EP0600191B1 - Heat pipe - Google Patents
Heat pipe Download PDFInfo
- Publication number
- EP0600191B1 EP0600191B1 EP93116291A EP93116291A EP0600191B1 EP 0600191 B1 EP0600191 B1 EP 0600191B1 EP 93116291 A EP93116291 A EP 93116291A EP 93116291 A EP93116291 A EP 93116291A EP 0600191 B1 EP0600191 B1 EP 0600191B1
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- European Patent Office
- Prior art keywords
- channel
- liquid
- flow
- heat
- heat pipe
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- 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.)
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- 239000007788 liquid Substances 0.000 claims description 29
- 239000007791 liquid phase Substances 0.000 claims description 2
- 230000002776 aggregation Effects 0.000 claims 1
- 238000004220 aggregation Methods 0.000 claims 1
- 239000012071 phase Substances 0.000 claims 1
- 210000001367 artery Anatomy 0.000 description 12
- 239000012530 fluid Substances 0.000 description 4
- 239000013529 heat transfer fluid Substances 0.000 description 4
- 238000009423 ventilation Methods 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- 230000006735 deficit Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000001771 impaired effect Effects 0.000 description 2
- 229910021529 ammonia Inorganic materials 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
- 238000000605 extraction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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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
- F28D15/025—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 having non-capillary condensate return means
Definitions
- the invention relates to an arrangement for the transfer of heat, consisting of a heat pipe filled with a heat transfer medium, in which at least one flow channel each is provided for the liquid heat transfer medium and for the heat transfer medium converted to the vaporous state, and in which means are provided in the liquid channel to in remove any gas or vapor bubbles from the liquid.
- 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 becomes heat-emitting Side headed.
- the steam condenses, the latent heat stored in it being dissipated to the environment, and the condensate produced flows back to the heat-absorbing side, the end of 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 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 frictional pressure loss is minimized, and with the same capillary forces, there is a substantially larger fluid mass flow 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 arterial wall is the fact that the pressure in the steam channel during the operation of the heat pipe 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 are reliably removed from the flow channel for the fluid during operation of the heat pipe, without this requiring an interruption in operation and without the performance of the heat pipe is significantly impaired.
- the heat pipe according to the invention makes use of a property of a two-phase flow consisting of a liquid and gas bubbles contained therein, which has become known from DE 38 26 919 C 1 in connection with a fuel storage device: If this flow is divided into two partial flows, one of which maintains the original direction, but the second is deflected, all gas bubbles flow with the diverted partial flow, while the partial flow flowing in the original direction is bubble-free.
- a completely automatic extraction of existing gas or vapor bubbles is achieved without an interruption in operation being required for this.
- the loss of performance resulting from the arrangement of one or more such bubble traps in the artery is significantly lower than in the known arrangements.
- FIG. 1 shows a part of the transport zone of a heat pipe located between the evaporator and the condenser area.
- the heat pipe is divided by a profiled sheet 1 into two channels 2 and 3, of which the upper channel 2 in the drawing, the steam channel, has the larger cross-sectional area.
- the lower channel 3 forms the liquid channel for the thermal fluid flowing back from the condenser area to the evaporator area.
- an aperture 4 is arranged, which takes up part of the cross-sectional area of this channel 3.
- a cage 5 is arranged in the downstream direction, which consists of a wire mesh.
- the aperture 4 in the embodiment described here consists of a multi-layer wire mesh.
- the direction of flow of the liquid medium is indicated by arrows in FIG. 1.
- the total flow of this medium is divided into two partial flows, one of which continues to flow unhindered in its original direction of flow, while the other is sharply deflected behind the orifice 4 and thereby reaches the cage 5.
- This second sub-stream also contains practically all steam or Gas bubbles 6 contained in the incoming liquid. This phenomenon can be explained by the fact that the liquid, as the component with the greater mass inertia, has a greater desire to maintain the original direction of flow, while the considerably lighter bubbles 6 follow the deflected liquid flow due to their lower inertia.
