EP0147866A2 - Plattenwärmetauscher - Google Patents

Plattenwärmetauscher Download PDF

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Publication number
EP0147866A2
EP0147866A2 EP84116425A EP84116425A EP0147866A2 EP 0147866 A2 EP0147866 A2 EP 0147866A2 EP 84116425 A EP84116425 A EP 84116425A EP 84116425 A EP84116425 A EP 84116425A EP 0147866 A2 EP0147866 A2 EP 0147866A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
plates
plate
plate heat
fine structure
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
EP84116425A
Other languages
English (en)
French (fr)
Other versions
EP0147866B1 (de
EP0147866A3 (en
Inventor
Poy Holmberg
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.)
UK Secretary of State for Defence
ABB Technology FLB AB
Original Assignee
UK Secretary of State for Defence
Flaekt AB
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
Priority claimed from SE8307215A external-priority patent/SE8307215L/xx
Application filed by UK Secretary of State for Defence, Flaekt AB filed Critical UK Secretary of State for Defence
Priority to AT84116425T priority Critical patent/ATE41228T1/de
Publication of EP0147866A2 publication Critical patent/EP0147866A2/de
Publication of EP0147866A3 publication Critical patent/EP0147866A3/en
Application granted granted Critical
Publication of EP0147866B1 publication Critical patent/EP0147866B1/de
Expired 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
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other

Definitions

  • the present invention relates to a plate heat exchanger designed for heat exchange between gaseous media in accordance with the preamble of Claim I.
  • Plate heat exchangers of this type are used primarily in heat recovery systems in ventilation plants. As a rule, it is the heat from an exhaust air flow to an intake air flow that is transmitted in that the respective flows pass through the heat exchanger in separate flow passages in so-called cross-current.
  • a common design feature of such heat exchangers is cross-laid flat plates provided with distance members, the latter being formed by and comprising a part of the plate and elaborated as round nipples or oblong nipples extending in the flow direction.
  • the distance between these distance members must be selected large in relation to their height to avoid unfavourable generation of turbulence in the heat exchanger. Consequently, the material thickness of the plates, which are often made of aluminium, must be chosen relatively large in order for the plates to be able to withstand the large pressure differential between the plates which is common without their deflection becoming excessive. Since the material cost comprises a significant portion of the cost of a finished heat exchanger the relatively large material thickness thus consistutes a considerable disadvantage for this type of heat exchanger.
  • a common embodiment of the pleated plates gives triangular flow passages and permits the choice of small material thicknesses.
  • One disadvantage, however, is that the triangular shape of the flow passage together with laminar flow necessitates a large heating area, which results in narrow flow passages to prevent the volume of the heat exchanger from becoming excessively large.
  • the narrow flow passages give, among other things, an undesirably high increase in pressure drop upon condensate precipitation.
  • a further distadvantage is that the laminar flow formed with flat plates also in this case leads to narrow flow passages.
  • a seal for this type of heat exchanger plates is usually achieved by means of some kind of seal compound between the plates, alternatively by folding one edge of the plate around the edge of the adjacent plate which as a result provides an acceptable seal with a flat plate of the thickness indicated above.
  • the object of the present invention is to provide a heat exchanger which does not display the disadvantages of the prior art heat exchangers, but is made with plates which display essentially thinner material at the same time as the heat transfer capacity is improved. Moreover, the flow resistance, i.e., the pressure drop through the heat exchanger, must be retained at an acceptably low level, both when the heat exchanger surfaces are dry and when condensate is precipitated.
  • One object is also to obtain an efficient seal between the separate gas flow passages in the heat exchanger which implies that the adjacent plates are joined together in a for the manufacture efficent and rational way.
  • the invention is based on the insight that through the fine structure a friction pressure drop is obtained which effectively increases heat transfer without any appreciable increase in the flow resistance, which is due to the fact that a favourable generation of turbulence can be maintained in the duct.
  • the fine structure gives a substantial stiffening of the plates which, thanks to the invention, can be made with a material thickness (and thus a total material consumption) which is only between 20-30 per cent of the thickness of conventional plates.
  • the invention is further based on the insight that by means of a lengthwise pleating of the folded connecting edge of the plates, the folded part of the plate is prevented from springing back, i.e., in that locking of the connecting edge is achieved.
  • the invention is based on the insight that through the fine structure a friction pressure drop is obtained which effectively increases heat transfer without any appreciable increase in the flow resistance. This is ⁇ due to the fact that a favourable generation of turbulence can be maintained in the flow passages.
  • the fine structure gives a substantial stiffening of the plates which, thanks to the invention, can be made with a material thickness (and thus a total material consumption) which is only between 20-30% of the thickness of conventional plates.
  • the folded edges of the plates are also provided with lengthwise pleats.
  • Fig. 1 Shown in Fig. 1 is the principle of how three heat exchanger plates la, 1b and lc, are stacked upon each other and offset 90° in relation to each other. This figure does not show the means of how the separate plates are connected with each other.
  • Each plate is equipped with lengthwise distance members 2, devised as pleats in the plate. This results in the formation of extended rectangular flow passages designated 3a and 3b for the air which is thus made to pass in cross-current.
  • the air flows are indicated by the arrows A and B, respectively.
  • the width "b" (Fig. 2a) of the flow passages is between 10 to 50 mm, preferably between 20 -30 mm, and their height "h" corresponding to the pleat height of the distance members is greater than 1.5 mm, preferably 2-10 mm. It has been found that this form of flow passages is beneficial in view of heat transfer, pressure drop, strength and production technology.
  • the plates of the heat exchanger are made of aluminium material.
  • the plates are equipped with a friction pressure drop forming fine structure 4 in the form of corrugations as shown in Fig. 2a and 2b.
  • the corrugations are preferably arranged at right angles to the distance members.
  • the distance members can be designed with a fine structure.
  • the design of the fine structure in greater detail is demonstrated by the schematic Fig. 2b which shows a cross-section of a contact plate.
  • the corrugations of the fine structure display a pleat height S which amounts to between 0.1 and 1 mm.
  • the fine structure of the plate lb has a wavelength v of between 1 and 5.mm, preferably 3 mm, and its shape is triangular as indicated in the figure. The shape may also be sinusoidal or some interlying shape.
  • a fine structural plate has a material thickness (t) of less than 0.1 mm, and the fine structural thickness (T) of the plates, defined as the total thickness of the plate areas with undeformed fine structure (4), i.e., S plus t, amounts to 0.1 and 1 mm, preferably 0.5 mm.
  • Fig. 2a Shown in detail and schematically in Fig. 2a is an end view of two heat exchanger plates la and lb. Formed between two distance members 2 in the lower plate and the upper plate is the air flow passage 3 which is thus shown in cross-section.
  • the sides 5a and 5b of the distance members 2 are accordint to one embodyment pressed together towards each other to form a small gap 6 at the underside of the plate.
  • One effect of the gap 6 is that it contributes towards some generation of turbulence in the air on the underside of the plate, which is sufficient to increase the heat transfer coefficient, but only contributes to a minor extent towards an increase of the pressure drop in the flow passage.
  • the fine structure of the plate Ib has a wavelength v of between 2-5 mm, preferably 3 mm, and its shape is sinusoidal as shown in the figure.
  • the shape may also be triangular or some interlying shape.
  • FIG. 3 Shown in Fig. 3 is how a plurality of exchanger plates are combined into a heat exchanger package.
  • the heat exchanger package is usually ar; ranged so that the heat exchanger plates are disposed vertically.
  • the heat exchanger body is inclined towards the horizontal plane to facilitate discharge of condensate water precipitated in the flow passage.
  • Fig. 4, 5a and 5b as well as 6 show in detail how a bottom heat exchanger plate according to the invention is connected at its end edge with a top heat exchanger plate.
  • a necessity for the heat exchanger package to function properly is that the plates are joined effectively, both from a mechanical and a sealing point of view. A leakage between the separated flow passages should be avoided as far as possible and may in some applications prove definitely harmful.
  • Fig. 6 shows how the heat exchanger plate terminating along the distance members at its two end sides 10a, b displays a lengthwise section of end zones lla, b. Each contact plate also displays at its two end sides 20a, b terminating across the distance members, a lengthwise section 21a, b, in which a folding edge 22a, b is arranged.
  • the plate displays the notches 26.
  • the edges 22a, b are intended to be joined with an adjacent plate in such a way that they will be folded around the adjacent edge zone area, by which a folded edge 23 is formed.
  • the folding edge 22a, 22b displays a distance section 25 which by its size corresponds to the distance between the adjacent plates determined by the pleat height, and forms a seal of the side for the corresponding flow passages 3a, 3b at the ends of the plates.
  • the folded edge 23 extends over the corresponding edge zone area and encloses this.
  • the edge 23 and the enclosing material also display a lengthwise pleating 24 which extends along the whole width of the plate and is designed to achieve locking of the edge 23 and, if necessary, thus prevent the folding edge 22a, b from springing back.
  • the fine structure in the pleating of the two plates is partly deformed owing to their being pressed together and forms an effective seal between the plates. In effect, the thickness resulting from the compression is not larger than the plate thickness T defined in figure 2b.
  • An especially purposeful embodiment according to the invention is the arrangement of downfolding the distance member, as shown in Fig. 5a, and then covering from the underlying plate it by the edge 23.
  • the fine structure of the plates stacked upon each other including the folding edge 22a, b and the edge 23) has been deformed so that the common thickness, on the whole, still is enclosed in the plate thickness T, as defined in the figure 2b.
  • This condition can be accomplished also when both sides 5a, 5b of the distance members 2 are provided with a fine structure.
  • the pleating 24 displays according the invention a wavelength Y and a waveheight y which are dimensioned so that they give rise to a stretching of the material that at least corresponds to the surface expansion ensuing from the deformation of the fine structure in the pleating.
  • the wavelength Y of the pleating amounts to about 10 mm and its waveheight y to about 2 mm.
  • the surface expansion of the fine structure amounts to between 1% and 10%, preferably 3%.
  • a very effective seal between the separate flow passages is achieved by this method.
  • the stretching of the folded edge 23 brought about (effected) by the lengtwise pleating 24 smoothes out the fine structure of the edge 23 and renders a pleated, smooth and tight joint.
  • the downfolded distance members 2 can be enclosed in thickness T of the plates thanks to the fine structure.
  • the shown embodiment of the plate heat exchanger is intended in the first instance for application in comfort ventilation plants, but obviously the invention is not limited to this embodiment.
EP19840116425 1983-12-29 1984-12-28 Plattenwärmetauscher Expired EP0147866B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84116425T ATE41228T1 (de) 1983-12-29 1984-12-28 Plattenwaermetauscher.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
SE8307215A SE8307215L (sv) 1983-12-29 1983-12-29 Plattvermevexlare
SE8307215 1983-12-29
SE8404845 1984-09-27
SE8404845A SE8404845L (sv) 1983-12-29 1984-09-27 Plattvermevexlare

Publications (3)

Publication Number Publication Date
EP0147866A2 true EP0147866A2 (de) 1985-07-10
EP0147866A3 EP0147866A3 (en) 1985-11-06
EP0147866B1 EP0147866B1 (de) 1989-03-08

Family

ID=26658606

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19840116425 Expired EP0147866B1 (de) 1983-12-29 1984-12-28 Plattenwärmetauscher

Country Status (5)

Country Link
EP (1) EP0147866B1 (de)
DE (1) DE3477052D1 (de)
DK (1) DK160587C (de)
FI (1) FI78983C (de)
NO (1) NO162312C (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2494059A (en) * 2011-08-26 2013-02-27 Hs Marston Aerospace Ltd Heat exchanger comprising a plurality of laminates

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105202960A (zh) * 2015-10-10 2015-12-30 安陆火凤凰铝材有限责任公司 一种铝管式换热器

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB510197A (en) * 1938-02-18 1939-07-28 Charles Otto Wagner Improvements relating to sheet metal heat interchanging apparatus for fluids
GB510206A (en) * 1938-03-17 1939-07-28 Charles Otto Wagner Improvements relating to heat interchange apparatus of the metal sheet or strip typefor fluids
US2596642A (en) * 1945-05-28 1952-05-13 Jarvis C Marble Heat exchanger
US3893509A (en) * 1974-04-08 1975-07-08 Garrett Corp Lap joint tube plate heat exchanger
FR2317617A1 (fr) * 1975-07-11 1977-02-04 Alusuisse Echangeur thermique en feuilles minces
FR2318398A1 (fr) * 1975-07-18 1977-02-11 Munters Ab Carl Procede de realisation d'un corps d'echange de chaleur pour des echangeurs a recuperation
FR2377598A1 (fr) * 1977-01-14 1978-08-11 Munters Ab Carl Echangeur de chaleur a plaques
GB2071838A (en) * 1979-08-23 1981-09-23 Hisaka Works Ltd Plate type heat exchanger
US4298061A (en) * 1980-08-15 1981-11-03 The Singer Company Heat exchanger with crimped flange seam

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB510197A (en) * 1938-02-18 1939-07-28 Charles Otto Wagner Improvements relating to sheet metal heat interchanging apparatus for fluids
GB510206A (en) * 1938-03-17 1939-07-28 Charles Otto Wagner Improvements relating to heat interchange apparatus of the metal sheet or strip typefor fluids
US2596642A (en) * 1945-05-28 1952-05-13 Jarvis C Marble Heat exchanger
US3893509A (en) * 1974-04-08 1975-07-08 Garrett Corp Lap joint tube plate heat exchanger
FR2317617A1 (fr) * 1975-07-11 1977-02-04 Alusuisse Echangeur thermique en feuilles minces
FR2318398A1 (fr) * 1975-07-18 1977-02-11 Munters Ab Carl Procede de realisation d'un corps d'echange de chaleur pour des echangeurs a recuperation
FR2377598A1 (fr) * 1977-01-14 1978-08-11 Munters Ab Carl Echangeur de chaleur a plaques
GB2071838A (en) * 1979-08-23 1981-09-23 Hisaka Works Ltd Plate type heat exchanger
US4298061A (en) * 1980-08-15 1981-11-03 The Singer Company Heat exchanger with crimped flange seam

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2494059A (en) * 2011-08-26 2013-02-27 Hs Marston Aerospace Ltd Heat exchanger comprising a plurality of laminates
GB2494059B (en) * 2011-08-26 2015-05-20 Hs Marston Aerospace Ltd Heat exchanger

Also Published As

Publication number Publication date
FI78983B (fi) 1989-06-30
DK160587C (da) 1991-09-09
NO162312B (no) 1989-08-28
FI845151L (fi) 1985-06-30
FI78983C (fi) 1989-10-10
DK160587B (da) 1991-03-25
EP0147866B1 (de) 1989-03-08
NO162312C (no) 1989-12-06
DK622484D0 (da) 1984-12-21
DE3477052D1 (en) 1989-04-13
FI845151A0 (fi) 1984-12-28
NO845268L (no) 1985-07-01
EP0147866A3 (en) 1985-11-06
DK622484A (da) 1985-06-30

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