few embodiments schematically not to scale.
  • FIG. 1 shows a hot-gas engine comprising a heat transfer device, in which the switching element is formed by a liquid layer in a reservoir between the two spaces.
  • FIGS. 2 and 3 show hot-gas engines, in which the reservoir serving as a switching element comprises a medium which transports heat by means of an evaporation-condensation process, the pressure of said medium being variable by the supply or outlet of an inert gas in the reservoir.
  • FIGS. 4 and 5 show a hot-gas engine in which the reservoir serving as a switching element comprises a medium transporting heat by means of an evaporationcondensation process, which medium can be withdrawn holly or partly from the reservoir and be stored in an auxiliary reservoir communicating therewith.
  • FIGS. 6a and 6b each show two hot-gas engines communicating each via a heat transfer device with a common heat source, each transfer device comprises as a switching element a reservoir in which a medium is contained which transports heat by means of an evaporation-condensation process and which medium can be stored wholly or partly in an auxiliary reservoir.
  • reference numeral 1 designates the cylinder of a hot-gas engine in that part in which in operation the cyclic medium is constantly at a high temperature.
  • the cylinder comprises a displacer 2 which is capable of displacing hot cyclic medium from the expansion space 4 towards the cold side of the engine by moving upwardly and by means of a driving gear (not shown) connected with the displacer rod 3.
  • the cyclic medium passes through a heater 5, a regenerator 6 and a cooler 7. Heat can be supplied from without through the wall of the which is a heat exchanger to the cyclic medium in the expansion space 4.
  • the wall of the heater 5 forms a heat passing wall 8 of a closed space 9, which forms part of a heat transfer device 10.
  • the space 9 has furthermore a further heat passing wall 11 and is otherwise thermally isolated from the surroundings.
  • the heat transfer device 10 comprises furthermore a closed space 12 comprising on the one hand a heat passing wall 13 and on the other hand a further heat passing wall 14, and being otherwise thermally isolated from the surroundings.
  • the further heat passing walls 11 and 14 form, in addition, heat passing walls of a reservoir 15, which is otherwise thermally isolated from the surroundings.
  • the term heat passing wall has to denote a wall having low thermal resistivity. These are not only walls of material of high thermal conductivity but also walls of materials of lower thermal conductivity, provided the thickness of the wall is sufficiently small.
  • the further heat passing wall 13 of the space 12 is in thermal contact with a heat source 16 of high temperature, which may be a heat accumulator storing latent heat and/or sensible heat.
  • the heat accumulator may be secured to the heat passing wall 13 or it may be arranged separately therefrom.
  • the heat accumulator may be arranged inside the space 12; it has then to be possible to recharge the heat accumulator after use.
  • the spaces 9 and 12 are both filled partly with a suitably chosen quantity of liquid transporting medium, which can evaporate at the temperature level of the heat source.
  • suitable transporting media are, for example, the metals sodium, potassium, lithium, cadmium, cesium, metal salts such as the metalogenes, zinc chloride, aluminum bromide, cadmium iodide, calcium iodide, zinc bromide or mixtures thereof.
  • metal salts such as the metalogenes, zinc chloride, aluminum bromide, cadmium iodide, calcium iodide, zinc bromide or mixtures thereof.
  • Suitable for use are furthermore nitrates, nitrites or mixtures thereof.
  • the reservoir 15 contains a liquid which forms a thermal connection between the further heat passing walls 11 and 14. In the operation of the hot-gas engine the liquid layer remains in the liquid phase. It may be chosen in accordance with the choice of the transporting medium in the spaces 9 and 12 determined by the temperature of the heater of the heat source.
  • the thermal expansion of the small quantity of liquid in the reservoir 15 may be compensated for by connecting an expansion vessel with the liquid inlet 17, which is not shown in the drawing.
  • the device operates as follows:
  • the heat source 16 supplies heat through the heat passing wall 13 to theliquid transporting medium inside the space 12 on said wall.
  • This transporting medium evaporates and moves to the further heat passing wall 14 owing to the locally prevailing low vapor pressure as a result of the comparatively low local temperature.
  • the movement of the vapor is indicated by broken arrow lines,
  • the vapor then condenses on the further heat passing wall 14, while giving off evaporation heat to said wall. Under the action of gravity the condensate flows back to the heat passing wall 13, where it is again evaporated
  • the flow of the condensate is indicated by full arrows.