- Bubble traps of this type can be installed at several points in the artery 3. If, for example, the heat pipe consists of several - possibly welded - partial elements, it is advantageous to arrange them at the beginning of each partial element. In addition, such a bubble trap at the inlet of the evaporator has also proven to be advantageous.
- the cage is integrated into the inner structure of the heat pipe.
- an extruded profile 11 is used in the heat pipe shown in cross section in FIG. 2, which has two channels 12 and 13 for the transport of vaporous heat transfer medium as well as two channels 14 for the liquid phase and creates 15.
- two areas 18 and 19 are additionally separated by two web-like projections 16 and 17 of the extruded profile 11, which serve as so-called auxiliary arteries and whose function will not be discussed in more detail here.
- the cage 20 which in the case of the exemplary embodiment described here forms, as it were, a separate subspace which extends over the entire area of the transport zone and into the evaporator zone, in front of which there is one in the upstream direction is arranged in the figure, not shown.
- the dimensions of this diaphragm correspond approximately to the cross section of the portion of the liquid channel formed by the cage 20.
- those parts of the extruded profile 11 which separate the vapor space from the liquid space from the cage 20 are perforated.
- the dividing walls between the vapor and the liquid space are provided with narrow slots 21, which are used for connection to circumferential grooves, not shown in the figure.
- the vapor or gas bubbles contained in the liquid collect in the Cage 20, so that the cross sections of the channels 14 and 15 above contain a practically bubble-free liquid flow.
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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)
- External Artificial Organs (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
Die Erfindung betrifft eine Anordnung zur Übertragung von Wärme, bestehend aus einem mit einem Wärmeträgermedium gefüllten Wärmerohr, in dem wenigstens je ein Strömungskanal für das flüssige und für das in den dampfförmigen Aggregatzustand überführte Wärmeträgermedium vorgesehen sind und bei dem im Flüssigkeitskanal Mittel vorgesehen sind, um in der Flüssigkeit befindliche Gas- oder Dampfblasen aus dieser zu entfernen.The invention relates to an arrangement for the transfer of heat, consisting of a heat pipe filled with a heat transfer medium, in which at least one flow channel each is provided for the liquid heat transfer medium and for the heat transfer medium converted to the vaporous state, and in which means are provided in the liquid channel to in remove any gas or vapor bubbles from the liquid.
Wärmerohre oder "heat pipes" für den Transport von Wärme sind insbesondere aus dem Bereich der Raumfahrttechnik bereits bekannt. Bei diesen 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 Verdampferende, zurück. Die dabei auftretende Dampfströmung ist eine übliche 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 these, a liquid, usually ammonia, is evaporated on the heat-emitting side and the steam becomes heat-emitting Side headed. There, the steam condenses, the latent heat stored in it being dissipated to the environment, and the condensate produced flows back to the heat-absorbing side, the end of 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 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 frictional pressure loss is minimized, and with the same capillary forces, there is a substantially larger fluid mass flow 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 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 Venturi-düse, 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 described in which measures for removing bubbles and thus preventing blockages by glass bubbles are described 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 is also present as a jet pump via an intake pipe in the artery Sucks off gas bubbles.
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 arterial wall is the fact that the pressure in the steam channel during the operation of the heat pipe 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 während des Betriebes des Wärmerohres zuverlässig aus dem Strömungskanal für das Fluid entfernt werden, ohne daß hierzu eine Betriebsunterbrechung erforderlich ist und ohne daß die Leistungsfähigkeit des Wärmerohres wesentlich beeinträchtigt wird.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 are reliably removed from the flow channel for the fluid during operation of the heat pipe, without this requiring an interruption in operation and without the performance of the heat pipe is significantly impaired.
Die Erfindung löst diese Aufgabe durch ein Wärmerohr mit den kennzeichnenden Merkmalen des Patentanspruchs 1.The invention solves this problem by means of a heat pipe with the characterizing features of patent claim 1.
