EP0177904B1 - Device for exchange of heat between two gases conducted in cross-flow to each other - Google Patents

Device for exchange of heat between two gases conducted in cross-flow to each other Download PDF

Info

Publication number
EP0177904B1
EP0177904B1 EP85112570A EP85112570A EP0177904B1 EP 0177904 B1 EP0177904 B1 EP 0177904B1 EP 85112570 A EP85112570 A EP 85112570A EP 85112570 A EP85112570 A EP 85112570A EP 0177904 B1 EP0177904 B1 EP 0177904B1
Authority
EP
European Patent Office
Prior art keywords
gas
channels
circular ring
plates
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP85112570A
Other languages
German (de)
French (fr)
Other versions
EP0177904A2 (en
EP0177904A3 (en
Inventor
Horst Daschmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Balcke Duerr AG
Original Assignee
Balcke Duerr AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Balcke Duerr AG filed Critical Balcke Duerr AG
Priority to AT85112570T priority Critical patent/ATE50861T1/en
Publication of EP0177904A2 publication Critical patent/EP0177904A2/en
Publication of EP0177904A3 publication Critical patent/EP0177904A3/en
Application granted granted Critical
Publication of EP0177904B1 publication Critical patent/EP0177904B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • F28D9/0018—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 apparatus having an annular form without any annular circulation of the heat exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

Definitions

  • the invention relates to a device for exchanging the heat between two gases which are conducted in cross-flow with one another, preferably for reheating cleaned flue gases behind flue gas desulfurization systems, with a plurality of flow channels arranged approximately parallel to one another, the partitions of which on one side with the heat-emitting and on the other side with the acted upon by heat-absorbing gas and are arranged in a circular ring so that the flow channels are alternately flowed through in the axial and radial directions.
  • DE-B-23 42 173 also shows a plate heat exchanger with plates arranged in a ring.
  • the known plate heat exchangers have the disadvantage that on the one hand they have a large construction volume and on the other hand that their flow channels are very difficult to access and are therefore difficult to clean.
  • the invention has for its object to develop a device of the type described in such a way that a gas pressure resulting in a small pressure loss is achieved while reducing the dimensions and the possibility of cleaning the channels is improved.
  • the solution to this problem by the invention is characterized in that the axially through-flow channels are connected to at least one supply line or discharge line for the one gas by means of an end-face hood and the radially through-flow channels are connected via an external annular channel provided with at least one connecting piece and Are connected via a central tube through one of the hoods with the supply or discharge of the other gas.
  • the circular ring with the flow channels is arranged with a vertical longitudinal central axis and the device is mounted on supports. This results in a compact structural unit that can be easily installed on foundations to be erected on site.
  • the flow channels are formed by plates.
  • the plates arranged approximately radially in the annulus are aligned with their surfaces approximately parallel to the longitudinal center axis of the annulus. This results in flow channels that run perpendicularly and parallel to the vertical longitudinal axis of the device and that run horizontally and radially to the longitudinal axis of the device, which can be cleaned in a simple manner.
  • the plates can also be oriented with their surface perpendicular to the longitudinal center axis of the annulus, the plates being provided with the flow channels for the openings forming a gas. In this embodiment, the ratio of the flow cross-sections for the channels through which a gas flows can be changed in a simple manner by design and number of openings.
  • the radially flowed channels in the axial direction of the annulus can be divided by partition plates into a plurality of channel sections through which flow flows in opposite directions, of which one channel section opens into the ring channel and the other channel sections are connected to one another via deflection chambers.
  • the gas flows involved in the heat exchange are no longer conducted in a simple cross flow but in a cross counter flow. This is particularly advantageous for smaller quantities of gas for the purpose of enlarging the heat exchange surface while maintaining a compact design.
  • the invention proposes the plates arranged in the annulus. to divide into several sections in the radial direction of the annulus. This results not only in a simpler manufacture and assembly of the plates, but also in an enlargement of the heat exchanger area and an improvement in the flow conditions, because a larger number of plate sections can be accommodated by dividing the plates into individual plate sections on the outer parts of the annulus. Despite the increasing cross-sectional area in the radial direction, the dimensions of the individual flow channels can be kept approximately the same.
  • the invention further proposes that in the radial direction to form channels through which the annulus flows by plates arranged parallel to one another and to form the channels through which flow in the axial direction of the annulus by plates extending at an acute angle to one another.
  • this embodiment results in a triangular flow cross section for the channels through which flow is in the axial direction, it avoids changes in the channel cross section in the flow direction.
  • the flow channels are formed by tubes which extend between perforated plates arranged parallel to one another. These perforated plates each form the radially outer or radially inner end of the heat exchange surface. By manufacturing them using pipes, there is a cheaper way to manufacture them in individual cases.
  • this alternative embodiment is particularly well suited for high pressure differences between the two gases participating in the heat exchange.
  • the pipes arranged between the perforated plates can have a constant flow cross-section over their entire pipe length. According to a further feature, however, they can also have a smaller flow cross section in the region of the radially inner perforated plate than in the region of the radially outer perforated plate. In the case of a radially outward flow direction, this results in an increasing flow cross section of the tubes, as a result of which the increase in volume resulting from the heating of the gas can be at least partially compensated for in such a way that no significant increase in the flow velocity occurs.
  • the flow channels according to the invention can also be formed by plate pairs, which are connected to one another in a gas-tight manner at least at the edges and, through a corresponding shaping, form tubular flow channels.
  • the flow cross section of the channels in the flow direction of the gas can be chosen relatively freely.
  • the heat exchanger illustrated by means of an exemplary embodiment can be used for heating or cooling gases, the heat exchange taking place between two gases G1 and G2 which are guided in cross-flow with one another.
  • the heat exchanger is mainly used as an air preheater in the power plant area or as a heat exchanger in wet desulphurization and denitrification plants, the flue gas being heated up after the flue gas desulfurization system and heated up after the flue gas desulfurization system and after the Ent embroidery is cooled before being introduced into the flue gas fireplace.
  • Other areas of application are waste heat and heat recovery systems in various industrial sectors.
  • the heat exchange takes place between a plurality of flow channels arranged approximately parallel to one another, which are arranged in a circular ring 1.
  • the longitudinal central axis 1a of the circular ring 1 extends in the vertical direction.
  • the circular ring 1 is surrounded by a housing which comprises a lower hood 2, which covers one end face of the circular ring 1, and an upper hood 3, which covers the other end face of the circular ring 1.
  • the cylindrical circumference of the circular ring 1 is surrounded by an annular channel 4 which, in the exemplary embodiment, has two connecting pieces 4a lying opposite one another.
  • the inside of the circular ring 1 is connected to a vertical central tube 5, which is closed at its lower end by a cover 5a and protrudes from the hood 3 with its upper end.
  • this hood 3 is in turn provided with two connection pieces 3a lying opposite one another, whereas the lower cover 2 has a central connection piece 2a pointing downward.
  • the gas G1 to be heated which is, for example, a purified gas coming from a flue gas desulfurization system, enters the upper hood 3 centrally from above. It flows downward in the central tube 5 and, after a deflection, comes from the inside into the circular ring 1, which is divided into individual flow channels by a plurality of plates arranged approximately parallel to one another.
  • the plates 6 are aligned in the vertical direction in accordance with the illustration in FIG. 2. They are radial in circular ring 1, so that their surfaces run parallel to the longitudinal central axis 1 a of circular ring 1. In each case two adjacent plates 6 form a flow channel 7a or 7r, the flow channel 7a in the axial direction of the circular ring 1 and the flow channel 7r in the radial direction of the circular ring 1 being flowed through by the gas G1 to be warmed up or by the heat-emitting gas G2.
  • Figures 3 to 5 show that adjacent plates 6 to form an axial flow channel 7a on the outer and inner circumference of the annulus 1 are connected by strip-shaped connectors 8a, whereas the radial flow channels 7r are connected by adjacent plates 6 and connectors 8b are formed, which are each arranged in the manner of a strip in the end faces of the circular ring 1.
  • the warmed gas G1 is removed from the ring channel 4 through the connection piece 4a from the heat exchanger and, for example, fed to a flue gas chimney.
  • the heat-emitting gas G2 is supplied from below via the central connecting piece 2a to the lower hood 2 of the heat exchanger. Accordingly, it flows from below into the end face of the circular ring 1 formed by the plates 6 into the flow channels 7a running in the axial direction of the circular ring 1, as indicated by the arrows in FIG. 1. Via the surface of the plates 6, this gas G2 gives off part of its heat to the gas G1 to be heated, which flows in cross-flow to the gas G2. After the heat exchange, the gas G2 leaves the circular ring 1 on the upper end face and enters the upper hood 3, which is penetrated in the middle by the central tube 5. The cooled gas G2 finally comes out of the hood 3 via the connecting pieces 3a which are opposite one another. If it is a flue gas to be desulfurized, it is then fed to the flue gas desulfurization system.
  • FIG. 1 supports 9 are shown, through which the heat exchanger combined to form a unit is raised and can be placed on a local foundation.
  • the partial section in FIG. 1 further shows that a cleaning device 10 is arranged in both the upper hood 3 and in the central tube 5, with the aid of which the flow channels 7a and 7r can be cleaned.
  • These cleaning devices 10 are preferably designed to be movable, so that all flow channels 7a and 7r are cleaned in succession by one circulation of the cleaning devices 10.
  • the plates 6 can be arranged in the manner which can be seen in particular in FIG. 5.
  • This illustration shows that the channels 7r through which flow flows in the radial direction of the circular ring 1 are formed by plates 6 arranged parallel to one another. This results in a channel cross section that remains constant in the direction of flow.
  • the channels 7a through which the annular ring 1 flows in the axial direction are formed by plates 6 which run at an acute angle to one another. This results in an approximately triangular or trapezoidal flow cross-section of the channels 7a, but without the channel cross-section narrowing in the flow direction.
  • plates 11 are used which are aligned with their surface at right angles to the longitudinal central axis 1a of the circular ring 1, as can be seen in particular in FIG. 6. These plates 11 are provided with openings formed into tubular pieces 11 a, so that when adjacent plates 11 are joined together there are tubular flow channels 7 a which run at right angles to the flow channels 7 r which are formed by the plates 11.
  • flow channels 7a and 7r which run at right angles to one another, result with an axial or radial course of the flow direction with respect to the circular ring 1, the heat-exchanging surfaces again being formed by a plurality of plates 11 arranged approximately parallel to one another.
  • a segment-like section of these plates 11 arranged in the circular ring 1 is shown schematically in FIG. 6.
  • the plates 6 and 11 are preferably made of sheet metal. They can be protected against corrosion by enamelling. In addition, a combination of different materials is possible, so that non-metallic materials can also be used in the area of the dew point.
  • the cleaning devices 10 which are only indicated schematically, can be formed by steam blowers or other blowing devices with air or water.
  • the arrangement of the plates 6 and 11 in the circular ring 1 results in short plate lengths, so that the flow channels 7a and 7r formed thereby can be cleaned properly.
  • this design results in low flow resistances, so that the heat exchanger described above works with low pressure drops
  • FIG. 8 shows a modified embodiment of the heat exchanger, in which the plates aligned with their surface parallel to the longitudinal central axis 1a of the circular ring 1 are divided into two plate sections 6b and 6c. This results in larger ones. Dimensions of the circular ring 1 not only easier to manufacture and easier to assemble, but it also creates the possibility to accommodate a larger number of plate sections 6b on the outer part of the circular ring 1 than there are plate sections 6c on the inner part of the circular ring 1. In spite of the enlargement of the base area increasing in the radial direction, the flow cross sections of the individual flow channels 7a and 7r can be approximated in this way. As shown in FIG. 8, an annular gap is left between the plate sections 6b and 6c, so that there is a problem-free transition of the gas flowing through the plate sections 6c and 6b in the radial direction.
  • FIG. 9 shows a further modified embodiment of the heat exchanger, although its basic structure corresponds to that of the embodiment according to FIG. 1.
  • the plates 6, which in turn are aligned with their surface parallel to the longitudinal central axis 1a of the circular ring 1 and form axially continuous flow channels 7a, with respect to their radially flowed channels 7r through separating plates 12 into individual channel sections 1b, 1c, 1st divided.
  • the gas flow G1 introduced into the central tube 5 from above is conducted exclusively into the upper channel section 1b, through which it flows radially outwards.
  • the gases enter a deflection chamber 13a which is arranged on the outer circumference of the channel sections 1b and 1c.
  • the gases G1 are deflected and introduced radially from the outside into the channel section ic, which they consequently flow through with a radially inward flow direction.
  • the gases G1 arrive in a further deflection chamber 13b, which is designed in the manner of a tube piece and in the extension of the central tube 5, from which the deflection chamber 13b is separated by the cover 5a.
  • the gases C1 are also deflected in this deflection chamber 13b, so that they subsequently flow through the lowermost channel section 1d with the flow direction directed radially outward.
  • the gases G1 finally enter the ring channel 4, which they leave via the two connecting pieces 4a.
  • the flow channels are formed by individual tubes 14, which are arranged in the radial direction in the circular ring 1.
  • the radially inner ends of the tubes 14 open into a perforated plate 15i.
  • the radially outer ends of the tubes 14 are fastened to a perforated plate 15a.
  • These perforated plates 15a and 15i serve not only to secure the position of the pipes 14, but also to separate the gas G1 flowing through the pipes 14 from the gas G2, which flows through the circular ring 1 in the axial direction from bottom to top in accordance with the arrows shown in FIG. 10.
  • the perforated plates 15a and 15i of the tubes 14 combined into segments according to FIG. 10 are connected gas-tight to one another at the adjacent edges, preferably welded.
  • the tubes 14 arranged in the radial direction in the circular ring 1 with a constant flow cross-section, for example with a circular or oval cross-section
  • the flow cross-section of the tubes 14 increases in the flow direction, for example by the through to at least partially compensate for the increase in volume of the heating of the gas G1, so that there is no significant increase in the flow velocity.
  • the tubes 14, which in the initial state have a circular cross section are flattened at the radially inner end, as is evident from the openings in the perforated plate 15i in FIG. 10. This results in a smaller flow cross section at the radially inner end of the tubes 14 than at the radially outer end.
  • FIG. 11 shows another possible embodiment of the flow channels which effect the heat exchange.
  • pairs of plates 16a, 16b are used in each case, which form tube-like flow channels 16c between them.
  • the gas G1 flows through these flow channels 16c.
  • the gas G2 is conducted in cross flow between the plate pairs 16a, 16b.
  • the plates 16a and 16b of a pair of plates are connected to one another in a gas-tight manner at the edges running in the radial direction in the circular ring 1, preferably welded.
  • the plates 16a and 16b are provided with bends 16d, which thus take over the function of the perforated plates 15a and 15i in the embodiment according to FIG. 10, namely the radially inner and radially outer end of a segment of the heat exchange surface.
  • edges 16e projecting like strips are finally formed on the bends 16d, which are welded to one another and in this way result in a gas-tight seal.
  • tubular flow channels 16c can be matched to the respective application. As can be seen in FIG. 11, it is possible to offset the flow channels 16c formed by the individual plate pairs 16a, 16b in relation to the adjacent plate pair 16a, 16b in the flow direction of the gas G2. Such an offset is also possible in the embodiment according to FIG. 10 by appropriate arrangement of the tubes 14.

