EP0600192B1 - Heat pipe - Google Patents
Heat pipe Download PDFInfo
- Publication number
- EP0600192B1 EP0600192B1 EP93116292A EP93116292A EP0600192B1 EP 0600192 B1 EP0600192 B1 EP 0600192B1 EP 93116292 A EP93116292 A EP 93116292A EP 93116292 A EP93116292 A EP 93116292A EP 0600192 B1 EP0600192 B1 EP 0600192B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat
- heat pipe
- 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.)
- Expired - Lifetime
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
- 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. There, the steam condenses, the latent heat stored in it being dissipated to the environment, and the condensate formed flows back 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.
- 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 drop in the Venturi nozzle must be considerable, i.e. the nozzle must have a comparatively large cross-sectional constriction. 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 restart process is simplified and accelerated considerably.
- 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)
Description
Die Erfindung betrifft eine Anordnung zum Abführen von Wärme, bestehend aus wenigstens einem mit einem Wärmeträgermedium gefüllten Wärmerohr, in dem wenigstens je ein Strömungskanal für das flüssige und für das in den dampfförmigen Aggregatzustand überführte Wärmeträgermedium vorhanden sind und bei dem Mittel vorgesehen sind, um im Flüssigkeitskanal befindliche Blasen zu entfernen sowie aus wenigstens einem mit dem Wärmerohr in thermischem Kontakt stehenden Radiator.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.
Wärmerohre oder "heat pipes" für den Transport von Wärme sind, insbesondere aus dem Bereich der Raumfahrttechnik bereits bekannt. Bei diesem wird auf der wärmeabgebenden Seite eine Flüssigkeit, in der Regel Ammoniak, verdampft und der Dampf wird zur wärmeabgebenden Seite geleitet. Dort kondensiert der Dampf, wobei die in ihm gespeicherte latente Wärme an die Umgebung abgeführt wird, und das entstehende Kondensat fließt wieder zur wärmeaufnehmenden Seite, dem Verdampfer, zurück. Die dabei auftretende Dampfströmung ist eine normale Druckströmung, während die Flüssigkeitsströmung eine Kapillarströmung ist. Unterschiedliche Krümmungsradien der Grenzfläche zwischen der Flüssigkeit und dem Dampf im Verdampferende einerseits und im Kondensatorende andererseits und die dadurch hervorgerufenen Kapillarkräfte bewirken eine Druckdifferenz in Richtung Verdampferende, die die Strömung antreibt. Die sich einstellende Strömungsgeschwindigkeit ergibt sich aus dem Gleichgewicht zwischen dem Druckverlust aufgrund von Reibungskräften und der wirksamen Druckdifferenz der Kapillarkräfte.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. There, the steam condenses, the latent heat stored in it being dissipated to the environment, and the condensate formed flows back 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. Different radii of curvature of the interface between the liquid and the vapor in the evaporator end on the one hand and in the condenser end on the other hand and the capillary forces caused thereby cause a pressure difference in the direction of the evaporator end which drives the flow. The resulting flow velocity results from the equilibrium between the pressure loss due to frictional forces and the effective pressure difference of the capillary forces.
Moderne Kochleistungswärmerohre sind in der Lage, auch bei vergleichsweise geringen Temperaturdifferenzen, Wärmemengen in der Größenordnung von etwa 1 kW über Entfernungen zwischen einem und etwa 20 Metern zu transportieren.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.
Diese im Vergleich zu konventionellen Wärmerohren höhere Leistung der Hochleistungswärmerohre wird dadurch erzielt, daß für den Transport der Flüssigkeit Kanäle unterschiedlicher Abmessungen verwendet werden: Während im Verdampfungsbereich eine Vielzahl sehr kleiner, in Umfangsrichtung verlaufender Kanäle mit Kapillargeometrien verwendet wird, um große treibende Kapillarkräfte zu erzielen, erfolgt die Strömungsführung im Kondensatorbereich sowie in der Transportzone über nur wenige Strömungskanäle, gegebenenfalls einem einzigen Kanal mit relativ großem Durchmesser, der auch als Arterie bezeichnet wird. Auf diese Weise wird der reibungsbedingte Druckverlust minimiert und es ergibt sich bei gleichen Kapillarkräften ein wesentliche größerer Fluidmassenstrom und als dessen Folge ein ebenfalls wesentlich höherer Wärmestrom.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.