  • the heat absorbed by the further heat passing wall 14 passes through the liquid layer in the reservoir 15 and through the further heat passing wall 11 to the space 9 and causes evaporation of liquid transporting medium contained inside said space on the further heat passing wall 11.
  • the evaporation-condensation process performed inside the space 9 is identical to that in the space 12.
  • the evaporation heat released by the condensation of transporting medium on the heat passing wall 8 passes through said wall to the cyclic medium in the expansion space 4 in order to compensate for the caloric energy converted into mechanical energy during the expansion of the cyclic medium and also in order to compensate for the normal caloric losses.
  • the heat transport from the heat source 16 to the heater 5 has to be interrupted, for example, for stopping the engine, this can be carried out in a simple manner by removing the liquid from the reservoir 15 via the liquid outlet 18 and, if necessary, by further exhausting the reservoir 15. Even if the heat source 16 continues supplying heat, for example, if it is a heat accumulator, the supplied heat cannot attain the heater 5.
  • the sole consequence is that an evaporation-condensation process is performed only inside the space 12 until the vapor pressure in the portion of the space 12 adjacent the further heat passing wall 14 is equal to the vapor pressure at the heat passing wall 13, the latter being determined by the temperature of the heat source 16.
  • the space 12 has to be structurally formed so that its walls can withstand the potential maximum vapor pressure.
  • the reservoir 15 accommodates radiation screens 19, which prevent the radiation heat from the further heat passing wall 14 from reaching the further heat passing wall 11.
  • the reservoir 15 is partly filled with liquid transporting medium.
  • a duct 20 communicates with the reservoir and includes a cook 21, which is adapted to establish a communication between the reservoir 15 and either the gas cylinder 22 containing a compressed inert gas or a pumping device 23. Between the cock 21 and the gas cylinder 22 a pressure reducing valve 24 is provided and between the cock 21 and the pumping device 23 a vapor trap 25 is arranged for transporting medium.
  • inert gas is supplied from the gas cylinder 22 to the reservoir 15.
  • the pressure'of the inert gas produces such as increase in the boiling point of the transporting medium in the reservoir 15 that the new boiling point exceeds the temperature of the further heat passing wall 14.
  • the evaporation of liquid transporting medium in the reservoir is then stopped and hence also the heat transport from the further heat passing wall 14 to the further heat passing wall 1 1.
  • the reservoir 15 is communicated with the pumping device 23, which pumps away the inert gas from the reservoir 15. Any medium vapor carried along with the inert gas can condensate in the vapor trap 25 by cooling and be held therein.
  • FIG. 3 shows a device which is substantially identical to that of FIG. 2. Corresponding parts are designated by the same reference numerals as in FIG. 2.
  • the device shown in FIG. 3 difiers essentially from that of FIG. 2 by the presence of porous masses of material 26, 27 and 28 on the inner walls of the space 9, the reservoir 15 and the space 12.
  • These porous masses of material have such a capillary structure that by utilizing the surface tension of the liquid transporting medium in the space or the reservoir respectively, in the given operational state of the space or the reservoir respectively, they are capable of conducting by capillary action the condensate formed on the comparatively cold heat passing wall, on the heat passing wall of the space or on the reservoir respectively back to the comparatively hot heat passing wall, the further heat passing wall of the space or the reservoir respectively.
  • condensate in reservoir 15 is conveyed from the further heat passing wall 11 to the further heat passing wall 14 via the porous mass of material 27 and in space 9 from the heat passing wall 8 to the further heat passing wall 11 via the porous mass of material 26.
  • FIG. 3 The operation of the device shown in FIG. 3 is otherwise similar to that of FIG. 2 so that further description is dispensed with.
  • the porous mass of material may be formed by ceramic material, by wireor tape-shaped material of metal or metal alloys or by an array of tubes and the like. The choice depends inter alia upon the chosen heat transporting medium and on the prevailing temperatures in the operation of the device.
  • FIG. 4 shows a hot-gas engine comprising a heat transfer device between the heater and the heat source, the difference from that of FIG. 3 being that the reservoir 15 in the present case is in open communication through a vapor duct 29 with an auxiliary reservoir 30, in which a heating coil 31 and a cooling coil 31 are arranged. If the heat transfer between the heat source 16 and the heater has to be interrupted, this is performed by cooling the auxiliary reservoir 30. Owing to the low temperature then prevailing in the auxiliary reservoir transporting medium vapor will flow through the vapor duct 29 from the reservoir to the auxiliary reservoir, in which it will condense or even solidify. It is thus possible to withdraw the whole quantity of medium from the reservoir 15 and to store it in the auxiliary reservoir 30.
