EP0177904A2 - Dispositif pour l'échange de chaleur entre deux gaz en flux croisé - Google Patents

Dispositif pour l'échange de chaleur entre deux gaz en flux croisé Download PDF

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Publication number
EP0177904A2
EP0177904A2 EP85112570A EP85112570A EP0177904A2 EP 0177904 A2 EP0177904 A2 EP 0177904A2 EP 85112570 A EP85112570 A EP 85112570A EP 85112570 A EP85112570 A EP 85112570A EP 0177904 A2 EP0177904 A2 EP 0177904A2
Authority
EP
European Patent Office
Prior art keywords
flow
channels
plates
gas
circular ring
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.)
Granted
Application number
EP85112570A
Other languages
German (de)
English (en)
Other versions
EP0177904B1 (fr
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/de
Publication of EP0177904A2 publication Critical patent/EP0177904A2/fr
Publication of EP0177904A3 publication Critical patent/EP0177904A3/de
Application granted granted Critical
Publication of EP0177904B1 publication Critical patent/EP0177904B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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 guided in cross-flow with one another with a plurality of approximately hollow hollow bodies arranged approximately parallel to one another, each of which is supplied with the heat-emitting or with the heat-absorbing gas on one side, preferably for reheating cleaned flue gases behind flue gas desulfurization systems.
  • Plate heat exchangers Devices of the type described above, which are also referred to as plate heat exchangers, are known in various designs. They have the disadvantage that on the one hand they have a large structural 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, with a simultaneous reduction in dimensions, a gas pressure resulting in a small pressure loss is achieved and the possibility of cleaning the channels formed by the hollow profile body is improved.
  • the solution to this problem by the invention is characterized in that the hollow profile bodies are arranged in a circular ring and the channels between the hollow profile bodies alternate in the axial and radial directions are flowed through, the axially flowed channels are connected by at least one front hood to at least one supply line or discharge line for the one gas and the radially flowed channels via an external annular channel provided with at least one connecting piece and via a central tube guided through one of the hoods are connected to the supply or discharge of the other gas.
  • the circular ring with the hollow profile bodies is arranged with a vertical longitudinal 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 hollow profile bodies are formed by plates.
  • the plates arranged approximately radially in the annulus are aligned with their surfaces approximately parallel to the annulus axis. 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 aligned with their surface perpendicular to the circular axis, the plates being provided with flow channels for the openings forming a gas.
  • 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 in the case of smaller quantities of gas in order to enlarge the heat exchange surface while maintaining a compact design.
  • the invention proposes dividing the plates arranged in the circular ring into a plurality of sections in the radial direction of the circular ring. 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 that in radial In this way, the dimensions of the individual flow channels can be kept approximately the same in the direction of the increasing cross-sectional area.
  • the invention further proposes that flowed through in the radial direction of the annulus To form channels by means of plates arranged parallel to one another and to form the channels through which flow in the axial direction of the circular ring by means of plates which abut one another at an acute angle.
  • 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 hollow profile bodies 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, they can also have a smaller flow cross section in the area of the radially inner perforated plate than in the area 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 hollow profile bodies 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 invention proposes 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 end-face 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.
  • the heat exchanger shown with the aid of an exemplary embodiment can be used for heating or cooling gases, the heat exchange taking place between two gases G1 and G2 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 desulphurization plant and being cooled after the denitrification before being introduced into the flue gas chimney.
  • Other areas of application are waste heat and heat recovery systems in various industrial sectors.
  • the heat exchange takes place between a plurality of profile hollow bodies arranged approximately parallel to one another, which are arranged in a circular ring 1.
  • the longitudinal central axis la 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 when off example has two opposite connecting pieces 4a.
  • 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 Gl to be heated which is, for example, a 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. They are radial in the annulus 1, so that their surfaces are parallel to the longitudinal central axis la of the annulus 1.
  • 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 through which the gas G1 to be heated or the heat-releasing gas G2 flows.
  • Figures 3 to 5 show that adjacent plates 6 to form a flow channel 7a extending in the axial direction on the outer and inner circumference of the annulus 1 by strip-shaped connecting pieces 8a with each other are connected, whereas the radial flow channels 7r are formed by adjacent plates 6 and connecting pieces 8b, which are each arranged in the manner of a strip in the end faces of the circular ring 1.
  • the heated gas G1 is removed from the ring channel 4 through the connecting 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. 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.l 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.l also shows that a cleaning device 10 is arranged both in the upper hood 3 and in the central tube 5, with the help 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.
  • 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 have a surface that is perpendicular to the longitudinal central axis la of the circular ring 1 are directed, as can be seen in particular in FIG.
  • These plates 11 are provided with openings 11 a, which are formed into tubular pieces, so that when adjacent plates 11 are joined together, tubular flow channels 7 a result which are perpendicular to the flow channels 7 r 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.
  • 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 la of the circular ring 1 are divided into two plate sections 6b and 6c.
  • the flow cross sections of the individual flow channels 7a and 7r can be brought closer to one another in this way.
  • FIG. 8 shows, 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 A further modified embodiment of the heat exchanger is shown in FIG. 9, although its basic structure corresponds to that of the embodiment according to FIG.
  • the plates 6, which in turn are aligned with their surface parallel to the longitudinal central axis la of the circular ring 1 and form axially continuous flow channels 7a, are divided into individual channel sections lb, lc, ld with respect to their radially flowed channels 7r by separating plates 12.
  • the gas flow G1 introduced into the central tube 5 from above is introduced 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 radially into the channel section 1c from the outside led, which they consequently flow through with a radially inward flow direction.
  • the gases G1 After leaving the channel section 1c, the gases G1 enter a further deflection chamber 13b, which is designed in the manner of a pipe section and in the extension of the central tube 5, from which the deflection chamber 13b is separated by the cover 5a.
  • the gases G1 are also deflected in this deflection chamber 13b, so that they then 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 hollow profile bodies 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 not only serve to secure the position of the tubes 14, but also to separate the gas G1 flowing through the tubes 14 from the gas G2, which, according to the arrows shown in FIG flows.
  • the perforated plates 15a and 15i of the tubes 14 combined into segments according to Flg.10 are gas-tightly connected 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 to compensate, at least partially, for the increase in volume resulting from 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 can be seen 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 A further possible embodiment of the hollow profile body which effects the heat exchange is finally shown in FIG. 11.
  • pairs of plates 16a, 16b are used, 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.
  • Plates 16a and 16b of a pair of plates are gas-tightly connected to one another, preferably welded, at the edges running in the radial direction in the circular ring 1.
  • the plates 16a and 16b are provided with bends 16d, which thus take over the task 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 Fig.ll reveals, 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP85112570A 1984-10-08 1985-10-04 Dispositif pour l'échange de chaleur entre deux gaz en flux croisé Expired - Lifetime EP0177904B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85112570T ATE50861T1 (de) 1984-10-08 1985-10-04 Vorrichtung zum austausch der waerme zwischen zwei im kreuzstrom zueinander gefuehrten gasen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19848429525U DE8429525U1 (de) 1984-10-08 1984-10-08 Vorrichtung zum austausch der waerme zwischen zwei im kreuzstrom zueinander gefuehrten gasen
DE8429525U 1984-10-08

