EP0273073A1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

Info

Publication number
EP0273073A1
EP0273073A1 EP86310212A EP86310212A EP0273073A1 EP 0273073 A1 EP0273073 A1 EP 0273073A1 EP 86310212 A EP86310212 A EP 86310212A EP 86310212 A EP86310212 A EP 86310212A EP 0273073 A1 EP0273073 A1 EP 0273073A1
Authority
EP
European Patent Office
Prior art keywords
heating
wall
housing
heating wall
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP86310212A
Other languages
English (en)
French (fr)
Inventor
Maurice A. White
Stuart G. Emigh
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
STIRLING ENGINE ASSOCIATES
Original Assignee
STIRLING ENGINE ASSOCIATES
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
Priority to US06/677,215 priority Critical patent/US4671064A/en
Application filed by STIRLING ENGINE ASSOCIATES filed Critical STIRLING ENGINE ASSOCIATES
Priority to EP86310212A priority patent/EP0273073A1/de
Publication of EP0273073A1 publication Critical patent/EP0273073A1/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • 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
    • 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
    • F28D15/04—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 with tubes having a capillary structure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/04—Constructions of heat-exchange apparatus characterised by the selection of particular materials of ceramic; of concrete; of natural stone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for heat-exchange media
    • 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
    • F02G2255/00—Heater 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

