EP1691158A1 - Plate heat exchanger - Google Patents
Plate heat exchanger Download PDFInfo
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- EP1691158A1 EP1691158A1 EP06001162A EP06001162A EP1691158A1 EP 1691158 A1 EP1691158 A1 EP 1691158A1 EP 06001162 A EP06001162 A EP 06001162A EP 06001162 A EP06001162 A EP 06001162A EP 1691158 A1 EP1691158 A1 EP 1691158A1
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- plate
- heat exchanger
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- plates
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- 238000009826 distribution Methods 0.000 claims abstract description 43
- 230000003068 static effect Effects 0.000 claims description 3
- 230000000149 penetrating effect Effects 0.000 claims description 2
- 239000012530 fluid Substances 0.000 abstract description 5
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000704 physical effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
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Classifications
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
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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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
Definitions
- the invention relates to a plate heat exchanger with a stack of plates, in which the plate interstices are flowed through laminar.
- plate heat exchangers consisting of a stack of equally sized and uniformly profiled plates in which adjacent plates alternately face their front sides or backs and in which the plates touch at the points where they touch and are supported against each other, welded or soldered.
- the known plate heat exchangers have an essential common feature: the flow paths between densely and parallel adjacent plates are always provided with baffles by ribs, corrugations, webs and similar profiles in order to minimize the formation of laminar boundary layers and thereby increase the heat transfer capacity ,
- the fluid flow between the plates should always be turbulent wherever possible. Accordingly high is the pressure loss, which increases approximately quadratically with the volume flow.
- the closer the flow labyrinth through which a fluid flows turbulently the smaller the plate distances and the shorter the unobstructed flow path sections, the greater the heat transfer capacity and the pressure loss and the higher the need for energy to convey the heat exchange media between the plates.
- Another common feature of the four plate heat exchangers mentioned above is that for the distribution of the heat exchange media between the plates and for collecting the heat exchange media from the plate interspaces in each corner of the plate stack exactly one channel is provided which leads vertically through the plate stack and only in the each affected plate interstices has a gap in it.
- a relatively large proportion per plate is not used as a heat exchanger surface, these are the surfaces of the vertical distribution and collection channels themselves and the plate surface portions, which are not flown on both sides of different heat exchange media.
- This type of distribution in one corner or collection in another corner of the plates also does not make it easy to evenly distribute the flows of the heat exchange media across the plate interspaces. For this, the relatively high pressure loss is exploited as a result of equipping the plates with ribs, corrugations, ridges and similar profiles in the region of the plates where the heat transfer takes place.
- Rib heat exchangers are used when the heat exchange medium of one circuit (which always flows through the ribbed side) has a much lower heat transfer coefficient than that of the other, un-filtered circuit.
- the ribbing always has the purpose of significantly increasing the heat exchanger surface. It is described in detail that so the heat of a gas that flows through the laminar laminar, is transferred to a (liquid-flowed) pipe or vice versa.
- the document DE 693 16 990 T2 shows how deliberately laminar flows in countercurrent heat exchangers are used with non-slit channels. This is z. B. shell and tube heat exchangers (or tubular heat exchangers) with coat known. In the document DE 693 16 990 T2 are adjacent equal sized channels with gleich workedem or square cross-section.
- the advantages in a high heat exchange surface easily imaginable as "porosity”
- in a high intrinsic capacity in a high compressive strength and in an acceptably low pressure drop, as long as the flow in the Hagen-Poiseuille area, ie laminar he follows.
- the difficulties are, as mentioned in DE 693 16 990 T2 and solved there according to the invention in an interesting way, especially in the complex uniform distribution of flows, ie in the distribution and collection of both heat exchanger media at the opposite ends of the heat exchanger.
- the object of the invention is to provide a plate heat exchanger, with a very high heat transfer density is achieved despite very low pressure losses and in which the largest possible proportion of the plate surface is used for heat transfer.
- the plate interstices are formed as laminar flow gaps, so that the plate interstices are flowed through laminar by the heat exchange media.
- the distance of the plates is selected accordingly.
- the plate surfaces can be predominantly unprofiled and smooth. Because of the laminar flow in the plate heat exchanger according to the invention, this may also be referred to as a laminar flow plate heat exchanger.
- Every second plate gap in the stack of plates is flowed through by the same heat exchange medium in the same direction, ie in DC. In this way results in a parallel arrangement of flow areas with the same flow direction. Adjacent plate interstices are flowed through by different heat exchange media in opposite directions, ie in countercurrent. This results in a parallel arrangement of flow regions with opposite flow directions.
- the plates of the stack are the same size.
- the plates are preferably used with a rectangular shape.
- plate heat exchangers are possible when using flat and smooth plates, which despite very low pressure losses have a much higher heat transfer density than is possible with known, aimed at turbulent flows heat exchangers.
- small plate spacings are necessary that impurities, suspended solids or the surfaces adhesively changing chemicals in the heat exchange media can enforce the heat exchanger. Therefore, the application is limited to clear, pure or at least filtered heat exchange media.
- the distribution channels and / or the collecting channels have a circular cross-section.
- An advantageous embodiment of the invention provides that the distribution channels and / or the collecting ducts are designed as aligned in a main direction of flow slots.
- the collecting ducts and the distribution channels have the same shape.
- the collecting ducts have a larger hydraulic diameter than the distribution channels.
- An advantageous embodiment of the invention provides that the distribution of the at least one of the heat exchange media in the associated plate interspaces and its collection from the plate interspaces via a forced, a flow cross-section narrowing deflection takes place up to the extreme edge of the plate at which the entry into the / outlet from takes place the free disc spaces.
- the tension and pressure anchors are arranged in lines parallel to the flow direction and symmetrical to the distribution channels and the collecting channels.
- the tension and pressure anchors are arranged at regular intervals.
- the plate spacings are the same for both heat exchanger media.
