EP0415584B1 - Stapelverdampfer - Google Patents

Stapelverdampfer Download PDF

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Publication number
EP0415584B1
EP0415584B1 EP19900308796 EP90308796A EP0415584B1 EP 0415584 B1 EP0415584 B1 EP 0415584B1 EP 19900308796 EP19900308796 EP 19900308796 EP 90308796 A EP90308796 A EP 90308796A EP 0415584 B1 EP0415584 B1 EP 0415584B1
Authority
EP
European Patent Office
Prior art keywords
coolant
stack type
ribs
type evaporator
evaporator according
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
EP19900308796
Other languages
English (en)
French (fr)
Other versions
EP0415584A3 (en
EP0415584A2 (de
Inventor
Kawakatsu Mikihito
Kenji Sakamoto
Hidenori Esaki
Yuji Yamamoto
Nobuyuki Okuda
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.)
Honda Motor Co Ltd
Showa Aluminum Can Corp
Original Assignee
Honda Motor Co Ltd
Showa Aluminum Corp
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 JP1223685A external-priority patent/JP2533197B2/ja
Priority claimed from JP10429190A external-priority patent/JPH043861A/ja
Application filed by Honda Motor Co Ltd, Showa Aluminum Corp filed Critical Honda Motor Co Ltd
Publication of EP0415584A2 publication Critical patent/EP0415584A2/de
Publication of EP0415584A3 publication Critical patent/EP0415584A3/en
Application granted granted Critical
Publication of EP0415584B1 publication Critical patent/EP0415584B1/de
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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—Evaporators

Definitions

  • the present invention relates to a stack type evaporator for use in the car cooling system or the like, and more particularly to a stack type evaporator which comprises a plurality of plate-shaped tubular elements each having inner paths for coolant, wherein a plurality of air paths are defined through and by a fin member interposed between one tubular element and the next.
  • evaporators for the uses mentioned above comprise tubular elements whose inner paths for coolant are in fluid communication with each other in such a state that a coolant circuit is formed between an inlet and an outlet of the coolant.
  • a mist of coolant enters the inlet and flows through the circuit so that heat exchange takes place between the coolant and the air passing through the air paths.
  • the coolant is thus gradually evaporated to become a gas which then flows out of the evaporator through the outlet.
  • Fig. 12 shows one of the known tubular elements (such as disclosed in Japanese Utility Model Publication Sho. 53-32375) which has one end portion formed with a delivery header 10 a and a return header 10 b .
  • a coolant stream circuit is formed such that coolant flows through the delivery header 10 a into the inside of the tubular member, advances toward the other end portion thereof where it makes a U-turn and then flows back to the return header 10 b .
  • Such a coolant stream within the circuit is made turbulent by the existence of many protruding inner ribs 70 possessed by each of dish-shaped core plates 60 which are secured to each other at their peripheries so as to form a space for the coolant circuit therebetween, the ribs 70 being disposed within the space.
  • the ribs 70 are oblique with respect to the flow direction of coolant stream, and as shown by solid lines and broken lines in Fig. 12, each rib 70 of one core plate 60 and each corresponding rib 70 of the other core plate firmly coupled with the one core plate intersect one another.
  • the U-turn of the coolant stream within the circuit of the tubular element is likely to cause a "channel" or uneven flow of coolant in the circuit, thereby bringing about a substantial decrease in the effective heat transfer surface.
  • the mutually intersection ribs 70 disposed oblique to the direction of coolant flow are disadvantageous in that pressure loss of coolant increases unfavourably in the tubular elements near an outlet port of the evaporator, in spite of lowered efficiency of heat transfer due to the increasing ratio of gas in the coolant which is getting near the outlet.
  • Such a disadvantage depreciates the value of an expected advantage, that is an improved heat transfer efficiency, which will be obtained owing to violent turbulence of coolant in the tubular elements disposed near an inlet port of the evaporator.
  • a stack type evaporator with fin members interposed between a plurality of stacked plate-shaped tubular elements with inlet and outlet header portions is disclosed in DE-A-3 536 325. Additionally an evaporator having tubular elements with coolant paths formed by alternating ribs at the core plates is disclosed in US-A-4 371 034.
