EP0600192A1 - Caloduc - Google Patents

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Publication number
EP0600192A1
EP0600192A1 EP93116292A EP93116292A EP0600192A1 EP 0600192 A1 EP0600192 A1 EP 0600192A1 EP 93116292 A EP93116292 A EP 93116292A EP 93116292 A EP93116292 A EP 93116292A EP 0600192 A1 EP0600192 A1 EP 0600192A1
Authority
EP
European Patent Office
Prior art keywords
heat pipe
heat
radiator
liquid
thermal contact
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.)
Granted
Application number
EP93116292A
Other languages
German (de)
English (en)
Other versions
EP0600192B1 (fr
Inventor
Reinhard Dr. Schlitt
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.)
Airbus Defence and Space GmbH
Original Assignee
Daimler Benz Aerospace AG
Erno Raumfahrttechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daimler Benz Aerospace AG, Erno Raumfahrttechnik GmbH filed Critical Daimler Benz Aerospace AG
Publication of EP0600192A1 publication Critical patent/EP0600192A1/fr
Application granted granted Critical
Publication of EP0600192B1 publication Critical patent/EP0600192B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F28D15/0258—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 means to remove contaminants, e.g. getters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion

Definitions

  • the invention relates to an arrangement for dissipating heat, consisting of at least one heat pipe filled with a heat transfer medium, in which there are at least one flow channel each for the liquid and for the heat transfer medium converted into the vaporous state and in which means are provided in the liquid channel remove any bubbles and from at least one radiator in thermal contact with the heat pipe.
  • Heat pipes or "heat pipes” for the transport of heat are already known, in particular from the field of space technology. This is usually a liquid on the heat-emitting side Ammonia, evaporates and the steam is directed to the heat-emitting side. The steam condenses there, the latent heat stored in it being dissipated to the surroundings, and the condensate that flows back again to the heat-absorbing side, the evaporator.
  • the steam flow that occurs is a normal pressure flow, while the liquid flow is a capillary flow.
  • Modern cooking performance heat pipes are able to transport heat quantities of the order of about 1 kW over distances between one and about 20 meters, even with comparatively small temperature differences.
  • This higher performance of the high-performance heat pipes compared to conventional heat pipes is achieved by using channels of different dimensions for the transport of the liquid: While in the evaporation area a large number of very small, circumferential channels with capillary geometries are used to achieve large driving capillary forces, the flow in the condenser area and in the transport zone takes place via only a few flow channels, possibly a single channel with a relatively large diameter, which is also referred to as an artery. In this way the friction-related pressure loss is minimized and, with the same capillary forces, a significantly larger fluid mass flow results and, as a result, also a significantly higher heat flow.
  • a major problem with the operation of such high-performance heat pipes is that their function can be significantly impaired or completely interrupted if there are bubbles in the artery from the vapor of the heat transfer fluid or from gaseous, non-condensable foreign substances. These may either have happened to be there when the heat pipe was put into operation, but they may also have arisen due to operational overloading of the heat pipe, for example overheating at the end of the evaporator and the evaporation zone drying out briefly. The bubbles can interrupt the transport of the heat transfer fluid to the heat-absorbing zone, so that it dries out further and the function of the heat pipe is blocked.
  • the heat pipe design handbook volume 1, B&K Engineering Inc., Towson, Maryland 21204, USA, pages 149 and 152, therefore describes two heat pipes in which measures for removing bubbles and thus for preventing blockages are described Glass bubbles are provided. These measures consist in one case of an arrangement with ventilation holes in the wall between the artery and the steam channel, in the other case a venturi nozzle which is arranged in the transport area for the steam and which at the same time sucks off gas bubbles present in the artery as a jet pump via an intake pipe .
  • a disadvantage of an arrangement of ventilation holes in the artery wall is the fact that during the Operation of the heat pipe, the pressure in the steam channel is significantly higher than in the artery, so that an operation interruption is required to transfer gas bubbles from the artery into the steam channel.
  • the ventilation holes are blocked by liquid bridges, which first have to evaporate before the gas bubbles can pass through, these breaks in operation require a comparatively long period of time before the heat pipe is ready for use again.
  • the arrangement of a Venturi nozzle in the steam channel has the following disadvantage: If there is no gas bubble in the suction area of the nozzle, a, albeit small, amount of heat transfer fluid constantly collects from the artery in the suction pipe. If a gas bubble now reaches the suction opening, the amount of liquid must first be removed from the suction pipe so that it can be sucked out of the artery. Because of the associated large pressure loss of the flow in the intake manifold, the pressure reduction caused in the Venturi nozzle must be considerable, i.e. the nozzle must have a comparatively large narrowing of the cross section. On the other hand, however, this leads to a considerable impairment of the steam flow due to the pressure loss and thus to a greatly reduced performance of the heat pipe.
  • the object of the invention is to design a heat pipe of the type mentioned in such a way that vapor bubbles of the heat transfer fluid and bubbles from non-condensable gas can be removed from the flow channel for the fluid simply and quickly, that is to say without interrupting operation, even if they are already in operation most of the flow cross section of the Take up the artery or if these blisters are caused by overload in the evaporation zone.
  • the invention solves this problem by a heat pipe with the characterizing features of claim 1.
  • Advantageous further developments are characterized by the features of the subclaims.
  • the heat pipe according to the invention is to a large extent fault-tolerant to overloads occurring during operation, since the start-up or Weider start-up process is considerably simplified and accelerated.
  • a particularly important advantage of the heat pipe according to the invention is that it is possible not only to remove bubbles from non-condensable gases from the liquid channel, but also to effectively remove steam bubbles.
  • the arrangement shown in a plan view in FIG. 1 comprises a main heat pipe 1, two auxiliary heat pipes 2 and 3 and two radiators 4 and 5.
  • the main radiator 4 is in direct thermal contact with the condenser-side end of the main heat pipe 1, while the much smaller auxiliary radiator 5 is arranged thermally separated from the main radiator 4.
  • the Thermal separation of the two radiators is achieved both by the distance between them, as can be seen in FIG. 3, and optionally by an insulation arranged between the two.
  • the auxiliary radiator 5 is in direct thermal contact with the condenser-side end regions of the two auxiliary heat pipes 2 and 3, which have a substantially smaller cross section than the main heat pipe 1. With the latter, they are thermally coupled at the common evaporator end, as the illustration in FIG. 2 shows. This is done via contact surfaces 6, 7 and 8, which are each molded onto the evaporator-side end regions of the heat pipes 1 to 3 and which are connected directly to one another.
  • Figures 2 and 3 also show the inner structure of the main heat pipe 1, which is divided by an axial extrusion 9 into two liquid channels or arteries 10 and 11 and two steam channels 12 and 13. Below the two liquid channels 10 and 11, separated from them by a perforated sheet 14, in the exemplary embodiment described here there also runs another channel 15 through which the liquid flows, which serves as a trap for gas or vapor bubbles contained in the liquid.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Geometry (AREA)
  • Central Heating Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP93116292A 1992-11-28 1993-10-08 Caloduc Expired - Lifetime EP0600192B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4240081 1992-11-28
DE4240081A DE4240081C1 (de) 1992-11-28 1992-11-28 Wärmerohr

