US3525386A - Thermal control chamber - Google Patents

Thermal control chamber Download PDF

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Publication number
US3525386A
US3525386A US3525386DA US3525386A US 3525386 A US3525386 A US 3525386A US 3525386D A US3525386D A US 3525386DA US 3525386 A US3525386 A US 3525386A
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Prior art keywords
heat
heat pipe
working fluid
pipe
inert gas
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George M Grover
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US Atomic Energy Commission (AEC)
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US Atomic Energy Commission (AEC)
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    • 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
    • F28D15/0233—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 the conduits having a particular shape, e.g. non-circular cross-section, annular
    • 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
    • F28D15/0266—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 separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • 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
    • F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
    • 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
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/65—Means for temperature control structurally associated with the cells
    • H01M10/655—Solid structures for heat exchange or heat conduction
    • H01M10/6552—Closed pipes transferring heat by thermal conductivity or phase transition, e.g. heat pipes
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M8/00—Fuel cells; Manufacture thereof
    • H01M8/04—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids
    • H01M8/04007—Auxiliary arrangements, e.g. for control of pressure or for circulation of fluids related to heat exchange
    • H01M8/04067—Heat exchange or temperature measuring elements, thermal insulation, e.g. heat pipes, heat pumps, fins
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/10—Energy storage using batteries
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/50—Fuel cells

Definitions

  • This invention relates to temperature control in a chamber housing a heat source which generates variable quantities of heat.
  • This invention may be employed in conjunction with a battery or fuel cell which generates a variable quantity of heat depending upon the electrical power being withdrawn. During periods of heavy power requirements heat must be radiated away to keep the unit from overheating and during light power loads little or no heat needs t be radiated away.
  • radiators including mechanical shutters for covering the radiators during periods of low, power requirement.
  • this solution has drawbacks because the shutter system is complex and unreliable.
  • Heat pipes of the type described by Grover, Cotter and Erickson in Structures of Very High Thermal Conductance, Journal of Applied Physics, vol. 35, 1900 (June 1964) have established themselves as efficient and reliable heat transfer devices.
  • This invention employs two heat pipes with a common section of wall between them. The first heat pipe transports heat to the common wall and it is transported and radiated to the outside by the second heat pipe.
  • the first heat pipe contains an inert gas as well as a condensable working fluid.
  • the inert gas is pumped to the condenser end of the pipe (the end farthest from the heat source) and compressed until the pressure of the inert gas equals the pressure of the vapor of the working fluid. If the heat supplied t the evaporator end of the pipe (the end nearest the heat source) chcanges, two effects are noticed. First, the temperature of the pipe increases slightly. Second, the inert gas is compressed further because the vapor pressure of the working fluid is increased. This causes an increase in the active volume of recirculating heat pipe working fluid and, consequently, an increase in the radiating area. Thus an additional heat input causes both an increase in radiating area and a small increase in pipe temperature. When the volume of inert gas is relatively large, only a small change of temperature would cause a relatively large change of radiating area. Hence, the temperature change ccan be relatively small for large change in the heat input to the pipe.
  • the change in the size of the radiating area would represent the limit of control.
  • By coupling the first heat pipe to a second heat pipe by conduction through the thin common wall much greater quantities of heat can be controlled.
  • the first heat pipes active area does not reach the common wall, very little heat is removed from the system.
  • With a small increase in area so that the second heat pipe is brought int the system, very much larger quantities of heat can be dissipated.
  • This change is accomplished with only a small movement of the vapor-gas interface and consequently requires only a small increase in inert gas pressure in the first heat pipe.
  • This means that the temperature change in the first heat pipe is very small between the two extreme cases of very little heat input to very large heat input.
  • the double heat pipe arrangement acts something like a radiating area amplifier, thus providing closer control of the input temperature.
  • the heat pipe 2 When heat is generated in fuel cell 1, the heat is transferred to the heat pipe 2 which will be designated the 'primary heat pipe.
  • This heat pipe consists of an enclosed container lined with capillary wicking, partially filled with a working fluid and partially filled with an inert gas. The heat absorbed causes evaporation of the working fluid and pumps the inert gas into the attached stem 4 of the primary heat pipe. Until the temperature of the primary heat pipe reaches the design value, heat is lost only by conduction through the insulation 3. As the temperature approaches the design value, the vapor pressure forces the inert gas further into the stem 4 and the vapor-gas interface 9 moves toward surface 6. This action exposes the common wall 10 between the primary heat pipe 2 and the secondary heat pipe 5 to the working area of the primary heat pipe.
  • Condensation occurs on the common wall 10 transferring the latent heat of condensation to the secondary heat pipe which sets the secondary heat pipe into operation.
  • the secondary heat pipe transfers the heat from the evaporator section near the common wall 10 to the condenser section and the heat is radiated to the outside at surface 7.
  • the exact quantity of inert gas necessary for proper operation of the primary heat pipe depends on the desired temperature to be maintained in the battery compartment. For instance, if it is desired to hold the temperature at C., and if water is the working fluid, a quantity of gas is initially admitted such that the pressure of the compressed gas in the stem is 760 torr when the common wall 10 is exposed to the circulating working fluid of the primary heat pipe. Since the volume of the stem under the common wall 10 can be made small relative to the total volume of the stem, the pressure in the stem and hence in the working fluid will remain approximately at 760 torr.
  • the secondary heat pipe 5 is shown in the form of a circular container.
  • the secondary heat pipe may be filled with an inert gas which will be compressed radially outward with an increased heat input through the common surface 10, thus causing the interface 8 to move radially outward exposing more radiating surface 7.
  • other heat pipes may be connected to the second heat pipe in the same manner the second heat pipe was connected to the first in order to further increase the radiating area.
  • the working presure would be about 350 torr at 100 C., but since the freezing point is 68.7 C., the risk of freezing the working fluid is much less than when using water.
  • This invention has special utility in connection with space craft. Heat pipes have been shown to work successfully in space. The durability and reliability of the invention are of major importance when used in conditions making repair and servicing impossible.
  • a device for maintaining a heat generating body at a constant temperature comprising a first enclosed container partially surrounding the heat generating body and a second enclosed container connected to the first container by a common wall at a point remote from the heat generating body, said first container having a portion extending beyond said common wall, both of the containers being lined with a capillary material and partially filled with a condensable working fluid and partially filled with an inert gas, the ratio of the quantity of said working fluid to the quantity of said inert gas being selected so that said working fluid is in contact with at least a portion of said common wall only at a predetermined operating temperature and higher temperatures.

Description

Aug. 25, 1970 G. M. GROVER THERMAL CONTROL CHAMBER Filed Jan. 22 1969- v (NVENTOR. George M. Grover United States Patent Ofiice 3,525,386 Patented Aug. 25, 1970 US. Cl. 16532 5 Claims ABSTRACT OF THE DISCLOSURE A device for maintaining an enclosure containing a heat generating body at a constant temperature even though the quantity of heat generated by said body varies. A first heat pipe transfers heat to a second heat pipe through a surface common to both heat pipes and the heat is radiated away by the second heat pipe.
The invention described herein was made in the course of, or under, a contract with the US. Atomic Energy Commission.
This invention relates to temperature control in a chamber housing a heat source which generates variable quantities of heat. This invention may be employed in conjunction with a battery or fuel cell which generates a variable quantity of heat depending upon the electrical power being withdrawn. During periods of heavy power requirements heat must be radiated away to keep the unit from overheating and during light power loads little or no heat needs t be radiated away.
To control the heat dissipation prior art devices have employed radiators including mechanical shutters for covering the radiators during periods of low, power requirement. However, this solution has drawbacks because the shutter system is complex and unreliable.
It is therefore an object of this invention to provide a reliable and yet relatively uncomplicated device for controlling the heat exchange between a heat generating body and the outside.
Heat pipes of the type described by Grover, Cotter and Erickson in Structures of Very High Thermal Conductance, Journal of Applied Physics, vol. 35, 1900 (June 1964) have established themselves as efficient and reliable heat transfer devices. This invention employs two heat pipes with a common section of wall between them. The first heat pipe transports heat to the common wall and it is transported and radiated to the outside by the second heat pipe.
The first heat pipe contains an inert gas as well as a condensable working fluid. The inert gas is pumped to the condenser end of the pipe (the end farthest from the heat source) and compressed until the pressure of the inert gas equals the pressure of the vapor of the working fluid. If the heat supplied t the evaporator end of the pipe (the end nearest the heat source) chcanges, two effects are noticed. First, the temperature of the pipe increases slightly. Second, the inert gas is compressed further because the vapor pressure of the working fluid is increased. This causes an increase in the active volume of recirculating heat pipe working fluid and, consequently, an increase in the radiating area. Thus an additional heat input causes both an increase in radiating area and a small increase in pipe temperature. When the volume of inert gas is relatively large, only a small change of temperature would cause a relatively large change of radiating area. Hence, the temperature change ccan be relatively small for large change in the heat input to the pipe.
If the first heat pipe could only get rid of its heat by radiation then the change in the size of the radiating area would represent the limit of control. By coupling the first heat pipe to a second heat pipe by conduction through the thin common wall, much greater quantities of heat can be controlled. When the first heat pipes active area does not reach the common wall, very little heat is removed from the system. With a small increase in area so that the second heat pipe is brought int the system, very much larger quantities of heat can be dissipated. This change is accomplished with only a small movement of the vapor-gas interface and consequently requires only a small increase in inert gas pressure in the first heat pipe. This means that the temperature change in the first heat pipe is very small between the two extreme cases of very little heat input to very large heat input. The double heat pipe arrangement acts something like a radiating area amplifier, thus providing closer control of the input temperature.
The above and other objeects and advantages will be made apparent from a consideration of the accompanying drawing wherein the single figure shows a side view of applicants invention operably connected to a heat generating source such as a fuel cell.
When heat is generated in fuel cell 1, the heat is transferred to the heat pipe 2 which will be designated the 'primary heat pipe. This heat pipe consists of an enclosed container lined with capillary wicking, partially filled with a working fluid and partially filled with an inert gas. The heat absorbed causes evaporation of the working fluid and pumps the inert gas into the attached stem 4 of the primary heat pipe. Until the temperature of the primary heat pipe reaches the design value, heat is lost only by conduction through the insulation 3. As the temperature approaches the design value, the vapor pressure forces the inert gas further into the stem 4 and the vapor-gas interface 9 moves toward surface 6. This action exposes the common wall 10 between the primary heat pipe 2 and the secondary heat pipe 5 to the working area of the primary heat pipe. Condensation occurs on the common wall 10 transferring the latent heat of condensation to the secondary heat pipe which sets the secondary heat pipe into operation. The secondary heat pipe transfers the heat from the evaporator section near the common wall 10 to the condenser section and the heat is radiated to the outside at surface 7.
The exact quantity of inert gas necessary for proper operation of the primary heat pipe depends on the desired temperature to be maintained in the battery compartment. For instance, if it is desired to hold the temperature at C., and if water is the working fluid, a quantity of gas is initially admitted such that the pressure of the compressed gas in the stem is 760 torr when the common wall 10 is exposed to the circulating working fluid of the primary heat pipe. Since the volume of the stem under the common wall 10 can be made small relative to the total volume of the stem, the pressure in the stem and hence in the working fluid will remain approximately at 760 torr.