  • medium condensed or solidified in the auxiliary reservoir 30 has first to be evaporated before the return to the reservoir 15 is possible and in operation the auxiliary reservoir 30 has to be kept hot.
  • a liquid duct 32 joining on the one hand that portion of the auxiliary reservoir 30 in which liquid or solidified medium can be stored and on the other hand the reservoir 15.
  • the liquid duct 32 includes a porous filling mass 33, which contributes to the use of the liquid duct 32 in addition as a liquid trap.
  • the liquid duct 32 can be cooled for this purpose and can be heated with the aid of the heating coil 31, which surrounds herein not only the auxiliary reservoir 30 but also the liquid duct 32.
  • the auxiliary reservoir 30 and the liquid duct 32 are cooled. Then medium vapor is again conveyed from the reservoir 15 through the vapor duct 29 to the auxiliary reservoir 30. This vapor is condensed and solidified in the auxiliary reservoir. This operation continues until the reservoir 15 has become dry, so that the heat transfer in this reservoir is cut off.
  • the porous filling mass 33 performs during the solidification process also the function of flow resistor, which ensures that liquid medium can pass only with comparatively low speed through the liquid duct 32 so that owing to this low speed solidification of liquid in the liquid duct 32 is additionally facilitated. The passage is then cut off so that the liquid medium can readily solidify in the auxiliary reservoir 30.
  • liquid in the liquid duct 32 Even without porous filling mass it is possible to cause solidification of liquid in the liquid duct 32, for example, by constructing a portion of the liquid duct in the form of a bend, which is filled with liquid and cooled.
  • FIGS. 6a and 6b show assemblies in which two hotgas engines communicate each via a heat transfer device with a single common heat source.
  • FIG. 6a Since the construction and the operation of the heat transfer devices of FIG. 6a are identical to those of the device of FIG. 5, a further description may be dispensed with. Corresponding parts are designated by the same reference numerals as in FIG. 5.
  • the device shown permits in a simple manner of interrupting or restoring at will the heat transfer from the heat source 16 to the heater of a hot-gas engine or to the heater of the two hot-gas engines. This is particularly important when the heat source is formed by a heat accumulator, which supplies heat continuously to the spaces 12.
  • a thermal equilibrium is established between the heat accumulator 16 and the space 12 concerned.
  • the device shown in FIG. 6b differs from that shown in FIG. 6a only to such an extent that the two heat transfer devices have a common space 12 having a single heat passing wall 13, through which heat from the heat source 16 can be supplied to the medium inside the space 12.
  • medium evaporates and flows in two directions towards the two further heat passing walls 14 of the space 12, where it condenses, while giving off its condensation heat.
  • the condensate is conducted by the capillary action of the appropriately chosen porous mass of material 28 back to the heat passing wall 13, where it evaporates again.
  • the switching element may also be a reservoir filled with a liquid forming a thermally conducting layer between the further heat passing walls 11 and 14. A regulation of the liquid level then results in a control of the heat passing surface and hence of the heat transfer.
  • the further heat passing walls of the spaces 9 and 12 also form the heat passing walls of the reservoir 15.
  • the reservoir may have its own heat passing walls, which are in contact with the further heat passing walls of the spaces 9 and 12.
  • a hot-gas machine such as a hot-gas reciprocating engine or turbine, in which a gaseous medium performs a closed thermodynamic cycle, said machine comprising a heat exchanger in which the cyclic medium receives heat from without from a heat source, such as a heat accumulator, and a heat transfer device being arranged between the heat source and the heat exchanger, and containing a heat-transporting medium which absorbs heat from the heat source while changing from the liquid to the vapor phase, and gives off heat to the heat exchanger while changing from the vapor to the liquid phase, characterized in that the heat transfer device comprises at least two closed spaces containing heat-transporting medium and arranged one after the other in the direction of heat transport, the distal ends of said spaces being provided with heatpassing walls through which heat from the heat source can be supplied to the transporting medium and through which the medium can give off heat to the heat exchanger, whereas the proximal ends of said spaces comprise further heat-passing walls between which a switching element is provided for establishing a thermal contact between said further
