EP0577969B1 - Heat-pipe - Google Patents
Heat-pipe Download PDFInfo
- Publication number
- EP0577969B1 EP0577969B1 EP93108818A EP93108818A EP0577969B1 EP 0577969 B1 EP0577969 B1 EP 0577969B1 EP 93108818 A EP93108818 A EP 93108818A EP 93108818 A EP93108818 A EP 93108818A EP 0577969 B1 EP0577969 B1 EP 0577969B1
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- EP
- European Patent Office
- Prior art keywords
- channel
- heat
- arrangement according
- shut
- liquid
- 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
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- 239000007788 liquid Substances 0.000 claims description 28
- 238000012546 transfer Methods 0.000 claims description 14
- 229910001285 shape-memory alloy Inorganic materials 0.000 claims description 4
- 230000002776 aggregation Effects 0.000 claims 1
- 238000004220 aggregation Methods 0.000 claims 1
- 230000007423 decrease Effects 0.000 claims 1
- 238000005485 electric heating Methods 0.000 claims 1
- 210000001367 artery Anatomy 0.000 description 10
- 239000007789 gas Substances 0.000 description 10
- 239000013529 heat transfer fluid Substances 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 238000009423 ventilation Methods 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- HZEWFHLRYVTOIW-UHFFFAOYSA-N [Ti].[Ni] Chemical compound [Ti].[Ni] HZEWFHLRYVTOIW-UHFFFAOYSA-N 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 229910001000 nickel titanium Inorganic materials 0.000 description 2
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000006735 deficit Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 239000012808 vapor phase Substances 0.000 description 1
- 238000013022 venting Methods 0.000 description 1
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
- F28D15/04—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
- F28D15/046—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 characterised by the material or the construction of the capillary structure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/06—Control arrangements therefor
Definitions
- the invention relates to an arrangement for the transfer of heat, consisting of a heat pipe filled with a heat transfer medium, in each of which there is a flow channel for the liquid and for the heat transfer medium converted to the vaporous state, and in which means are further provided for in the liquid channel To convey bubbles into the steam channel.
- Heat pipes or "heat pipes” for the transport of heat are already known, in particular from the field of space technology.
- a liquid usually ammonia
- the steam condenses there, and the latent heat stored in it evaporates into the environment is discharged, and the resulting condensate flows back to the heat-absorbing side, to the evaporator.
- the steam flow that occurs is a normal pressure flow, while the liquid flow is a capillary flow.
- Modern high-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 pipe compared to conventional heat pipes is achieved by using channels of different dimensions for the transport of the liquid: While a large number of very small channels with capillary geometries are used in the evaporation area to achieve large driving capillary forces, the flow is guided in the Condenser area and in the transport zone 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 Gas 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 of a valve 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 .
- 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 from the artery is constantly collected 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 quickly and easily from the flow channel for the fluid and thus safe commissioning of such a pipe, either for the first time or after an interruption in operation caused, for example, by overloading is guaranteed.
- 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 controllable shut-off device provided in a further embodiment of the invention makes it possible for the the removal of steam bubbles to be carried out by briefly opening the end of the evaporator either to be controlled manually or to initiate it fully automatically in order to significantly accelerate the venting.
- the actuating force required for opening can in a particularly advantageous manner thermostatically, electromagnetically or by using an actuator made of a so-called memory alloy ("shape memory alloy”), such as. B. nickel-titanium.
- the section shown in FIG. 1 shows the transport zone of a high-performance heat pipe in the central area, to which the evaporator zone is connected in the left part of the drawing and the condenser zone in the right part.
- the transport zone consists of a flow channel 1 for the evaporated heat transfer medium and, arranged in the image below, a second flow channel 2, the artery, in which the heat transfer medium liquefied again at the end of the condenser flows back to the end of the evaporator.
- the liquid channel 2 is designed in such a way that its capillary radius, which is relevant for the formation of gas or vapor bubbles, constantly increases starting from the end of the evaporator and reaches its greatest value at the end of the condenser.
- FIGS. 2 and 3 differs from the one described above in that in this case the wall 13 separating the steam channel 11 from the liquid channel 12 runs parallel to the longitudinal axis of the heat pipe and in this case the conical taper of the capillary cross section of the liquid channel 12 in the direction of the evaporator end is achieved by a wedge-shaped plate 17 arranged on the partition 13 and projecting into the liquid channel 12. The wedge height and thus the cross-sectional area of this sheet 17 increases continuously towards the end of the evaporator.