Abstract

1. Device for exchanging heat between two gases (G1, G2) which are conveyed in crossflow to one another, preferably for reheating scrubbed flue gases after flue gas desulphurizing plant, with a plurality of flow channels (7a, 7r) which are arranged approximately parallel to one another and the dividing walls of which are acted upon on one side by the heat-emitting gas and on the other by the heat-absorbing gas and are arranged in a circular ring (1) such that gas flows through the flow channels (7a, 7r) in the axial and in the radial direction in turn, characterised in that the channels (7a) through which gas flows axially are connected via a respective end hood (2, 3) to at least one supply line or discharge line for one gas (G2) and the channels (7r) through which gas flows radially are connected via an outer ring channel, which is provided with at least one connection sleeve (4a), and via a central tube (5), which extends through one of the hoods (3), to the supply line or discharge line for the other gas (G1).

Description

Die Erfindung betrifft eine Vorrichtung zum Austausch der Wärme zwischen zwei im Kreuzstrom zueinander geführten Gasen, vorzugsweise zur Wiederaufheizung gereinigter Rauchgase hinter Rauchgasentschwefelungsanlagen, mit einer Mehrzahl etwa parallel zueinander angeordneter Strömungskanäle, deren Trennwände auf der einen Seite mit dem wärmeabgebenden und auf der anderen Seite mit dem wärmeaufnehmenden Gas beaufschlagt und in einem Kreisring so angeordnet sind, daß die Strömungskanäle abwechselnd in axialer und radialer Richtung durchtrömt werden.The invention relates to a device for exchanging the heat between two gases which are conducted in cross-flow with one another, preferably for reheating cleaned flue gases behind flue gas desulfurization systems, with a plurality of flow channels arranged approximately parallel to one another, the partitions of which on one side with the heat-emitting and on the other side with the acted upon by heat-absorbing gas and are arranged in a circular ring so that the flow channels are alternately flowed through in the axial and radial directions.

Eine Vorrichtung der voranstehend beschriebenen Art ist aus der JP-A-52 28757 bekannt. Auch die DE-B-23 42 173 zeigt einen Plattenwärmeaustauscher mit ringförmig angeordneten Platten.A device of the type described above is known from JP-A-52 28757. DE-B-23 42 173 also shows a plate heat exchanger with plates arranged in a ring.

Die bekannten Plattenwärmeaustauscher besitzen den Nachteil, daß sie einerseits ein großes Bauvolumen aufweisen und daß ihre Strömungskanäle andererseits sehr schwer zugänglich und deshalb nur mit großem Aufwand zu reinigen sind.The known plate heat exchangers have the disadvantage that on the one hand they have a large construction volume and on the other hand that their flow channels are very difficult to access and are therefore difficult to clean.

Der Erfindung liegt die Aufgabe zugrunde, eine Vorrichtung der eingangs beschriebenen Art derart weiterzubilden, daß bei gleichzeitiger Verringerung der Abmessungen eine einen geringen Druckverlust zur Folge habende Gasführung erzielt und die Möglichkeit zur Reinigung der Kanäle verbessert wird.The invention has for its object to develop a device of the type described in such a way that a gas pressure resulting in a small pressure loss is achieved while reducing the dimensions and the possibility of cleaning the channels is improved.

Die Lösung dieser Aufgabenstellung durch die Erfindung ist dadurch gekennzeichnet, daß die axial durchströmten Kanäle durch jeweils eine stimseitige Haube an mindestens eine Zuleitung bzw. Ableitung für das eine Gas angeschlossen sind und die radial durchströmten Kanäle über einen außenliegenden, mit mindestens einem Anschlußstutzen versehenen Ringkanal sowie übber ein durch eine der Hauben geführtes Zentralrohr mit der Zuleitung bzw. Ableitung des anderen Gases verbunden sind.The solution to this problem by the invention is characterized in that the axially through-flow channels are connected to at least one supply line or discharge line for the one gas by means of an end-face hood and the radially through-flow channels are connected via an external annular channel provided with at least one connecting piece and Are connected via a central tube through one of the hoods with the supply or discharge of the other gas.

Mit diesem Vorschlag der Erfindung ergibt sich ein Wärmetauscher für zwei im Kreuzstrom zueinander geführte Gase, dessen Gasführungen nur geringe Druckverluste zur Folge haben, obwohl die Abmessungen des Wärmetauschers gegenüber denen bekannter Bauarten erheblich verkleinert werden konnten. Die Anordnung der Strömungskanäle auf einem Kreisring schafft darüber hinaus die Möglichkeit einer einfachen und wirkungsvollen Reinigung der Kanäle, so daß sich insgesamt der Bauaufwand für den Wärmetauscher verringert.With this proposal of the invention, there is a heat exchanger for two gases guided in cross flow to one another, the gas routing of which results in only slight pressure losses, although the dimensions of the heat exchanger could be reduced considerably compared to those of known designs. The arrangement of the flow channels on a circular ring also creates the possibility of a simple and effective cleaning of the channels, so that the overall construction costs for the heat exchanger are reduced.

Bei einer weiteren Ausgestaltung der Erfindung ist der Kreisring mit den Strömungskanälen mit senkrechter Längsmittelachse angeordnet und die Vorrichtung auf Stützen aufgeständert. Hierdurch ergibt sich eine kompakte Baueinheit, die auf einfache Weise auf ortsseitig zu errichtenden Fundamenten aufgestellt werden kann.In a further embodiment of the invention, the circular ring with the flow channels is arranged with a vertical longitudinal central axis and the device is mounted on supports. This results in a compact structural unit that can be easily installed on foundations to be erected on site.

Gemäß einem weiteren Merkmal der Erfindung sind die Strömungskanäle durch Platten gebildet. Bei einer bevorzugten Ausführungsform der Erfindung sind die etwa radial im Kreisring angeordneten Platten mit ihren Oberflächen etwa parallel zur Längsmittelachse des Kreisringes ausgerichtet. Auf diese Weise ergeben sich senkrecht und parallel zur senkrechten Längsachse der Vorrinchtung verlaufende sowie waagerecht und radial zur Längsachse der Vorrichtung verlaufende Strömungskanäle, die auf einfache Weise gereinigt werden können. Sei einem alternativen Vorschlag der Erfindung können die Platten mit ihrer Oberfläche auch rechtwinklig zur Längsmitteiachse des Kreisringes ausgerichtet sein, wobei die Platten mit die Strömungskanäle für das eine Gas bildenden Durchbrechungen versehen sind. Bei dieser Ausführungsform läßt sich durch Ausbildung und Anzahl der Durchbrechungen das Verhältnis der Strömungsquerschnitte für die jeweils von einem Gas durchflossenen Kanäle auf einfache Weise verändern.According to a further feature of the invention, the flow channels are formed by plates. In a preferred embodiment of the invention, the plates arranged approximately radially in the annulus are aligned with their surfaces approximately parallel to the longitudinal center axis of the annulus. This results in flow channels that run perpendicularly and parallel to the vertical longitudinal axis of the device and that run horizontally and radially to the longitudinal axis of the device, which can be cleaned in a simple manner. In an alternative proposal of the invention, the plates can also be oriented with their surface perpendicular to the longitudinal center axis of the annulus, the plates being provided with the flow channels for the openings forming a gas. In this embodiment, the ratio of the flow cross-sections for the channels through which a gas flows can be changed in a simple manner by design and number of openings.

Gemäß einem weiteren Merkmal der Erfindung können die radial durchströmten Kanäle in axialer Richtung des Kreisringes durch Trennbleche in mehrere gegenläufig durchströmte Kanalabschnitte unterteilt werden, von denen ein Kanalabschnitt im Ringkanal mündet und die anderen Kanalabschnitte über Umlenkkammern miteinander verbunden sind. Hierdurch werden die am Wärmeaustausch beteiligten Gasströme nicht mehr in einem einfachen Kreuzstrom, sondern in einem Kreuzgegenstrom geführt. Dies ist insbesondere bei kleineren Gasmengen zwecks Vergrö-Berund der Wärmeaustauschfläche unter Beibehaltung einer kompakten Bauweise von Vorteil.According to a further feature of the invention, the radially flowed channels in the axial direction of the annulus can be divided by partition plates into a plurality of channel sections through which flow flows in opposite directions, of which one channel section opens into the ring channel and the other channel sections are connected to one another via deflection chambers. As a result, the gas flows involved in the heat exchange are no longer conducted in a simple cross flow but in a cross counter flow. This is particularly advantageous for smaller quantities of gas for the purpose of enlarging the heat exchange surface while maintaining a compact design.

Bei größeren Abmessungen der Vorrichtung kann es Schwierigkeiten bereiten, die Platten mit Abmessungen herzustellen, welche den gesamten Querschnitt des Kreisringes ausfüllen. Zur Vermeidung dieser Schwierigkeiten wird mit der Erfindung vorgeschlagen, die im Kreisring angeordneten Platten. in radialer Richtung des Kreisringes in mehrere Abschnitte aufzuteilen. Hierdurch ergibt sich nicht nur eine einfachere Herstellung und Montage der Platten, sondern auch eine Vergrößerung der Wärmetauscherfläche und eine Verbesserung der Strömungsverhältnisse, weil durch die Aufteilung der Platten in einzelne Plattenabschnitte auf den weiter außenliegenden Teilen des Kreisringes eine größere Anzahl von Plattenabschnitten untergebracht werden kann. Trotz der in radialer Richtung nach außen zunehmenden Querschnittsfläche können auf dieser Weise die Abmessungen der einzelnen Strömungskanäle etwa gleich gehalten werden.With larger dimensions of the device, it can be difficult to produce the plates with dimensions that fill the entire cross section of the annulus. To avoid these difficulties, the invention proposes the plates arranged in the annulus. to divide into several sections in the radial direction of the annulus. This results not only in a simpler manufacture and assembly of the plates, but also in an enlargement of the heat exchanger area and an improvement in the flow conditions, because a larger number of plate sections can be accommodated by dividing the plates into individual plate sections on the outer parts of the annulus. Despite the increasing cross-sectional area in the radial direction, the dimensions of the individual flow channels can be kept approximately the same.

Um bei der Bildung der Strömungskanäle durch jeweils zwei nebeneinanderliegende und parallel zur Längsachse des Kreisringes ausgerichtete Platten Querschnittsverengungen der Kanäle in Strömungsrichtung des jeweiligen Gases zu vermeiden, die zu unerwünschten Druckverlusten führen können, wird mit der Erfindung weiterhin vorgeschlagen, die in radialer Richtung des Kreisringes durchströmten Kanäle durch parallel zueinander angeordnete Platten zu bilden und die in axialer Richtung des Kreisringes durchströmten Kanäle durch spitzwinklig zueinander verlaufende Platten zu bilden. Diese Ausführungsform ergibt zwar für die in axialer Richtung durchströmten Kanäle einen dreieckförmigen Strömungsquerschnitt, vermeidet jedoch Veränderungen des Kanalquerschnittes in Strömungsrichtung.In order to avoid cross-sectional constrictions of the channels in the flow direction of the respective gas when the flow channels are formed by two plates lying next to one another and aligned parallel to the longitudinal axis of the annulus, which can lead to undesirable pressure losses, the invention further proposes that in the radial direction to form channels through which the annulus flows by plates arranged parallel to one another and to form the channels through which flow in the axial direction of the annulus by plates extending at an acute angle to one another. Although this embodiment results in a triangular flow cross section for the channels through which flow is in the axial direction, it avoids changes in the channel cross section in the flow direction.

Bei einer alternativen Ausführungsform sind die Strömungskanäle durch Rohre gebildet, die sich zwischen parallel zueinander angeordneten Lochplatten erstrecken. Diese Lochplatten bilden jeweils den radial außenliegenden bzw. radial innenliegenden Abschluß der Wärmeaustauschfläche. Durch deren Herstellung unter Verwendung von Rohren ergibt sich im Einzelfall eine preiswertere Herstellmöglichkeit. Außerdem ist diese alternative Ausführungsform für hohe Druckdifferenzen zwischen den beiden am Wärmeaustausch teilnehmenden Gasen besonders gut geeignet.In an alternative embodiment, the flow channels are formed by tubes which extend between perforated plates arranged parallel to one another. These perforated plates each form the radially outer or radially inner end of the heat exchange surface. By manufacturing them using pipes, there is a cheaper way to manufacture them in individual cases. In addition, this alternative embodiment is particularly well suited for high pressure differences between the two gases participating in the heat exchange.

Die zwischen den Lochplatten angeordneten Rohre können über ihre gesamte Rohrlänge einen gleichbleidenden Strömungsquerschnitt haben. Sie können gemäß einem weiteren Merkmal aber auch im Bereich der radial innenliegenden Lochplatte einen kleineren Strömungsquerschnitt aufweisen als im Bereich der radial außenliegenden Lochplatte. Hierdurch ergibt sich bei einer radial nach außen gerichteten Strömungsrichtung ein zunehmender Strömungsquerschnitt der Rohre, wodurch die durch die Erwärmung des Gases entstehende Volumenvergrößerung zumindest teilweise so kompensiert werden kann, daß keine wesentliche Erhöhung der Strömungsgeschwindigkeit auftritt.The pipes arranged between the perforated plates can have a constant flow cross-section over their entire pipe length. According to a further feature, however, they can also have a smaller flow cross section in the region of the radially inner perforated plate than in the region of the radially outer perforated plate. In the case of a radially outward flow direction, this results in an increasing flow cross section of the tubes, as a result of which the increase in volume resulting from the heating of the gas can be at least partially compensated for in such a way that no significant increase in the flow velocity occurs.