Vorteilhafte Weiterbildungen, die eine optimale Ausgestaltung des erfindungsgemäßen Wärmerohres im Hinblick auf eine möglichst geringere Beeinträchtigung der maximal erzielbaren Wärmetransportleistung bei gleichzeitig hoher Ausfallsicherheit und Fehlertoleranz zum Ziel haben, sind in den weiteren Ansprüche angegeben.Advantageous further developments, which aim at an optimal configuration of the heat pipe according to the invention with regard to the least possible impairment of the maximum achievable heat transport performance with high reliability and fault tolerance, are specified in the further claims.
Das Wärmerohr nach der Erfindung macht dabei Gebrauch von einer Eigenschaft einer aus einer Flüssigkeit und darin enthaltenen Gasblasen bestehenden Zweiphasenströmung, die aus der DE 38 26 919 C 1 in Zusammenhang mit einer Treibstoff-Bevorratungsvorrichtung bekannt geworden ist: Wird diese Strömung in zwei Teilströme aufgeteilt, von denen der eine die ursprüngliche Richtung beibehält, der zweite jedoch umgelenkt wird, so fließen alle Gasblasen mit dem umgelenkten Teilstrom, während der in der ursprünglichen Richtung weiterfließende Teilstrom blasenfrei ist. Somit wird bei dem Wärmerohr nach der Erfindung eine völlig selbsttätige Absaugung vorhandener Gas- oder Dampfblasen erreicht, ohne daß hierfür eine Betriebsunterbrechung erforderlich ist. Zugleich ist die Leistungseinbuße, die aus der Anordnung einer oder mehrerer derartiger Blasenfallen in der Arterie resultiert, wesentlich geringer als bei den bekannten Anordnungen.The heat pipe according to the invention makes use of a property of a two-phase flow consisting of a liquid and gas bubbles contained therein, which has become known from DE 38 26 919 C 1 in connection with a fuel storage device: If this flow is divided into two partial flows, one of which maintains the original direction, but the second is deflected, all gas bubbles flow with the diverted partial flow, while the partial flow flowing in the original direction is bubble-free. Thus, in the heat pipe according to the invention, a completely automatic extraction of existing gas or vapor bubbles is achieved without an interruption in operation being required for this. At the same time, the loss of performance resulting from the arrangement of one or more such bubble traps in the artery is significantly lower than in the known arrangements.
Im folgenden soll die Erfindung anhand eines in der Zeichnung dargestellten Ausführungsbeispiels näher erläutert werden. Es zeigen:
- Fig. 1
- einen Längsschnitt durch ein erstes Wärmerohr,
- Fig. 2
- ein zweites Wärmerohr im Querschnitt und
- Fig. 3
- eine perspektivische Darstellung der inneren Struktur der in Fig. 2 gezeigten Anordnung.
- Fig. 1
- a longitudinal section through a first heat pipe,
- Fig. 2
- a second heat pipe in cross section and
- Fig. 3
- a perspective view of the inner structure of the arrangement shown in Fig. 2.