- the image also shows the liquid / vapor interface 14 and the capillary structure 15.
- Fig. 4 shows an embodiment of an advantageous shut-off device 16 in the manner of an electromagnetic valve.
- the shut-off device 16 is constructed identically to the shut-off device 6 of the arrangement shown in FIG. 1. It consists of a stamp 21, which is held on a shaft 22, which in turn is designed as an armature for an electromagnet.
- the latter is formed by a cylindrical current-carrying coil 23 which surrounds a cylindrical extension 25 of the heat pipe in a separate housing 24, this extension 25 having a smaller diameter than the actual heat pipe and at the same time serving as a guide for the shaft 22.
- a compression spring 26 is arranged, which presses the sealing surface of the plunger 21 against the evaporator-side end of the wall 13 and of the wedge-shaped plate 17.
- the plunger 21 is pulled away from the wall 13 for a short time, thus creating an opening between the liquid duct 12 and the steam duct 11. Vapor or gas bubbles that have accumulated on the evaporator-side end of the liquid channel 12 at this time can quickly escape into the vapor channel 11 through this opening.
- the liquid channel 12 fills up to the capillary structure 15 completely with the liquid heat transfer medium, as a result of which the prerequisite for starting up the heat pipe is given.
- the heat transfer medium passes through the capillaries located on the inner wall of the tube in the evaporator area into the steam channel 11, where it evaporates while absorbing the heat to be removed.
- the brief opening process is controlled in that a current pulse flows through the coil 23 via connecting lines 27 and thereby pulls the shaft 22 into the extension 25 against the force of the compression spring 26.
- a thermostatically controlled shut-off device instead of such an electromagnetic valve, which is formed by a heating device and an actuator, the temperature-dependent expansion of which is converted into a movement of the plunger closing the passage opening.
- an element made of a shape memory alloy, for example nickel titanium, is also suitable as an actuator.
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- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Central Heating Systems (AREA)
- Surgical Instruments (AREA)
Description
Die Erfindung betrifft eine Anordnung zur Übertragung von Wärme, bestehend aus einem mit einem Wärmeträgermedium gefüllten Wärmerohr, in dem je ein Strömungskanal für das flüssige und für das in den dampfförmigen Aggregatzustand überführte Wärmeträgermedium vorhanden sind und bei dem ferner Mittel vorgesehen sind, um im Flüssigkeitskanal befindliche Blasen in den Dampfkanal zu befördern.The invention relates to an arrangement for the transfer of heat, consisting of a heat pipe filled with a heat transfer medium, in each of which there is a flow channel for the liquid and for the heat transfer medium converted to the vaporous state, and in which means are further provided for in the liquid channel To convey bubbles into the steam channel.
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, zum 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. In this case, a liquid, usually ammonia, is evaporated on the heat-emitting side and the steam is directed to the heat-emitting side. The steam condenses there, and the latent heat stored in it evaporates into the environment is discharged, and the resulting condensate flows back to the heat-absorbing side, to 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 Hochleistungswärmerohre 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 high-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 Hochleistungswärmerohr wird dadurch erzielt, daß für den Transport der Flüssigkeit Kanäle unterschiedlicher Abmessungen verwendet werden: Während im Verdampfungsbereich eine Vielzahl sehr kleiner 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 einen 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 wesentlich größerer Fluidmassenstrom und als dessen Folge ein ebenfalls wesentlich höherer Wärmestrom.This higher performance of the high-performance heat pipe compared to conventional heat pipes is achieved by using channels of different dimensions for the transport of the liquid: While a large number of very small channels with capillary geometries are used in the evaporation area to achieve large driving capillary forces, the flow is guided in the Condenser area and in the transport zone 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 Gasblasen 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 Ventildüse, die im Transportbereich für den Dampf angeordnet ist und die zugleich als Strahlpumpe über ein Ansaugrohr in der Arterie vorhandene Gasblasen absaugt.The heat pipe design handbook,
Nachteilig bei einer Anordnung von Entlüftungslöchern in der Arterienwand, wie sie, allerdings für ein konventionelles Axialrillenwärmerohr auch in der BE-A-903 187 beschrieben ist, 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, as described, however, for a conventional axial groove heat pipe in BE-A-903 187, is the fact that the pressure in the steam channel is significantly higher than in the artery during operation of the heat pipe is so that to transfer gas bubbles from the artery into an interruption of operation is required in the steam duct. 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 from the artery is constantly collected 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 aus dem Strömungskanal für das Fluid entfernt werden können und damit eine sichere Inbetriebnahme eines derartigen Rohres, entweder erstmalig oder nach einer beispielsweise durch Überlastung hervorgerufenen Betriebsunterbrechung, gewährleistet ist.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 quickly and easily from the flow channel for the fluid and thus safe commissioning of such a pipe, either for the first time or after an interruption in operation caused, for example, by overloading is guaranteed.