  • This invention relates to devices that are intended to transfer heat from one fluid to another, particularly such devices that are suitable for use in hot gas engines.
  • Heat is frequently needed to be added to, or extracted from a stream of moving fluid. This is commonly done by heat exchangers which transfer heat between two streams of moving fluid.
  • heat exchangers which transfer heat between two streams of moving fluid.
  • a common example is in Stirling or hot-gas engines which require three heat exchangers called a heater, cooler and regenerator.
  • the regenerator is a special type of heat exchanger with heat storage capability, and will not be discussed further.
  • Heaters and coolers have design requirements which apply to other types of heat exchangers and include: High efficiency of transfer; controlled resistance to flow of fluid; capability to resist high temperatures and pressures; and, low cost of construction.
  • heater exchangers have been developed to accomplish the above design criteria.
  • the methods can be characterized as cylinder heating, finned heat exchangers, tubular heat exchangers, baffle arrangements, and combinations of the above. Additionally, heat pipes have been used with each of the above structures. Construction of a suitable heater has, nonetheless, been one of the primary obstacles to widespread adoption of Stirling or hot gas engines.
  • the simplest method used is aiming a burner or other heat source at the cylinder of the engine. This method is used with small engines for demonstration purposes. This method has the advantage of low cost and simplicity, both the efficiency of heat transfer is low and the method cannot be scaled up for use in larger engines.
  • a variation of the above method is accomplished by adding fins to the cylinder to make a finned heat exchanger.
  • This method can also be accomplished by adding a separate finned heat exchanger.
  • the fins add to the efficiency of heat transfer by increasing the area exposed to heat.
  • the addition of fins adds to the cost of construction as they must be welded or brazed to the cylinder or heat exchanger to operate at high temperature.
  • the fins do not affect the pressure handling capability of the device where there is still a trade-off between thin walls for efficient transfer and thick walls for pressure resistance. As a result of the above factors, fins are generally only used in small engines.
  • a tubular heat exchanger usually consists of a series of bent tubes running between the cylinder and regenerator.
  • the tubes are arranged to be exposed to a burner or other heat source.
  • the tubes should have thin walls. Thin walled tubing, however, is limited in its pressure handling capability. Additionally, the numerous small tubes must be assembled and joined to the cylinder increasing the cost of construction. Nonetheless, tubular heat exchangers are the type most commonly used for larger engines.
  • a heat pipe to convey heat from a small burner to a large heat exchanger structure.
  • a heat pipe is a cavity filled with a vaporizable liquid, such as sodium metal and an inert gas.
  • a vaporizable liquid such as sodium metal and an inert gas.
  • One portion of the cavity is heated, and the liquid vaporized. This is called the evaporation area.
  • the load is located at another portion of the cavity called the condensation area. At the condensation area, the liquid condenses, transferring its heat of evaporation to the load. The result is a conveying of heat with low loss.
  • the use of heat pipes cannot increase the pressure or temperature capabilities.
  • baffle arrangements have been tried alone, or in combination with the other methods.
  • the baffles can increase thermal efficiency, but at an increase in construction cost.
  • no method has been found that provides high thermal efficiency at low cost with the ability to be exposed to constant high temperatures and pressures at controlled flow resistance.
  • the device has the ability to transfer heat to or from a stream of fluid with high efficiency and controlled flow resistance. Ability to withstand continuous high temperatures and pressure is achieved at minimal construction cost. Finally, the device is adaptable to mass production methods.
  • the device is comprised of at least one annular fluid passage that is surrounded on one or both sides by heating walls.
  • the heating walls are constructed of large diameter thinwall tubing to minimize cost and maximize heat transfer.
  • the thin walls are separated by spacers which allow passage of a second fluid which may be a coolant or heat transfer medium, while providing support to the walls.
  • the spacers are designed to be placed under compression by either multiple annular passages, or annular passages and insulation passages, so that no thick walls of high temperature materials are needed.
  • the device is designed so that all components are cylinders of various sizes with the exception of the ends and manifold block.
  • the device is shown as attached to a Stirling cycle engine as a heater, but it is realized that the invention is equally useable in other applications, or as a cooler.
  • a second embodiment is illustrated which includes a single heating wall for lower cost of construction.
  • Figure 1 is a sectional elevation view of the device in use as a heater on a Stirling or hot gas engine. This view is a partial sectional view of concentric cylinders and only one side of the assembly is shown for clarity, the other side being identical. As the device is shown attached to an engine, several components of the engine are shown to illustrate the use of the device that are not essential to use of the invention in other heat exchanger applications.
  • Pressure shell 1 is of substantial thickness to contain the high pressure fluids within the device and engine. Since pressure shell 1 is not subjected to high temperatures, it may be constructed of any high strength material, such as steel, which has the added advantage of low cost.
  • a displacer 3 oscillates within cylinder 2 of the engine.
  • One end of cyliner 2 of the engine is constantly exposed to high temperatures and must, therefore, be constructed of a super alloy. Such materials are expensive, but only a thinwall tube is required in this embodiment.
  • the top of cylinder 2 is closed by a cylinder head 6, which, along with cylinder 2 and the top of displacer 3, defines the expansion space 4 of the engine.
  • regenerator 7 is housed between cylinder 2 and an outer wall 8, which is also made of heat resistant material.
  • the purpose of the invention is to transfer heat from an outside source 9 (not shown) to the shuttling gas stream.
  • the device will also work in reverse if the engine is powered by a motor to act as a refrigerator, in which case, heat is transferred from the gas stream to the outside 9.
  • outside source 9 is a burner or equivalent heat source, such as radioactive material or solar concentrator. While the preferred embodiments are herein functionally described with reference to heat delivery by means of a heat pipe, it is readily apparent that a pumped heat transfer material, such as a liquid metal, can be substituted for the heat pipe 10 and adjacent structure with minimal modification.
  • Heat source 9 is connected to a heat pipe 10.
  • Heat pipe 10 is a space containing gas and a vaporizable material, such as sodium or potassium metal. Heat source 9 vaporizes the material which then fills heat pipe 10 and areas connected to heat pipe 10. The vaporized material condenses on the walls of such areas, releasing its heat of vaporization to such walls.
  • Heat pipe 10 enters the device via a hole or annular hole in top plate 11.
  • the junction may be brazed or welded.
  • Top plate 11 forms the top housing of the device and is ring shaped with an inner housing cylinder 12 joined to its inner surface, and a outer housing cylinder 13 joined to its outer surface.
  • the housing cylinders 12, 13 may be joined to top plate 11 by brazing or welding, and are constructed of a high temperature alloy.
  • inner housing cylinder 12 is joined at its other end to cylinder head 6 by brazing or welding. In another environment a separate flange would replace cylinder head 6.
  • outer housing cylinder 13 is attached to the outer regenerator housing 8.
  • Multifoil insulation 14 is comprised of several layers of heat reflective material, such as nickel separated by layers of an insulating fluid, such as Xenon or carbon dioxide gases.
  • Wall 13 is at a high temperature so insulation is necessary if pressure shell 1 is made of material that cannot be exposed to constant high temperatures. Additionally, if the hot engine gas is operating at high pressure, the counter balancing force of the pressure of insulating gas allows walls 12 and 13 to be constructed of thin wall tubing as there is little pressure differential. This completes the outer housing of the device.
  • outer regenerator wall 8 continues into the housing to constitute the outer most heating wall 17 of the device.
  • Wall 17 is constructed of thinwall tubing to increase the heat transfer.
  • an inner condenser section 19 is formed between inner housing wall 12 and an inner heating wall 21. One end of inner heating wall 21 is attached to cylinder head 6 in this embodiment.
  • a central condenser section 22 is formed between outer central heating wall 24 and inner central heating wall 23.
  • wall 23 is an extension of cylinder 2 and is joined to wall 24 by a central flange 26.
  • the outer ends of heating walls 23 and 24 are attached to manifold block 27.
  • Walls 21 and 17 are also attached to manifold block 27.
  • Manifold block 27 is sized so that an inner heating area 28 is formed between heating walls 21 and 23, and an outer heating area 29 is formed between heating walls 17 and 24. Communication between the inner heating space 28 and the outer heating space 29 is possible through a passage 35 in manifold block 27.
  • Manifold block 27 also provides several passages 30 for material in heat pipe 10 to enter the central condensing region 22.
  • Spiders 31, 32 and 33 are thus put under compressive stress. Spiders 31 and 33 have passages on the side facing the heating walls 17 and 21 for passage of fluid from heat pipe 10. Inner spider 32 has such passages on both sides. Spiders 31, 32 and 33 can be constructed of any material that is resistant to high temperatures and is strong under compression. Ceramics and glasses are particularly suitable as they can be cheaply molded, but corrugated metal can also be used.
  • spiders 31, 32 and 33 as integrated into the described heat exchanger, allow low cost construction and high thermal efficiency. These advantages are achieved primarily as a result of allowing thin annular heating walls 17, 21, 23 and 24 by carrying the pressure loads in heating spaces 28 and 29 with the spiders 31, 32 and 33 used in conjunction with pressurized regions 14, 34, and 36.
  • gas moves through regenerator 7 into outer heating area 29 where the gas is surrounded by heating walls 17 and 24, which heat the gas.
  • the gas then proceeds through the passage 35 in manifold block 27, and into inner heating area 28.
  • area 28 the gas is surrounded on both sides by heating walls 21 and 23, and is heated further.
  • the hot gas then exits through port 5 into expansion space 4.
  • displacer 3 moves toward cylinder head 6, the gas returns through port 5 into space 28, 35, then 29, and returns to regenerator 7. From the above description, it is apparent that the device can work in either direction.
  • heat can be extracted from the gas and transferred to a heat sink at 9.
  • the device is normally operated in a position inverted to that shown in Figure 1, so that condensed fluid in heat pipe 10 returns to the vicinity of heat source by gravity.
  • heat pipe operation when oriented as shown is possible by utilizing metal wicking (not shown), such as wire mesh screens attached to the condensation walls so that capillary action returns the condensate to the heat source 9 through heat pipe 10.
  • the device can also operate as a cooler, if heat pipe 10 and areas 18, 19 and 22 are filled with a cooling fluid.
  • FIG. 2 is a plan section view along line A-A of Figure 1. This figure clearly shows the circular nature of the device, although only a segment of each circle is shown, it being realized that the device is symmetrical.
  • Pressure shell 1 surrounds the device and is filled with high pressure insulation gas in regions 14 and 36. Area 14 may also be filled with multifoil insulation as described above.
  • outer housing wall 13 which along with outer heating wall 17, defines the outer condensing section of the heat pipe.
  • Spider 31 fits between walls 13 and 17, and provides a plurality of pillars for transmitting compressive forces between walls 13 and 17.
  • the area between pillars 41 forms channels which constitute the condensing section 18 of the heat pipe.
  • the outer heating passage 29 is seen to be an annular section between heating walls 17 and 24.
  • the central condenser section is similar to the outer condenser section except that condensing section passages 22 are formed on both sides of spider 32. It should be noted that spider 32 is designed to provide unbroken pillars between walls 24 and 23.