Publications (2)

Publication Number Publication Date
EP0600192A1 true EP0600192A1 (fr) 1994-06-08
EP0600192B1 EP0600192B1 (fr) 1996-04-24

Family

ID=6473914

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93116292A Expired - Lifetime EP0600192B1 (fr) 1992-11-28 1993-10-08 Caloduc

Country Status (3)

Country Link
US (1) US5358033A (fr)
EP (1) EP0600192B1 (fr)
DE (2) DE4240081C1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2840394A1 (fr) * 2002-05-30 2003-12-05 Cit Alcatel Dispositif de transfert de chaleur pour satellite comprenant un evaporateur
DE102006045701A1 (de) * 2006-09-27 2008-04-03 Osram Opto Semiconductors Gmbh Kühlvorrichtung und Anordnung mit Kühlvorrichtung

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6065529A (en) * 1997-01-10 2000-05-23 Trw Inc. Embedded heat pipe structure
US6938679B1 (en) * 1998-09-15 2005-09-06 The Boeing Company Heat transport apparatus
RU2219455C2 (ru) * 2002-02-04 2003-12-20 Открытое акционерное общество "Ракетно-космическая корпорация "Энергия" им. С.П.Королева" Тепловая труба
CA2572548C (fr) * 2004-07-02 2014-09-02 Discus Dental Impressions, Inc. Dispositifs d'eclairage dentaire offrant un puits thermique ameliore
US9315280B2 (en) * 2012-11-20 2016-04-19 Lockheed Martin Corporation Heat pipe with axial wick
US12196496B2 (en) * 2022-09-25 2025-01-14 Aic Inc. Liquid-cooled cooling structure

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2255566A1 (en) * 1973-12-24 1975-07-18 Dornier System Gmbh Solar heating panel and heat transfer conduit - has fin shaped arrangements extending from conduit
US4485670A (en) * 1981-02-13 1984-12-04 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Heat pipe cooled probe
US4583587A (en) * 1984-05-31 1986-04-22 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Multi-leg heat pipe evaporator
US4880050A (en) * 1988-06-20 1989-11-14 The Boeing Company Thermal management system
US4917177A (en) * 1989-09-21 1990-04-17 Thermacore, Inc. Cooled artery extension

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3618660A (en) * 1969-11-21 1971-11-09 Euratom Heat transfer device
US4422501A (en) * 1982-01-22 1983-12-27 The Boeing Company External artery heat pipe
US4627487A (en) * 1983-12-19 1986-12-09 Hughes Aircraft Company Separate liquid flow heat pipe system
US4941527A (en) * 1989-04-26 1990-07-17 Thermacore, Inc. Heat pipe with temperature gradient

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2255566A1 (en) * 1973-12-24 1975-07-18 Dornier System Gmbh Solar heating panel and heat transfer conduit - has fin shaped arrangements extending from conduit
US4485670A (en) * 1981-02-13 1984-12-04 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Heat pipe cooled probe
US4583587A (en) * 1984-05-31 1986-04-22 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Multi-leg heat pipe evaporator
US4880050A (en) * 1988-06-20 1989-11-14 The Boeing Company Thermal management system
US4917177A (en) * 1989-09-21 1990-04-17 Thermacore, Inc. Cooled artery extension

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2840394A1 (fr) * 2002-05-30 2003-12-05 Cit Alcatel Dispositif de transfert de chaleur pour satellite comprenant un evaporateur
US7174950B2 (en) 2002-05-30 2007-02-13 Alcatel Heat transfer system for a satellite including an evaporator
DE102006045701A1 (de) * 2006-09-27 2008-04-03 Osram Opto Semiconductors Gmbh Kühlvorrichtung und Anordnung mit Kühlvorrichtung

Also Published As

Publication number Publication date
DE4240081C1 (de) 1994-04-28
US5358033A (en) 1994-10-25
DE59302367D1 (de) 1996-05-30
EP0600192B1 (fr) 1996-04-24

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