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 invention solves this problem by a heat pipe with the characterizing features of
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.
Dabei ist es aus den US 41 16 266 und US 41 70 262 in Verbindung mit Wärmerohren im Prinzip bereits bekannt, daß die Querschnitte der Flüssigkeitskanäle für den Rücktransport des Wärmeträgermediums, d.h. in Richtung auf den Verdampfer, kontinuierlich abnimmt. Die aus diesen Druckschriften bekannten Wärmerohre gehören jedoch nicht zu der eingangs definierten Gattung von Hochleistungswärmerohren, bei denen jeweils nur ein Strömungskanal für das flüssige und das in den dampfförmigen Aggregatzustand überführte Wärmeträgermediums vorhanden sind. Vielmehr handelt es sich bei diesen bekannten Wärmerohren um solche mit dochtartigen Strukturen, in denen eine Vielzahl feiner Kapillarröhren den Transport des Verdampferfluids bewirkt. Veränderliche Kappillarradien dienen dabei dem Zweck, durch eine Verminderung des Strömungswiderstandes die Transportleistung solcher Wärmerohre im normalen Betrieb, d.h. ohne dem Vorhandensein von Blasen, zu erhöhen.It is known in principle from US 41 16 266 and US 41 70 262 in connection with heat pipes that the cross sections of the liquid channels for the return transport of the heat transfer medium, i.e. towards the evaporator, continuously decreasing. However, the heat pipes known from these publications do not belong to the class of high-performance heat pipes defined at the outset, in which only one flow channel is present for the liquid and the heat transfer medium converted into the vaporous state. Rather, these known heat pipes are those with wick-like structures, in which a large number of fine capillary tubes effect the transport of the evaporator fluid. Variable capillary radii serve the purpose of reducing the flow resistance of the transport performance of such heat pipes in normal operation, i.e. without the presence of bubbles.
Die in weiterer Ausgestaltung der Erfindung vorgesehene ansteuerbare Absperrvorrichtung ermöglicht es, den für das Entfernen von Dampfblasen durchzuführenden Vorgang durch einen kurzzeitigen Öffnungsvorgang des verdampferseitigen Endes entweder manuell anzusteuern oder aber diesen voll automatisch zu initiieren, um so die Entlüftung erheblich zu beschleunigen. Die zur Öffnung erforderliche Betätigungskraft kann dabei auf besonders vorteilhafte Weise thermostatisch, elektromagnetisch oder aber durch die Verwendung eines Stellgliedes aus einer sogenannten Gedächtnislegierung ("shape memory alloy"), wie z. B. Nickel-Titan, erzeugt werden.The controllable shut-off device provided in a further embodiment of the invention makes it possible for the the removal of steam bubbles to be carried out by briefly opening the end of the evaporator either to be controlled manually or to initiate it fully automatically in order to significantly accelerate the venting. The actuating force required for opening can in a particularly advantageous manner thermostatically, electromagnetically or by using an actuator made of a so-called memory alloy ("shape memory alloy"), such as. B. nickel-titanium.
Im folgenden soll die Erfindung anhand von Ausführungsbeispielen näher erläutert werden. Es zeigen:
- Fig. 1 und 2
- je einen Längsschnitt durch einen Teil eines Hochleistungswärmerohres,
- Fig. 3
- einen Schnitt gemäß III-III durch die in Fig. 2 dargestellte Anordnung und
- Fig. 4
- eine Ausführungsform im Längsschnitt durch das verdampferseitige Ende des in Fig. 2 dargestellte Wärmerohres.
- 1 and 2
- a longitudinal section through part of a high-performance heat pipe,
- Fig. 3
- a section along III-III through the arrangement shown in Fig. 2 and
- Fig. 4
- an embodiment in longitudinal section through the evaporator end of the heat pipe shown in Fig. 2.