- the plate spacings are different for both heat exchanger media.
- each second plate interspace the two plate ends penetrated by the distribution channels / collection channels of the adjacent plate interspaces are open and that the heat exchange medium flowing in these plate interspaces, via these openings, directly into the stack of plates enters and exits, these plate interstices are free of their own distribution channels / collection channels.
- a plate end which is penetrated by the collecting channels / distribution channels of the adjacent plate interspaces, is open and that the heat exchange medium flowing in these plate interspaces via these openings from the stack of plates
- These plate interspaces are formed at this plate end without distribution / collection channels, while they are closed at the other end of the plate, whereas at the other end of the plate the adjacent plate interstices are open and without distribution channels / collection channels.
- Fig. 1 shows a schematic representation of a plate heat exchanger with a stack of plates 1. Plate spaces between the plates 1 are traversed by heat exchange media. Every second plate gap is flowed through by the same heat exchange medium in the same direction, ie in DC. In this way results in a parallel arrangement of flow areas with the same flow direction. Adjacent plate interstices are flowed through by different heat exchange media in opposite directions, ie in countercurrent. This results in a parallel arrangement of flow regions with opposite flow directions.
- a plurality of parallel distribution channels 3 are provided, which lead vertically through the stack and have an opening only in the respectively assigned plate interspaces, preferably in the form of a gap.
- the distribution and collection channels 3, 4 are the smaller, the more they are, and of course smaller than just a single channel would have to be in one corner of the stack.
- the distribution and collection channels 3, 4 are elongated to minimize the reduction of the flow area in the adjacent plate gap.
- the shape of the collecting channels 4, in particular with regard to the cross-sectional configuration, is preferably not the same as the shape of the distribution channels 3.
- the collecting channels 4 expediently have a larger hydraulic diameter than the distribution channels 3 in order to ensure the most uniform flow velocity distribution in the gaps and minimal pressure losses during distribution and to achieve a collection.
- the plates 1 are supported against each other. So that these supports disturb the laminar flow of the heat exchange medium as little as possible, they are minimized in number, punctiform and arranged in lines along the flow direction (see reference numerals 6a, 6b in Fig. 1 and 5).
- the dot shape is statically more advantageous than a line shape.
- Another advantageous possibility to distribute the heat transfer medium evenly between the plates 1, is to dispense with a maximum of two vertical channels within the stack of plates and from outside of the plate interspaces in this in or out of these flow out (see reference numerals 8, 9, 10 in Fig. 1).
- the advantages are a better land use of the plates 1 and avoiding the additional pressure losses associated with the distribution / collection.
- a particularly advantageous variant is when both ends of the plate heat exchanger are immersed in one and the same heat exchange medium, have no channels for this heat exchange medium, are hydraulically connected again outside the heat exchanger and have a height difference (8). Then, due to the particularly low pressure loss, this heat exchanger medium can circulate solely by gravity as soon as heat is supplied or withdrawn via the other heat exchanger medium.
Abstract
Description
Die Erfindung betrifft einen Plattenwärmetauscher mit einem Stapel von Platten, bei dem die Plattenzwischenräume laminar durchströmt werden.The invention relates to a plate heat exchanger with a stack of plates, in which the plate interstices are flowed through laminar.
Bekannt sind aus dem Dokument FR-2 323 119 A1 Plattenwärmetauscher, die aus einem Stapel gleichgroßer und gleichförmig profilierter Platten bestehen, in dem benachbarte Platten sich abwechselnd ihre Vorderseiten oder ihre Rückseiten zuwenden und in dem die Platten an den Stellen, an denen sie sich berühren und gegeneinander abstützen, verschweißt oder verlötet sind.Known from document FR-2 323 119 A1 are plate heat exchangers consisting of a stack of equally sized and uniformly profiled plates in which adjacent plates alternately face their front sides or backs and in which the plates touch at the points where they touch and are supported against each other, welded or soldered.
Bekannt sind auch aus dem Dokument DE 198 58 652 A1 Plattenwärmetauscher mit mehreren gewellten, nebeneinander angeordneten und zueinander abgedichteten Flächen und zwei voneinander getrennten Strömungswegen mit unterschiedlichen Strömungsquerschnitten.Also known from the document DE 198 58 652 A1 plate heat exchanger having a plurality of corrugated, juxtaposed and mutually sealed surfaces and two separate flow paths with different flow cross sections.
In dem Dokument DE 694 22 207 T2 (EP 0611941 B1) wird durch Rippen in den Platten eine Labyrinthkammer zwischen benachbarten Platten gebildet.In document DE 694 22 207 T2 (EP 0611941 B1), a labyrinth chamber is formed between adjacent plates by ribs in the plates.
Anstelle von gleichförmigen Profilen, Rippen oder von Wellen, welche in die Platten geprägt sind, werden in dem Dokument DE 33 39 932 A1 zur Erhöhung der Quervermischung eines zwischen zwei benachbarten Platten fließenden Fluids Stege an den Flächen befestigt.Instead of uniform profiles, ribs or waves, which are embossed in the plates, in the document DE 33 39 932 A1 to increase the cross-mixing of a fluid flowing between two adjacent plates webs attached to the surfaces.
Neben ihren Besonderheiten weisen die bekannten Plattenwärmetauscher ein wesentliches gemeinsames Merkmal auf: Immer werden die Strömungswege zwischen dicht und parallel nebeneinander liegenden Platten durch Rippen, Wellen, Stege und ähnliche Profile mit Schikanen versehen, um die Ausbildung laminarer Grenzschichten zu minimieren und hierdurch das Wärmeübertragungsvermögen zu erhöhen. Die Fluid-Strömung zwischen den Platten soll immer möglichst überall turbulent sein. Dementsprechend hoch ist auch der Druckverlust, der sich annähernd quadratisch mit dem Volumenstrom erhöht. Allgemein gilt: Je enger das Fließlabyrinth ist, durch welches ein Fluid turbulent fließt, je kleiner also die Plattenabstände und je kürzer die unbehinderten Fließwegabschnitte sind, um so größer sind das Wärmeübertragungsvermögen und der Druckverlust und um so höher ist der Bedarf an Energie, um die Wärmetauschermedien zwischen den Platten hindurchzubefördern.In addition to their peculiarities, the known plate heat exchangers have an essential common feature: the flow paths between densely and parallel adjacent plates are always provided with baffles by ribs, corrugations, webs and similar profiles in order to minimize the formation of laminar boundary layers and thereby increase the heat transfer capacity , The fluid flow between the plates should always be turbulent wherever possible. Accordingly high is the pressure loss, which increases approximately quadratically with the volume flow. In general, the closer the flow labyrinth through which a fluid flows turbulently, the smaller the plate distances and the shorter the unobstructed flow path sections, the greater the heat transfer capacity and the pressure loss and the higher the need for energy to convey the heat exchange media between the plates.
Ein weiterer Effekt wird in den bekannten Plattenwärmetauschern gleichermaßen erreicht. Durch die Ausstattung der Platten mit Rippen, Wellen, Stegen und ähnlichen Profilen wird ein dichtes Muster von Berührungsstellen zwischen benachbarten Platten geschaffen, was den Wärmetauschern eine gewisse Druckfestigkeit verleiht. Ohne vielfältige gegenseitige Abstützung sind Räume zwischen parallel nebeneinander liegenden Platten nur für niedrigste Drükke geeignet, bei denen die Platten noch nicht verformt werden.Another effect is equally achieved in the known plate heat exchangers. By providing the plates with ribs, corrugations, ridges and like profiles, a dense pattern of contact points between adjacent plates is created, which gives the heat exchangers a certain compressive strength. Without multiple mutual support spaces between parallel juxtaposed plates are only suitable for lowest pressures, in which the plates are not deformed yet.
Ein weiteres gemeinsames Merkmal der vier eingangs genannten Plattenwärmetauscher besteht darin, daß zur Verteilung der Wärmetauschermedien zwischen die Platten und zur Sammlung der Wärmetauschermedien aus den Plattenzwischenräumen in jeder Ecke des Plattenstapels jeweils genau ein Kanal vorgesehen ist, der senkrecht durch den Plattenstapel führt und nur in die jeweils betroffenen Plattenzwischenräume hinein einen Spalt aufweist. Dadurch wird pro Platte ein relativ großer Anteil nicht als Wärmetauscherfläche genutzt, das sind die Flächen der senkrechten Verteil- und Sammelkanäle selbst sowie die Plattenflächenanteile, die nicht beidseitig von verschiedenen Wärmetauschermedien angeströmt werden. Diese Art der Verteilung in der einen Ecke bzw. der Sammlung in einer anderen Ecke der Platten macht es auch nicht leicht, die Ströme der Wärmetauschermedien über die Plattenzwischenräume völlig gleichmäßig zu verteilen. Dazu wird der relativ hohe Druckverlust als Folge der Ausstattung der Platten mit Rippen, Wellen, Stegen und ähnlichen Profilen in dem Bereich der Platten, wo die Wärmeübertragung stattfindet, ausgenutzt.Another common feature of the four plate heat exchangers mentioned above is that for the distribution of the heat exchange media between the plates and for collecting the heat exchange media from the plate interspaces in each corner of the plate stack exactly one channel is provided which leads vertically through the plate stack and only in the each affected plate interstices has a gap in it. As a result, a relatively large proportion per plate is not used as a heat exchanger surface, these are the surfaces of the vertical distribution and collection channels themselves and the plate surface portions, which are not flown on both sides of different heat exchange media. This type of distribution in one corner or collection in another corner of the plates also does not make it easy to evenly distribute the flows of the heat exchange media across the plate interspaces. For this, the relatively high pressure loss is exploited as a result of equipping the plates with ribs, corrugations, ridges and similar profiles in the region of the plates where the heat transfer takes place.
Aus dem Dokument DE 197 58 567 C2 ist bekannt, daß bei Rippenwärmetauschern auch laminare Strömungen genutzt werden. Rippenwärmetauscher werden eingesetzt, wenn das Wärmetauschermedium des einen Kreises (das stets die gerippte Seite durchströmt) eine viel geringere Wärmeübergangszahl hat als das des anderen, unberippten Kreises. Die Berippung hat dabei immer den Zweck, die Wärmetauscheroberfläche wesentlich zu vergrößern. Es wird detailliert geschildert, daß so die Wärme eines Gases, das die Rippen laminar durchströmt, auf ein (mit Flüssigkeit durchströmtes) Rohr übertragen wird oder umgekehrt.From the document DE 197 58 567 C2 it is known that in rib heat exchangers and laminar flows are used. Rib heat exchangers are used when the heat exchange medium of one circuit (which always flows through the ribbed side) has a much lower heat transfer coefficient than that of the other, un-filtered circuit. The ribbing always has the purpose of significantly increasing the heat exchanger surface. It is described in detail that so the heat of a gas that flows through the laminar laminar, is transferred to a (liquid-flowed) pipe or vice versa.
In dem Dokument DE 693 16 990 T2 wird gezeigt, wie mit nicht spaltförmigen Kanälen bewußt laminare Strömungen in Gegenstrom-Wärmetauschern genutzt werden. Das ist z. B. von Rohrbündelwärmetauschern (oder Röhrenwärmetauschern) mit Mantel bekannt. In dem Dokument DE 693 16 990 T2 handelt es sich um benachbarte gleich große Kanäle mit gleichseitigem oder quadratischem Querschnitt. Hier, wie auch beim Rohrbündelwärmetauscher liegen die Vorteile in einer hohen Wärmetauscherfläche (leicht vorstellbar als "Porösität"), in einer hohen Eigenkapazität, in einer hohen Druckfestigkeit und in einem akzeptabel geringen Druckverlust, solange die Strömung im Hagen-Poiseuille-Bereich, also laminar erfolgt. Die Schwierigkeiten liegen, wie in DE 693 16 990 T2 genannt und dort erfindungsgemäß auf interessante Weise gelöst, vor allem in der aufwändigen Gleichverteilung der Strömungen, also in der Verteilung und Sammlung beider Wärmetauschermedien an den gegenüberliegenden Enden des Wärmetauschers.The document DE 693 16 990 T2 shows how deliberately laminar flows in countercurrent heat exchangers are used with non-slit channels. This is z. B. shell and tube heat exchangers (or tubular heat exchangers) with coat known. In the document DE 693 16 990 T2 are adjacent equal sized channels with gleichseitigem or square cross-section. Here, as well as the shell and tube heat exchanger, the advantages in a high heat exchange surface (easily imaginable as "porosity"), in a high intrinsic capacity, in a high compressive strength and in an acceptably low pressure drop, as long as the flow in the Hagen-Poiseuille area, ie laminar he follows. The difficulties are, as mentioned in DE 693 16 990 T2 and solved there according to the invention in an interesting way, especially in the complex uniform distribution of flows, ie in the distribution and collection of both heat exchanger media at the opposite ends of the heat exchanger.
Aufgabe der Erfindung ist es, einen Plattenwärmetauscher zu schaffen, mit dem trotz sehr geringer Druckverluste eine sehr hohe Wärmeübertragungsdichte erreicht wird und bei dem ein möglichst großen Anteil der Plattenfläche zur Wärmeübertragung nutzbar ist.The object of the invention is to provide a plate heat exchanger, with a very high heat transfer density is achieved despite very low pressure losses and in which the largest possible proportion of the plate surface is used for heat transfer.
Diese Aufgabe wird erfindungsgemäß durch einen Plattenwärmetauscher nach Anspruch 1 gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand von abhängigen Unteransprüchen.This object is achieved by a plate heat exchanger according to
Erfindungsgemäß ist ein Plattenwärmetauscher mit einem Stapel von Platten geschaffen, wobei:
- jeder zweite Plattenzwischenraum von demselben Wärmetauschermedium im Gleichstrom und benachbarte Plattenzwischenräume im Gegenstrom von einem anderen Wärmetauschermedium durchströmt werden;
- die Platten an Stellen, an denen die Platten sich berühren und gegeneinander abstützen, verschweißt oder verlötet sind;
- sich im Volumenstrombereich der Wärmetauschermedien innerhalb des Stapels in den durchflossenen Plattenzwischenräumen zwischen Plattenoberflächen eine laminare Strömung ausbildet;
- mehrere an einem Plattenende nebeneinander angeordnete, die Platten an einem Ende durchdringende Verteilkanäle gebildet sind, um mindestens eines der Wärmetauschermedien aus den Verteilerkanälen durch Öffnungen in zugeordnete Plattenzwischenräume zu verteilen; und
- mehrere am anderen Plattenende angeordnete Sammelkanäle gebildet sind, um das mindestens eine der Wärmetauschermedien zu sammeln.
- flowing through each second plate interspace of the same heat exchange medium in the DC and adjacent plate interspaces in countercurrent flow from another heat exchange medium;
- the panels at locations where the panels touch and abut each other, welded or soldered;
- in the volume flow area of the heat exchange media within the stack, a laminar flow forms in the inter-plate gaps between plate surfaces;
- a plurality of juxtaposed at a plate end, the plates at one end penetrating distribution channels are formed to distribute at least one of the heat exchange media from the distribution channels through openings in the associated plate interspaces; and
- a plurality of collecting ducts arranged at the other end of the plate are formed in order to collect the at least one of the heat exchanger media.
Zwischen den Platten des Stapels sind die Plattenzwischenräumen als Laminarströmungs-Zwischenräume gebildet, so daß die Plattenzwischenräume von den Wärmetauschermedien laminar durchströmt werden. Der Abstand der Platten ist entsprechend gewählt. Zum optimierten Ausbilden der Laminarströmung können die Plattenoberflächen überwiegend unprofiliert und glatt ausgeführt werden. Wegen der laminaren Strömung in dem erfindungsgemäßen Plattenwärmetauscher kann dieser auch als Laminarströmungs-Plattenwärmetauscher bezeichnet werden.Between the plates of the stack, the plate interstices are formed as laminar flow gaps, so that the plate interstices are flowed through laminar by the heat exchange media. The distance of the plates is selected accordingly. For optimized formation of the laminar flow, the plate surfaces can be predominantly unprofiled and smooth. Because of the laminar flow in the plate heat exchanger according to the invention, this may also be referred to as a laminar flow plate heat exchanger.
Jeder zweite Plattenzwischenraum in dem Stapel von Platten wird von demselben Wärmetauschermedium in gleicher Richtung durchströmt, also im Gleichstrom. Auf diese Weise ergibt sich eine parallele Anordnung von Strömungsbereichen mit gleicher Strömungsrichtung. Benachbarte Plattenzwischenräume werden von unterschiedlichen Wärmetauschermedien in entgegengesetzten Richtungen durchströmt, also im Gegenstrom. Hierdurch ergibt sich eine parallele Anordnung von Strömungsbereichen mit entgegengesetzten Strömungsrichtungen.Every second plate gap in the stack of plates is flowed through by the same heat exchange medium in the same direction, ie in DC. In this way results in a parallel arrangement of flow areas with the same flow direction. Adjacent plate interstices are flowed through by different heat exchange media in opposite directions, ie in countercurrent. This results in a parallel arrangement of flow regions with opposite flow directions.
Bevorzugt sind die Platten des Stapels gleichgroß. Die Platten werden bevorzugt mit einer rechteckige Form verwendet.Preferably, the plates of the stack are the same size. The plates are preferably used with a rectangular shape.
Es ist bekannt, daß laminare Strömungen extrem druckverlustarm fließen. Allerdings tauschen laminar fließende Strömungen in weiten Plattenabständen auch schlecht ihre Wärme mit den Oberflächen, an denen sie entlangfließen, weil sich ruhende Grenzschichten ausbilden. Wenn beim Plattenwärmetauscher der Plattenabstand ständig verkleinert wird, werden im selben Maß auch die ruhenden Fluid-Grenzschichten dünner. Die Strömung bleibt selbst bei sehr hohen Fließgeschwindigkeiten noch absolut laminar und der Druckverlust relativ klein.It is known that laminar flows flow extremely low pressure loss. However, laminar-flowing currents at wide plate intervals also poorly exchange their heat with the surfaces along which they flow because dormant boundary layers form. If the plate distance is constantly reduced in the plate heat exchanger, the dormant fluid boundary layers are thinner to the same extent. The flow remains absolutely laminar even at very high flow rates and the pressure loss is relatively small.
Wenn die Strömung des Wärmetauschermediens (vgl. beispielsweise DE 198 58 652 A1) zwischen zwei Platten aufgrund des dreidimensionalen Wellenrasters völlig turbulent von einer Ecke des Plattenzwischenraums zur anderen fließt, geschieht dies mit einem bis zu 1000-fachen Druckabfall, als wenn derselbe Volumenstrom zwischen zwei völlig ebenen und glatten Platten derselben Größe mit demselben Plattenabstand völlig laminar erfolgen würde. Die Wärmeübertragung vom laminar fließenden Wärmetauschermedium auf die ebene Platte ist bei gleichem Plattenabstand schlechter als vom turbulent fließenden auf die gewellte Platte. Der Druckverlust der turbulenten Strömung zwischen den gewellten Platten ändert sich umgekehrt proportional etwa mit der fünften Potenz des Plattenabstandes, der Druckverlust der laminaren Strömung zwischen den ebenen und glatten Platten nur mit der dritten Potenz.If the flow of the heat exchanger media (see, for example, DE 198 58 652 A1) flows completely turbulently between two plates due to the three-dimensional wave raster from one corner of the plate gap to the other, this is done with an up to 1000-fold pressure drop, as if the same volume flow between two completely flat and smooth plates of the same size would be made completely laminar with the same plate spacing. The heat transfer from the laminar heat exchange medium to the flat plate is worse at the same plate spacing than from the turbulent flowing to the corrugated plate. The pressure loss of the turbulent flow between the corrugated plates changes inversely proportionally to about the fifth power of the disk spacing, the laminar flow pressure loss between the even and smooth disks only to the third power.
Wird der Abstand zwischen ebenen und glatten Platten so sehr verringert, daß sich bei gleichem Volumenstrom ein gleiches Wärmeübertragungsvermögen einstellt, dann beträgt der hierbei auftretende Druckverlust immer noch nur einen Bruchteil des Druckverlustes der turbulenten Strömung zwischen den gewellten Platten. Wird der Abstand zwischen den völlig ebenen und glatten Platten so sehr verringert, daß sich bei gleichem Volumenstrom ein gleicher Druckverlust wie bei der turbulenten Strömung zwischen den gewellten Platten einstellt, dann beträgt das Wärmeübertragungsvermögen der laminaren Strömung hier ein Vielfaches der turbulenten.If the distance between flat and smooth plates is reduced so much that sets an equal heat transfer capacity at the same volume flow, then the pressure loss occurring here is still only a fraction of the pressure loss of the turbulent flow between the corrugated plates. If the distance between the completely flat and smooth plates is reduced so much that at the same volume flow an equal pressure drop as in the turbulent flow between the corrugated plates sets, then the heat transfer capacity of the laminar flow is here many times the turbulent.
In Anwendung dieser Sachverhalte sind bei Verwendung von ebenen und glatten Platten Plattenwärmetauscher ermöglicht, die trotz sehr geringer Druckverluste eine viel höhere Wärmeübertragungsdichte aufweisen, als dies bei bekannten, auf turbulente Strömungen abzielenden Wärmetauschern möglich ist. Allerdings sind dazu so kleine Plattenabstände notwendig, daß Verunreinigungen, Schwebstoffe oder die Oberflächen adhäsiv verändernde Chemikalien in den Wärmetauschermedien den Wärmetauscher zusetzen können. Deshalb ist die Anwendung auf klare, reine oder zumindest gefilterte Wärmetauschermedien begrenzt.In application of these facts plate heat exchangers are possible when using flat and smooth plates, which despite very low pressure losses have a much higher heat transfer density than is possible with known, aimed at turbulent flows heat exchangers. However, so small plate spacings are necessary that impurities, suspended solids or the surfaces adhesively changing chemicals in the heat exchange media can enforce the heat exchanger. Therefore, the application is limited to clear, pure or at least filtered heat exchange media.
Überall dort jedoch, wo diese Wärmetauscher anwendbar sind, können mit dem erfindungsgemäßen Plattenwärmetauscher gegenüber üblichen Plattenwärmetauschern viel Material, Platz und Förderenergie gespart werden.Wherever these heat exchangers are applicable, however, much material, space and conveying energy can be saved with the plate heat exchanger according to the invention in comparison with conventional plate heat exchangers.
Zweckmäßig kann bei einer Weiterbildung der Erfindung vorgesehen sein, daß die Verteilkanäle und / oder die Sammelkanäle einen kreisrunden Querschnitt aufweisen.Appropriately, it may be provided in a development of the invention that the distribution channels and / or the collecting channels have a circular cross-section.
Eine vorteilhafte Ausgestaltung der Erfindung sieht vor, daß die Verteilkanäle und / oder die Sammelkanäle als in einer Hauptfließrichtung ausgerichtete Langlöcher ausgeführt sind.An advantageous embodiment of the invention provides that the distribution channels and / or the collecting ducts are designed as aligned in a main direction of flow slots.
Bei einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, daß die Sammelkanäle und die Verteilkanäle die gleiche Form aufweisen.In a preferred embodiment of the invention it is provided that the collecting ducts and the distribution channels have the same shape.
Zweckmäßig kann bei einer Weiterbildung der Erfindung vorgesehen sein, daß die Sammelkanäle einen größeren hydraulischen Durchmesser aufweisen als die Verteilkanäle.Appropriately may be provided in a development of the invention that the collecting ducts have a larger hydraulic diameter than the distribution channels.
Eine vorteilhafte Ausgestaltung der Erfindung sieht vor, daß die Verteilung des mindestens einen der Wärmetauschermedien in die zugeordneten Plattenzwischenräume und dessen Sammlung aus den Plattenzwischenräumen über eine erzwungene, einen Fließquerschnitt verengende Umlenkung bis an den äußersten Plattenrand erfolgt, an dem der Eintritt in die /Austritt aus den freien Plattenzwischenräumen erfolgt.An advantageous embodiment of the invention provides that the distribution of the at least one of the heat exchange media in the associated plate interspaces and its collection from the plate interspaces via a forced, a flow cross-section narrowing deflection takes place up to the extreme edge of the plate at which the entry into the / outlet from takes place the free disc spaces.
Vorteilhaft ist bei einer Fortbildung der Erfindung vorgesehen, daß zur druckfesten, statischen Fixierung paarweise benachbarter Platten Berührungspunkte als Zug- und Druckanker, deren Oberfläche minimiert und Druckverhältnissen beider Wärmetauschermedien angepaßt ist, in die Platten einprofiliert sind.Advantageous is provided in a development of the invention that for pressure-resistant, static fixation of pairs adjacent plates touch points as tension and pressure anchors whose surface is minimized and pressure ratios of both heat exchanger media is adapted, are profiled into the plates.
Bei einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, daß die Zug- und Druckanker in Linien parallel zur Fließrichtung und symmetrisch zu den Verteilkanälen und den Sammelkanälen angeordnet sind.In a preferred embodiment of the invention it is provided that the tension and pressure anchors are arranged in lines parallel to the flow direction and symmetrical to the distribution channels and the collecting channels.
Zweckmäßig kann bei einer Weiterbildung der Erfindung vorgesehen sein, daß die Zug- und Druckanker in gleichmäßigen Abständen angeordnet sind.Appropriately may be provided in a development of the invention that the tension and pressure anchors are arranged at regular intervals.
Zweckmäßig kann bei einer Weiterbildung der Erfindung vorgesehen sein, daß die Plattenabstände für beide Wärmetauschermedien gleich sind.Appropriately, it may be provided in a development of the invention that the plate spacings are the same for both heat exchanger media.
Bei einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, daß die Plattenabstände für beide Wärmetauschermedien verschieden sind.In a preferred embodiment of the invention it is provided that the plate spacings are different for both heat exchanger media.
Vorteilhaft ist bei einer Fortbildung der Erfindung vorgesehen, daß alle Plattenränder geschlossen sind und daß sowohl die Verteilung als auch die Sammlung der Wärmetauschermedien in benachbarten Plattenzwischenräumen über die Verteilkanäle und die Sammelkanäle erfolgt.Advantageously, it is provided in a development of the invention that all plate edges are closed and that both the distribution and the collection of heat exchange media takes place in adjacent plate interspaces via the distribution channels and the collecting channels.
Bei einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, daß für jeden zweiten Plattenzwischenraum die beiden Plattenenden, die von den Verteilkanälen / Sammelkanälen der Nachbar-Plattenzwischenräume durchdrungen werden, offen sind und daß das in diesen Plattenzwischenräumen fließende Wärmetauschermedium über diese Öffnungen direkt in den Stapel von Platten ein- und austritt, wobei diese Plattenzwischenräume frei von eigenen Verteilkanälen / Sammelkanälen sind.In a preferred embodiment of the invention it is provided that for each second plate interspace the two plate ends penetrated by the distribution channels / collection channels of the adjacent plate interspaces are open and that the heat exchange medium flowing in these plate interspaces, via these openings, directly into the stack of plates enters and exits, these plate interstices are free of their own distribution channels / collection channels.
Zweckmäßig kann bei einer Weiterbildung der Erfindung vorgesehen sein, daß für jeden zweiten Plattenzwischenraum ein Plattenende, welches von den Sammelkanälen / Verteilkanälen der Nachbar-Plattenzwischenräume durchdrungen wird, offen ist und daß das in diesen Plattenzwischenräumen fließende Wärmetauschermedium über diese Öffnungen aus dem Stapel von Platten ein- / austritt, wobei diese Plattenzwischenräume an diesem Plattenende ohne Verteil- / Sammelkanälen gebildet sind, während sie am anderen Plattenende geschlossen sind, wohingegen am anderen Plattenende die Nachbar-Plattenzwischenräume offen und ohne Verteilkanäle / Sammelkanäle ausgeführt sind.Conveniently, it may be provided in a further development of the invention that for each second plate interspace, a plate end, which is penetrated by the collecting channels / distribution channels of the adjacent plate interspaces, is open and that the heat exchange medium flowing in these plate interspaces via these openings from the stack of plates These plate interspaces are formed at this plate end without distribution / collection channels, while they are closed at the other end of the plate, whereas at the other end of the plate the adjacent plate interstices are open and without distribution channels / collection channels.