Ein wesentliches Problem beim Betrieb derartiger Hochleistungswärmerohre liegt darin, daß ihre Funktion erheblich beeinträchtigt bzw. ganz unterbrochen werden kann, wenn sich Blasen aus dem Dampf des Wärmeträgerfluids oder aus gasförmigen, nicht kondensierbaren Fremdstoffen in der Arterie befinden. Diese können sich entweder bereits bei der Inbetriebnahme des Wärmerohres zufällig dort befunden haben, sie können aber auch durch eine betriebsbedingte Überlastung des Wärmerohres, beispielsweise eine Überhitzung am Verdampferende bei kurzzeitiger Austrocknung der Verdampfungszone, entstanden sein. Die Blasen können den Transport des Wärmeträgerfluids zur wärmeaufnehmenden Zone unterbrechen, so daß diese weiter austrocknet und das Wärmerohr in seiner Funktion blockiert wird.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.
In der Literaturstelle Heat Pipe Design Handbook, Volume 1, B & K Engineering Inc., Towson, Maryland 21204, USA, Seiten 149 und 152, sind deshalb zwei Wärmerohre beschrieben, bei denen Maßnahmen zur Entfernung von Blasen und damit zur Vermeidung von Blockaden durch Glasblasen vorgesehen sind. Diese Maßnahmen bestehen in einem Fall aus einer Anordnung mit Entlüftungsbohrungen in der Wand zwischen der Arterie und dem Dampfkanal, im anderen Fall aus einer Venturidüse, die im Transportbereich für den Dampf angeordnet ist und die zugleich als Strahlpumpe über ein Ansaugrohr in der Arterie vorhandene Gasblasen absaugt.In the heat pipe design handbook, volume 1, B&K Engineering Inc., Towson, Maryland 21204, USA, pages 149 and 152, two heat pipes are therefore described, in which measures are used to remove bubbles and thus prevent blockages 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 .
Nachteilig bei einer Anordnung von Entlüftungslöchern in der Arterienwand ist der Umstand, daß während des Betriebes des Wärmerohrs der Druck im Dampfkanal wesentlich höher als in der Arterie ist, so daß zur Überführung von Gasblasen aus der Arterie in den Dampfkanal eine Betriebsunterbrechung erforderlich ist. Da dann aber die Entlüftungsbohrungen von Flüssigkeitsbrücken blockiert sind, die zunächst verdampfen müssen bevor die Gasblasen hindurchtreten können, erfordern diese Betriebspausen einen vergleichsweise langen Zeitraum, bevor das Wärmerohr wieder einsatzbereit ist.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. However, since 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.
Die Anordnung einer Venturidüse im Dampfkanal hat andererseits den folgenden Nachteil: Befindet sich keine Gasblase im Ansaugbereich der Düse, so sammelt sich ständig eine, wenn auch geringe, Menge an Wärmeträgerfluid aus der Arterie im Ansaugrohr. Wenn nun eine Gasblase vor die Ansaugöffnung gelangt, so muß, damit diese aus der Arterie abgesaugt werden kann, zunächst die Flüssigkeitsmenge aus dem Ansaugrohr entfernt werden. Wegen des damit verbundenen großen Druckverlustes der Strömung im Ansaugrohr muß die in der Venturidüse hervorgerufene Druckminderung beträchtlich sein, d.h., die Düse muß eine vergleichsweise starke Querschnittsverengung aufweisen. Dies aber führt auf der anderen Seite zu einer erheblichen Beeinträchtigung der Dampfströmung infolge des Druckverlustes und damit zu einer stark herabgesetzten Leistungsfähigkeit des Wärmerohres.The arrangement of a Venturi nozzle in the steam channel, on the other hand, 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 drop in the Venturi nozzle must be considerable, i.e. the nozzle must have a comparatively large cross-sectional constriction. 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.