  • An object of the present invention which was made in view of the problems in the known evaporators, is to provide a stack type evaporator which is low in its pressure loss of coolant but high in its heat transfer efficiency.
  • a stack type evaporator comprises a plurality of plate-shaped tubular elements of a predetermined thickness, the tubular elements being stacked side by side in a direction of the thickness with a fin member interposed between two of such tubular elements and being composed respectively of a pair of dish-shaped core plates which are provided with a plurality of ribs protruding from a flat body and are fixed to each other at their peripheries so as to form coolant paths, in the pair of core plates facing each other with their ribs arranged inwardly, characterized in that each tubular element comprises an inlet header portion disposed at an end and an outlet header portion disposed at another end, the ribs of each core plate extending parallel with a flow direction of the coolant and arranged at regular intervals of distance to form a row in a direction perpendicular to the flow direction and each rib protruding from one of the paired core plates being disposed intermediate between two ribs protruding from the other core plate in the pair so that end surfaces
  • the coolant which flows through the tubular elements each provided with the inlet header portion at one end and with the outlet header portion at the other end need not to make any U-turn.
  • any uneven flow of the coolant does not occur in the evaporator of the invention, thereby eliminating the problem that the effective heat transfer surface is decreased and the pressure loss is increased due to the U-turn of coolant in the known apparatuses.
  • the coolant can flow through the coolant circuit of evaporator smoothly without being disturbed by the ribs which are formed parallel with the flow direction so that heat transfer takes place uniform throughout the circuit extending from an inlet pipe to an outlet pipe for the coolant, with a decreased pressure loss and with an improved overall efficiency or heat transfer.
  • such a high rib pitch in the invention does not significantly reduce the equivalent diameter of coolant paths but makes easier the manufacture of the core plates in the invention. It is also advantageous that the outer flat surfaces of the core plates are so broad that the area of contact with the corrugated fins is increased to further improve the heat exchange efficiency.
  • Embodiments of the invention which are applied to stack type, evaportors made of aluminum or its alloys for use in the car cooling system will now be described in detail.
  • Figs. 1 to 4 illustrate a stack type evaporator manufactured according to a first embodiment of the invention.
  • This evaporator comprises a plurality of plate-shaped tubular elements 1 which are disposed upright and stacked side by side in a horizontal direction.
  • the evaporator also comprises corrugated fin members 2, most of them being interposed respectively between two adjacent tubular elements 1 and remaining one of them disposed outside of the outer-most tubular element.
  • Each corrugated fin member 2 is fixed integral with the tubular elements.
  • Each of the tubular elements 1 is, as shown in Figs. 1 to 4, provided with upper and lower header portions 1 a and 1 b (which function either as an inlet or as an outlet header portion, as will become apparent from the description given hereinafter) which are bulky and disposed respectively at opposite ends in a longitudinal direction of the element.
  • Coolant paths 1 c extending longitudinally of the element 1 are formed intermediate between and in fluid connection with the header portions 1 a and 1 b , the coolant paths 1 c as a whole thereby assuming a flat path for coolant.
  • the adjacent tubular elements 1 are tightly combined one another at their header portions 1 a and 1 b which are in close contact and in fluid connection with each other owing to coolant-flowing openings 1 d .
  • the upper header portion 1 a of the right-hand (in the drawings) outermost tubular element 1 is connected to a coolant inlet pipe 3
  • the upper header portion 1 a of the left-hand (in the drawings) outermost tubular element 1 is connected to a coolant outlet pipe 4.
  • Small blind plates are mounted between the upper header portions 1 a of the second and third tubular elements near the coolant inlet, between those of the eighth and ninth ones and between the fourteenth and fifteenth ones near the coolant outlet so as to close the coolant-flowing openings 1 d .
  • the small blind plates are also interposed between the lower header portions 1 b of the fifth and sixth tubular elements and between those of the eleventh and twelfth ones so as to close the coolant-flowing openings 1 d .