Publications (3)

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

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ID=6771478

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85112570A Expired - Lifetime EP0177904B1 (fr) 1984-10-08 1985-10-04 Dispositif pour l'échange de chaleur entre deux gaz en flux croisé

Country Status (3)

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EP (1) EP0177904B1 (fr)
AT (1) ATE50861T1 (fr)
DE (2) DE8429525U1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992008941A1 (fr) * 1989-05-22 1992-05-29 Packinox S.A. Echangeur thermique a conduits a plaques
GR1001064B (el) * 1991-09-06 1993-04-28 Ioannis Chortis Εναλλακτης θερμοτητας σχηματος κοιλου κυλινδρου
EP0933608A1 (fr) * 1996-10-17 1999-08-04 Honda Giken Kogyo Kabushiki Kaisha Echangeur de chaleur
EP2177364A2 (fr) 2004-03-04 2010-04-21 Brother Kogyo Kabushiki Kaisha Cartouche d'encre et imprimante à jet d'encre
WO2010142306A1 (fr) * 2009-06-10 2010-12-16 Gea Ecoflex Gmbh Procédé pour faire fonctionner un échangeur de chaleur à plaques et système de condenseur avec échangeur de chaleur à plaques

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
HUE039196T2 (hu) 2011-11-15 2018-12-28 Henkel Ag & Co Kgaa Párátlanító
DE202011110575U1 (de) 2011-11-15 2014-09-29 Henkel Ag & Co. Kgaa Tablette für einen Luftentfeuchter
FR3009073A1 (fr) * 2013-07-29 2015-01-30 Didier Costes Reacteur surgenerateur a sodium et azote

Citations (4)

* 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
GB1133291A (en) * 1966-01-18 1968-11-13 Daimler Benz Ag Improvements relating to recuperative heat exchangers
DE2342173B2 (de) * 1972-11-16 1978-11-30 Avco Corp., Cincinnati, Ohio (V.St.A.) Stapeiförmiger Plattenwärmeaustauscher

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5228757A (en) * 1975-08-30 1977-03-03 Nippon Denso Co Ltd Heat exchanger

Patent Citations (4)

* 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
GB1133291A (en) * 1966-01-18 1968-11-13 Daimler Benz Ag Improvements relating to recuperative heat exchangers
DE2342173B2 (de) * 1972-11-16 1978-11-30 Avco Corp., Cincinnati, Ohio (V.St.A.) Stapeiförmiger Plattenwärmeaustauscher

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 1, Nr. 83, 30. Juli 1977; & Jp - A - 52 28757 (NIPPON DENSO K.K.) 03.03.1977 *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992008941A1 (fr) * 1989-05-22 1992-05-29 Packinox S.A. Echangeur thermique a conduits a plaques
GR1001064B (el) * 1991-09-06 1993-04-28 Ioannis Chortis Εναλλακτης θερμοτητας σχηματος κοιλου κυλινδρου
EP0933608A1 (fr) * 1996-10-17 1999-08-04 Honda Giken Kogyo Kabushiki Kaisha Echangeur de chaleur
EP0933608A4 (fr) * 1996-10-17 1999-12-15 Honda Motor Co Ltd Echangeur de chaleur
US6192975B1 (en) 1996-10-17 2001-02-27 Honda Giken Kogyo Kabushiki Kaisha Heat exchanger
EP2177364A2 (fr) 2004-03-04 2010-04-21 Brother Kogyo Kabushiki Kaisha Cartouche d'encre et imprimante à jet d'encre
WO2010142306A1 (fr) * 2009-06-10 2010-12-16 Gea Ecoflex Gmbh Procédé pour faire fonctionner un échangeur de chaleur à plaques et système de condenseur avec échangeur de chaleur à plaques

Also Published As

Publication number Publication date
ATE50861T1 (de) 1990-03-15
DE8429525U1 (de) 1985-02-21
EP0177904B1 (fr) 1990-03-07
EP0177904A3 (en) 1988-09-28
DE3576398D1 (de) 1990-04-12

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