Anstelle von einfachen Platten oder zwischen Lochblechen angeordneten Rohren können die erfindungsgemäßen Strömungskanäle auch durch Plattenpaare gebildet werden, die zumindest an den Rändern miteinander gasdicht verbunden sind und durch eine entsprechende Formgebung rohrartige Strömungskanäle bilden. Bei dieser Ausführungsform kann der Strömungsquerschnitt der Kanäle in Strömungsrichtung des Gases verhältnismäßig frei gewählt werden.Instead of simple plates or pipes arranged between perforated plates, the flow channels according to the invention can also be formed by plate pairs, which are connected to one another in a gas-tight manner at least at the edges and, through a corresponding shaping, form tubular flow channels. In this embodiment, the flow cross section of the channels in the flow direction of the gas can be chosen relatively freely.

Sowohl bei der Bildung der Strömungskanäle durch Rohre als auch bei der Verwendung von Strömungskanäle bildenden Platenpaaren besteht die Möglichkeit, die in radialer Richtung der Vorrichtung durchströmten Kanäle in nebeneinanderliegenden Reihen oder relativ zueinander versetzt anzuordnen bzw. auszubilden, so daß das in axialer Richtung der Vorrichtung strömende Gas hinsichtlich seines Strömungsverlaufes ebenfalls beeinflußt werden kann.Both when forming the flow channels through pipes and when using pairs of plates forming flow channels, there is the possibility of arranging or forming the channels through which flow in the radial direction of the device is arranged in adjacent rows or offset relative to one another, so that the flow in the axial direction of the device Gas can also be influenced in terms of its flow pattern.

Mit der Erfindung wird schließlich vorgeschlagen, im Bereich mindestens einer stimseitigen Haube eine Reinigunsvorrichtung für die in axialer Richtung des Kreisringes durchströmten Kanäle und im Bereich des Zentralrohres und/oder des Ringkanals eine weitere Reinigungsvorrichtung für die in radialer Richtung durchströmten Kanäle vorzusehen. Mit Hilfe dieser Reinigungsvorrichtungen können die Wärmetauschflächen der Profilhohlkörper und damit die Strömungskanäle zuverlässig gereinigt werden, wobei neben einer periodischen Reinigung - ggf. nach einer Abschaltung des Wärmetauschers - auch eine ständige Reinigung möglich ist.Finally, it is proposed with the invention to provide a cleaning device for the channels through which flow flows in the axial direction of the circular ring in the area of at least one front-side hood and a further cleaning device for the channels through which flow flows in the radial direction in the area of the central tube and / or the ring channel. With the help of these cleaning devices, the heat exchange surfaces of the hollow profile bodies and thus the flow channels can be reliably cleaned, and in addition to periodic cleaning - if necessary after switching off the heat exchanger - continuous cleaning is also possible.

Auf der Zeichnung sind verschiedene Ausführungsbeispiele des erfindungsgemäßen Wärmetauschers mit unterschiedlichen Ausführungen hinsichtlich der Plattenanordnung dargestellt, und zwar zeigen :

  • Fig. 1 eine hälftig im senkrechten Schnitt gezeichnete Seitenansicht des Wärmetauschers,
  • Fig. 2 eine Draufsicht auf den Wärmetauscher nach Fig. 1, wobei 1/4 des Wärmetauschers in einem waagerechten Schnitt dargestellt ist,
  • Fig. 3 eine perspektivische Ansicht einer aus mehreren Platten gebildeten Wärmeaustauschfläche, wobei die einzelnen Platten mit ihrer Oberfläche parallel zur Längsmittelachse des Kreisringes ausgerichtet sind,
  • Fig. 4 eine perspektivische Darstellung zweier nebeneinanderliegender, axial bzw. radial durchströmter Kanäle gemäß der Ausbildung nach Fig. 3,
  • Fig. 5 eine Draufsicht auf die Kanäle nach Fig. 4,
  • Fig. 6 eine der Fig. 3 entsprechende Darstellung einer zweiten Ausfünrungsform, bei der die einzelnen Platten rechtwinklig zur Längsachse des Kreisringes ausgerichtet und mit Durchbrechungen zur Bildung von Strömungskanälen versehen sind,
  • Fig. 7 eine Stimansicht einiger der Platten nach Fig. 6,
  • Fig. 8 eine der Fig. 2 entsprechende Darstellung einer weiteren Ausführungsform, bei der die einzelnen Platten in Plattenabschnitte unterteilt sind,
  • Fig. 9 eine der Fig. 1 entsprechende Darstellung einer abgewandelten Ausführungsform, bei der die Platten zur Schaffung eines Kreuzgegenstromes hinsichtlich ihrer radial durchströmten Strömungskanäle durch Trennbleche unterteilt sind,
  • Fig. 10 eine perspektivische Darstellung einer aus mehreren Rohren gebildeten Wärmeaustauschfläche und
  • Fig. 11 eine der Fig. 10 entsprechende Darstellung einer Wärmeaustauschfläche, bei der die Strömungskanäle durch Plattenpaare gebildet werden.
Various exemplary embodiments of the heat exchanger according to the invention with different designs with regard to the plate arrangement are shown in the drawing, namely:
  • 1 is a side view of the heat exchanger drawn in half in vertical section,
  • 2 is a plan view of the heat exchanger according to FIG. 1, 1/4 of the heat exchanger being shown in a horizontal section,
  • 3 is a perspective view of a heat exchange surface formed from a plurality of plates, the surface of the individual plates being aligned parallel to the longitudinal central axis of the annulus,
  • 4 is a perspective view of two adjacent, axially or radially flowed through channels according to the embodiment of FIG. 3,
  • 5 is a plan view of the channels of FIG. 4,
  • 6 shows a representation corresponding to FIG. 3 of a second embodiment, in which the individual plates are aligned at right angles to the longitudinal axis of the circular ring and are provided with openings to form flow channels,
  • 7 is a front view of some of the plates of FIG. 6,
  • 8 shows a representation corresponding to FIG. 2 of a further embodiment, in which the individual plates are divided into plate sections,
  • 9 shows a representation corresponding to FIG. 1 of a modified embodiment in which the plates are divided by separating plates with regard to their radially flowed flow channels in order to create a cross-counterflow,
  • 10 is a perspective view of a heat exchange surface formed from a plurality of tubes and
  • 11 shows a representation of a heat exchange surface corresponding to FIG. 10, in which the flow channels are formed by plate pairs.

Der anhand enes Ausführungsbeispiels dargestellte Wärmetauscher kann für die Aufheizung oder Abkülung von Gasen eingesetzt werden, wobei der Wärmeaustausch zwischen zwei im Kreuzstrom zueinander geführten Gasen G1 und G2 erfolgt. Hauptsächlich wird der Wärmetauscher eingesetzt als Luftvorwärmer im Kraftwerksbereich oder als Wärmetauscher in Naßentschwefelungs- und Entstickungsantagen, wobei das Rauchgas nach der Rauchgasentschwefelungsanlage aufgeheizt und nach der Rauchgasentschwefelungsanlage aufgeheizt und nach der Entstickung vor Einleitung in den Rauchgaskamin abgekühlt wird. Weitere Anwendungsgebiete sind Abwärme- bzw. Wärmerückgewinnungsanlagen in verschiedenen Industriebereichen.The heat exchanger illustrated by means of an exemplary embodiment can be used for heating or cooling gases, the heat exchange taking place between two gases G1 and G2 which are guided in cross-flow with one another. The heat exchanger is mainly used as an air preheater in the power plant area or as a heat exchanger in wet desulphurization and denitrification plants, the flue gas being heated up after the flue gas desulfurization system and heated up after the flue gas desulfurization system and after the Ent embroidery is cooled before being introduced into the flue gas fireplace. Other areas of application are waste heat and heat recovery systems in various industrial sectors.

Der Wärmeaustausch erfolgt zwischen einer Mehrzahl etwa parallel zueinander angeordneter Strömungskanälen, die in einem Kreisring 1 angeordnet sind. Beim Ausführungsbeispiel nach den Figuren 1 und 2 verläuft die Längsmittelachse 1a des Kreisringes 1 in senkrechter Richtung. Der Kreisring 1 ist von einem Gehäuse umgeben, das eine untere, die eine Stirnfläche des Kreisringes 1 überdeckende Haube 2 und eine obere Haube 3 umfaßt, welche die andere Stirnfläche des Kreisringes 1 abdeckt. Der zylindrische Umfang des Kreisringes 1 ist von einem Ringkanal 4 umgeben, der beim Ausführungsbeispiel zwei sich gegenüberliegende Anschlußstutzen 4a aufweist. Das Innere des Kreisringes 1 ist an ein senkrecht stehendes Zentralrohr 5 angeschlossen, das an seinem unteren Ende durch einen Deckel 5a abgeschlossen ist und mit seinem oberen Ende aus der Haube 3 herausragt. Diese Haube 3 ist beim Ausführungsbeispiel wiederum mit zwei einander gegenüberliegenden Anschlußstutzen 3a versehen, wogegen die untere Haube 2 einen zentralen, nach unten weisenden Anschlußstutzen 2a aufweist.The heat exchange takes place between a plurality of flow channels arranged approximately parallel to one another, which are arranged in a circular ring 1. In the exemplary embodiment according to FIGS. 1 and 2, the longitudinal central axis 1a of the circular ring 1 extends in the vertical direction. The circular ring 1 is surrounded by a housing which comprises a lower hood 2, which covers one end face of the circular ring 1, and an upper hood 3, which covers the other end face of the circular ring 1. The cylindrical circumference of the circular ring 1 is surrounded by an annular channel 4 which, in the exemplary embodiment, has two connecting pieces 4a lying opposite one another. The inside of the circular ring 1 is connected to a vertical central tube 5, which is closed at its lower end by a cover 5a and protrudes from the hood 3 with its upper end. In the exemplary embodiment, this hood 3 is in turn provided with two connection pieces 3a lying opposite one another, whereas the lower cover 2 has a central connection piece 2a pointing downward.

Beim Ausführungsbeispiel tritt gemäß den in den Figuren 1 und 2 eingezeichneten Pfeilen das aufzuwärmende Gas G1, bei dem es sich beispielsweise um ein von einer Rauchgasentschwefelungsanlage kommendes gereinigtes Gas handelt, von oben her zentral in die obere Haube 3 ein. Es strömt im Zentralrohr 5 nach unten und tritt nach einer Umlenkung von innen kommend in den Kreisring 1 ein, der durch eine Mehrzahl von etwa parallel zueinander angeordneten Platten in einzelne Strömungskanäle aufgeteilt ist.In the exemplary embodiment, according to the arrows shown in FIGS. 1 and 2, the gas G1 to be heated, which is, for example, a purified gas coming from a flue gas desulfurization system, enters the upper hood 3 centrally from above. It flows downward in the central tube 5 and, after a deflection, comes from the inside into the circular ring 1, which is divided into individual flow channels by a plurality of plates arranged approximately parallel to one another.

Bei der ersten Ausführungsform gemäß den Figuren 3 bis 5 sind die Platten 6 in Übereinstimmung mit der Darstellung in Fig. 2 in senkrechter Richtung ausgerichtet. Sie stehen mit radialem Verlauf im Kreisring 1, so daß ihre Oberflächen parallel zur Längsmittelachse 1a des Kreisringes 1 verlaufen. Jeweils zwei benachbarte Platten 6 bilden einen Strömungskanal 7a bzw. 7r, wobei der Strömungskanal 7a in axialer Richtung des Kreisringes 1 und Strömungskanal 7r in radialer Richtung des Kreisringes 1 vom aufzuwärmenden Gas G1 bzw. vom wärmeabgebenden Gas G2 durchströmt wird.In the first embodiment according to FIGS. 3 to 5, the plates 6 are aligned in the vertical direction in accordance with the illustration in FIG. 2. They are radial in circular ring 1, so that their surfaces run parallel to the longitudinal central axis 1 a of circular ring 1. In each case two adjacent plates 6 form a flow channel 7a or 7r, the flow channel 7a in the axial direction of the circular ring 1 and the flow channel 7r in the radial direction of the circular ring 1 being flowed through by the gas G1 to be warmed up or by the heat-emitting gas G2.

Die Figuren 3 bis 5 zeigen, daß benachbarte Platten 6 zur Bildung eines in axialer Richtung verlaufenden Strömungskanals 7a am äußeren und inneren Umfang des Kreisringes 1 durch streifenförmige Verbindungsstücke 8a miteinander verbunden sind, wogegen die in radialer Richtung verlaufenden Strömungskanäle 7r durch benachbarte Platten 6 und Verbindungsstücke 8b gebildet werden, die jeweils in der Art eines Streifens in den stirnseitigen Flächen des Kreisringes 1 angeordnet sind.Figures 3 to 5 show that adjacent plates 6 to form an axial flow channel 7a on the outer and inner circumference of the annulus 1 are connected by strip-shaped connectors 8a, whereas the radial flow channels 7r are connected by adjacent plates 6 and connectors 8b are formed, which are each arranged in the manner of a strip in the end faces of the circular ring 1.

Das aufzuwärmende, über das Zentralrohr 5 den radialen Strömungskanälen 7r von der Mitte her zugeführte Gas C1 durchströmt waagerecht und in radialer Richtung den Kreisring 1 nach außen und tritt in den Ringkanal 4 ein, der den Kreisring 1 umgibt. Aus dem Ringkanal 4 ein, der den Kreisring 1 umgibt. Aus dem Ringkanal 4 wird das aufgewärmte Gas G1 durch die Anschtußstutzen 4a aus dem Wärmetauscher abgeführt und beispielsweise einem Rauchgaskamin zugeführt.The gas C1 to be warmed up and fed to the radial flow channels 7r from the center through the central tube 5 flows horizontally and in the radial direction through the circular ring 1 and enters the ring channel 4 which surrounds the circular ring 1. From the ring channel 4, which surrounds the circular ring 1. The warmed gas G1 is removed from the ring channel 4 through the connection piece 4a from the heat exchanger and, for example, fed to a flue gas chimney.

Das wärmeabgebende Gas G2 wird beim Ausführungsbeispiel von unten kommend über den zentralen Anschlußstutzen 2a der unteren Haube 2 des Wärmetauschers zugeführt. Es gelangt demgemäß von unten her in die Stirnseite des durch die Platten 6 gebildeten Kreisringes 1 in die in axialer Richtung des Kreisringes 1 verlaufenden Strömungskanäle 7a, wie die Pfeile in Fig. 1 andeuten. Über die Oberfläche der Platten 6 gibt dieses Gas G2 einen Teil seiner Wärme an das aufzuwärmende Gas G1 ab, das im Kreuzstrom zum Gas G2 strömt. Nach dem Wärmeaustausch verläßt das Gas G2 den Kreisring 1 an der oberen Stirnseite und tritt in die obere Haube 3 ein, die in der Mitte vom Zentralrohr 5 durchdrungen wird. Das abgekühlte Gas G2 gelangt schließlich über die einander gegenüberliegenden Anschlußstutzen 3a aus der Haube 3. Sofern es sich um ein zu entschwefelndes Rauchgas handelt, wird es anschließend der Rauchgasentschwefelungsanlage zugeführt.In the exemplary embodiment, the heat-emitting gas G2 is supplied from below via the central connecting piece 2a to the lower hood 2 of the heat exchanger. Accordingly, it flows from below into the end face of the circular ring 1 formed by the plates 6 into the flow channels 7a running in the axial direction of the circular ring 1, as indicated by the arrows in FIG. 1. Via the surface of the plates 6, this gas G2 gives off part of its heat to the gas G1 to be heated, which flows in cross-flow to the gas G2. After the heat exchange, the gas G2 leaves the circular ring 1 on the upper end face and enters the upper hood 3, which is penetrated in the middle by the central tube 5. The cooled gas G2 finally comes out of the hood 3 via the connecting pieces 3a which are opposite one another. If it is a flue gas to be desulfurized, it is then fed to the flue gas desulfurization system.

In Fig. 1 sind Stützen 9 eingezeichnet, durch die der zu einer Baueinheit zusammengefaßte Wärmetauscher aufgeständert ist und auf einem ortsseitigen Fundament aufgestellt werden kann. Der Teilschnitt in Fig. 1 zeigt weiterhin, daß sowohl in der oberen Haube 3 als auch im Zentralrohr 5 jeweils eine Reinigungsvorrichtung 10 angeordnet ist, mit deren Hilfe die Strömungskanäle 7a bzw. 7r gereinigt werden können. Diese Reinigungsvorrichtungen 10 sind vorzugsweise verfahrbar ausgeführt, so daß durch einen Umlauf der Reinigungsvorrichtungen 10 nacheinander sämtliche Strömungskanäle 7a und 7r gereinigt werden.In Fig. 1 supports 9 are shown, through which the heat exchanger combined to form a unit is raised and can be placed on a local foundation. The partial section in FIG. 1 further shows that a cleaning device 10 is arranged in both the upper hood 3 and in the central tube 5, with the aid of which the flow channels 7a and 7r can be cleaned. These cleaning devices 10 are preferably designed to be movable, so that all flow channels 7a and 7r are cleaned in succession by one circulation of the cleaning devices 10.

Um eine Querschnittsverringerung in Strömungsrichtung der Gase G1 bzw. G2 innerhalb der Strömungskanäle 7a bzw. 7r zu vermeiden, können die Platten 6 in der insbesondere in Fig. 5 erkennbaren Weise angeordnet werden. Diese Darstellung zeigt, daß die in radialer Richtung des Kreisringes 1 durchströmten Kanäle 7r durch parallel zueinander angeordnete Platten 6 gebildet sind. Es ergibt sich somit ein in Strömungsrichtung gleichbleibender Kanalquerschnitt. Die in axialer Richtung des Kreisringes 1 durchströmten Kanäle 7a werden dagegen durch spitzwinklig zueinander verlaufende Platten 6 gebildet. Hieraus resultiert zwar ein etwa dreieckförmiger bzw. trapezförmiger Strömungsquerschnitt der Kanäle 7a, ohne daß jedoch eine Verengung des Kanalquerschnittes in Strömungsrichtung erfolgt. Auf diese Weise ist es möglich, trotz der im wesentlichen radialen und damit sternförmigen Ausrichtung der Platten 6 Verengungen der Kanaiquerschnitte in Strömungsrichtung der. Gase G1 und G2 zu vermeiden. Um die jeweiligen Abstände der Platten 6 voneinander exakt einzuhalten, können diese gemäß Fig. 5 mit Noppen 6a versehen sein, die entweder aufgesetzt oder ausgeprägt sind und für die Einhaltung des jeweiligen Plattenabstandes sorgen.In order to avoid a cross-sectional reduction in the flow direction of the gases G1 or G2 within the flow channels 7a or 7r, the plates 6 can be arranged in the manner which can be seen in particular in FIG. 5. This illustration shows that the channels 7r through which flow flows in the radial direction of the circular ring 1 are formed by plates 6 arranged parallel to one another. This results in a channel cross section that remains constant in the direction of flow. In contrast, the channels 7a through which the annular ring 1 flows in the axial direction are formed by plates 6 which run at an acute angle to one another. This results in an approximately triangular or trapezoidal flow cross-section of the channels 7a, but without the channel cross-section narrowing in the flow direction. In this way it is possible, despite the essentially radial and thus star-shaped alignment of the plates 6, narrowing of the canal sections in the flow direction of the. Avoid gases G1 and G2. To the respective distances of the According to FIG. 5, plates 6 must be exactly adhered to one another, these can be provided with knobs 6a, which are either attached or pronounced and ensure that the respective plate spacing is maintained.