Die Erfindung wird im folgenden anhand eines bevorzugten Ausführungsform unter Bezugnahme auf Figuren einer Zeichnung näher erläutert. Hierbei zeigen:
- Fig. 1
- eine schematische Darstellung eines Plattenwärmetauschers mit einem Stapel von Platten;
- Fig. 2
- eine Schnittdarstellung des Plattenwärmetauschers nach Fig. 1 entlang einer Linie AA;
- Fig. 3
- eine Schnittdarstellung des Plattenwärmetauschers nach Fig. 1 entlang einer Linie BB;
- Fig. 4
- eine Schnittdarstellung des Plattenwärmetauschers nach Fig. 1 entlang einer Linie CC; und
- Fig. 5
- eine Schnittdarstellung des Plattenwärmetauschers nach Fig. 1 entlang einer Linie DD.
- Fig. 1
- a schematic representation of a plate heat exchanger with a stack of plates;
- Fig. 2
- a sectional view of the plate heat exchanger of Figure 1 along a line AA.
- Fig. 3
- a sectional view of the plate heat exchanger of Figure 1 along a line BB.
- Fig. 4
- a sectional view of the plate heat exchanger of Figure 1 taken along a line CC ..; and
- Fig. 5
- a sectional view of the plate heat exchanger of FIG. 1 along a line DD.
Fig. 1 zeigte eine schematische Darstellung eines Plattenwärmetauschers mit einem Stapel von Platten 1. Plattenzwischenräume zwischen den Platten 1 werden von Wärmetauschermedien durchströmt. Jeder zweite Plattenzwischenraum wird von demselben Wärmetauschermedium in gleicher Richtung durchströmt, also im Gleichstrom. Auf diese Weise ergibt sich eine parallele Anordnung von Strömungsbereichen mit gleicher Strömungsrichtung. Benachbarte Plattenzwischenräume werden von unterschiedlichen Wärmetauschermedien in entgegengesetzten Richtungen durchströmt, also im Gegenstrom. Hierdurch ergibt sich eine parallele Anordnung von Strömungsbereichen mit entgegengesetzten Strömungsrichtungen.Fig. 1 shows a schematic representation of a plate heat exchanger with a stack of
Um platzsparend das Wärmetauschermedium gleichmäßig in zugeordnete Plattenzwischenräume zwischen die Platten 1 zu verteilen, sind mehrere parallele Verteilkanäle 3 vorgesehen, die senkrecht durch den Stapel führen und nur in die jeweils zugeordnete Plattenzwischenräume hinein eine Öffnung aufweisen, vorzugsweise in Form eines Spalts. Analoges gilt für die Sammlung des Wärmetauschermediums in Sammelkanälen 4 nach dem Wärmetausch.
Die Verteil- und die Sammelkanäle 3, 4 sind um so kleiner, je mehr es sind, und natürlich auch kleiner, als nur ein einziger Kanal in einer Ecke des Stapels sein müßte. Bevorzugt sind die Verteil- und die Sammelkanäle 3, 4 länglich ausgeführt, um die Verringerung des Strömungsquerschnitts im benachbarten Plattenzwischenraum zu minimieren.In order to space-effectively distribute the heat exchange medium in allocated plate interspaces between the
The distribution and
Die Form der Sammelkanäle 4, insbesondere hinsichtlich der Querschnittsgestaltung, ist bevorzugt nicht gleich der Form der Verteilkanäle 3. Zweckmäßig weisen die Sammelkanäle 4 einen größeren hydraulischen Durchmesser auf als die Verteilkanäle 3, um eine möglichst gleichmäßige Fließgeschwindigkeitsverteilung in den Spalten und minimale Druckverluste bei der Verteilung und Sammlung zu erzielen.The shape of the collecting
Mittels Leit- und Umlenkvorrichtungen 5 wird unmittelbar an den Kanälen dafür gesorgt, daß das Wärmetauschermedium im Plattenzwischenraum stets entlang der gesamten Plattenlänge von einem Plattenrand zum anderen fließt und nicht von Kanalaustritt zu Kanaleintritt auch einen kürzeren Weg findet.By means of guiding and deflection devices 5 is provided directly to the channels that the heat exchange medium always flows in the plate gap along the entire plate length from one plate edge to another and not from channel exit to channel entry also finds a shorter way.
Es kann vorgesehen sein, den Abstand zwischen den ebenen und glatten Platten 1 für beide Wärmetauschermedien verschieden zu wählen (vgl. Bezugszeichen 2a, 2b in den Fig. 2 bis 5), um verschiedenen physikalischen Eigenschaften beider Wärmetauschermedien bzw. um ganz allgemein den unterschiedlichen Anforderungen an den Druckverlust gerecht werden zu können.It can be provided to choose the distance between the flat and
Um auch dem statischen Druck beider Wärmetauschermedien standhalten zu können, sind die Platten 1 gegeneinander abgestützt. Damit diese Abstützungen die laminare Strömung des Wärmetauschermediums möglichst wenig stören, werden sie in der Zahl minimiert, punktförmig ausgeführt und in Linien entlang der Fließrichtung angeordnet (vgl. Bezugszeichen 6a, 6b in Fig. 1 und 5). Die Punktform ist statisch vorteilhafter als eine Linienform.In order to withstand the static pressure of both heat exchanger media, the
Eine andere vorteilhafte Möglichkeit, das Wärmeträgermedium gleichmäßig zwischen die Platten 1 zu verteilen, besteht darin, auf maximal zwei senkrechte Kanäle innerhalb des Stapels von Platten zu verzichten und es von außerhalb der Plattenzwischenräume in diese hinein- oder aus diesen herausfließen zu lassen (vgl. Bezugszeichen 8, 9, 10 in Fig. 1). Die Vorteile bestehen in einer besseren Flächennutzung der Platten 1 und in der Vermeidung der mit der Verteilung / Sammlung verbundenen zusätzlichen Druckverluste. Eine besonders vorteilhafte Variante liegt dann vor, wenn beide Enden des Plattenwärmetauschers in ein und dasselbe Wärmetauschermedium getaucht sind, für dieses Wärmetauschermedium keine Kanäle aufweisen, außerhalb des Wärmetauschers hydraulisch nochmals miteinander verbunden sind und einen Höhenunterschied aufweisen (8). Dann kann dieses Wärmetauschermedium aufgrund des besonders geringen Druckverlustes allein durch die Schwerkraft zirkulieren, sobald über das andere Wärmetauschermedium Wärme zugeführt oder entzogen wird.Another advantageous possibility to distribute the heat transfer medium evenly between the
Die in der vorstehenden Beschreibung, den Ansprüchen und der Zeichnung offenbarten Merkmale der Erfindung können sowohl einzeln als auch in beliebiger Kombination für die Verwirklichung der Erfindung in ihren verschiedenen Ausführungsformen von Bedeutung sein.The features of the invention disclosed in the foregoing description, in the claims and in the drawing may be of importance both individually and in any combination for the realization of the invention in its various embodiments.