Aufgabe der Erfindung ist es, ein Wärmerohr der eingangs genannten Art so auszubilden, daß Dampfblasen des Wärmeträgerfluids sowie Blasen aus nicht kondensierbarem Gas einfach und schnell, d.h. ohne Betriebsunterbrechung, aus dem Strömungskanal für das Fluid entfernt werden können, auch wenn sie vor der Inbetriebnahme bereits den größten Teil des Strömungsquerschnittes der Arterie einnehmen oder wenn diese Blasen durch Überlastung in der Verdampfungszone entstanden sind. Die Erfindung löst diese Aufgabe durch ein Wärmerohr mit den kennzeichnenden Merkmalen des Patentanspruchs 1. Vorteilhafte Weiterbildungen sind durch die Merkmale der Unteransprüche gekennzeichnet.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.
Das Wärmerohr nach der Erfindung ist dabei in hohem Maße fehlertolerant gegenüber im Betrieb auftretenden Überlastungen, da der Start- bzw. Wiederanfahrvorgang wesentlich vereinfacht und beschleunigt wird. Ein besonders wichtiger Vorteil des erfindungsgemäßen Wärmerohres liegt ferner darin, daß es möglich ist, nicht nur Blasen aus nicht-kondensierbaren Gasen aus dem Flüssigkeitskanal zu entfernen, sondern ebenso wirksam auch Dampfblasen.The heat pipe according to the invention is to a large extent fault-tolerant to overloads occurring during operation, since the start-up or restart process is simplified and accelerated considerably. 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.
Im folgenden soll die Erfindung anhand eines Ausführungsbeispiels näher erläutert werden. Es zeigen:
- Fig. 1
- eine Draufsicht auf eine Anordnung zum Abführen von Wärme und
- Fig. 2 und 3
- je einen Querschnitt durch die in Fig. 1 dargestellte Anordnung gemäß II-II bzw. III-III.
- Fig. 1
- a plan view of an arrangement for dissipating heat and
- 2 and 3
- a cross section through the arrangement shown in Fig. 1 according to II-II and III-III.
Die in Fig. 1 in einer Draufsicht dargestellte Anordnung umfaßt ein Hauptwärmerohr 1, zwei Hilfswärmerohre 2 und 3 sowie zwei Radiatoren 4 und 5. Von letzteren steht der größere der beiden, der Hauptradiator4, in direktem thermischen Kontakt mit dem kondensatorseitigen Ende des Hauptwärmerohres 1, während der wesentlich kleiner ausgelegte Hilfsradiator 5 vom Hauptradiator 4 thermisch getrennt angeordnet ist. Die thermische Trennung der beiden Radiatoren wird dabei sowohl durch den Abstand zwischen diesen erreicht, wie aus Fig. 3 ersichtlich ist, als auch gegebenenfalls durch eine zwischen beiden angeordnete Isolierung.The arrangement shown in a plan view in FIG. 1 comprises a main heat pipe 1, two
Der Hilfsradiator 5 steht in direktem thermischen Kontakt mit den kondensatorseitigen Endbereichen der beiden Hilfswärmerohre 2 und 3, die einen wesentlich geringeren Querschnitt als das Hauptwärmerohr 1 aufweisen. Mit letzterem sind sie am gemeinsamen Verdampferende thermisch gekoppelt, wie die Darstellung in Fig. 2 zeigt. Dies geschieht über Kontaktflächen 6,7 und 8, die jeweils an die verdampferseitigen Endbereiche der Wärmerohre 1 bis 3 angeformt sind und die unmittelbar miteinander verbunden sind.The
Die Figuren 2 und 3 zeigen ferner den inneren Aufbau des Hauptwärmerohres 1, das durch ein in Axialrichtung verlaufendes Strangpreßprofil 9 in je zwei Flüssigkeitskanäle oder Arterien 10 und 11 sowie in zwei Dampfkanäle 12 und 13 unterteilt ist. Unterhalb der beiden Flüssigkeitskanäle 10 und 11, durch ein perforiertes Blech 14 von diesen getrennt, verläuft bei dem hier beschriebenen Ausführungsbeispiel ferner ein weiterer von der Flüssigkeit durchströmter Kanal 15, der als Falle für in der Flüssigkeit enthaltene Gas- oder Dampfblasen dient.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