  • each space comprises a porous mass of material which connects the heat-passing wall with the further heat-passing wall.
  • a machine as claimed in claim 1 characterized in that the switching element is formed by a reservoir having two heat-passing walls, each of which is in contact with a further heat-passing wall or which are formed also by a further heat-passing wall, the reservoir containing a heat transporting medium, the pressure and the quantity of which can be controlled.
  • a machine as claimed in claim 3 characterized in that the heat transporting medium in the reservoir transports heat from a hot heat-passing wall to a cold heat-passing wall of the reservoir while changing from the liquid phase to the vapor phase at the absorption of heat from the hot heat-passing wall of the reservoir and while changing from the vapor phase to the liquid phase when giving off heat to the cold heat-passing wall of the reservoir, there being provided an auxiliary reservoir comprising a portion operating as a liquid space and a portion operating as a vapor space, the auxiliary reservoir being in open communication with the reservoir through a vapor duct connected with the vapor space, the auxiliary reservoir being capable of absorbing cold from a cold source for condensing and/or solidifying transporting medium in the liquid space or of absorbing heat from a heat source for melting and/or evaporating transporting medium in said liquid space.
  • auxiliary reservoir also is in open communication with the reservoir via a liquid duct connected with the liquid space of the auxiliary reservoir, through which duct liquid transporting medium can flow from the auxiliary reservoir to the reservoir, said liquid duct comprising a liquid trap which can be cooled and in which liquid transporting medium can solidify for cutting off the liquid duct.
  • a machine as claimed in claim 5 characterized in that the liquid trap is formed by at least a portion of the liquid duct in which a porous filling mass is arranged,
  • a machine as claimed in claim 3 characterized in that the reservoir accommodates radiation screens for preventing heat transfer by radiation between the heat passing walls of the reservoir.
  • a hot-gas engine in which a gaseous medium performs a closed thermodynamic cycle, said machine operable with a heat source and including a heatexchanger in which said gaseous medium receives heat from said source, and a heat transfer device which contains a heat-transporting medium and is disposed between the heat source and the heat exchanger, this transfer device comprising means defining at least two closed spaces containing said heat-transporting medium, these spaces positioned sequentially and thus having two remote, distal ends and two adjacent proximal ends, each of said ends comprising a heat-passing wall,
  • Apparatus according to claim 9 comprising a porous mass within said spaces which mass connects each remote wall with a proximal wall of each space.
  • said switching element comprises a main reservoir having two heat-passing walls, each of which is in contact with a proximal heat-passing wall, the reservoir containing a heat-transporting medium, the pressure and the quantity of which can be controlled.
  • Apparatus according to claim 11 wherein said heat-transporting medium in the main reservoir transports heat from a hot heat-passing wall to a cold heatpassing wall of the main reservoir while changing from the liquid phase to the vapor phase at the absorption of heat from the hot heat-passing wall of the main reservoir and while changing from the vapor phase to the liquid phase when giving off heat to the cold heatpassing wall of the main reservoir, the apparatus further comprising an auxiliary reservoir having a portion operating as a liquid space and a portion operating as a vapor space, the auxiliary reservoir being in open communication with the main reservoir through a vapor duct connected with the vapor space, the auxiliary reservoir being capable of absorbing cold from a cold source for condensing and/or solidifying transporting medium in the liquid space or of absorbing heat from a heat source for melting and/or evaporating transporting medium in said liquid space.
  • auxiliary reservoir also is in open communication with the main reservoir via a liquid duct connected with the liquid space of the auxiliary reservoir, through which duct liquid transporting medium can flow from the auxiliary reservoir to the reservoir, said liquid duct comprising a liquid trap which can be cooled and in which liquid transporting medium can solidify for cutting off the liquid duct.
  • liquid trap is formed by at least a portion of the liquid duct in which a porous filling mass is arranged.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
US93104A 1969-12-24 1970-11-27 Hot-gas machine comprising a heat transfer device Expired - Lifetime US3702533A (en)