Der in Fig. 1 dargestellte Schnitt zeigt im mittleren Bereich die Transportzone eines Hochleistungswärmerohres, an die sich im linken Teil der Zeichnung die Verdampferzone, im rechten Teil die Kondensatorzone anschließt. Die Transportzone besteht aus einem Strömungskanal 1 für das verdampfte Wärmeträgermedium sowie, im Bild darunter liegend angeordnet, einem zweiten Strömungskanal 2, der Arterie, in dem das am Kondensatorende wieder verflüssigte Wärmeträgermedium zum Verdampferende zurückfließt. Der Flüssigkeitskanal 2 ist so gestaltet, daß sein für die Ausbildung von Gas- oder Dampfblasen relevanter kapillarer Radius, vom Verdampferende ausgehend, ständig zunimmt und seinen größten Wert am Kondensatorende erreicht. Bei dem in Fig. 1 dargestellten Wärmerohr wird diese dadurch erreicht, daß die die beiden Strömungskanäle 1 und 2 trennende Wand 3 unter einem von Null verschiedenen Winkel zur Längsachse des Wärmerohres angeordnet ist. Im Bild erkennbar sind ferner die Grenzfläche 4 zwischen der flüssigen und der dampfförmigen Phase sowie eine in tangentialer Richtung umlaufende feine Kapillarstruktur 5 an der Innenwand des Wärmerohres. Auf eine Ausführungsform mit einer Vorrichtung 6 zum verdampferseitigen Abschluß des Wärmerohres zur Freigabe einer Durchtrittsöffnung zwischen dem Flüssigkeitskanal 2 und dem Dampfkanal 1 wird im Zusammenhang mit den Erläuterungen zur Fig. 4 näher eingegangen.The section shown in FIG. 1 shows the transport zone of a high-performance heat pipe in the central area, to which the evaporator zone is connected in the left part of the drawing and the condenser zone in the right part. The transport zone consists of a
Zunächst ist in den Figuren 2 und 3 ein zweites Wärmerohr dargestellt, das sich von dem vorangehend beschriebenen dadurch unterscheidet, daß in diesem Fall die den Dampfkanal 11 vom Flüssigkeitskanal 12 trennende Wand 13 parallel zur Längsachse des Wärmerohres verläuft und daß in diesem Fall die konische Verjüngung des kapillaren Querschnitts des Flüssigkeitskanals 12 in Richtung auf das Verdampferende durch ein an der Trennwand 13 angeordnetes, in den Flüssigkeitskanal 12 ragendes keilförmiges Blech 17 erreicht wird. Die Keilhöhe und damit die Querschnittsfläche dieses Bleches 17 nimmt in Richtung auf das Verdampferende kontinuierlich zu. Im Bild zu erkennen sind ferner wieder die Grenzfläche 14 Flüssigkeit/Dampf sowie die Kapillarstruktur 15.First of all, a second heat pipe is shown in FIGS. 2 and 3, which differs from the one described above in that in this case the
Fig. 4 zeigt ein Ausführungsbeispiel einer vorteilhaften Absperrvorrichtung 16 nach Art eines elektromagnetischen Ventils. Die Absperrvorrichtung 16 ist dabei identisch aufgebaut wie die Absperrvorrichtung 6 der in Fig. 1 gezeigten Anordnung. Sie besteht aus einem Stempel 21, der auf einem Schaft 22 gehaltert ist, welcher wiederum als Anker für einen Elektromagneten ausgebildet ist. Letzterer wird von einer zylindrischen stromdurchflossenen Spule 23 gebildet, die in einem separaten Gehäuse 24 einen zylindrischen Ansatz 25 des Wärmerohres umgibt, wobei dieser Ansatz 25 einen geringeren Durchmesser als das eigentliche Wärmerohr aufweist und zugleich als Führung für den Schaft 22 dient. Zwischen dem Schaft 22 und dem stirnseitigen Abschluß des Ansatzes 25 ist eine Druckfeder 26 angeordnet, die die Dichtfläche des Stempels 21 gegen das verdampferseitige Ende der Wand 13 sowie des keilförmigen Bleches 17 preßt.Fig. 4 shows an embodiment of an advantageous shut-off