Gas- oder Dampfblasen, die sich in der Verdampferzone des Wärmerohres 1 befinden und die sich dort entweder bereits aufgrund einer ungünstigen Fluidverteilung vor der Inbetriebnahme im Orbit befanden, die durch eine kurzzeitige Überlastung entstanden sind oder die über die Kanäle 12,13 oder 15 dorthin transportiert wurden, werden dadurch aufgelöst, daß das in diesen Kanälen befindliche Kondensat unterkühlt wird. Dies wird mit Hilfe der Hilfswärmerohre 2 und 3 erreicht, die mit dem Hilfsradiator 5 verbunden sind und die die für die Unterkühlung des Kondensats erforderliche zusätzliche Wärmeabfuhr sicherstellen.Gas or vapor bubbles, which are located in the evaporator zone of the heat pipe 1 and which were either already in orbit due to an unfavorable fluid distribution prior to commissioning, which were caused by a brief overload or which transported there via
Claims (4)
- Arrangement for dissipating heat, consisting of at least one first heat pipe (1), filled with a heat transfer medium, within which there is at least one flow channel for the liquid heat transfer medium and at least one flow channel for the heat transfer medium transferred in the vaporous state of aggregation and in which there are provided means for removing bubbles present in the liquid channel, and of at least one first radiator (4) which is in thermal contact with the heat pipe, characterized in that the means consist of at least one further heat pipe (2,3), provided in addition to the one or more first heat pipes (1), which is in thermal contact, on the evaporator side, with the evaporator region of the first heat pipe (1) and which is thermally coupled, at its end on the condenser side, with a second radiator (5) which, in turn, is disposed so as to be thermally isolated from the first radiator (4) connected to the first heat pipe (1).
- Arrangement according to Claim 1, characterized in that the diameter of the further heat pipe (2) is considerably smaller than that of the first heat pipe (1).
- Arrangement according to Claim 2, characterized in that the second radiator (5) is considerably smaller than the first radiator (4).
- Arrangement according to Claim 3, characterized in that, in addition to the one or more first heat pipes (1), there are two heat pipes (2,3), disposed symmetrically relative to the latter, both of which are in thermal contact with the second radiator (5) at their end regions on the condenser side.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4240081 | 1992-11-28 | ||
| DE4240081A DE4240081C1 (en) | 1992-11-28 | 1992-11-28 | Heat pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0600192A1 EP0600192A1 (en) | 1994-06-08 |
| EP0600192B1 true EP0600192B1 (en) | 1996-04-24 |
Family
ID=6473914
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP93116292A Expired - Lifetime EP0600192B1 (en) | 1992-11-28 | 1993-10-08 | Heat pipe |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US5358033A (en) |
| EP (1) | EP0600192B1 (en) |
| DE (2) | DE4240081C1 (en) |
Families Citing this family (6)
| 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 |
| FR2840394B1 (en) * | 2002-05-30 | 2004-08-27 | Cit Alcatel | HEAT TRANSFER DEVICE FOR SATELLITE COMPRISING AN EVAPORATOR |
| EP1776058B1 (en) * | 2004-07-02 | 2018-12-26 | Discus Dental, LLC | Dental light device having an improved heat sink |
| DE102006045701A1 (en) * | 2006-09-27 | 2008-04-03 | Osram Opto Semiconductors Gmbh | Cooling device for cooling heat source of arrangement i.e. headlight part, of motor vehicle, has heat conductive pipes coupled together thermally, where heat from heat source is conducted to cooling body by one or both pipes |
| US9315280B2 (en) * | 2012-11-20 | 2016-04-19 | Lockheed Martin Corporation | Heat pipe with axial wick |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3618660A (en) * | 1969-11-21 | 1971-11-09 | Euratom | Heat transfer device |
| JPS5096942A (en) * | 1973-12-24 | 1975-08-01 | ||
| 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 |