Claims (14)
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102005002432A DE102005002432B3 (en) | 2005-01-19 | 2005-01-19 | Lamina-flow plate heat exchanger for space heating has one or both heat exchange media distributed between plates via distribution channels |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1691158A1 true EP1691158A1 (en) | 2006-08-16 |
| EP1691158B1 EP1691158B1 (en) | 2008-11-26 |
Family
ID=36089144
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP06001162A Not-in-force EP1691158B1 (en) | 2005-01-19 | 2006-01-19 | Plate heat exchanger |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1691158B1 (en) |
| AT (1) | ATE415606T1 (en) |
| DE (2) | DE102005002432B3 (en) |
| ES (1) | ES2322385T3 (en) |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2323119A1 (en) | 1975-09-02 | 1977-04-01 | Parca Norrahammar Ab | Stacked plate heat exchanger - has plates pressed and stamped with helical dividing walls and mating projections |
| US4335782A (en) * | 1974-07-01 | 1982-06-22 | The Garrett Corporation | Heat exchanger method |
| DE3339932A1 (en) | 1983-11-04 | 1985-05-15 | Bayer Ag, 5090 Leverkusen | Gap-type heat exchanger having webs |
| EP0611941A2 (en) | 1993-02-19 | 1994-08-24 | GIANNONI S.r.l. | A plate-type heat exchanger and related plates |
| DE69316990T2 (en) | 1992-11-05 | 1998-08-20 | Level Energietech Bv | HEAT EXCHANGER |
| DE19858652A1 (en) | 1997-12-19 | 1999-06-24 | Swep International Ab | Plate heat exchanger |
| DE19758567C2 (en) | 1997-11-28 | 2003-11-13 | Gerhard Luther | Laminar flat finned heat exchanger |
| US20040011514A1 (en) * | 2000-05-19 | 2004-01-22 | Holm Karl Martin | Plate pack, flow distribution device and plate heat exchanger |
| WO2004099696A1 (en) * | 2003-05-06 | 2004-11-18 | Meggitt (Uk) Ltd | Heat exchanger core |
| EP1484567A2 (en) * | 2000-06-23 | 2004-12-08 | Dana Canada Corporation | Heat exchanger with parallel flowing fluids |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6893619B1 (en) * | 2000-09-13 | 2005-05-17 | Ford Global Technologies, Llc | Plate-frame heat exchange reactor with serial cross-flow geometry |
| JP2005516171A (en) * | 2001-06-06 | 2005-06-02 | バッテル・メモリアル・インスティチュート | Fluid processing apparatus and method |
-
2005
- 2005-01-19 DE DE102005002432A patent/DE102005002432B3/en not_active Expired - Fee Related
-
2006
- 2006-01-19 DE DE502006002150T patent/DE502006002150D1/en not_active Expired - Fee Related
- 2006-01-19 EP EP06001162A patent/EP1691158B1/en not_active Not-in-force
- 2006-01-19 AT AT06001162T patent/ATE415606T1/en not_active IP Right Cessation
- 2006-01-19 ES ES06001162T patent/ES2322385T3/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4335782A (en) * | 1974-07-01 | 1982-06-22 | The Garrett Corporation | Heat exchanger method |
| FR2323119A1 (en) | 1975-09-02 | 1977-04-01 | Parca Norrahammar Ab | Stacked plate heat exchanger - has plates pressed and stamped with helical dividing walls and mating projections |
| DE3339932A1 (en) | 1983-11-04 | 1985-05-15 | Bayer Ag, 5090 Leverkusen | Gap-type heat exchanger having webs |
| DE69316990T2 (en) | 1992-11-05 | 1998-08-20 | Level Energietech Bv | HEAT EXCHANGER |
| EP0611941A2 (en) | 1993-02-19 | 1994-08-24 | GIANNONI S.r.l. | A plate-type heat exchanger and related plates |
| DE69422207T2 (en) | 1993-02-19 | 2000-06-21 | Giannoni S P A | Plate heat exchangers and corresponding plates |
| DE19758567C2 (en) | 1997-11-28 | 2003-11-13 | Gerhard Luther | Laminar flat finned heat exchanger |
| DE19858652A1 (en) | 1997-12-19 | 1999-06-24 | Swep International Ab | Plate heat exchanger |
| US20040011514A1 (en) * | 2000-05-19 | 2004-01-22 | Holm Karl Martin | Plate pack, flow distribution device and plate heat exchanger |
| EP1484567A2 (en) * | 2000-06-23 | 2004-12-08 | Dana Canada Corporation | Heat exchanger with parallel flowing fluids |
| WO2004099696A1 (en) * | 2003-05-06 | 2004-11-18 | Meggitt (Uk) Ltd | Heat exchanger core |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102005002432B3 (en) | 2006-04-13 |
| EP1691158B1 (en) | 2008-11-26 |
| ATE415606T1 (en) | 2008-12-15 |
| ES2322385T3 (en) | 2009-06-19 |
| DE502006002150D1 (en) | 2009-01-08 |
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