  • the inner condensing section is formed similar to, but in reverse of, the outer condensing section, with inner heating wall 21, spider 33 and inner housing wall 12.
  • the inner heating area 28 is thus formed between heated walls 21, 23 and is also seen to be an annular space.
  • the central area 36 of the device is filled with a compressed insulating gas that supports inner housing wall 12 against the compressive forces transmitted to it from inner heating area 28 through heating wall 21 and spider 33.
  • Figure 3 is a sectional plan view of line B-B of Figure 1.
  • Line B-B passes through the passage 35 between annular heating areas 28 and 29.
  • Parts 1, 14, 13, 31, 17, 29, 28, 21, 33, 12 and 36 are substantially identical to those in Figure 2. It is apparent that the fluid flows from outer heating passage 29 through area 35 and into inner heating passage 28. Flow in the reverse direction is also possible.
  • passage 35 is formed by the spaces between a series of tubes 42, the interiors of which form passages 30. A portion of the central spider 32 can be seen through passages 30. As passages 30 area is also filled with hot vaporized liquid, additional heat transfer can occur in this crossover region.
  • Tubes 42 must be sufficiently thick to contain the pressure differential between areas 30 and 35, but this is the only high temperature portion of the device that may require thicker walled tubing, although the relatively small diameter of the tubes minimizes this potential problem.
  • Figure 4 is a detail of the manifold block of the invention. Only half of manifold block 27 is shown to allow view of sections through passages 30 and 35.
  • Manifold block 27 is comprised of a top flange 47, a bottom flange 43, and a series of tubes 42. The interiors of tubes 42 form a passage 30, and the area defined by the top of flange 43, the bottom of flange 47 and the areas between tubes 42 form passage 35.
  • flanges 43 and 47 are provided with holes to accept tubes 42. This construction would be used if manifold 27 is constructed by welding. Manifold block 27 could also be made by casting or electroforming, in which case it would be one piece.
  • Lower flange 43 provides an outer surface 44 to accept and join to outer central heating wall 24 and a surface 46 to accept and join to inner central heating wall 23 as shown in Figure 1.
  • top flange 47 provides surfaces 48 and 49 to accept and join to outer heating wall 17 and inner heating wall 21 respectively.
  • the radial distance between surfaces 44 and 48, and between 49 and 46, determine the size of passages 28 and 29.
  • the size of passages 28 and 29 determines the resistance to flow of the device.
  • Manifold block 27 provides a simple means to adjust the flow resistance to a pre-determined value.
  • Figure 5 is a section elevation view of a second embodiment of the invention.
  • the device is surrounded by a pressure wall 101 and insulation 114 in a manner similar to the Figure 1 embodiment.
  • the device is shown connected to a Stirling engine as in the Figure 1 embodiment.
  • the regenerator of the engine is shown at 107 and a piston 103 is near the top 106 of cylinder 102.
  • Spaces 114, 134 and 136 are pressurized with insulating gas as in the Figure 1 embodiment.
  • a heat pipe 110 is connected to a source of high temperature and is filled with a conductive media such as sodium vapor.
  • the conductive media is contained between an outer annular containment wall 113 which also serves as an outer wall for regenerator 107 and an inner annular containment wall 112 which are connected to heat pipe 10 by a top cap 111.
  • a bottom cap 126 seals to outer containment wall 113 and an outer heater wall 117.
  • An inner heater wall 121 is connected to outer heater wall 117 by a heater top cap 147.
  • inner heater wall 121 and inner containment wall 112 are sealed to cylinder head 106. It is thus apparent that the conductive media area between walls 113 and 117 and caps 126 and 111 is connected to the area between walls 121 and 112 and cap 111 and cylinder top 106.
  • An interior non-heated wall 102 protrudes into the annular space between heater walls 117 and 121 to divide this area into inner and outer annular heat spaces 128 and 129, respectfully. Spaces 128 and 129 are connected by a passage 135. The result is a long path for gases circulating between regenerator 107 and the space 104 between piston 103 and cylinder top 106. Ceramic or metal spacers 131 and 133 between walls 113 and 117 and 121 and 112, respectively, allow heater walls 117 and 121 to be thin for good heat transfer. Spacers 131 and 133 include passages 118 and 119, respectively, for passage of the conductive media.
  • heater walls 117 and 121 are rapidly heated to a temperature similar to that of heat pipe 110. Any gas flowing between regenerator 102 and area 104 must thus pass along the entire length of heating walls 117 and 121 and is thereby heated with high efficiency.
  • FIG. 6 is a partial plan section view along line C-C of Figure 5. This figure shows the annular nature of the invention.
  • An outer pressure shell 101 surrounds the device.
  • Multifoil insulation 114 filled with pressurized insulating gas is adjacent to shell 101.
  • Outer containment wall 113 and inner containment wall 112 enclose the hot portion of the device and are adjacent to and in contact with ceramic spiders 131 and 133, respectively.
  • Spiders 131 and 133 include passages 118 and 119 for the conductive media.
  • Outer heating wall 117 and inner heating wall 121 also contact spiders 131 and 133.
  • a wall 102 divides the space between heating walls 117 and 121 into two passages 129 and 128.
  • area 136 and the vicinity of insulator 114 are filled with pressurized insulating gas.
  • Passages 129 and 128 are filled with pressurized working fluid. Since the conductive media in passages 118 and 119 is at a lower relative pressure, spacers 131 and 133 are under constant compressive stress. Use of ceramic for spacers 131 and 133 allows use of thin walls for heater walls 117 and 121 due to its high compressive strength. Other materials having similar characteristics may be substituted for ceramics.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Ceramic Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP86310212A 1983-08-01 1986-12-30 Wärmetauscher Withdrawn EP0273073A1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US06/677,215 US4671064A (en) 1983-08-01 1984-11-30 Heater head for stirling engine
EP86310212A EP0273073A1 (de) 1986-12-30 1986-12-30 Wärmetauscher