| 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 |
| 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 |
| US4941527A (en) * | 1989-04-26 | 1990-07-17 | Thermacore, Inc. | Heat pipe with temperature gradient |
| US4917177A (en) * | 1989-09-21 | 1990-04-17 | Thermacore, Inc. | Cooled artery extension |
-
1992
- 1992-11-28 DE DE4240081A patent/DE4240081C1/en not_active Expired - Fee Related
-
1993
- 1993-10-08 EP EP93116292A patent/EP0600192B1/en not_active Expired - Lifetime
- 1993-10-08 DE DE59302367T patent/DE59302367D1/en not_active Expired - Fee Related
- 1993-11-29 US US08/158,422 patent/US5358033A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| DE4240081C1 (en) | 1994-04-28 |
| US5358033A (en) | 1994-10-25 |
| EP0600192A1 (en) | 1994-06-08 |
| DE59302367D1 (en) | 1996-05-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0600191B1 (en) | Heat pipe | |
| DE69915776T2 (en) | Side part for heat exchangers and heat exchangers with side plates | |
| EP0334142B1 (en) | Evaporator unit | |
| DE60315095T2 (en) | Thermosyphon for electronic devices for cooling with a non-uniform air flow | |
| EP0577969B1 (en) | Heat-pipe | |
| DE102007034710B4 (en) | Two-stage absorption cooler | |
| EP0600192B1 (en) | Heat pipe | |
| DE3310236A1 (en) | Refrigerant distributor for the evaporator of a refrigerator or heat pump | |
| DE2339013A1 (en) | RADIATOR ELEMENT | |
| EP3105650A1 (en) | Cooling arrangement for a computer system | |
| EP3507559B1 (en) | Heat exchanger integration | |
| DE2820874A1 (en) | PLATE EVAPORATOR | |
| DE602004010640T2 (en) | EVAPORATOR AND HEAT EXCHANGER WITH EXTERNAL CIRCUIT FLOW AND HEAT PUMP SYSTEM AND AIR CONDITIONING WITH THE EVAPORATOR OR HEAT EXCHANGER | |
| DE112012004635T5 (en) | Interior condenser | |
| DE102004047304A1 (en) | Subcooling condenser | |
| DE3228311C2 (en) | Evaporation crucible for vacuum evaporation systems | |
| DE102009023985A1 (en) | Waste heat recovery device | |
| EP0574678A1 (en) | Heat-pipe | |
| DE2414295C2 (en) | Heat exchanger for the condensation of steam | |
| DE202017104743U1 (en) | Heat exchanger with microchannel structure or wing tube structure | |
| DE2839638A1 (en) | DRY COOLING SYSTEM FOR POWER PLANTS | |
| EP0130361B1 (en) | Heat exchanger end palte with arrangement for cooling | |
| DE8002070U1 (en) | COMPRESSOR COOLING ARRANGEMENT | |
| EP2108912B1 (en) | Condenser, in particular for a vehicle cooling system | |
| EP3001434B1 (en) | Radiator for cooling a coolant liquid of a transformer |
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): BE DE FR NL |
|
| 17P | Request for examination filed |
Effective date: 19940817 |
|
| RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: DAIMLER-BENZ AEROSPACE AKTIENGESELLSCHAFT |
|
| 17Q | First examination report despatched |
Effective date: 19951013 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): BE DE FR NL |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Effective date: 19960424 |
|
| REF | Corresponds to: |
Ref document number: 59302367 Country of ref document: DE Date of ref document: 19960530 |
|
| ET | Fr: translation filed | ||
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed | ||
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 19980609 Year of fee payment: 6 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 19981021 Year of fee payment: 6 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 19981030 Year of fee payment: 6 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: CD Ref country code: FR Ref legal event code: CA |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20000501 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20000630 |
|
| NLV4 | Nl: lapsed or anulled due to non-payment of the annual fee |
Effective date: 20000501 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20000801 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |