EP0061779A2 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- EP0061779A2 EP0061779A2 EP82102715A EP82102715A EP0061779A2 EP 0061779 A2 EP0061779 A2 EP 0061779A2 EP 82102715 A EP82102715 A EP 82102715A EP 82102715 A EP82102715 A EP 82102715A EP 0061779 A2 EP0061779 A2 EP 0061779A2
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- European Patent Office
- Prior art keywords
- tubes
- heat exchanger
- exchanger according
- another
- solder
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
- F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D53/00—Making other particular articles
- B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
- B21D53/027—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers by helically or spirally winding elongated elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
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- 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
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
- F28F1/045—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular with assemblies of stacked elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/14—Fastening; Joining by using form fitting connection, e.g. with tongue and groove
Definitions
- the invention relates to a heat exchanger in which the fluids participating in the heat exchange are guided in a single tube in cocurrent or countercurrent.
- the surface sections through which heat is transferred from one fluid to the other should be dimensioned as large as possible in a heat exchanger.
- this requirement means that the larger the total heat exchange surface, the larger the space occupied by the respective heat exchanger.
- the fluids in a heat exchanger are usually guided in elongated components, for example pipes, such heat exchangers not only require a large amount of space, but also e.g. cylindrical shape, which means a disproportionately large space requirement, especially in small systems.
- coaxial condensers and evaporators have coaxial tubes, which are arranged helically or helically. To produce these heat exchangers, a first tube is pushed into a second so that there is a coaxial arrangement and then these tubes are bent into a spiral.
- the disadvantage of this design is that the inner tube with its outer jacket comes to rest on the inner jacket of the outer tube, which has the consequence that there is a severe impairment of the heat transfer from one fluid to the other at the linear contact point of the two tubes.
- the invention seeks to remedy this.
- the invention as characterized in the claims, solves the problem of creating a heat exchanger in which the fluids participating in the heat exchange are each guided in a single tube, in which the respective tubes lie flat against one another along their entire length.
- the advantages achieved by the invention are essentially to be seen in the fact that the heat exchanger takes up a small space for a given flow volume and given total heat exchange surface, and that the shape of the heat exchanger can be easily adapted to predetermined spatial conditions.
- the heat exchanger according to FIG. 1 has a first tube 1 and a second tube 2.
- the first tube 1 has an inlet or outlet 3 and an outlet or inlet 5.
- the second tube 2 has an inlet or outlet 4 and an outlet or inlet 6.
- the fluids flowing through this heat exchanger obviously flow in cocurrent or countercurrent, depending on the respective technical circumstances.
- the two tubes 1, 2 are close together and are spirally laid in turns. The spiral described by the pipes, i.e. the two spirals, on a flat surface. Because this form of training can be regarded as practically two-dimensional, because the third dimension depends only on the tube thickness, this heat exchanger takes up a relatively small space.
- the tubes do not have a circular cross-sectional shape. Accordingly, an embodiment with tubes of square cross-sectional shape is shown in FIG. 2. These tubes, which are arranged in the spiral shape mentioned and have a square cross-sectional shape, abut one another with side walls. The tubes are soldered together to achieve good heat transfer. Correspondingly, a solder, a solder metal 7 is arranged between the side walls of the tubes. Obviously, the soldering also gives the heat exchanger the necessary mechanical strength.
- the manufacture of the heat exchanger is carried out as follows. First, the pipes 1, 2, in their original, rectilinear shape, are placed parallel next to each other. A ribbon-shaped solder, a ribbon-shaped solder metal, is inserted between these tubes in such a way that the arrangement shown in FIG. 2 is present, but only two tubes are present on average. The tubes and the solder are then connected to one another at points, for example at one end. The tubes 1, 2 with the solder 7 located between them are then laid in turns so that they assume the shape shown in FIG. 1. Thereafter, tubes with 1, 2 are fixed in the wound position with the solder 7 by at least one further punctiform connection. The entire arrangement is then immersed in an induction bath. The solder melts in it, so that the pipes 1, 2 are soldered along their entire longitudinal extent and the heat exchanger is thus produced.
- the tubes 1, 2 do not necessarily have to have the square cross-sectional shape shown in FIG. 2.
- 3 shows an embodiment in which the tubes are in a triangular cross-sectional shape, the solder 7 again being arranged between the abutting side walls of the tubes.
- This embodiment according to FIG. 3 is also a space-saving design.
- these walls are structured according to a further embodiment.
- Such a design is shown in FIG. 4.
- the cross-sectional area of the first tube 1 is different from the cross-sectional surface of the second tube 2.
- a vaporous fluid flows through the first pipe 1 and water flows through the second pipe 2, an application which is present, for example, in heat pump systems.
- Side walls of the pipes 1, 2 which abut one another have successive depressions 9 and projections 8. These tooth-like designs mesh with one another, so that the area dimension of the heat transfer areas is increased.
- the tubes are not soldered to one another here.
- the tubes 1, 2 again have the same cross-sectional area and are connected to one another again with a solder 7.
- the difference to the embodiment of FIG. 4 is that the two side walls of the pipes 1, 2 through which the heat transfer takes place have an increased areal area, the walls here being simply wave-shaped, the respective wave troughs and wave peaks engaging with one another.
- FIG. 6 A further embodiment of the heat exchanger is shown in FIG. 6. It has been said in the description of FIG. 1 that the spiral, ie the two Spirals, which are described by the tubes 1,2, lie on a flat surface. 6, the tubes are also deformed in such a way that they describe the envelope of a hollow circular cone.
- the advantage of this design is that there is a clear gradient in the pipes. A gradient is often necessary due to a given medium, for example if a medium enters in the gaseous state and is liquefied in the heat exchanger, and thus must have a gradient with respect to the horizontal.
- the envelope of the heat exchanger i.e. at least its projection onto a surface, not circular (it should be understood that here the envelope of the spiral is viewed as a circle for simplicity).
- the envelope curve can thus describe a rectangle, as in FIG. 6 or a hexagon as in FIG. 7, or any other polygon, polygon.
- the heat exchanger can now be designed in any spatial and planar form, such that it can be arranged in an entire system, for example a heat pump system, in such a way that it takes up the smallest amount of space.
- FIG. 9 shows an embodiment in which the tubes 1, 2 are arranged in the form of a hollow cylinder.
- This embodiment has the particular advantage that apparatus, e.g. Pumps and other units of a plant containing the heat exchanger, e.g. a heat pump system, can be arranged in the cylindrical cavity circumscribed by the pipes 1,2. Significant space savings are possible.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Die Erfindung betrifft einen Wärmetauscher, in welchem die am Wärmetausch teilnehmenden Fluide in jeweils einem einzigen Rohr im Gleich- oder Gegenstrom geführt sind.The invention relates to a heat exchanger in which the fluids participating in the heat exchange are guided in a single tube in cocurrent or countercurrent.
Um eine gute Wirksamkeit zu erreichen, sollten in einem Wärmetauscher die Flächenabschnitte, durch die hindurch die Wärmeübertragung von einem zum anderen Fluid stattfindet, so gross als möglich bemessen sein. Bei gegebenen Durchflussvolumen der am Wärmetausch teilnehmenden Fluide und bei gegebener struktureller Ausbildung der Rohre zwecks Erhöhung der wärmeübertragenden Fläche, beispielsweise Rippen, bedeutet diese Forderung, dass je grösser die gesamte Wärmetauschfläche ist desto grösser der vom jeweiligen Wärmetauscher eingenommene Raum ist. Da die Fluide in einem Wärmetauscher üblicherweise in langgestreckten Bauteilen, beispielsweise Rohren, geführt sind, weisen solche Wärmetauscher nicht nur einen grossen Raumbedarf auf, sondern eine z.B. zylindrische Form, welche insbesondere bei kleinen Anlagen einen unverhältnismässig grossen Raumbedarf bedeutet.In order to achieve good effectiveness, the surface sections through which heat is transferred from one fluid to the other should be dimensioned as large as possible in a heat exchanger. Given the given flow volume of the fluids participating in the heat exchange and given the structural design of the pipes in order to increase the heat transfer surface, for example fins, this requirement means that the larger the total heat exchange surface, the larger the space occupied by the respective heat exchanger. Since the fluids in a heat exchanger are usually guided in elongated components, for example pipes, such heat exchangers not only require a large amount of space, but also e.g. cylindrical shape, which means a disproportionately large space requirement, especially in small systems.
Um diesen Nachteil zu beheben, sind verschiedene Ausbildungen bekannt, die bei gegebener Wärmetauschfläche und gegebenem Durchflussvolumen einen verhältnismässig kleinen Raum beanspruchen. Beispielsweise sind sogenannte Koaxial-Kondensatoren und -Verdampfer bekannt. Diese weisen koaxial zueinander verlaufende Rohre auf, welche wendel- bzw. schraubenlinienförmig angeordnet sind. Zur Herstellung dieser Wärmetauscher wird ein erstes Rohr in ein zweites hineingeschoben, so dass eine koaxiale Anordnung vorliegt und danach werden diese Rohre zur Wendel gebogen. Der Nachteil dieser Ausbildung ist jedoch, dass das innere Rohr mit seinem Aussenmantel an den Innenmantel des äusseren Rohres zu liegen kommt, welches zur Folge hat, dass an der linienförmigen Berührungsstelle der zwei Rohre eine starke Beeinträchtigung des Wärmeüberganges von dem einen zum anderen Fluid stattfindet.In order to remedy this disadvantage, various designs are known which require a relatively small space for a given heat exchange surface and a given flow volume. For example, so-called coaxial condensers and evaporators are known. These have coaxial tubes, which are arranged helically or helically. To produce these heat exchangers, a first tube is pushed into a second so that there is a coaxial arrangement and then these tubes are bent into a spiral. The disadvantage of this design, however, is that the inner tube with its outer jacket comes to rest on the inner jacket of the outer tube, which has the consequence that there is a severe impairment of the heat transfer from one fluid to the other at the linear contact point of the two tubes.
Hier will die Erfindung Abhilfe schaffen. Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, löst die Aufgabe, einen Wärmetauscher zu schaffen, in welchem die am Wärmetausch teilnehmenden Fluide in jeweils einem einzigen Rohr geführt sind, bei dem die jeweiligen Rohre entlang ihrer gesamten Länge flächig aneinanderliegen.The invention seeks to remedy this. The invention, as characterized in the claims, solves the problem of creating a heat exchanger in which the fluids participating in the heat exchange are each guided in a single tube, in which the respective tubes lie flat against one another along their entire length.
Die durch die Erfindung erreichten Vorteile sind im wesentlichen darin zu sehen, dass der Wärmetauscher bei gegebenem Durchflussvolumen und gegebener, gesamten Wärmetauschfläche einen kleinen Raum einnimmt, und dass der Wärmetauscher formmässig an vorgegebene räumliche Bedingungen leicht angepasst werden kann.The advantages achieved by the invention are essentially to be seen in the fact that the heat exchanger takes up a small space for a given flow volume and given total heat exchange surface, and that the shape of the heat exchanger can be easily adapted to predetermined spatial conditions.
Bei einem Verfahren zum Herstellen eines solchen Wärmetauschers, bei welchem die Rohre entlang ihrer gesamten Länge miteinander verlötet sind, werden die jeweiligen Fluid führenden Rohre parallel zueinander verlaufendnebeneinander angeordnet, darauf zwischen.den nebeneinanderliegenden Rohren ein bandförmiges Lötmittel angeordnet, und nachfolgend die Rohre mit dem dazwischen gelegenen Lötmittel in Windungen gelegt und in dieser Form derart zusammengehalten, dass die Rohre und das Lötmittel aneinander anliegen und ausschliesslich werden nachfolgend die Rohre und das Lötmittel in ein Induktionsbad getaucht, um eine Verlötung der Rohre zu erzeugen.In a method for producing such a heat exchanger, in which the tubes are soldered to one another along their entire length, the respective fluid-carrying tubes are arranged parallel to one another, next to which a ribbon-shaped solder is arranged between the adjacent tubes, and subsequently the tubes with the in between placed solder in turns and held together in this form such that the tubes and the solder lie against each other and only then the tubes and the solder are immersed in an induction bath to produce a soldering of the tubes.
Im folgenden wird die Erfindung anhand von mehrere Ausführungswege darstellenden Zeichnungen näher erläutert. Es zeigt:
- Fig. 1 eine Aufsicht auf einen Wärmetauscher mit spiralförmig verlaufenden Rohren,
- Fig. 2 einen Schnitt durch den in der Fig. gezeigten Wärmetauscher, .
- Fig. 3 einen Schnitt gleich dem der Fig. 2, wobei jedoch die Querschnittsform der Rohre ein Dreieck ist,
- Fig. 4 eine weitere Querschnittsform von Rohren,
- Fig. 5 eine noch weitere Querschnittsform von Rohren,
- Fig. 6 einen Schnitt durch einen Wärmetauscher, dessen Rohre einen hohlen Kreiskegel beschreiben,
- Fig. 7 eine Aufsicht auf eine weitere Grundrissform eines Wärmetauschers,
- Fig. 8 den Grundriss einer noch weiteren Ausbildungsform des Wärmetauschers, und
- Fig. 9 einen Schnitt durch einen hohlzylindrischen Wärmetauscher.
- 1 is a plan view of a heat exchanger with spirally extending tubes,
- FIG. 2 shows a section through the heat exchanger shown in FIG.
- 3 is a section similar to that of FIG. 2, but the cross-sectional shape of the tubes is a triangle,
- 4 shows a further cross-sectional shape of pipes,
- 5 shows a still further cross-sectional shape of pipes,
- 6 shows a section through a heat exchanger, the tubes of which describe a hollow circular cone,
- 7 is a plan view of a further layout of a heat exchanger,
- Fig. 8 shows the floor plan of yet another embodiment of the heat exchanger, and
- Fig. 9 shows a section through a hollow cylindrical heat exchanger.
Der Wärmetauscher nach Fig. l weist ein erstes Rohr 1 und ein zweites Rohr 2 auf. Das erste Rohr 1 weist einen Eintritt bzw. Austritt 3 und einen Austritt bzw. Eintritt 5 auf. Das zweite Rohr 2 weist einen Eintritt bzw. Austritt 4 und einen Austritt bzw. Eintritt 6 auf. Die diesen Wärmetauscher durchströmenden Fluide strömen offensichtlich im Gleich- oder Gegenstrom, abhängig von den jeweiligen technischen Gegebenheiten. Die zwei Rohre 1,2 liegen eng aneinander und sind spiralförmig in Windungen gelegt. Dabei liegt die von den Rohren beschriebene Spirale, d.h. die zwei Spiralen, in einer ebenen Fläche. Dadurch, dass diese Ausbildungsform als praktisch zweidimensional angesehen werden kann, weil die dritte Dimension lediglich von der Rohrdicke abhängig ist, nimmt dieser Wärmetauscher einen verhältnismässig kleinen Raum ein.The heat exchanger according to FIG. 1 has a first tube 1 and a
Im Gegensatz zu bekannten Ausbildungen weisen die Rohre jedoch keine kreisförmige Querschnittsform auf. Demgemäss ist in der Fig. 2 eine Ausführung mit Rohren quadratischer Querschnittsform gezeigt. Diese, in der erwähnten Spiralform angeordneten Rohre mit quadratischer Querschnittsform, liegen mit Seitenwänden aneinander an. Zur Erreichung einer guten Wärmeübertragung sind die Rohre miteinander verlötet. Entsprechend ist zwischen den Seitenwänden der Rohre ein Lötmittel, ein Lotmetall 7 angeordnet. Offensichtlich gibt die Verlötung dem Wärmetauscher auch die notwendige mechanische Festigkeit.In contrast to known designs, however, the tubes do not have a circular cross-sectional shape. Accordingly, an embodiment with tubes of square cross-sectional shape is shown in FIG. 2. These tubes, which are arranged in the spiral shape mentioned and have a square cross-sectional shape, abut one another with side walls. The tubes are soldered together to achieve good heat transfer. Correspondingly, a solder, a
Die Herstellung des Wärmetauschers wird folgendermassen durchgeführt. Zuerst werden die Rohre 1,2 in ihrer usprünglichen, geradlinig verlaufenden Form parallel nebeneinander gelegt. Zwischen diesen Rohren wird ein bandförmiges Lötmittel, ein bandförmiges Lotmetall eingefügt, derart, dass die in der Fig. 2 gezeigte Anordnung vorliegt, wobei jedoch im Schnitt nur zwei Rohre vorhanden sind. Danach werden die Rohre und das Lötmittel an beispielsweise einem Ende miteinander punktförmig verbunden. Darauf werden die Rohre 1,2 mit dem dazwischen gelegenen Lötmittel 7 in Windungen gelegt, so dass sie die in Fig. 1 gezeigte Formgebung annehmen. Danach werden Rohre mit 1,2 mit dem Lötmittel 7 durch mindestens eine weitere punktförmige Verbindung in der gewundenen Stellung fixiert. Darauf wird die ganze Anordnung in ein Induktionsbad getaucht. Darin schmilzt das Lötmittel, so dass ein Verlöten der Rohre 1,2 entlang ihrer gesamten Längsausdehnung stattfindet und somit ist der Wärmetauscher hergestellt.The manufacture of the heat exchanger is carried out as follows. First, the
Die Rohre 1,2 müssen nicht unbedingt die in der Fig. 2 gezeigte, quadratische Querschnittsform aufweisen. In der Fig. 3 ist eine Ausführung gezeigt, bei welcher die Rohre in einer dreieckigen Querschnittsform vorliegen, wobei wieder das Lötmittel 7 zwischen den aneinander anliegenden Seitenwänden der Rohre angeordnet sind. Auch diese Ausführung nach der Fig. 3 ist eine raumsparende Ausbildung.The
Zur Erhöhung der Wärmetauschfläche, d.h. derjenigen Flächen der Rohre, durch welche der Wärmeübergang stattfindet, sind diese Wände gemäss einer weiteren Ausführung strukturiert ausgebildet. In der Fig. 4 ist eine solche Ausbildung gezeigt. Dabei ist die Querschnittsfläche des ersten Rohres 1 von der Querschnittsoberfläche des zweiten Rohres 2 verschieden. Beispielsweise ist das erste Rohr 1 von einem dampfförmigen Fluid und das zweite Rohr 2 von Wasser durchströmt, eine Anwendung, die beispielsweise in Wärmepumpenanlagen vorhanden ist. Aneinander anliegende Seitenwände der Rohre 1,2 weisen aufeinanderfolgende Senkungen 9 und Vorsprünge 8 auf. Diese zahnförmigen Ausbildungen kämmen miteinander, so dass das Flächenmass der Wärmedurchtrittsflächen erhöht ist. Im Gegensatz zu den in den Fig. 2 und 3 gezeigten Ausführungsformen sind hier die Rohre nicht miteinander verlötet. Bei dieser Ausbildungsform liegen die Rohre lediglich unter Ausübung eines gegenseitigen Druckes eng aneinander. Auch muss bemerkt werden, dass die Rohrseiten 10 und 11, durch die kein Wärmetausch erfolgt, dennoch am Wärmetausch teilnehmen. Da die Rohre offensichtlich aus einem gut wärmeleitenden Material hergestellt sind, erfolgt auch eine Wärmeübertragung bei den Wänden 10, 11 durch das jeweilige Metall.To increase the heat exchange surface, i.e. of the surfaces of the pipes through which the heat transfer takes place, these walls are structured according to a further embodiment. Such a design is shown in FIG. 4. The cross-sectional area of the first tube 1 is different from the cross-sectional surface of the
Bei der Ausführung nach der Fig. 5 weisen die Rohre 1,2 wieder dieselbe Querschnittsfläche auf und sind wieder mit einem Lötmittel 7 miteinander verbunden. Der Unterschied zur Ausführung der Fig. 4 ist her der, dass beide Seitenwände der Rohre 1,2, durch welche die Wärmeübertragung stattfindet, ein vergrössertes Flächenmass aufweisen, wobei hier die Wände einfach wellenförmig ausgebildet sind, wobei die jeweiligen Wellentäler und Wellenberge ineinander eingreifen.In the embodiment according to FIG. 5, the
In der Fig. 6 ist eine noch weitere Ausführung des Wärmetauschers dargestellt. Es ist bei der Beschreibung der Fig. 1 gesagt worden, dass die Spirale, d.h. die zwei Spiralen, die von den Rohren 1,2 beschrieben sind, in einer ebenen Fläche liegen. In der Fig. 6 sind nun die Rohre zudem derart verformt, dass sie die Hüllkurve eines hohlen Kreiskegels beschreiben. Der Vorteil dieser Formgebung ist der, dass ein eindeutiges Gefälle in den Rohren vorliegt. Ein Gefälle ist oft aufgrund eines gegebenen Mediums notwendig, beispielsweise, wenn ein Medium im gasförmigen Zustand eintritt und im Wärmetauscher verflüssigt wird, und somit im Bezug auf die Horizontale ein Gefälle aufweisen muss.A further embodiment of the heat exchanger is shown in FIG. 6. It has been said in the description of FIG. 1 that the spiral, ie the two Spirals, which are described by the
In den Fig. 6 und 7 ist gezeigt, dass die Hüllkurve des Wärmetauschers, d.h. mindestens dessen Projektion auf eine Fläche, nicht kreisförmig (wobei zu verstehen ist, dass hier die Hüllkurve der Spirale vereinfachend als Kreis betrachtet ist) sein muss. Die Hüllkurve kann also ein Rechteck, wie nach der Fig. 6 oder ein Sechseck wie nach der Fig. 7, oder irgendwelches anderes Vieleck, Polygon beschreiben. Dadurch, dass die Möglichkeit gegeben ist, die Rohre einerseits räumlich, wie beispielsweise in der Fig. 6 gezeigt, anzuordnen und andererseits die Möglichkeit gegeben ist, die Hüllkurve des Wärmetauschers zu wählen, lässt sich nun der Wärmetauscher in beliebigen räumlichen und flächigen Formen auslegen, derart, dass er in einer gesamten Anlage, beispielsweise einer Wärmepumpenanlage, derart angeordnet werden kann, dass er ein kleinstes Mass an Raum beansprucht.6 and 7 it is shown that the envelope of the heat exchanger, i.e. at least its projection onto a surface, not circular (it should be understood that here the envelope of the spiral is viewed as a circle for simplicity). The envelope curve can thus describe a rectangle, as in FIG. 6 or a hexagon as in FIG. 7, or any other polygon, polygon. Because there is the possibility of arranging the pipes spatially on the one hand, as shown, for example, in FIG. 6, and on the other hand there is the possibility of choosing the envelope of the heat exchanger, the heat exchanger can now be designed in any spatial and planar form, such that it can be arranged in an entire system, for example a heat pump system, in such a way that it takes up the smallest amount of space.
In der Fig. 9 ist eine Ausführungsform gezeigt, bei welcher die Rohre 1,2 in Form eines Hohlzylinders angeordnet sind. Diese Ausführungsform weist insbesondere den Vorteil auf, dass Apparate, z.B. Pumpen und andere Einheiten einer der Wärmetauscher enthaltenden Anlage, z.B. einer Wärmepumpenanlage, im von den Rohren 1,2 umschriebenen, zylindrischen Hohlraum angeordnet werden können. Damit sind bedeutende Raumersparnisse möglich.9 shows an embodiment in which the
Claims (13)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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CH2195/81 | 1981-03-31 | ||
CH219581 | 1981-03-31 |
Publications (2)
Publication Number | Publication Date |
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EP0061779A2 true EP0061779A2 (en) | 1982-10-06 |
EP0061779A3 EP0061779A3 (en) | 1983-03-30 |
Family
ID=4228106
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP82102715A Withdrawn EP0061779A3 (en) | 1981-03-31 | 1982-03-31 | Heat exchanger |
Country Status (4)
Country | Link |
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EP (1) | EP0061779A3 (en) |
JP (1) | JPS57166497A (en) |
DE (2) | DE3122947A1 (en) |
NO (1) | NO821079L (en) |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1983002315A1 (en) * | 1981-12-30 | 1983-07-07 | Daniel Ringqvist | Device for the transfer of heat between different polluted fluid media |
EP0143672A2 (en) * | 1983-11-25 | 1985-06-05 | POWER SHAFT ENGINE, Société dite | External combustion engine |
EP0168637A2 (en) * | 1984-06-14 | 1986-01-22 | Etablissement Agura | Gas-fired heater, especially a condensing heater, with a spirally formed smoke duct, method for making such a heater and heater made by such a method |
CH677968A5 (en) * | 1988-03-08 | 1991-07-15 | Sulzer Ag | Heat exchanger for mfg. crystals - has plates in circular ring with eccentric drive shaft for scrapers |
EP0582835A1 (en) * | 1992-08-11 | 1994-02-16 | Steyr Nutzfahrzeuge Ag | Heat-exchanger |
WO2001019412A1 (en) * | 1998-08-20 | 2001-03-22 | Hans Biermaier | Device for the thermal sterilization of liquids |
AT409544B (en) * | 2000-08-04 | 2002-09-25 | Vaillant Gmbh | Sorption heat pump with adsorber-desorber heat exchanger, integrates evaporator-condenser unit into base of common, vacuum-tight vessel |
AT409669B (en) * | 2000-08-04 | 2002-10-25 | Vaillant Gmbh | Sorption heat pump with adsorber-desorber heat exchanger, integrates evaporator-condenser unit into base of common, vacuum-tight vessel |
WO2002101312A1 (en) * | 2001-06-09 | 2002-12-19 | Nnc Limited | Heat exchanger |
AT412171B (en) * | 2001-08-16 | 2004-10-25 | Vaillant Gmbh | Heat exchanger for an evaporator or condenser of an adsorption heat pump comprises a plate-like base body having a planar end face on which a spiral fluid-conveying pipe having a hemispherical cross-section is positioned |
WO2004105455A2 (en) * | 2003-05-21 | 2004-12-02 | Molex Incorporated | Memory card connector |
WO2009115284A1 (en) * | 2008-03-20 | 2009-09-24 | Valeo Systemes Thermiques | Heat exchanger and integrated air-conditioning assembly including such exchanger |
EP2423630A1 (en) * | 2010-08-24 | 2012-02-29 | Electricité de France | Improved heat exchanger |
WO2013037381A1 (en) * | 2011-09-15 | 2013-03-21 | Patrick Gilbert | Conduit assemblies for heat exchangers and the like |
US20150330714A1 (en) * | 2012-12-05 | 2015-11-19 | Polyvision, Naamloze Vennootschap | Spiral or helical counterflow heat exchanger |
US20190063842A1 (en) * | 2017-07-28 | 2019-02-28 | Fluid Handling Llc | Fluid routing methods for a spiral heat exchanger with lattice cross section made via additive manufacturing |
US20200355397A1 (en) * | 2017-08-28 | 2020-11-12 | Cosmogas S.R.L. | Heat exchanger for a boiler, and heat-exchanger tube |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3220957A1 (en) * | 1982-06-03 | 1983-12-08 | Parca Norrahammar AB, 56200 Norrahammar | Spiral heat exchanger |
DE3505789A1 (en) * | 1985-02-20 | 1986-08-21 | Grote, Paul, 2901 Friedrichsfehn | SPIRAL HEAT EXCHANGER |
DE3706941A1 (en) * | 1987-03-04 | 1988-09-15 | Seiler Geb Fritz Ursula | Gas cooler with integrated condensate precipitation (elimination, separation) |
DE3724790A1 (en) * | 1987-07-30 | 1989-02-09 | Schilling Heinz Kg | Heat exchange module for opposite flowing media with parallel pipes cast in heat-conducting material |
DE4142203C2 (en) * | 1990-12-24 | 1996-01-18 | Franz R Prof Dr Ing Stupperich | Spiral heat exchanger with triangular tube cross section |
DE102010027338B4 (en) * | 2010-07-15 | 2012-04-05 | Benteler Automobiltechnik Gmbh | Heat exchanger in a motor vehicle |
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US2131265A (en) * | 1937-03-01 | 1938-09-27 | Dow Chemical Co | Spiral heat interchanger and method of making same |
DE668493C (en) * | 1938-12-03 | Wilhelm Geldbach Dr Ing | Spiral heat exchanger for gas separation plants | |
GB803759A (en) * | 1955-11-24 | 1958-10-29 | Gen Electric Co Ltd | Improvements in or relating to refrigerator condensers |
FR1350529A (en) * | 1963-03-15 | 1964-01-24 | Ames Crosta Mills & Company Lt | Improvements to heat exchangers |
DE1907881A1 (en) * | 1969-02-17 | 1970-09-03 | Becker Dr Ing Kurt | Flat coils for cross-flow heat exchangers |
US3602298A (en) * | 1969-04-25 | 1971-08-31 | Mecislaus Joseph Ciesielski | Heat exchanger |
FR2155770A1 (en) * | 1971-10-04 | 1973-05-25 | Ind Chauffage | Spiral tube heat exchanger - with tubes contacting shell to define shell-side flow |
US4253225A (en) * | 1979-10-10 | 1981-03-03 | Carrier Corporation | Method of manufacturing a heat exchanger element |
US4316502A (en) * | 1980-11-03 | 1982-02-23 | E-Tech, Inc. | Helically flighted heat exchanger |
-
1981
- 1981-06-10 DE DE19813122947 patent/DE3122947A1/en not_active Withdrawn
- 1981-06-10 DE DE19818117144U patent/DE8117144U1/en not_active Expired
- 1981-08-28 JP JP56134353A patent/JPS57166497A/en active Pending
-
1982
- 1982-03-30 NO NO821079A patent/NO821079L/en unknown
- 1982-03-31 EP EP82102715A patent/EP0061779A3/en not_active Withdrawn
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DE668493C (en) * | 1938-12-03 | Wilhelm Geldbach Dr Ing | Spiral heat exchanger for gas separation plants | |
DE273142C (en) * | 1912-10-15 | 1914-04-20 | ||
US2131265A (en) * | 1937-03-01 | 1938-09-27 | Dow Chemical Co | Spiral heat interchanger and method of making same |
GB803759A (en) * | 1955-11-24 | 1958-10-29 | Gen Electric Co Ltd | Improvements in or relating to refrigerator condensers |
FR1350529A (en) * | 1963-03-15 | 1964-01-24 | Ames Crosta Mills & Company Lt | Improvements to heat exchangers |
DE1907881A1 (en) * | 1969-02-17 | 1970-09-03 | Becker Dr Ing Kurt | Flat coils for cross-flow heat exchangers |
US3602298A (en) * | 1969-04-25 | 1971-08-31 | Mecislaus Joseph Ciesielski | Heat exchanger |
FR2155770A1 (en) * | 1971-10-04 | 1973-05-25 | Ind Chauffage | Spiral tube heat exchanger - with tubes contacting shell to define shell-side flow |
US4253225A (en) * | 1979-10-10 | 1981-03-03 | Carrier Corporation | Method of manufacturing a heat exchanger element |
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Cited By (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1983002315A1 (en) * | 1981-12-30 | 1983-07-07 | Daniel Ringqvist | Device for the transfer of heat between different polluted fluid media |
EP0143672A2 (en) * | 1983-11-25 | 1985-06-05 | POWER SHAFT ENGINE, Société dite | External combustion engine |
EP0143672A3 (en) * | 1983-11-25 | 1987-12-16 | POWER SHAFT ENGINE, Société dite | External combustion engine |
EP0168637A2 (en) * | 1984-06-14 | 1986-01-22 | Etablissement Agura | Gas-fired heater, especially a condensing heater, with a spirally formed smoke duct, method for making such a heater and heater made by such a method |
EP0168637A3 (en) * | 1984-06-14 | 1986-07-02 | Etablissement Agura | Gas-fired heater, especially a condensing heater, with a spirally formed smoke duct, method for making such a heater and heater made by such a method |
CH677968A5 (en) * | 1988-03-08 | 1991-07-15 | Sulzer Ag | Heat exchanger for mfg. crystals - has plates in circular ring with eccentric drive shaft for scrapers |
EP0582835A1 (en) * | 1992-08-11 | 1994-02-16 | Steyr Nutzfahrzeuge Ag | Heat-exchanger |
WO2001019412A1 (en) * | 1998-08-20 | 2001-03-22 | Hans Biermaier | Device for the thermal sterilization of liquids |
AT409544B (en) * | 2000-08-04 | 2002-09-25 | Vaillant Gmbh | Sorption heat pump with adsorber-desorber heat exchanger, integrates evaporator-condenser unit into base of common, vacuum-tight vessel |
AT409669B (en) * | 2000-08-04 | 2002-10-25 | Vaillant Gmbh | Sorption heat pump with adsorber-desorber heat exchanger, integrates evaporator-condenser unit into base of common, vacuum-tight vessel |
WO2002101312A1 (en) * | 2001-06-09 | 2002-12-19 | Nnc Limited | Heat exchanger |
AT412171B (en) * | 2001-08-16 | 2004-10-25 | Vaillant Gmbh | Heat exchanger for an evaporator or condenser of an adsorption heat pump comprises a plate-like base body having a planar end face on which a spiral fluid-conveying pipe having a hemispherical cross-section is positioned |
WO2004105455A2 (en) * | 2003-05-21 | 2004-12-02 | Molex Incorporated | Memory card connector |
WO2004105455A3 (en) * | 2003-05-21 | 2005-03-24 | Molex Inc | Memory card connector |
WO2009115284A1 (en) * | 2008-03-20 | 2009-09-24 | Valeo Systemes Thermiques | Heat exchanger and integrated air-conditioning assembly including such exchanger |
US9920999B2 (en) | 2008-03-20 | 2018-03-20 | Valeo Systemes Thermiques | Heat exchanger and integrated air-conditioning assembly including such exchanger |
CN102037305B (en) * | 2008-03-20 | 2015-03-18 | 法雷奥热***公司 | Heat exchanger and integrated air-conditioning assembly including such exchanger |
FR2928997A1 (en) * | 2008-03-20 | 2009-09-25 | Valeo Systemes Thermiques | HEAT EXCHANGER AND INTEGRATED AIR CONDITIONING ASSEMBLY COMPRISING SUCH AN EXCHANGER. |
EP2423630A1 (en) * | 2010-08-24 | 2012-02-29 | Electricité de France | Improved heat exchanger |
FR2964183A1 (en) * | 2010-08-24 | 2012-03-02 | Electricite De France | IMPROVED THERMAL EXCHANGER |
WO2013037381A1 (en) * | 2011-09-15 | 2013-03-21 | Patrick Gilbert | Conduit assemblies for heat exchangers and the like |
JP2014526669A (en) * | 2011-09-15 | 2014-10-06 | ギルバート,パトリック | Piping assembly for heat exchanger etc. |
US20150330714A1 (en) * | 2012-12-05 | 2015-11-19 | Polyvision, Naamloze Vennootschap | Spiral or helical counterflow heat exchanger |
US10094621B2 (en) * | 2012-12-05 | 2018-10-09 | Polyvision, Naamloze Vennootschap | Spiral or helical counterflow heat exchanger |
US20190063842A1 (en) * | 2017-07-28 | 2019-02-28 | Fluid Handling Llc | Fluid routing methods for a spiral heat exchanger with lattice cross section made via additive manufacturing |
US11193716B2 (en) * | 2017-07-28 | 2021-12-07 | Fluid Handling Llc | Fluid routing methods for a spiral heat exchanger with lattice cross section made via additive manufacturing |
US11898804B2 (en) | 2017-07-28 | 2024-02-13 | Fluid Handling Llc | Fluid routing methods for a spiral heat exchanger with lattice cross section made via additive manufacturing |
US20200355397A1 (en) * | 2017-08-28 | 2020-11-12 | Cosmogas S.R.L. | Heat exchanger for a boiler, and heat-exchanger tube |
US11598555B2 (en) * | 2017-08-28 | 2023-03-07 | Cosmogas S.R.L. | Heat exchanger for a boiler, and heat-exchanger tube |
Also Published As
Publication number | Publication date |
---|---|
DE8117144U1 (en) | 1981-11-26 |
NO821079L (en) | 1982-10-01 |
JPS57166497A (en) | 1982-10-13 |
DE3122947A1 (en) | 1982-10-07 |
EP0061779A3 (en) | 1983-03-30 |
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