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP86310212A EP0273073A1 (de) 1986-12-30 1986-12-30 Wärmetauscher

Publications (1)

Publication Number Publication Date
EP0273073A1 true EP0273073A1 (de) 1988-07-06

Family

ID=8196258

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86310212A Withdrawn EP0273073A1 (de) 1983-08-01 1986-12-30 Wärmetauscher

Country Status (1)

Country Link
EP (1) EP0273073A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012006743A1 (en) * 2010-07-15 2012-01-19 Dana Canada Corporation Annular axial flow ribbed heat exchanger

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB619277A (en) * 1945-12-03 1949-03-07 Philips Nv Improvements in or relating to hot-gas engines
FR971467A (fr) * 1947-09-11 1951-01-17 Philips Nv Machine dans laquelle un fluide gazeux de composition chimique invariable accomplit un cycle thermodynamique fermé
GB689484A (en) * 1949-08-17 1953-03-25 Philips Nv Improvements in or relating to heat exchangers
FR2038152A1 (en) * 1969-04-02 1971-01-08 United Aircraft Corp High temperature wall structure
US3717993A (en) * 1970-11-02 1973-02-27 Gen Motors Corp Preheater assembly for stirling engine
FR2306342A1 (fr) * 1975-04-01 1976-10-29 Philips Nv Moteur a piston a gaz chaud
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
DE2713174A1 (de) * 1976-04-05 1977-10-13 Ford Werke Ag Waermetauscher fuer einen stirlingmotor, insbesondere fuer kraftfahrzeuge
US4446698A (en) * 1981-03-18 1984-05-08 New Process Industries, Inc. Isothermalizer system