Vor der ersten Inbetriebnahme des Wärmerohres oder nach einem Ausfall infolge Überlastung wird bei einer Anordnung mit einer Absperrvorrichtung der Stempel 21 für kurze Zeit von der Wand 13 weggezogen und damit eine Öffnung zwischen dem Flüssigkeitskanal 12 und dem Dampfkanal 11 geschaffen. Dampf- bzw. Gasblasen die sich zu diesem Zeitpunkt am verdampferseitigen Ende des Flüssigkeitskanals 12 angesammelt haben, können durch diese Öffnung rasch in den Dampfkanal 11 entweichen. Dadurch füllt sich der Flüssigkeitskanal 12 wieder bis zur Kapillarstruktur 15 hin vollständig mit dem flüssigen Wärmeträgermedium, wodurch die Voraussetzung für die Inbetriebnahme des Wärmerohres gegeben ist. Das Wärmeträgermedium gelangt über die an der Innenwand des Rohres im Verdampferbereich befindlichen Kapillaren in den Dampfkanal 11, wo es unter Aufnahme der abzuführenden Wärme verdampft.Before the heat pipe is put into operation for the first time or after a failure due to overloading, in an arrangement with a shut-off device, the
Der kurzzeitige Öffnungsvorgang wird dadurch kontrolliert, daß die Spule 23 über Anschlußleitungen 27 von einem Strompuls durchflossen wird und dadurch den Schaft 22 gegen die Kraft der Druckfeder 26 in den Ansatz 25 hereinzieht. Es ist im Rahmen der Erfindung aber auch möglich, anstelle eines solchen elektromagnetischen Ventils eine thermostatisch kontrollierte Absperrvorrichtung vorzusehen, die von einer Aufheizeinrichtung sowie einem Stellglied gebildet wird, dessen temperaturabhängige Dehnung in eine Bewegung des die Durchtrittsöffnung verschließenden Stempels umgesetzt wird. Schließlich ist als Stellglied auch ein Element aus einer Formgedächtnislegierung, zum Beispiel Nickel-Titan, geeignet.The brief opening process is controlled in that a current pulse flows through the
Claims (8)
- Arrangement for the transfer of heat, comprising a heat pipe, which is filled with a heat transfer medium and in which there is a flow channel for the liquid heat transfer medium and a flow channel for the heat transfer medium converted into the vapour condition of aggregation and in which moreover means are provided for conveying bubbles situated in the liquid channel into the vapour channel, characterized in that the liquid channel (2, 12) has a cross-sectional area which increases continuously in the direction of the condenser end.
- Arrangement according to claim 1, characterized in that a wall (3) separating the liquid channel (2) from the vapour channel (1) extends obliquely relative to the longitudinal axis of the pipe.
- Arrangement according to claim 1 or 2, characterized in that provided on the wall (13) is a projection (17), which protrudes into the interior of the liquid channel (12) and extends in a longitudinal direction of the pipe and whose cross-sectional area decreases in the direction of the condenser end.
- Arrangement according to one of claims 1 to 3, characterized in that a through opening between the liquid channel (2, 12) and the vapour channel (1, 11) is provided at the evaporator end of the heat pipe, which through opening is closable by means of an externally controllable shut-off device (6, 16).
- Arrangement according to claim 4, characterized in that the shut-off device (6, 16) takes the form of an electromagnetically operated valve.
- Arrangement according to claim 4, characterized in that the shut-off device comprises an electric heating device and a temperature-dependently deformable actuator.
- Arrangement according to claim 4, characterized in that the shut-off device comprises an actuator made of a shape memory alloy.