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NL696919338A NL151496B (nl) 1969-12-24 1969-12-24 Warmtetransportinrichting met een transportmedium, dat fase-overgangen ondergaat.

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US (1) US3702533A (de)
AT (1) AT306452B (de)
BE (1) BE760704A (de)
CA (1) CA917930A (de)
CH (1) CH530605A (de)
DE (1) DE2065851C2 (de)
DK (1) DK130605B (de)
FR (1) FR2074202A5 (de)
GB (1) GB1335996A (de)
NL (1) NL151496B (de)
NO (1) NO132290C (de)
SE (1) SE360146B (de)

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US3817322A (en) * 1971-10-21 1974-06-18 Philips Corp Heating system
US3855795A (en) * 1973-01-30 1974-12-24 Us Health Heat engine
US3863452A (en) * 1972-09-22 1975-02-04 Philips Corp Hot-gas engine heater
US3880230A (en) * 1973-06-01 1975-04-29 Isothermics Heat transfer system
US3924674A (en) * 1972-11-07 1975-12-09 Hughes Aircraft Co Heat valve device
US4052854A (en) * 1974-07-22 1977-10-11 North American Philips Corporation Heat transfer interface between a high temperature heat source and a heat sink
US4055953A (en) * 1973-10-31 1977-11-01 U.S. Philips Corporation Hot-gas reciprocating engine
US4069864A (en) * 1976-06-28 1978-01-24 Martin Marietta Corporation Gas filled swivel joint for cryogenic heat pipes
US4106554A (en) * 1977-07-25 1978-08-15 Westinghouse Electric Corp. Heat pipe heat amplifier
US4286652A (en) * 1975-04-04 1981-09-01 Cabinet A. Zewen Gas-controlled heat-pipe thermostat of high precision
US4387762A (en) * 1980-05-22 1983-06-14 Massachusetts Institute Of Technology Controllable heat transfer device
US4586334A (en) * 1985-01-23 1986-05-06 Nilsson Sr Jack E Solar energy power generation system
US4753072A (en) * 1987-02-11 1988-06-28 Stirling Power Systems Corporation Stirling engine heating system
US5379601A (en) * 1993-09-15 1995-01-10 International Business Machines Corporation Temperature actuated switch for cryo-coolers