Bei der in den Figuren 6 und 7 dargestellten zweiten Ausführungsmöglichkeit für die wärmeaustauschenden Flächen werden Platten 11 verwendet, die mit ihrer Oberfläche rechtwinklig zur Längsmittelachse 1a des Kreisringes 1 ausgerichtet sind, wie insbesondere Fig. 6 erkennen läßt Diese Platten 11 sind mit zu Rohrstücken ausgebildeten Durchbrechungen 11 a versehen, so daß sich bei einem Aneinanderfügen benachbarter Platten 11 rohrförmige Strömungskanäle 7a ergeben, die rechtwinklig zu den Strömungskanälen 7r verlaufen, die durch die Platten 11 gebildet werden.In the second embodiment of the heat-exchanging surfaces shown in FIGS. 6 and 7, plates 11 are used which are aligned with their surface at right angles to the longitudinal central axis 1a of the circular ring 1, as can be seen in particular in FIG. 6. These plates 11 are provided with openings formed into tubular pieces 11 a, so that when adjacent plates 11 are joined together there are tubular flow channels 7 a which run at right angles to the flow channels 7 r which are formed by the plates 11.

Auch bei dieser Ausführungsform ergeben sich somit rechtwinklig zueinander verlaufende Stfömungskanäle 7a bzw. 7r mit axialem bzw. radialem Verlauf der Strömungsrichtung bezüglich des Kreisringes 1, wobei die wärmetauschenden Flächen wiederum durch eine Mehrzahl von etwa parallel zueinander angeordneten Platten 11 gebildet sind. Ein segmentartiger Abschnitt dieser im Kreisring 1 angeordneten Platten 11 ist in Fig. 6 schematisch gezeichnet.In this embodiment, too, flow channels 7a and 7r, which run at right angles to one another, result with an axial or radial course of the flow direction with respect to the circular ring 1, the heat-exchanging surfaces again being formed by a plurality of plates 11 arranged approximately parallel to one another. A segment-like section of these plates 11 arranged in the circular ring 1 is shown schematically in FIG. 6.

Selbstverständlich ist es möglich, die Gasführung abweichend vom Ausführungsbeispiel nach den Figuren 1 und 2 vorzunehmen und die Strömungsrichtung der Gase G1 und G2 abzuändern. Die Platten 6 bzw. 11 werden vorzugsweise aus Blech hergestellt. Sie können gegen Korrosion durch eine Emaillierung geschützt werden. Außerdem ist eine Kombination aus verschiedenen Materialien möglich, so daß im Bereich des Taupunktes auch nichtmetallische Werkstoffe eingesetzt werden können.Of course, it is possible to deviate from the exemplary embodiment according to FIGS. 1 and 2 and to change the flow direction of the gases G1 and G2. The plates 6 and 11 are preferably made of sheet metal. They can be protected against corrosion by enamelling. In addition, a combination of different materials is possible, so that non-metallic materials can also be used in the area of the dew point.

Die nur schematisch angedeuteten Reinigungsvorrichtungen 10 können durch Dampfbläser oder andere Blaseinrichtungen mit Luft oder Wasser gebildet sein. Durch die Anordnung der Platten 6 bzw. 11 im Kreisring 1 ergeben sich kurze Plattenlängen, so daß die hierdurch gebildeten Strömungskanäle 7a bzw. 7r einwandfrei gereinigt werden können. Außerdem ergibt diese Ausbildung geringe Strömungswiderstände, so daß der voranstehend beschriebene Wärmetauscher mit geringen Druckverlusten arbeitetThe cleaning devices 10, which are only indicated schematically, can be formed by steam blowers or other blowing devices with air or water. The arrangement of the plates 6 and 11 in the circular ring 1 results in short plate lengths, so that the flow channels 7a and 7r formed thereby can be cleaned properly. In addition, this design results in low flow resistances, so that the heat exchanger described above works with low pressure drops

Die Fig. 8 zeigt eine abgewandelte Ausführungsform des Wärmetauschers, bei der die mit ihrer Oberfläche parallel zur Längsmittelachse 1a des Kreisringes 1 ausgerichteten Platten in zwei Plattenabschnitte 6b und 6c aufgeteilt sind. Hierdurch ergeben sich bei größeren. Abmessungen des Kreisringes 1 nicht nur einfacher herzustellende und leichter zu montierende Einbaukörper, sondern es wird auch die Möglichkeit geschaffen, auf dem äußeren Teil des Kreisringes 1 eine größere Anzahl von Plattenabschnitten 6b unterzubringen als Plattenabschnitte 6c auf dem inneren Teil des Kreisringes 1 vorhanden sind. Trotz der- in radialer Richtung nach außen zunehmenden Vergrößerung der Grundfläche können auf diese Weise die Strömungsquerschnitte der einzelnen Strömungskanäle 7a bzw. 7r einander angenähert werden. Wie Fig. 8 zeigt, wird zwischen den Plattenabschnitten 6b und 6c ein Ringspalt gelassen, so daß sich ein problemloser Obergang des die Plattenabschnitte 6c und 6b in radialer Richtung durchströmenden Gases ergibt.FIG. 8 shows a modified embodiment of the heat exchanger, in which the plates aligned with their surface parallel to the longitudinal central axis 1a of the circular ring 1 are divided into two plate sections 6b and 6c. This results in larger ones. Dimensions of the circular ring 1 not only easier to manufacture and easier to assemble, but it also creates the possibility to accommodate a larger number of plate sections 6b on the outer part of the circular ring 1 than there are plate sections 6c on the inner part of the circular ring 1. In spite of the enlargement of the base area increasing in the radial direction, the flow cross sections of the individual flow channels 7a and 7r can be approximated in this way. As shown in FIG. 8, an annular gap is left between the plate sections 6b and 6c, so that there is a problem-free transition of the gas flowing through the plate sections 6c and 6b in the radial direction.

In Fig. 9 ist eine weitere abgewandelte Ausführungsform des Wärmetauschers dargestellt, obwohl dessen Grundaufbau dem der Ausführungsform nach Fig. 1 entspricht. Bei der Ausführungsform nach Fig. 9 sind die wiederum mit ihrer Oberfläche parallel zur Längsmittelachse 1 a des Kreisringes 1 ausgerichteten Platten 6, die axial durchgehende Strömungskanäle 7a bilden, bezüglich ihrer radial durchströmten Kanäle 7r durch Trennbleche 12 in einzelne Kanalabschnitte 1b, 1 c, 1 unterteilt. Wie Fig. 9 zeigt, wird der von oben in das Zentralrohr 5 eingeführte Gasstrom G1 ausschließlich in den oberen Kanalabschnitt 1b engeleitet, den er radial nach außen durchströmt. Die Gase gelangen in eine Umlenkkammer 13a, die am Außenumfang der Kanalabschnitte 1b und 1c angeordnet ist. In dieser Umlenkkammer 13a werden die Gase G1 umgelenkt und radial von außen in den Kanalabschnitt ic eingeführt, den sie demzufolge mit radial nach innen gerichteter Strömungsrichtung durchströmen. Nach Verlassen des Kanalabschnittes 1c gelangen die Gase G1 in eine weitere Umlenkkammer 13b, die in der Art eines Rohrstückes und in Verlängerung des Zentralrohres 5 ausgebildet ist, von dem die Umlenkkammer 13b durch den Deckel 5a abgetrennt ist. Auch in dieser Umlenkkammer 13b erfolgt eine Umlenkung der Gase C1, so daß diese anschließend den untersten Kanalabschnitt 1d mit radial nach außen gerichteter Strömungsrichtung durchströmen. Die Gase G1 gelangen schließlich in den Ringkanal 4, den sie über die beiden Anschlußstutzen 4a verlassen.FIG. 9 shows a further modified embodiment of the heat exchanger, although its basic structure corresponds to that of the embodiment according to FIG. 1. In the embodiment according to FIG. 9, the plates 6, which in turn are aligned with their surface parallel to the longitudinal central axis 1a of the circular ring 1 and form axially continuous flow channels 7a, with respect to their radially flowed channels 7r through separating plates 12 into individual channel sections 1b, 1c, 1st divided. As shown in FIG. 9, the gas flow G1 introduced into the central tube 5 from above is conducted exclusively into the upper channel section 1b, through which it flows radially outwards. The gases enter a deflection chamber 13a which is arranged on the outer circumference of the channel sections 1b and 1c. In this deflection chamber 13a, the gases G1 are deflected and introduced radially from the outside into the channel section ic, which they consequently flow through with a radially inward flow direction. After leaving the channel section 1c, the gases G1 arrive in a further deflection chamber 13b, which is designed in the manner of a tube piece and in the extension of the central tube 5, from which the deflection chamber 13b is separated by the cover 5a. The gases C1 are also deflected in this deflection chamber 13b, so that they subsequently flow through the lowermost channel section 1d with the flow direction directed radially outward. The gases G1 finally enter the ring channel 4, which they leave via the two connecting pieces 4a.

Bei dieser Ausführungsform ergibt sich somit eine Gasführung, bei welcher das aufzuwärmende Gas G1 im Kreuzgegenstrom zum wärmeabgebenden Gas G2 geführt wird, wobei das Gas G2 den Kreisring ausschließlich axial durchströmt, das Gas G1 jedoch durch zeifache Umlenkung in den Umlenkkammern 13a und 13b nicht nur im Kreuzstrom zum Gas G2 geführt wird, sondern zusätzlich im Gegenstrom infolge der Unterteilung der radial durchströmten Kanäle 7r durch Trennbleche 12 in mehrere gegenläufig durchströmte Kanalabschnitte 1b, 1c und 1d.In this embodiment, there is thus a gas routing in which the gas G1 to be warmed is passed in countercurrent to the heat-releasing gas G2, the gas G2 flowing through the circular ring exclusively axially, but the gas G1 by deflecting it three times in the deflection chambers 13a and 13b not only in the Cross flow is led to the gas G2, but additionally in countercurrent as a result of the subdivision of the radially flowed channels 7r by dividing plates 12 into a plurality of channel sections 1b, 1c and 1d with opposite flows.

In Fig. 10 ist eine weitere Möglichkeit zur Ausbildung der wärmeaustauschenden Flächen im Kreisring 1 der Vorrichtung dargestellt. Bei dieser Ausführungsform werden die Strömungskanäle durch einzelne Rohre 14 gebildet, die in radialer Richtung im Kreisring 1 angeordnet sind. Die radial innenliegenden Enden der Rohre 14 münden in einem Lochblech 15i. Die radial außenliegenden Enden der Rohre 14 sind an einem Lochblech 15a befestigt. Diese Lochbleche 15a und 15i dienen nicht nur der Lagesicherung der Rohre 14, sondern auch der Trennung des die Rohre 14 durchströmenden Gases G1 vom Gas G2, das entsprechend den in Fig. 10 eingezeichneten Pfeilen in axialer Richtung von unten nach oben den Kreisring 1 durchströmt Die Lochbleche 15a und 15i der zu Segmenten gemäß Fig. 10 zusammengefaßten Rohre 14 werden an den benachbarten Kanten gasdicht miteinander verbunden, vorzugsweise verschweißt.10 shows a further possibility for the formation of the heat-exchanging surfaces in the circular ring 1 of the device. In this embodiment, the flow channels are formed by individual tubes 14, which are arranged in the radial direction in the circular ring 1. The radially inner ends of the tubes 14 open into a perforated plate 15i. The radially outer ends of the tubes 14 are fastened to a perforated plate 15a. These perforated plates 15a and 15i serve not only to secure the position of the pipes 14, but also to separate the gas G1 flowing through the pipes 14 from the gas G2, which flows through the circular ring 1 in the axial direction from bottom to top in accordance with the arrows shown in FIG. 10. The perforated plates 15a and 15i of the tubes 14 combined into segments according to FIG. 10 are connected gas-tight to one another at the adjacent edges, preferably welded.

Obwohl es ohne weiteres möglich ist, die in radialer Richtung im Kreisring 1 angeordneten Rohre 14 mit gleichbleibendem Strömungsquerschnitt auszuführen, beispielsweise mit kreisförmigem oder ovalem Querschnitt, kann es in besonderen Fällen zweckmäßig sein, daß der Strömungsquerschnitt der Rohre 14 in Strömungsrichtung zunimmt beispielsweise um die durch die Erwärmung des Gases G1 entstehende Volumenvergrößerung zumindest teilweise zu kompensieren, so daß keine wesentliche Erhöhung der Strömungsgeschwindigkeit auftritt. Beim Ausführungsbeispiel nach Fig. 10 sind zu diesem Zweck die im Ausgangszustand einen kreisförmigen Querschnitt aufweisenden Rohre 14 am radial innenliegenden Ende abgeflacht, wie dies durch die Öffnungen im Lochblech 15i in Fig. 10 hervorgeht. Hierdurch entsteht am radial innenliegenden Ende der Rohre 14 ein kleinerer Strömungsquerschnitt als am radial außenliegenden Ende. Je stärker die Abflachung der Rohre 14 ist, um so größer ist die Querschnittsveränderung über die Länge der einzelnen Rohre 14.Although it is readily possible to design the tubes 14 arranged in the radial direction in the circular ring 1 with a constant flow cross-section, for example with a circular or oval cross-section, it may be expedient in special cases that the flow cross-section of the tubes 14 increases in the flow direction, for example by the through to at least partially compensate for the increase in volume of the heating of the gas G1, so that there is no significant increase in the flow velocity. In the exemplary embodiment according to FIG. 10, the tubes 14, which in the initial state have a circular cross section, are flattened at the radially inner end, as is evident from the openings in the perforated plate 15i in FIG. 10. This results in a smaller flow cross section at the radially inner end of the tubes 14 than at the radially outer end. The greater the flattening of the tubes 14, the greater the change in cross section over the length of the individual tubes 14.

Eine weitere Ausführungsmöglichkeit der den Wärmeaustausch bewirkenden Strömungskanäle zeigt schließlich die Fig. 11. Bei dieser Ausführungsform werden jeweils Paare von Platten 16a, 16b verwendet, die zwischen sich rohrartige Strömungskanäle 16c bilden. Durch diese Strömungskanäle 16c strömt beim Ausführungsbeispiel das Gas G1. Das Gas G2 wird im Kreuzstrom hierzu zwischen den Plattenpaaren 16a, 16b geführt.Finally, FIG. 11 shows another possible embodiment of the flow channels which effect the heat exchange. In this embodiment, pairs of plates 16a, 16b are used in each case, which form tube-like flow channels 16c between them. In the exemplary embodiment, the gas G1 flows through these flow channels 16c. For this purpose, the gas G2 is conducted in cross flow between the plate pairs 16a, 16b.

Um ein Vermischen der Gase G1 und G2 zu vermeiden, sind die Platten 16a und 16b eines Plattenpaares jeweils an den in radialer Richtung im Kreisring 1 verlaufenden Rändern gasdicht miteinander verbunden, vorzugsweise verschweißt. Am radial innenliegenden und am radial außenliegenden Ende sind die Platten 16a und 16b mit Abwinklungen 16d versehen, die somit die Aufgabe der Lochbleche 15a und 15i bei der Ausführungsform nach Fig. 10 übernehmen, nämlich den radial innenliegenden und radial außenliegenden Abschluß eines Segments der Wärmeaustauschfläche. Um benachbarte Plattenpaare 16a und 16b auf einfache Weise miteinander verbinden zu können, sind an den Abwinklungen 16d schließlich leistenartig hervorstehende Ränder 16e ausgebildet, die miteinander verschweißt werden und auf diese Weise einen gasdichten Abschluß ergeben.In order to avoid mixing of the gases G1 and G2, the plates 16a and 16b of a pair of plates are connected to one another in a gas-tight manner at the edges running in the radial direction in the circular ring 1, preferably welded. At the radially inner and at the radially outer end, the plates 16a and 16b are provided with bends 16d, which thus take over the function of the perforated plates 15a and 15i in the embodiment according to FIG. 10, namely the radially inner and radially outer end of a segment of the heat exchange surface. In order to be able to connect adjacent plate pairs 16a and 16b with one another in a simple manner, edges 16e projecting like strips are finally formed on the bends 16d, which are welded to one another and in this way result in a gas-tight seal.

Die Ausbildung der rohrartigen Strömungskanäle 16c kann auf den jeweiligen Einsatzzweck abgestimmt werden. Wie Fig. 11 erkennen läßt, ist es möglich, die durch die einzelnen Plattenpaare 16a, 16b gebildeten Strömungskanäle 16c im Verhältnis zu dem benachbarten Plattenpaar 16a, 16b in Strömungsrichtung des Gases G2 zu versetzen. Ein derartiger Versatz ist auch bei der Ausführungsform nach Fig. 10 durch entsprechende Anordnung der Rohre 14 möglich.The design of the tubular flow channels 16c can be matched to the respective application. As can be seen in FIG. 11, it is possible to offset the flow channels 16c formed by the individual plate pairs 16a, 16b in relation to the adjacent plate pair 16a, 16b in the flow direction of the gas G2. Such an offset is also possible in the embodiment according to FIG. 10 by appropriate arrangement of the tubes 14.

Bezugszeichenliste :Reference symbol list:

  • 1 Kreisring1 annulus
  • 1a Längsmittelachse1a longitudinal central axis
  • 1b Kanalabschnitt1b channel section
  • 1 c Kanalabschnitt1 c channel section
  • 1 d Kanalabschnitt1 d channel section
  • 2 untere Haube2 lower hood
  • 2a Anschlußstutzen2a connecting piece
  • 3 obere Haube3 upper hood
  • 3a Anschlußstutzen3a connecting piece
  • 4 Ringkanal4 ring channel
  • 4a Anschlußstutzen4a connecting piece
  • 5 Zentralrohr5 central tube
  • 5a Deckel5a lid
  • 6 Platte6 plate
  • 6a Noppe6a pimple
  • 6b Plattenabschnitt6b plate section
  • 6c Plattenabschnitt6c plate section
  • 7a axialer Strömungskanal7a axial flow channel
  • 7r radialer Strömungskanal7r radial flow channel
  • 8a Verbindungsstück8a connector
  • 8b Verbindungsstück8b connector
  • 9 Stütze9 support
  • 10 Reinigungsvorrichtung10 cleaning device
  • 11 Platte11 plate
  • 11 a Durchbrechung11 a breakthrough
  • 12 Trennbiech12 separating sheet
  • 13a Umlenkkammer13a deflection chamber
  • 13b Umlenkkammer13b deflection chamber
  • 14 Rohr14 pipe
  • 15a Lochblech15a perforated sheet
  • 15i Lochblech15i perforated sheet
  • 16a Platte16a plate
  • 16b Platte16b plate
  • 16c Strömungskanal16c flow channel
  • 16d Abwinklung16d deflection
  • 16e Rand16e edge
  • G1 aufzuwärmendes GasG1 Gas to be warmed up
  • G2 wärmeabgebendes GasG2 heat-emitting gas