- Arrangement according to one of claims 5 to 7, characterized in that the shut-off device (6, 16) is automatically controllable.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4222340 | 1992-07-08 | ||
| DE4222340A DE4222340C2 (en) | 1992-07-08 | 1992-07-08 | Heat pipe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0577969A1 EP0577969A1 (en) | 1994-01-12 |
| EP0577969B1 true EP0577969B1 (en) | 1995-11-29 |
Family
ID=6462708
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP93108818A Expired - Lifetime EP0577969B1 (en) | 1992-07-08 | 1993-06-02 | Heat-pipe |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US5360058A (en) |
| EP (1) | EP0577969B1 (en) |
| DE (2) | DE4222340C2 (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6167948B1 (en) | 1996-11-18 | 2001-01-02 | Novel Concepts, Inc. | Thin, planar heat spreader |
| RU2224967C2 (en) | 2001-08-09 | 2004-02-27 | Сидоренко Борис Револьдович | Evaporative chamber of contour heating pipe |
| WO2004046632A1 (en) * | 2002-11-16 | 2004-06-03 | Karl Heinz Gast | Storage heat exchanger, related operating methods and use |
| US7420810B2 (en) * | 2006-09-12 | 2008-09-02 | Graftech International Holdings, Inc. | Base heat spreader with fins |
| US8919427B2 (en) * | 2008-04-21 | 2014-12-30 | Chaun-Choung Technology Corp. | Long-acting heat pipe and corresponding manufacturing method |
| US9163883B2 (en) | 2009-03-06 | 2015-10-20 | Kevlin Thermal Technologies, Inc. | Flexible thermal ground plane and manufacturing the same |
| TWI494051B (en) * | 2012-11-19 | 2015-07-21 | Acer Inc | Fluid heat exchange apparatus |
| US9315280B2 (en) * | 2012-11-20 | 2016-04-19 | Lockheed Martin Corporation | Heat pipe with axial wick |
| CN103853297B (en) * | 2012-12-04 | 2017-06-20 | 宏碁股份有限公司 | Flow heat exchanger |
| US11026343B1 (en) | 2013-06-20 | 2021-06-01 | Flextronics Ap, Llc | Thermodynamic heat exchanger |
| WO2015014387A1 (en) * | 2013-07-29 | 2015-02-05 | Francois-Mathieu Winandy | Water desalination methods and facilities using mechanical vapour compression distillation |
| US11598594B2 (en) | 2014-09-17 | 2023-03-07 | The Regents Of The University Of Colorado | Micropillar-enabled thermal ground plane |
| US11988453B2 (en) | 2014-09-17 | 2024-05-21 | Kelvin Thermal Technologies, Inc. | Thermal management planes |
| US12104856B2 (en) | 2016-10-19 | 2024-10-01 | Kelvin Thermal Technologies, Inc. | Method and device for optimization of vapor transport in a thermal ground plane using void space in mobile systems |
| WO2018208801A1 (en) * | 2017-05-08 | 2018-11-15 | Kelvin Thermal Technologies, Inc. | Thermal management planes |
| US20200404805A1 (en) * | 2019-06-19 | 2020-12-24 | Baidu Usa Llc | Enhanced cooling device |
| WO2021258028A1 (en) | 2020-06-19 | 2021-12-23 | Kelvin Thermal Technologies, Inc. | Folding thermal ground plane |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3537514A (en) * | 1969-03-12 | 1970-11-03 | Teledyne Inc | Heat pipe for low thermal conductivity working fluids |
| US3865184A (en) * | 1971-02-08 | 1975-02-11 | Q Dot Corp | Heat pipe and method and apparatus for fabricating same |
| US4116266A (en) * | 1974-08-02 | 1978-09-26 | Agency Of Industrial Science & Technology | Apparatus for heat transfer |
| US4170262A (en) * | 1975-05-27 | 1979-10-09 | Trw Inc. | Graded pore size heat pipe wick |
| JPS57196089A (en) * | 1981-05-29 | 1982-12-01 | Hitachi Ltd | Heat pipe |
| US4422501A (en) * | 1982-01-22 | 1983-12-27 | The Boeing Company | External artery heat pipe |
| JPS5963492A (en) * | 1982-09-30 | 1984-04-11 | Sanyo Electric Co Ltd | Heat pipe |
| BE903187A (en) * | 1985-09-05 | 1986-03-05 | Belge Const Aeronautiques | Hermetically sealed tube capillary - has sheet defining permeable partitions with heat exchange surface |
-
1992
- 1992-07-08 DE DE4222340A patent/DE4222340C2/en not_active Expired - Fee Related
-
1993
- 1993-06-02 EP EP93108818A patent/EP0577969B1/en not_active Expired - Lifetime
- 1993-06-02 DE DE59301042T patent/DE59301042D1/en not_active Expired - Fee Related
- 1993-07-08 US US08/090,334 patent/US5360058A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| US5360058A (en) | 1994-11-01 |
| DE4222340A1 (en) | 1994-01-13 |
| EP0577969A1 (en) | 1994-01-12 |
| DE59301042D1 (en) | 1996-01-11 |
| DE4222340C2 (en) | 1996-07-04 |
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