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US4258554A (en) * 1977-06-22 1981-03-31 U.S. Philips Corporation Refrigerator
JPS55118561A (en) * 1979-03-05 1980-09-11 Hitachi Ltd Constant pressure type boiling cooler
CN108384581B (zh) * 2018-04-13 2024-04-26 东方电气集团东方锅炉股份有限公司 用于回收气化炉中合成气和熔渣高温显热的余热回收装置

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US1117444A (en) * 1913-08-14 1914-11-17 Joseph W Robinson Heater for motor-driven vehicles.
US1658375A (en) * 1925-08-07 1928-02-07 Siemens Schuckertwerke Gmbh Device for regulating the generation of steam in heat power plants
US2120909A (en) * 1936-07-04 1938-06-14 Gen Electric Elastic fluid condenser arrangement
US2820134A (en) * 1953-05-06 1958-01-14 Kobayashi Keigo Heating apparatus
DE1122970B (de) * 1960-04-26 1962-02-01 Metallgesellschaft Ag Thermoelektrische Kuehlanordnung

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DE847090C (de) * 1941-10-30 1952-08-21 Philips Nv Heissgasmotor
US3465813A (en) * 1967-07-26 1969-09-09 Trw Inc Method of and means for increasing the heat transfer capability of a heat pipe

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US1117444A (en) * 1913-08-14 1914-11-17 Joseph W Robinson Heater for motor-driven vehicles.
US1658375A (en) * 1925-08-07 1928-02-07 Siemens Schuckertwerke Gmbh Device for regulating the generation of steam in heat power plants
US2120909A (en) * 1936-07-04 1938-06-14 Gen Electric Elastic fluid condenser arrangement
US2820134A (en) * 1953-05-06 1958-01-14 Kobayashi Keigo Heating apparatus
DE1122970B (de) * 1960-04-26 1962-02-01 Metallgesellschaft Ag Thermoelektrische Kuehlanordnung

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3807904A (en) * 1971-03-05 1974-04-30 M Schuman Oscillating piston apparatus
US3817322A (en) * 1971-10-21 1974-06-18 Philips Corp Heating system
US3863452A (en) * 1972-09-22 1975-02-04 Philips Corp Hot-gas engine heater
US3924674A (en) * 1972-11-07 1975-12-09 Hughes Aircraft Co Heat valve device
US3855795A (en) * 1973-01-30 1974-12-24 Us Health Heat engine
US3880230A (en) * 1973-06-01 1975-04-29 Isothermics Heat transfer system
US4055953A (en) * 1973-10-31 1977-11-01 U.S. Philips Corporation Hot-gas reciprocating engine
US4052854A (en) * 1974-07-22 1977-10-11 North American Philips Corporation Heat transfer interface between a high temperature heat source and a heat sink
US4286652A (en) * 1975-04-04 1981-09-01 Cabinet A. Zewen Gas-controlled heat-pipe thermostat of high precision
US4069864A (en) * 1976-06-28 1978-01-24 Martin Marietta Corporation Gas filled swivel joint for cryogenic heat pipes
US4106554A (en) * 1977-07-25 1978-08-15 Westinghouse Electric Corp. Heat pipe heat amplifier
US4387762A (en) * 1980-05-22 1983-06-14 Massachusetts Institute Of Technology Controllable heat transfer device
US4586334A (en) * 1985-01-23 1986-05-06 Nilsson Sr Jack E Solar energy power generation system
US4753072A (en) * 1987-02-11 1988-06-28 Stirling Power Systems Corporation Stirling engine heating system
US5379601A (en) * 1993-09-15 1995-01-10 International Business Machines Corporation Temperature actuated switch for cryo-coolers

Also Published As

Publication number Publication date
NL6919338A (de) 1971-06-28
NO132290C (de) 1975-10-15
NO132290B (de) 1975-07-07
CA917930A (en) 1973-01-02
DK130605C (de) 1975-08-18
SE360146B (de) 1973-09-17
GB1335996A (en) 1973-10-31
FR2074202A5 (de) 1971-10-01
DE2065851C2 (de) 1982-12-16
DK130605B (da) 1975-03-10
DE2059055A1 (de) 1971-07-01
AT306452B (de) 1973-04-10
BE760704A (fr) 1971-06-22
CH530605A (de) 1972-11-15
NL151496B (nl) 1976-11-15
DE2059055B2 (de) 1976-07-22
DE2065851A1 (de) 1976-07-08

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