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB619277A (en) * 1945-12-03 1949-03-07 Philips Nv Improvements in or relating to hot-gas engines
FR971467A (fr) * 1947-09-11 1951-01-17 Philips Nv Machine dans laquelle un fluide gazeux de composition chimique invariable accomplit un cycle thermodynamique fermé
GB689484A (en) * 1949-08-17 1953-03-25 Philips Nv Improvements in or relating to heat exchangers
FR2038152A1 (en) * 1969-04-02 1971-01-08 United Aircraft Corp High temperature wall structure
US3717993A (en) * 1970-11-02 1973-02-27 Gen Motors Corp Preheater assembly for stirling 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
FR2306342A1 (fr) * 1975-04-01 1976-10-29 Philips Nv Moteur a piston a gaz chaud
DE2713174A1 (de) * 1976-04-05 1977-10-13 Ford Werke Ag Waermetauscher fuer einen stirlingmotor, insbesondere fuer kraftfahrzeuge
US4446698A (en) * 1981-03-18 1984-05-08 New Process Industries, Inc. Isothermalizer system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, vol. 9, no. 73 (M-368)[1796], 3rd April 1985; & JP-A-59 203 854 (ASAHI GLASS K.K.) 19-11-1984 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012006743A1 (en) * 2010-07-15 2012-01-19 Dana Canada Corporation Annular axial flow ribbed heat exchanger
GB2494342A (en) * 2010-07-15 2013-03-06 Dana Canada Corp Annular axial flow ribbed heat exchanger
US8944155B2 (en) 2010-07-15 2015-02-03 Dana Canada Corporation Annular axial flow ribbed heat exchanger
GB2494342B (en) * 2010-07-15 2016-02-24 Dana Canada Corp Annular axial flow ribbed heat exchanger

Similar Documents

Publication Publication Date Title
US4688399A (en) Heat pipe array heat exchanger
RU2717732C2 (ru) Конденсационный теплообменник, оснащенный теплообменным устройством
US6715285B2 (en) Stirling engine with high pressure fluid heat exchanger
US5076058A (en) Heat transfer head for a Stirling cycle machine
US4481771A (en) Heat exchanger stack apparatus
US3965976A (en) Heater tube arrangements
US4365474A (en) Module for constructing a double-acting four-cylinder Stirling engine
WO2018231194A1 (en) Counter-flow heat exchanger
US4671064A (en) Heater head for stirling engine
CN112012846A (zh) 一种自由活塞斯特林发动机
US3991457A (en) Heater tube arrangements
CN105756804A (zh) 一种用于自由活塞斯特林发动机的热端换热器
JPS61502005A (ja) 空気作動流体によるスタ−リングエンジン
EP0273073A1 (de) Wärmetauscher
US4488344A (en) Waste heat recovery system having thermal sleeve support for heat pipe
US4485865A (en) Waste heat recovery system having thermal sleeve support for heat pipe
US3863452A (en) Hot-gas engine heater
JPS63173834A (ja) スタ−リングエンジン用加熱器のヘツド
CN108592660B (zh) 一种用于斯特林热电转换装置的双盘管冷却器
CN113865402B (zh) 回热式热机的换热器及回热式热机
US20240271835A1 (en) Stirling engine with near isothermal working spaces
US12504237B2 (en) Multi-tiered regenerator
SU1478027A1 (ru) Теплообменник типа "труба в трубе
JPS63118594A (ja) 熱機関の低温側熱交換器
JPH11223400A (ja) 熱機関用の熱交換器

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT NL SE

17P Request for examination filed

Effective date: 19881210

17Q First examination report despatched

Effective date: 19890710

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19920317

RIN1 Information on inventor provided before grant (corrected)

Inventor name: EMIGH, STUART G.

Inventor name: WHITE, MAURICE A.