Die Darstellung in Fig. 1 gibt einen Teil der zwischen dem Verdampfer- und den Kondensatorbereich befindlichen Transportzone eines Wärmerohres wieder. Das Wärmerohr ist durch ein Profilblech 1 in zwei Kanäle 2 und 3 unterteilt, von denen der in der Zeichnung obere Kanal 2, der Dampfkanal, die größere Querschnittsfläche aufweist. Der untere Kanal 3 bildet den Flüssigkeitskanal für das vom Kondensatorbereich zum Verdampferbereich zurückströmende Wärmefluid.The illustration in FIG. 1 shows a part of the transport zone of a heat pipe located between the evaporator and the condenser area. The heat pipe is divided by a profiled sheet 1 into two
Im Flüssigkeitskanal 3, der sogenannten Arterie, ist eine Blende 4 angeordnet, die einen Teil der Querschnittsfläche dieses Kanals 3 einnimmt. Mit einem geringen Abstand hinter der Blende 4 ist in stromabwärtiger Richtung ein Käfig 5 angeordnet, der aus einem Drahtgeflecht besteht. Die Blende 4 besteht bei dem hier beschriebenen Ausführungsbeispiel aus einem mehrlagigen Drahtgewebe.In the
Die Strömungsrichtung des flüssigen Mediums ist in Fig. 1 durch Pfeile gekennzeichnet. An der Blende 4 wird der Gesamtstrom dieses Mediums in zwei Teilströme aufgeteilt, von denen der eine ungehindert in seiner ursprünglichen Strömungsrichtung weiterfließt, während der andere hinter der Blende 4 scharf umgelenkt wird und dadurch in den Käfig 5 gelangt. Dieser zweite Teilstrom enthält auch praktisch alle Dampf- oder Gasblasen 6, die in der anströmenden Flüssigkeit enthalten sind. Erklärbar ist dieses Phänomen durch die Tatsache, daß die Flüssigkeit als die Komponente mit der größeren Massenträgheit das stärkere Bestreben hat, die ursprüngliche Strömungsrichtung beizubehalten, während die erheblich leichteren Blasen 6 aufgrund ihrer geringeren Trägheit dem umgelenkten Flüssigkeitsstrom folgen.The direction of flow of the liquid medium is indicated by arrows in FIG. 1. At the orifice 4, the total flow of this medium is divided into two partial flows, one of which continues to flow unhindered in its original direction of flow, while the other is sharply deflected behind the orifice 4 and thereby reaches the cage 5. This second sub-stream also contains practically all steam or
Die mit der Flüssigkeitsströmung in den Käfig 5 beförderten Blasen 6 werden dort festgehalten, da aufgrund der höheren Oberflächenspannung die Poren des Käfigs 5 für das Gas nicht durchlässig sind, wohl aber für die im stromabwärtigen Bereich des Käfigs 6 wieder aus diesem ausströmende Flüssigkeit. Derartige Blasenfallen können an mehreren Stellen der Arterie 3 eingebaut werden. Sofern das Wärmerohr beispielsweise aus mehreren - gegebenenfalls zusammengeschweißten - Teilelementen besteht, ist es vorteilhaft, sie am Beginn jedes Teilelementes anzuordnen. Zusätzlich hat sich eine solche Blasenfalle auch am Eingang des Verdampfers als vorteilhaft erwiesen.The
Die Verwendung derartiger, aus einer Blende 4 und einem stromabwärts hinter dieser angeordneten Käfig 5, bestehenden Blasenfallen hat vor allem den Vorteil, daß die kontinuierliche Flüssigkeitsströmung zwischen den Kondensator und dem Verdampfer erhalten bleibt. Die im Käfig 5 gefangenen Blasen 6 können sich zwar am stromabwärtigen Ende dieses Käfigs 5 zu einer großen Blase 7 vereinigen, jedoch können diese, wegen der Form des Käfigs 5, nicht so groß werden, daß sie den gesamten Querschnitt des Flüssigkeitskanals 3 blockieren.The use of such bubble traps consisting of an orifice 4 and a cage 5 arranged downstream behind it has the particular advantage that the continuous liquid flow between the condenser and the evaporator is maintained. The