The secondary heat pipe 5 is shown in the form of a circular container. The secondary heat pipe may be filled with an inert gas which will be compressed radially outward with an increased heat input through the common surface 10, thus causing the interface 8 to move radially outward exposing more radiating surface 7. In addition, other heat pipes may be connected to the second heat pipe in the same manner the second heat pipe was connected to the first in order to further increase the radiating area.
Various Working fluids may be employed with this invention. For instance, using 1,1,1,2-tetrachloroethane, the working presure would be about 350 torr at 100 C., but since the freezing point is 68.7 C., the risk of freezing the working fluid is much less than when using water.
This invention has special utility in connection with space craft. Heat pipes have been shown to work successfully in space. The durability and reliability of the invention are of major importance when used in conditions making repair and servicing impossible.
What I claim is:
1. A device for maintaining a heat generating body at a constant temperature comprising a first enclosed container partially surrounding the heat generating body and a second enclosed container connected to the first container by a common wall at a point remote from the heat generating body, said first container having a portion extending beyond said common wall, both of the containers being lined with a capillary material and partially filled with a condensable working fluid and partially filled with an inert gas, the ratio of the quantity of said working fluid to the quantity of said inert gas being selected so that said working fluid is in contact with at least a portion of said common wall only at a predetermined operating temperature and higher temperatures.
2. The device of claim 1 wherein the second container is circular.
3. The device of claim 1 wherein the condensable Working fluid is water. 7
4. The device of claim 1 wherein the condensable working fluid is 1,l,1,2-tetrachloroethane.
5. The device of claim 3 wherein one or more enclosed containers, each lined with a capillary material and filled with a condensable working fluid and an inert gas, are connected to the second container and to the next succeeding container by a common wall in chain fashion.
References Cited UNITED STATES PATENTS 3,378,449 4/1968 Roberts et a1. l65l05 X 2,581,347 1/1952 Backstrom 165-105 X 1,754,314 4/1930 Gay 165-105 X ROBERT A. OLEARY, Primary Examiner A. W. DAVIS, JR., Assistant Examiner US. Cl. .XR.
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Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3675711A (en) * 1970-04-08 1972-07-11 Singer Co Thermal shield
US3724215A (en) * 1971-05-19 1973-04-03 Atomic Energy Commission Decomposed ammonia radioisotope thruster
US3782449A (en) * 1968-12-05 1974-01-01 Euratom Temperature stabilization system
US3827480A (en) * 1971-04-27 1974-08-06 Bbc Brown Boveri & Cie Electrically insulated double tube heat pipe arrangement
US3838668A (en) * 1972-12-26 1974-10-01 L Hays Combustion engine heat removal and temperature control
US3866424A (en) * 1974-05-03 1975-02-18 Atomic Energy Commission Heat source containing radioactive nuclear waste
US3924674A (en) * 1972-11-07 1975-12-09 Hughes Aircraft Co Heat valve device
US3958627A (en) * 1974-10-15 1976-05-25 Grumman Aerospace Corporation Transverse variable conductance heat pipe
US3985182A (en) * 1973-03-17 1976-10-12 Hitachi, Ltd. Heat transfer device
US4067237A (en) * 1976-08-10 1978-01-10 Westinghouse Electric Corporation Novel heat pipe combination
EP0000217A1 (en) * 1977-06-22 1979-01-10 Koninklijke Philips Electronics N.V. Refrigerator
US4162701A (en) * 1977-11-21 1979-07-31 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Thermal control canister
US4189527A (en) * 1979-01-17 1980-02-19 The United States Of America As Represented By The Secretary Of The Air Force Spherical heat pipe metal-hydrogen cell
US4314008A (en) * 1980-08-22 1982-02-02 General Electric Company Thermoelectric temperature stabilized battery system
US4324845A (en) * 1980-06-30 1982-04-13 Communications Satellite Corp. Metal-oxide-hydrogen cell with variable conductant heat pipe
US4329407A (en) * 1978-05-05 1982-05-11 Brown, Boveri & Cie Ag Electrochemical storage battery
US4383013A (en) * 1980-07-23 1983-05-10 Chloride Silent Power Limited High temperature multicell electrochemical storage batteries
US4413671A (en) * 1982-05-03 1983-11-08 Hughes Aircraft Company Switchable on-off heat pipe
US4420035A (en) * 1982-10-15 1983-12-13 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Thermal control system
US4523636A (en) * 1982-09-20 1985-06-18 Stirling Thermal Motors, Inc. Heat pipe
US4597675A (en) * 1983-04-04 1986-07-01 The Garrett Corporation Mean temperature sensor
US4617985A (en) * 1984-09-11 1986-10-21 United Kingdom Atomic Energy Authority Heat pipe stabilized specimen container
US5064732A (en) * 1990-02-09 1991-11-12 International Fuel Cells Corporation Solid polymer fuel cell system: high current density operation
US5358799A (en) * 1992-07-01 1994-10-25 Rolls-Royce And Associates Limited Fuel cell
US5443926A (en) * 1992-11-02 1995-08-22 Compagnie Europeenne D'accumulateurs Thermoregulated battery of accumulators, especially for an electric vehicle
US6260333B1 (en) 1999-10-19 2001-07-17 Sharon Manufacturing Co., Inc. Pressure pad for a container bottom sealing device
US20020090546A1 (en) * 2001-01-06 2002-07-11 Chunghwa Telecom Co., Ltd. Method for enhancing battery performance and apparatus using the same
US11270802B1 (en) * 2017-12-07 2022-03-08 Triad National Security, Llc Creep and cascade failure mitigation in heat pipe reactors