Claims (12)

1. Device for exchanging heat between two gases (G1, G2) which are conveyed in crossflow to one another, preferably for reheating scrubbed flue gases after flue gas desulphurizing plant, with a plurality of flow channels (7a, 7r) which are arranged approximately parallel to one another and the dividing walls of which are acted upon on one side by the heat-emitting gas and on the other by the heat-absorbing gas and are arranged in a circular ring (1) such that gas flows through the flow channels (7a, 7r) in the axial and in the radial direction in turn, characterised in that the channels (7a) through which gas flows axially are connected via a respective end hood (2, 3) to at least one supply line or discharge line for one gas (G2) and the channels (7r) through which gas flows radially are connected via an outer ring channel, which is provided with at least one connection sleeve (4a), and via a central tube (5), which extends through one of the hoods (3), to the supply line or discharge line for the other gas (G1).
2.. Device according to claim 1, characterised in that the circular ring (1) comprising the flow channels (7a, 7r) is arranged with a vertical longitudinal central axis (1 a) and the device is mounted on supports (9).
3. Device according to claim 1, characterised in that the flow channels (7a, 7r) are formed by plates (6, 11).
4. Device according to claims 1 to 3, characterised in that the surfaces of the plates (6), which are arranged approximately radially in the circular ring (1), extend approximately parallel to the longitudinal central axis (1 a) of the circular ring (1).
5. Device according to claims 1 to 3, characterised in that the surfaces of the plates (11) extend at a right angle to the longitudinal central axis (1 a) of the circular ring (1) and that the plates (11) are provided with openings (11 a) which form the flow channels (7a).
6. Device according to claim 4, characterised in that the channels (7r) through which gas flows radially are divided in the axial direction of the circular ring (1) by dividing sheets (12) into a plurality of channel sectons (1b, 1c, 1d) through which gas flows in opposite directions, one channel section (1d) ending in the ring channel (4) and the other channel sections (1b, 1c) being connected together via baffle chambers (13a, 13b).
7. Device according to at least one of claims 1 to 6, characterised in that the plates (6, 11), which are arranged in the circular ring, are divided in the radial direction of the circular ring (1) into a plurality of sections (6b, 6c).
8. Device according to at least one of claims 4, 6 and 7, characterised in that the channels (7r) through which gas flows in the radial direction of the circular ring (1) are formed by plates (6) which are arranged parallel to one another and that the channels (7a) through which gas flows in the axial direction of the circular ring (1) are formed by plates (6) which extend at an acute angle to one another.
9. Device according to claim 1, characterised in that the flow channels (7a, 7r) are formed by tubes (14) which extend between perforated plates (15a, 15i) which are arranged parallel to one another.
10. Device according to claim 9, characterised in that the tubes (14) have a smaller flow cross section in the area of the radially inner perforated plate (15i) than in the area of the radially outer perforated plate (15a).
11. Device according to claim 1, characterised in that the flow channels (7a, 7r) are formed by plate pairs (16a, 16b) which are connected together in a gastight manner at least at the edges and form tubular flow channels (16c).
12. Device according to at least one of claims 1 to 11, characterised in that a cleaning device (10) is provided in the area of at least one end hood (2, 3) for the channels (7a) through which gas flows in the axial direction of the circular ring (1) and a further cleaning device (10) is provided in the area of the central tube (5) and/or the ring channel (4) for the channels (7r) through which gas flows in the radial direction.
EP85112570A 1984-10-08 1985-10-04 Device for exchange of heat between two gases conducted in cross-flow to each other Expired - Lifetime EP0177904B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85112570T ATE50861T1 (en) 1984-10-08 1985-10-04 DEVICE FOR EXCHANGE OF HEAT BETWEEN TWO GASES TRANSMITTED IN CROSS-FLOW.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8429525U 1984-10-08
DE19848429525U DE8429525U1 (en) 1984-10-08 1984-10-08 DEVICE FOR EXCHANGING THE WARMTH BETWEEN TWO GASES LEADING IN A CROSS FLOW

Publications (3)

Publication Number Publication Date
EP0177904A2 EP0177904A2 (en) 1986-04-16
EP0177904A3 EP0177904A3 (en) 1988-09-28
EP0177904B1 true EP0177904B1 (en) 1990-03-07

Family

ID=6771478

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85112570A Expired - Lifetime EP0177904B1 (en) 1984-10-08 1985-10-04 Device for exchange of heat between two gases conducted in cross-flow to each other

Country Status (3)

Country Link
EP (1) EP0177904B1 (en)
AT (1) ATE50861T1 (en)
DE (2) DE8429525U1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012066150A1 (en) 2011-11-15 2012-05-24 Henkel Ag & Co. Kgaa Air dehumidifier
DE202011110575U1 (en) 2011-11-15 2014-09-29 Henkel Ag & Co. Kgaa Tablet for a dehumidifier

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2647198B1 (en) * 1989-05-22 1991-07-19 Packinox Sa PLATE CONDUIT HEAT EXCHANGER
GR1001064B (en) * 1991-09-06 1993-04-28 Ioannis Chortis Chortis heat exchanger of concave cylindrical shape
CA2269058C (en) * 1996-10-17 2003-04-15 Honda Giken Kogyo Kabushiki Kaisha Heat exchanger
US7350909B2 (en) 2004-03-04 2008-04-01 Brother Kogyo Kabushiki Kaisha Ink cartridge and inkjet printer
WO2010142306A1 (en) * 2009-06-10 2010-12-16 Gea Ecoflex Gmbh Method for operating a plate heat exchanger and condenser system having a plate heat exchanger
FR3009073A1 (en) * 2013-07-29 2015-01-30 Didier Costes SODIUM AND NITROGENOUS SURGENERATOR REACTOR

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1734962A (en) * 1924-03-11 1929-11-12 Lucille V Clarke Air heater
GB907839A (en) * 1958-02-11 1962-10-10 Parsons C A & Co Ltd Plate type heat exchangers
US3473604A (en) * 1966-01-18 1969-10-21 Daimler Benz Ag Recuperative heat exchanger
US3831674A (en) * 1972-11-16 1974-08-27 Avco Corp Plate type heat exchangers
JPS5228757A (en) * 1975-08-30 1977-03-03 Nippon Denso Co Ltd Heat exchanger

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012066150A1 (en) 2011-11-15 2012-05-24 Henkel Ag & Co. Kgaa Air dehumidifier
DE202011110575U1 (en) 2011-11-15 2014-09-29 Henkel Ag & Co. Kgaa Tablet for a dehumidifier

Also Published As

Publication number Publication date
DE3576398D1 (en) 1990-04-12
EP0177904A2 (en) 1986-04-16
EP0177904A3 (en) 1988-09-28
ATE50861T1 (en) 1990-03-15
DE8429525U1 (en) 1985-02-21

Similar Documents

Publication Publication Date Title
EP0992756A2 (en) Heat exchanger, more particularly for gases and liquids
DE2442420B2 (en) Desublimator for the extraction of sublimation products, especially phthalic anhydride, and reaction gases
DE2951352C2 (en) Flat tube heat exchanger
EP0826941A2 (en) Tubular heat exchange core
DE2804106C2 (en) Heat exchanger
EP1770345B1 (en) Heat exchange network and heat exchanger using same
EP0152560A1 (en) Matrix for a catalytic reactor for purifying exhaust gases
DE3502619C2 (en)
EP0177904B1 (en) Device for exchange of heat between two gases conducted in cross-flow to each other
DE2308480A1 (en) HEAT EXCHANGER
EP0449124A1 (en) Annular space heat exchanger
EP1748271B1 (en) Fins and tubes for a heat exchanger core
DE3339932A1 (en) Gap-type heat exchanger having webs
EP1625339A1 (en) Heat exchanger
DE2126226C3 (en) Heat exchanger
EP1788320B1 (en) Heat exchanger
DE10056229B4 (en) Heat exchanger for indirect heat exchange
EP0230982B1 (en) Cylindrical heat exchanger manufactured from prefabricated components, in particular a chimney recuperator
DE2947271A1 (en) Heat exchange rib forming strip - has guide fins in pairs at opposite edges of apertures protruding from strip plane
EP0209107B1 (en) Heat exchanger with a relieving rod for the heat exchange tubes
DE2029782C3 (en) Heat exchangers made from sheet metal
DE3018813C2 (en) Heat exchanger for indirect heat exchange between two media consisting of a tube sheet
DE10341644B4 (en) Helical heat exchanger
DE2912723C2 (en) Heat exchanger consisting of a series of flow channels in the form of a plate
EP0816776B1 (en) Gas fired water heater and water cooled combustion chamber

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE DE GB IT NL

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE DE GB IT NL

17P Request for examination filed

Effective date: 19880908

17Q First examination report despatched

Effective date: 19890404

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE DE GB IT NL

REF Corresponds to:

Ref document number: 50861

Country of ref document: AT

Date of ref document: 19900315

Kind code of ref document: T

ITF It: translation for a ep patent filed

Owner name: ING. ZINI MARANESI & C. S.R.L.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3576398

Country of ref document: DE

Date of ref document: 19900412

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19961021

Year of fee payment: 12

Ref country code: AT

Payment date: 19961021

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19961029

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19971004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19971031

BERE Be: lapsed

Owner name: BALCKE-DURR A.G.

Effective date: 19971031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980501

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19980501

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19981008

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19981217

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19991004

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19991004

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000801