Bei dem in den Figuren 2 und 3 dargestellten Wärmerohr ist der Käfig in die Innenstruktur des Wärmerohres integriert. Statt eines einfachen Profilblechs, wie im Fall des vorangehend beschriebenen Ausführungsbeispiels, ist bei dem in Fig. 2 im Querschnitt gezeigten Wärmerohr ein Strangpreßprofil 11 eingesetzt, das sowohl für den Transport dampfförmigen Wärmeträgermediums zwei Kanäle 12 und 13 als auch für die flüssige Phase zwei Kanäle 14 und 15 schafft. Innerhalb der Kanäle 14 und 15 werden durch zwei stegartige Ansätze 16 und 17 des Strangpreßprofils 11 zusätzlich zwei Bereiche 18 und 19 abgetrennt, die als sogenannte Hilfsarterien dienen und auf deren Funktion hier nicht näher eingegangen werden soll. Im unteren, gemeinsamen Teil der Kanäle 14 und 15 befindet sich der Käfig 20, der im Fall des hier beschriebenen Ausführungsbeispiels gleichsam einen separaten, sich über den gesamten Bereich der Transportzone bis in die Verdampferzone hinein sich erstreckenden Teilraum bildet, vor dem in stromaufwärtiger Richtung eine in der Figur nicht dargestellte Blende angeordnet ist. Die Abmessungen dieser Blende entsprechen dabei in etwa dem Querschnitt des vom Käfig 20 gebildeten Teilbereiches des Flüssigkeitskanals.In the heat pipe shown in Figures 2 and 3, the cage is integrated into the inner structure of the heat pipe. Instead of a simple profiled sheet, as in the case of the exemplary embodiment described above, an
Wie insbesondere die Fig. 3 zeigt, sind diejenigen Teile des Strangpreßprofils 11, die den Dampf- vom Flüssigkeitsraum von diesem wiederum den Käfig 20 trennen, jeweils perforiert ausgebildet. Zusätzlich sind in dem in Fig. 3 im Vordergrund dargestellten Verdampferbereich die Trennwände zwischen dem Dampf- und dem Flüssigkeitsraum mit schmalen Schlitzen 21 versehen, die der Verbindung mit in der Figur nicht dargestellten Umfangsrillen dienen. Auch bei dem hier beschriebenen Ausführungsbeispiel sammeln sich die in der Flüssigkeit enthaltenen Dampf- bzw. Gasblasen im Käfig 20, so daß die darüber befindlichen Querschnitte der Kanäle 14 und 15 eine praktisch blasenfreie Flüssigkeitsströmung enthalten.As shown in FIG. 3 in particular, those parts of the
Claims (5)
- Arrangement for transferring heat, consisting of a heat pipe, 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, in addition, there are provided means for conveying bubbles present in the liquid channel into the vapour channel, characterized in that the means consist of at least one screen (4), within the liquid channel (3,14,15) and filling a portion of the flow cross-section of this channel, behind which, in the downstream direction, cage-type partial regions (5,20) of the liquid channel (3,14,15) are separated by separating elements which are permeable only to the liquid phase, and not to the gaseous or vaporous phase.
- Arrangement according to Claim 1, characterized in that the partial regions (5) are fashioned as cages whose walls are formed by a wire mesh.
- Arrangement according to Claim 2, characterized in that several successive cages (5) are disposed at intervals within the liquid channel (3).
- Arrangement according to Claim 1, characterized in that the partial regions (20) are bounded by a perforated profile plate running in the longitudinal direction of the pipe.
- Arrangement according to any one of Claims 1 to 4, characterized in that the screen (4) consists of at least one layer of a wire mesh.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4240082 | 1992-11-28 | ||
DE4240082A DE4240082C1 (en) | 1992-11-28 | 1992-11-28 | Heat pipe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0600191A1 EP0600191A1 (en) | 1994-06-08 |
EP0600191B1 true EP0600191B1 (en) | 1996-04-24 |
Family
ID=6473915
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP93116291A Expired - Lifetime EP0600191B1 (en) | 1992-11-28 | 1993-10-08 | Heat pipe |
Country Status (3)
Country | Link |
---|---|
US (1) | US5346000A (en) |
EP (1) | EP0600191B1 (en) |
DE (2) | DE4240082C1 (en) |
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-
1992
- 1992-11-28 DE DE4240082A patent/DE4240082C1/en not_active Expired - Fee Related
-
1993
- 1993-10-08 EP EP93116291A patent/EP0600191B1/en not_active Expired - Lifetime
- 1993-10-08 DE DE59302366T patent/DE59302366D1/en not_active Expired - Fee Related
- 1993-11-29 US US08/158,411 patent/US5346000A/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE4240082C1 (en) | 1994-04-21 |
US5346000A (en) | 1994-09-13 |
EP0600191A1 (en) | 1994-06-08 |
DE59302366D1 (en) | 1996-05-30 |
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