EP0611941B1 - Plattenwärmetauscher und entsprechende Platten - Google Patents

Plattenwärmetauscher und entsprechende Platten Download PDF

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Publication number
EP0611941B1
EP0611941B1 EP94200302A EP94200302A EP0611941B1 EP 0611941 B1 EP0611941 B1 EP 0611941B1 EP 94200302 A EP94200302 A EP 94200302A EP 94200302 A EP94200302 A EP 94200302A EP 0611941 B1 EP0611941 B1 EP 0611941B1
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EP
European Patent Office
Prior art keywords
plate
ribs
type
plates
heat exchanger
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Expired - Lifetime
Application number
EP94200302A
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English (en)
French (fr)
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EP0611941A2 (de
EP0611941A3 (de
Inventor
Flavio Mele
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GIANNONI S.P.A.
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GIANNONI SpA
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Publication of EP0611941A2 publication Critical patent/EP0611941A2/de
Publication of EP0611941A3 publication Critical patent/EP0611941A3/de
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Publication of EP0611941B1 publication Critical patent/EP0611941B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media

Definitions

  • the present invention relates to a plate-type heat exchanger for liquids, specifically water, being of the type which is used in so-called compound boilers used at one time for space heating and dispensing heated water.
  • a boiler is arranged to heat the water in a closed primary circuit, which water is circulated, usually by means of low-head pumps, through the heating system and simultaneously supplied to the primary branch of a heat exchanger having a secondary branch connected to the water supply.
  • the output of the secondary branch is connected to the home hot-water distribution network.
  • a heat exchanger for such an application is to meet several conflicting requirements: it should be quite compact, possess high exchange efficiency, and produce limited pressure drops, especially across the primary circuit.
  • the liquid flow through the sanitary circuit is to also ensure effective and full removal of scale on the occasion of periodical servicing, that should desirably be kept to a minimum.
  • Plate heat exchangers have been known for this kind of application which are formed by a plurality of identical plates juxtaposed and attached to one another to form a bank of chambers consisting of first and second sets of adjacent chambers to one another, with the chambers of one set being communicated together through two sets of input and output openings, respectively, and with each chamber in the first set intervening between two chambers in the second set excepting the end chambers in the bank.
  • the plates are generally rectangular in shape, designed for upright installation, and have a plurality of raised ribs on the plate face, which ribs are formed by deep drawing and generally arranged in a chevron pattern along the direction of greater length or in a diagonal pattern.
  • the plates which are identical with one another, are juxtaposed to one another with the rib elevation pointing in the same direction throughout, but the chevron pattern pointing alternately in one and the opposite directions.
  • chambers which are identical with one another and formed by two parallel walls held apart by the rib height, the tips of the ribs bearing on an adjacent plate in a discontinuous fashion broken at the crossovers of the ribs located on opposite walls.
  • the ribs form a plurality of V-shaped channels communicated to one another at the crossovers with opposite ribs to produce a grid-like labyrinth which provides a flow path in a direction generally corresponding to the symmetry axis of the V-shaped ribs for a liquid admitted into the chambers.
  • the ribs perform multiple functions: additionally to stiffening the plates, which should be made thin for a good heat transfer, consistent with the requirements of operation under a pressure, they are effective to increase the transfer area, somewhat spread the flow over the entire chamber cross-section, and induce a turbulent motion in the liquid admitted into the exchanger, which ensures good transfer efficiency.
  • Heat exchangers of this kind are disclosed in US 4,249,597 (Van P. Carey) and CA 1 189 852 (Federer J.A. et al.).
  • the two hydraulic circuits formed by the exchanger which only differ by the size of the liquid inlet/outlet opening, are identical and present the same outflow cross-section.
  • the pressure drop across the sanitary circuit would be about 0.22 bar.
  • the pressure drop across the sanitary circuit is negligible compared to the normal conditions of water supply from the distribution network (3 to 6 bar)
  • the pressure drop across the primary is specially troublesome and cost-intensive and requires that circulation pumps of adequate head and power be used in the primary.
  • the thickness of the plates made of stainless steel, an illustrative value of 0.4 mm, the thickness of the chambers, i.e. the free distance between plates, would be in the 2 to 3 mm range.
  • the plate-type heat exchanger of this invention wherein a high transfer efficiency is ensured by a primary circuit exhibiting low pressure drops and a secondary circuit of increased length having a constrained flow path which is smooth and free of stagnation areas and ensures reduced formation of calcareous deposit, longer service life and more effective service interventions.
  • the plate-type heat exchanger of this invention being implemented with two different types of juxtaposed plates, a first type being provided with raised ribs intended to contact a flat surface of a plate of the second type to form a first type of labyrinth chamber which ensures a fixed path for the flow through the sanitary circuit with greater length and smaller cross-section than the primary circuit, while by placing a plate of the second type next to that of the first type, on the opposite face from that with the raised ribs, a second type of chamber is formed which ensures increased flow-through cross-section and decreased flow path length for the primary circuit flow.
  • Both plate types are provided with a second plurality of ribs intended for juxtaposition, preferably but not necessarily with the same orientation, which increase the transfer area to form a labyrinth across a perpendicular cross-section to the plane of the plates which ensures a flow cross-section with no abrupt changes, and hence with no major pressure drops either in the primary or the secondary circuit, while still generating the required turbulent flow due to the change in direction imparted to the flow.
  • the second plurality of ribs comprise at least two sets of ribs, a first set of ribs which extend along a transverse direction to the flow direction through the labyrinth of the first chamber type, and a second set of ribs which extend along the flow direction through the labyrinth of the first chamber type.
  • the first set of ribs is arranged proximate to the inlet of the sanitary circuit and cause, in relation to a corresponding sanitary outlet section of equal length, greater turbolence which enhances the efficiency of heat transfer in the exchanger area with the largest temperature differential, for a modest increase in the overall pressure drop due to uneven distribution of the load losses.
  • the plates of generic rectangular shape, have a rim or frame whose sides of grater lenght at least are slighty convex.
  • all the sides are convex and radiused each to the other and suitably slanted as to the plane of the plate, so as to form a conoidal surface, rather than pyramidal.
  • This surface provides a precise matching among plates and assures a perfect brazing of the plates among them.
  • the arrangement, in the two plate types, of the several sets of ribs of the second plurality is set so as to leave between adjacent sets a flat zone or portion of the plate, each provided or not with a rib of the first plurality.
  • the two plate types can be combined to obtain a whole family of heat exchangers having differing features and performances, suitable for differing applications and meeting differing requirements.
  • a first plate type 1 consists of an element, generally rectangular in shape (more properly, according to an aspect of the invention, having convex sides, at least the longer ones, which has four circular openings 2, 3, 4, 5 arranged proximate to the apices of the rectangle, and a slightly cone-shaped rim or frame 6 deep drawn from a flat sheet, preferably of stainless steel, from which the plate is formed.
  • the plate 1 is also provided with a first plurality of straight parallel ribs 10, 11, 12, 13 extending crosswise to the direction of greater spread of the plate 1, and therefore, horizontal in Figure 1.
  • the ribs being raised above the plate surface as viewed in Figure 1, are alternately offset from one another, with one end in contact with opposite walls of the frame 6 and the other end away from the frame.
  • This meander constitutes a flow passage for a liquid admitted into the labyrinth, such as through the opening 5, and discharged through the opening 2.
  • the flow passage has a much greater length than the height of the plate, and an outflow cross-section which is defined by the height of the ribs 10, 11, 12, 13 and their mutual spacing.
  • the plate 1 is also provided, additionally to the first plurality of ribs 10, 11, 12, 13, with a second plurality of ribs, which are also raised from the plate plane and have preferably, but not necessarily, a smaller height than the ribs of the first plurality.
  • the ribs being generally elongate and laid parallel to one another, are collectively denoted as sets thereof by the references 15, 17, 18, 19, 20, and as clearly shown in Figure 1, arranged in the outflow channel defined by the ribs 10, 11, 12, 13 along a variable direction with respect to the main direction of a liquid flow through the channel.
  • the ribs 15, 17 are elongate and arranged crosswise to the flow direction
  • the ribs 19, 20 are elongate and arranged substantially along the flow direction
  • the V-shaped ribs 18 are arranged partly along the flow direction and partly across it.
  • the second plurality of ribs serve, as explained hereinafter, the dual function of increasing the area of heat transfer between two fluids separated by the plate 1, and of producing a convenient turbulence in the flows of the two fluids for a more efficient transfer of heat.
  • Figures 5 to 8 show a second type of plate 21 of the heat exchanger according to the invention.
  • the plate 21, having a generally rectangular shape identical with that of the plate 1, is also provided with four openings 22, 23, 24, 25 identical with the openings 2, 3, 4, 5 in the plate 1 and arranged in the same pattern, a drawn rim 26 identical with the rim 6, and bearing collars 27, 28, 29, 30 which surround the homologous openings 22, 23, 24, 25 of the openings 2, 3, 4, 5, respectively.
  • the homologous collars 28, 30 are recessed below the plane of the plate 21, and the collars 27, 29, being the homologs of the collars 8, 9, are raised above the plane of the plate 21.
  • the plate 21 is also provided with a plurality of raised ribs, identical in pattern and shape with the ribs of the second plurality of ribs on the plate 1.
  • ribs are collectively denoted as sets thereof by the references 31, 32, 33, 34, 35, respectively corresponding to the sets 15, 17, 18, 19, 20.
  • the plate 21 has, between sets of ribs 31, 32, 34, 35, a continual flat surface for receiving the first plurality of ribs 10, 11, 12, 13 of the plate 1 thereon.
  • the plate 21 may also be provided with a plurality of parallel ribs being the homologs of the ribs 10, 11,12, 13 and recessed from the plate 21 rather than raised, in this case.
  • the combined elevation of the collars 16, 7 of the plate 1 and depression of the collars 28, 30 of the plate 21 are equal to the height or elevation of the ribs 10, 11, 12, 13.
  • the combined depression of the collars 8, 9 of the plate 1 and elevation of the collars 27, 29 of the plate 21 are equal to the height or elevation of the ribs 10, 11, 12, 13.
  • the chamber can be reached through the openings 2, 22 and 5, 25, the respective collars 8, 27 and 9, 29 whereof being spaced apart from each other.
  • the collars 28, 30 of the plate 21 are brought to bear on the corresponding collars 16, 7 of the plate 1, thereby shutting off the thus formed chamber from access through the openings 3, 4 in the plate 1 or the corresponding openings 23, 24 in the plate 21.
  • tops of the ribs 10, 11, 12, 13 will contact the flat surface of the plate 21 to form in the hollow the meander or flow channel described above.
  • the sets of ribs 15, 17, 18, 19, 20, respectively juxtaposed to the sets of ribs 31, 32, 33, 34, 35 form in the flow channel a labyrinth path which extends substantially in a perpendicular plane to the plane of the plate.
  • FIG 12 a sectional view taken in the plane VII-VII in Figure 1, shows in cross-section a section of the flow channel proximate to the openings 5, 25 along the flow direction, and brings out that the flow ⁇ of a liquid admitted into the channel is subjected to continual changes of direction as directed by the ribs.
  • outflow cross-section is variable, being slightly narrower at the sections defined by the rib walls.
  • Figure 13 a sectional view taken in the plane VIII-VIII in Figure 1, shows in cross-section a section of the flow channel proximate to the openings 2, 22 along a substantially perpendicular direction to the flow direction, and brings out that the flow ⁇ of a liquid admitted into the channel, at this section having a considerable heat transfer area, is subjected to no continual changes in direction or outflow cross-section.
  • any pressure drop of a moving fluid would be due essentially to the fluid internal viscosity and the residual fluid turbulence induced upstream.
  • the raised ribs 10, 11, 12, 13 on the plate 1 form no labyrinth within the chamber but merely an expanded cross-section passageway, and the resultant chamber constitutes a substantially straight, short flow channel between the openings 3, 23 and 4, 24 to which the plate ribs impart, as shown in Figure 11, a labyrinth pattern extending in a perpendicular plane to the plane of the plates.
  • the labyrinth ensures increased heat transfer area and convenient turbulence for a fluid admitted into the chamber, at much more limited load losses even with large flow rates because of the much shorter length of the flow section.
  • the primary circuit being formed by chambers of the second type in parallel with one another, is characterized by extremely low pressure drops, while the secondary or sanitary circuit, formed by chambers of the first type, is characterized by pressure drops which are not much higher and a circuit length effective to ensure a highly efficient transfer of heat.
  • the constrained flow path of the secondary circuit prevents the local formation of calcareous deposit and promotes, where necessary, a more effective descaling operation by forcing the descaling chemical through the same constrained path.
  • the heat transfer efficiency is further enhanced, at equal pressure drops, by the peculiar arrangement of the second plurality of ribs, which restrict to some extent the generation of turbulence, and attendant load losses, to a limited region of the chambers proximate to the secondary circuit inlet and the primary circuit outlet.
  • Figure 14 illustrates schematically the temperature variations of the two fluids, e.g. water, entering and exiting an exchanger in countercurrent relationship.
  • T1I and T2I Shown at T1I and T2I are the inflow temperatures of the primary and the secondary fluids, respectively, and at T1U, T2U the respective outflow temperatures.
  • the transfer of heat will, therefore, be stronger at the inlet than at the outlet, and it is in that region that the transfer efficiency ought to be ensured to prevent a laminar flow from generating, especially at small flow rates, temperature gradients within the fluid such as would limit the heat transfer rate.
  • the plate 1 may be provided with raised ribs such as 10, 11, 12, 13 which, instead of contacting the flat surface of a plate 21 overlying it, would contact corresponding recessed ribs in the plate 21.
  • the thickness of the chambers formed by the plates is essentially defined by the elevation and the depression of the collars, and may either be the same for both chamber types formed by the plates or be different, to adjust the average outflow cross-sections of the primary and secondary circuits for more or less different flow rates and make the pressure drops across the two circuits different.
  • the number of the plates and the chambers formed thereby may also be varied within a broad range to meet widely different space and capacity requirements.
  • connection of the exchanger thus formed to the primary and the secondary networks and the closure of the bank end plates are conventional and may be provided in a conventional manner.
  • an end plate denoted by the reference 40 may be similar to the plates of the first type, such as the plate 1, but without the openings 2, 3, 4, 5, thereby shutting off as by contact and brazing the openings 23 and 24 in the adjacent plate 41 of the second type to form in combination an end chamber of the first type.
  • a plate 42 may be provided, as by soldering or otherwise, with fittings 43, 44, 45, 46 for connection to inlet/outlet ducts of the primary and secondary circuits.
  • plates such as 1 an 21 may also be coupled together to form different type of chambers for the primary and secondary flow, by superimposing plates of type 1 to plates of type 21, the last one being rotated of 180° as to the position shown in fig. 5
  • opening 2 is axially aligned with opening 25 and likewise opening 5 is aligned with opening 22.
  • Collar 16 is coupled to collar 30 and likewise collar 7 is coupled to collar 28.
  • the contat point are distributed on the plate extension and, at equal plate thickness provide a higher pressure strenght by the exchanger so formed.
  • FIGs 15 and 16 show two plates modified to this purpose.
  • Plate 51 of fig. 15 has a ribs and openings arrangement equivalent to the one of the plate 1 of fig. 1.
  • the ribs all having equal height are of two kinds: a first kind of ribs, 52,53,54,55 extends alternately from one of the two plate side walls 155,56 having greater lenght, toward the opposite side wall, in a direction substantially perpendicular to the extension of such side walls so as to form a meander path in the plane of the path.
  • the ribs of the second kind are housed in this meander path. They are divided in a plurality of rib sets, the ribs in each set being parallel each to the other and extending in slanted direction as to the plate side walls of greater lenght.
  • Each rib set (possibly with the exception of ribs surrounding the flow input/output openings) form a band extending between opposed sidewalls of greater lenght of the plate.
  • the bands are spaced apart the one from the other by a flat portion or zone of the plate which portion too extends from a side wall of greater lenght towards the opposite one, not necessarily reaching it, as shown for better understanding only.
  • the ribs extend obliquely with opposed slanting from band to band.
  • the ribs of band 59 have a slape opposite to the one of the ribs in adjacent band 60.
  • ribs 52,53,54,55 (of the first type) is not exactly symmetrical relative to the center of the plate: it may be observed that while rib 52 is located within the spacing portion 62 in a position closer to the center of the plate, the rib 55 is symetrically located with an offset and a greater distance from the plate midline 66, the offset being equal to the rib width.
  • the ribs bands 57,58 are substantially arranged in specular relation to bands 61,60 relative to the midline 66 and band 59 comprises two half bands exactly specular as to the midline 66.
  • Figure 16 shows a second type of plate 67, equivalent to plate 21 of fig. 5, in the arrangement of ribs and opening.
  • Plate 67 has a size identical to the one of plate 51 and comprises a plurality of second kind ribs band 68,69,70,71,72 identically to bands 57,58,59,60,61 and identically located.
  • Plate 67 differs from plate 51 only for the reason that is not provided with ribs of the first kind, such as 52,53,54,55 in the spacing portions 73,74,75,76 corresponding to the spacing portions 62,63,64,65 of figure 15.
  • Plates of the first type only (figure 15), of the second type only (figure 16) or alternatively of the first and second type can be used to obtain heat exchangers having differing features and specifically meeting particular use requirements.
  • Plates of the first type may be superimposed the one to the other to form a bank, with a 180° center rotation, among adjacent plates.
  • a heat exchanger having a primary and sanitary circuit which circuits are identical each to the other and have a flow path in form of a meander in the plane of the plates.
  • the ribs of the second kind of two adjacent plate cross to form a labyrinth.
  • This kind of exchanger features high pressure drops and very high thermal transfer efficiency (perfect flow countercurrent).
  • Plates of the second kind may be superimposed the one to the other to form a bank, with a 180° center rotation among adjacent plates.
  • a heat exchanger is obtained having two identical primary and sanitary circuits where the fluid flows from one opening of the plates to the opening specular as to the plate midline 78.
  • the flow turbolence is provided by the labyrinth formed by the second kind ribs, distributed in bands and crossing each other.
  • Plates of the first and second type may be superimposed the one to the other to form a bank, with a 180° center rotation among adjacent plates as to the showing of figure 15,16.
  • a heat exchanger is obtained having a primary circuit completely different from the sanitary circuit, and similar to the one described with reference to the use of plates such as those of figure 1 and 5.
  • This exchanger is particularly suited for application where very high thermal exchange efficiency must be obtained with a low pressure drop on the primary circuit.

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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)
  • Separation By Low-Temperature Treatments (AREA)
  • Fuel Cell (AREA)

Claims (10)

  1. Plattenwärmetauscher, bei dem mehrere gerippte Platten nebeneinander liegen und aneinander befestigt sind, um eine Reihe von Kammern zu bilden, die aus einem ersten und einem zweiten Satz von gegenseitig angrenzenden Kammern besteht, wobei die Kammern jedes Satzes durch zwei Sätze von Einlaß- bzw. Auslaßöffnungen miteinander in Verbindung stehen, wobei jede Kammer des ersten Satzes mit Ausnahme der Endkammern in der Reihe zwischen zwei Kammern des zweiten Satzes angeordnet ist, wobei die Reihe der Kammern durch abwechselndes nebeneinander Anordnen von Platten eines ersten Typs (1, 51) und eines zweiten Typs (21, 67) gebildet ist, wobei die Platten des ersten Typs (1, 51) mit einer Vielzahl von parallelen Rippen (10, 11, 12, 13, 52, 53, 54, 55), die zueinander versetzt sind, versehen ist, wobei die Rippen über eine Seite der Platte (1, 51) erhaben und unter die andere Plattenseite vertieft sind, so daß sie beim Zusammenbringen mit einer entsprechenden Oberfläche einer Platte des zweiten Typs (21, 67) eine Kammer eines ersten Typs mit schlangenförmigem Verlauf, die in der Ebene der Platten liegt, durch nebeneinander Anordnen einer Platte eines zweiten Typs (21, 67) an die Seite mit den erhabenen Rippen der Platte des ersten Typs (1, 51) und eine Kammer eines zweiten Typs ohne schlangenförmigen Verlauf in der Ebene der Platten durch nebeneinander Anordnen einer Platte des zweiten Typs (21, 67) an die Seite der vertieften Rippen der Platte des ersten Typs (1, 51) bilden, wobei beide Plattentypen mit einer zweiten Vielzahl von Rippen (15, 17, 18, 19, 20, 31, 32, 33, 34, 35) versehen sind, die in ähnlicher Weise auf beiden Plattentypen angeordnet sind, wodurch beim nebeneinander Anordnen der beiden Plattentypen in einer beliebigen Reihenfolge die zweite Vielzahl von Rippen eine Labyrinthkammer bildet, die sich senkrecht zu der Ebene der Platten erstreckt.
  2. Wärmetauscher nach Anspruch 1,
    dadurch gekennzeichnet,
    daß die Berührungsfläche mit der ersten Vielzahl von Rippen die ebene Fläche der Platte des zweiten Typs ist.
  3. Wärmetauscher nach Anspruch 1,
    dadurch gekennzeichnet,
    daß die Berührungsfläche mit der ersten Vielzahl von Rippen die Spitze einer dritten Vielzahl von erhabenen Rippen auf der Platte des zweiten Typs ist, die in der entgegengesetzten Richtung zu derjenigen der ersten Vielzahl von Rippen vorsteht.
  4. Wärmetauscher nach Anspruch 1, 2 oder 3,
    dadurch gekennzeichnet,
    daß die zweite Vielzahl von Rippen einen ersten Satz (17) von länglichen Rippen aufweist, der sich in Querrichtung zur Strömungsrichtung durch die Kammer mit schlangenförmigem Verlauf erstreckt.
  5. Wärmetauscher nach Anspruch 4,
    dadurch gekennzeichnet,
    daß die zweite Vielzahl von Rippen einen zweiten Satz (19) von länglichen Rippen aufweist, der in Strömungsrichtung durch die Kammer mit schlangenförmigem Verlauf verläuft.
  6. Platte (21, 67) für einen Plattenwärmetauscher nach Anspruch 1, wobei die Platte (21, 67) eine Einfassung mit zwei abgewandten Seitenwänden (155, 56) größerer Länge und zwei abgewandten Seitenwänden kleinerer Länge und vier in den Ecken der Platte (21, 67) angeordnete Öffnungen (22, 23, 24, 25) aufweist, mit
    mehreren Sätzen (57, 58, 59, 60, 68, 69, 70, 71, 72) von Rippen, die nebeneinander verlaufen, wobei jeder Satz eine Reihe von Rippen bildet, die sich zwischen den abgewandten Seitenwänden größerer Länge (155, 56) erstreckt, wobei wenigstens eine Reihe der angrenzenden Reihen durch einen flachen Trennabschnitt (62, 63, 64, 65, 73, 74, 75, 76) der Platte, der sich von einer Seitenwand größerer Länge (155, 56) zu der entgegengesetzten erstreckt, auf Abstand gesetzt ist, wobei die Rippen bezüglich der Richtung der Seitenwände größerer Länge (155, 56) schräg verlaufen, wobei die Rippen über eine Seite der Platte (21, 67) erhaben und unter die andere Plattenseite vertieft sind.
  7. Platte (51) nach Anspruch 6, mit
    mehreren Rippen (52, 53, 54, 55), die über eine Seite der Platte erhaben und unter die andere Plattenseite vertieft sind, wobei sich jede Rippe in einem ersten, die Rippenreihen trennenden flachen Abschnitt (62, 63, 64, 65) abwechselnd von der einen oder der anderen Seitenwand (155, 56) größerer Länge in den Bereich des flachen Abschnitts zwischen den Seitenwänden größerer Länge erstreckt, um so einen schlangenförmigen Weg in der Ebene der Platte zu bilden.
  8. Platte nach Anspruch 6 oder 7,
    dadurch gekennzeichnet,
    daß die Rippen wenigstens eines Paar von angrenzenden Reihen (57, 58, 59, 60, 61, 68, 69, 70, 71, 72) sich wenigstens in der Nähe des flachen Trennabschnitts erstrecken, wobei ihre Schräge von Reihe zu Reihe in entgegengesetzter Richtung orientiert ist, und sie sich quer zu der Richtung der Rippen in der anderen Reihe des Paares erstrecken.
  9. Platte nach Anspruch 6, 7 oder 8,
    dadurch gekennzeichnet,
    daß die Platte rechteckförmig ist.
  10. Platte nach Anspruch 9,
    dadurch gekennzeichnet,
    daß wenigstens zwei Seitenwände größerer Länge (155, 56) der Einfassung konvex sind und eine konische Oberfläche zum Verbinden von angrenzenden Platten bilden.
EP94200302A 1993-02-19 1994-02-03 Plattenwärmetauscher und entsprechende Platten Expired - Lifetime EP0611941B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMI930323A IT1263611B (it) 1993-02-19 1993-02-19 Scambiatore di calore a piastre
ITMI930323 1993-02-19

Publications (3)

Publication Number Publication Date
EP0611941A2 EP0611941A2 (de) 1994-08-24
EP0611941A3 EP0611941A3 (de) 1995-07-05
EP0611941B1 true EP0611941B1 (de) 1999-12-22

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EP94200302A Expired - Lifetime EP0611941B1 (de) 1993-02-19 1994-02-03 Plattenwärmetauscher und entsprechende Platten

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DE (1) DE69422207T2 (de)
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DE102012013755A1 (de) 2012-07-12 2014-01-16 Al-Ko Kober Ag Wärmetauscherplatteneinheit, Wärmetauscher und Verfahren zur Herstellung eines Wärmetauschers
WO2020229162A1 (en) 2019-05-16 2020-11-19 Alfa Laval Corporate Ab A plate heat exchanger, a heat exchanging plate and a method of treating a feed such as sea water
US11486657B2 (en) 2018-07-17 2022-11-01 Tranter, Inc. Heat exchanger heat transfer plate

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JP3292128B2 (ja) * 1998-02-27 2002-06-17 ダイキン工業株式会社 プレート型熱交換器
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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001092788A1 (en) * 2000-06-02 2001-12-06 Rheem Australia Pty Ltd Flow path in water heater heat exchanger plates
DE102012013755A1 (de) 2012-07-12 2014-01-16 Al-Ko Kober Ag Wärmetauscherplatteneinheit, Wärmetauscher und Verfahren zur Herstellung eines Wärmetauschers
DE102012013755B4 (de) 2012-07-12 2021-11-18 AL-K0 THERM GmbH Wärmetauscherplatteneinheit, Wärmetauscher und Verfahren zur Herstellung eines Wärmetauschers
DE102012013755B8 (de) 2012-07-12 2022-01-13 Al-Ko Therm Gmbh Wärmetauscherplatteneinheit, Wärmetauscher und Verfahren zur Herstellung eines Wärmetauschers
US11486657B2 (en) 2018-07-17 2022-11-01 Tranter, Inc. Heat exchanger heat transfer plate
WO2020229162A1 (en) 2019-05-16 2020-11-19 Alfa Laval Corporate Ab A plate heat exchanger, a heat exchanging plate and a method of treating a feed such as sea water

Also Published As

Publication number Publication date
ITMI930323A0 (it) 1993-02-19
ITMI930323A1 (it) 1994-08-19
EP0611941A2 (de) 1994-08-24
DE69422207T2 (de) 2000-06-21
DE69422207D1 (de) 2000-01-27
EP0611941A3 (de) 1995-07-05
IT1263611B (it) 1996-08-27
ES2141191T3 (es) 2000-03-16

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