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2380166B (en) 2001-09-27 2003-09-24 Red Lan Foldable stroller

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1754314A (en) * 1928-04-28 1930-04-15 Frazer W Gay Cooling system for underground electric transmission lines
US2581347A (en) * 1943-07-09 1952-01-08 Electrolux Ab Absorption refrigeration apparatus and heating arrangement therefor
US3378449A (en) * 1967-07-27 1968-04-16 Atomic Energy Commission Usa Nuclear reactor adapted for use in space

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1754314A (en) * 1928-04-28 1930-04-15 Frazer W Gay Cooling system for underground electric transmission lines
US2581347A (en) * 1943-07-09 1952-01-08 Electrolux Ab Absorption refrigeration apparatus and heating arrangement therefor
US3378449A (en) * 1967-07-27 1968-04-16 Atomic Energy Commission Usa Nuclear reactor adapted for use in space

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3782449A (en) * 1968-12-05 1974-01-01 Euratom Temperature stabilization system
US3675711A (en) * 1970-04-08 1972-07-11 Singer Co Thermal shield
US3827480A (en) * 1971-04-27 1974-08-06 Bbc Brown Boveri & Cie Electrically insulated double tube heat pipe arrangement
US3724215A (en) * 1971-05-19 1973-04-03 Atomic Energy Commission Decomposed ammonia radioisotope thruster
US3924674A (en) * 1972-11-07 1975-12-09 Hughes Aircraft Co Heat valve device
US3838668A (en) * 1972-12-26 1974-10-01 L Hays Combustion engine heat removal and temperature control
US3985182A (en) * 1973-03-17 1976-10-12 Hitachi, Ltd. Heat transfer device
US3866424A (en) * 1974-05-03 1975-02-18 Atomic Energy Commission Heat source containing radioactive nuclear waste
US3958627A (en) * 1974-10-15 1976-05-25 Grumman Aerospace Corporation Transverse variable conductance heat pipe
US4067237A (en) * 1976-08-10 1978-01-10 Westinghouse Electric Corporation Novel heat pipe combination
FR2361636A1 (en) * 1976-08-10 1978-03-10 Westinghouse Electric Corp LAYOUT OF HEAT DUCTS
EP0000217A1 (en) * 1977-06-22 1979-01-10 Koninklijke Philips Electronics N.V. Refrigerator
US4162701A (en) * 1977-11-21 1979-07-31 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Thermal control canister
US4329407A (en) * 1978-05-05 1982-05-11 Brown, Boveri & Cie Ag Electrochemical storage battery
US4189527A (en) * 1979-01-17 1980-02-19 The United States Of America As Represented By The Secretary Of The Air Force Spherical heat pipe metal-hydrogen cell
US4324845A (en) * 1980-06-30 1982-04-13 Communications Satellite Corp. Metal-oxide-hydrogen cell with variable conductant heat pipe
US4383013A (en) * 1980-07-23 1983-05-10 Chloride Silent Power Limited High temperature multicell electrochemical storage batteries
US4314008A (en) * 1980-08-22 1982-02-02 General Electric Company Thermoelectric temperature stabilized battery system
US4413671A (en) * 1982-05-03 1983-11-08 Hughes Aircraft Company Switchable on-off heat pipe
US4523636A (en) * 1982-09-20 1985-06-18 Stirling Thermal Motors, Inc. Heat pipe
EP0198126A1 (en) * 1982-09-20 1986-10-22 Stirling Thermal Motors Inc. Heat pipe
US4420035A (en) * 1982-10-15 1983-12-13 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Thermal control system
US4597675A (en) * 1983-04-04 1986-07-01 The Garrett Corporation Mean temperature sensor
US4617985A (en) * 1984-09-11 1986-10-21 United Kingdom Atomic Energy Authority Heat pipe stabilized specimen container
US5064732A (en) * 1990-02-09 1991-11-12 International Fuel Cells Corporation Solid polymer fuel cell system: high current density operation
US5358799A (en) * 1992-07-01 1994-10-25 Rolls-Royce And Associates Limited Fuel cell
US5443926A (en) * 1992-11-02 1995-08-22 Compagnie Europeenne D'accumulateurs Thermoregulated battery of accumulators, especially for an electric vehicle
US6260333B1 (en) 1999-10-19 2001-07-17 Sharon Manufacturing Co., Inc. Pressure pad for a container bottom sealing device
US20020090546A1 (en) * 2001-01-06 2002-07-11 Chunghwa Telecom Co., Ltd. Method for enhancing battery performance and apparatus using the same
US6946216B2 (en) * 2001-01-06 2005-09-20 Acer Incorporated Method for enhancing battery performance and apparatus using the same
US11270802B1 (en) * 2017-12-07 2022-03-08 Triad National Security, Llc Creep and cascade failure mitigation in heat pipe reactors

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