  • Such blind plates cause the coolant flowing into the evaporator through the inlet pipe 3 to advance in zigzag patterns changing its flow direction at every boundary between adjacent groups of the tubular elements.
  • Heat exchange is effected between the coolant flowing in this way and air streams passing through air paths which are formed between the adjacent tubular elements and through the fin members 2, before the coolant leaves the evaporator through the outlet pipe 4.
  • a side plate 5 (Fig.4) is disposed outside of the outermost corrugated fin member 2.
  • the tubular elements 1 are each made by arranging two dish-shaped core plates 6 into an inside-to-inside relation and by subsequently soldering them at their perlpheries 6 a to be integral with each other.
  • the core plates 6 are manufactured by the pressing of any appropriate metal, preferably by the pressing of a brazing sheet.
  • the brazing sheet comprises an aluminum-based alloy core sheet having its front and back surfaces covered with a brazing metal which is applied by the cladding technique. End portions of each core plate 6 protrude outwardly to form expanded portions 9.
  • a coolant-flowing opening 1 d is formed through a ridge of each expanded portion, in a transverse direction of the core plate extends.
  • a flange 9 a protrudes from a semicircular edge of the elliptical opening 1 d .
  • ribs 7 Formed on inner surface of the core plate 6 are ribs 7 which contribute to the improvement of heat transfer efficiency in the evaporator described above.
  • the ribs 7 run parallel with a flow direction of coolant, i.e. longitudinally of the core plate and extend almost all over the entire length thereof.
  • the ribs 7 are located at regular intervals in the transverse direction although they are slightly offset as a whole toward one side edge of the core plate 6.
  • Two core plates 6 each having ribs 7 are brought into close contact so as to be soldered at their perlpheries 6 a .
  • the rib 7 of one core plate 6 is shown by solid lines and that of the other core plate is shown by broken lines alternate with each other. End surfaces of the ribs 7 of one core plate 6 tightly engage with and are soldered to a flat body 8 between two adjacent ribs 7 of the other core plate whereby the plurality of coolant paths 1 c are defined straight from the delivery header 1 a to the return header 1 b within tubular element 1.
  • Such straight coolant paths 1 c enhance smoothness of coolant flow by preventing uneven flow or violent agitation of the coolant from taking place in the tubular element 1. Further, the coolant flows so uniformly through all the paths that heat transfer is efficiently effected improving the heat transfer capacity of the evaporator.
  • any excessively high accuracy is not required in manufacturing this evaporator since the end surfaces of the ribs 7 in one core plate need not be strictly aligned with each other but may merely be placed on and soldered to the relatively wide flat body 8 of the other core plate 6, in a state such that as already described the ribs of two core plates alternate in a direction perpendicular to the flow direction of coolant.
  • This structure is also advantageous in that the two core plates 6 can be easily and securely soldered to enhance the mechanical strength and pressure resistance of the tubular elements 1 in the evaporator. Furthermore, such a structure is also effective to increase the heat transfer surface and to raise the heat transfer efficiency.
  • Another important feature of this embodiment resides in the shape of the ribs 7 which are wider at their ends so that the coolant paths 1 c are constricted at their portions near the inlet and outlet. This enables the coolant to flow more uniformly between the paths, preventing any inadvertent decrease in the effective surface of heat transfer.
  • width W1 of ribs 7 so as to fall within a range from two to four times the thickness "t" of the plate, as illustrated in Fig. 2.
  • an equivalent diameter of the coolant paths 1 c is designed to be as small as possible.
  • the evaporator in the second embodiment is also provided with the tubular elements 101 which have at their longitudinal ends an upper header portion 101 a and a lower header portion 101 b of a bulky shape.
  • the plate-like tubular elements 101 are disposed upright and stacked side by side with corrugated fin member 102 interposed between two of such elements.
  • One corrugated fin member 102 is located outside of the outermost tubular element 101 and is covered with a side plate 105.
  • Fluid communication passages formed through coolant-flowing openings 101 d is closed between the upper header portions 101 a of the fifth and sixth tubular elements near a coolant inlet, and between those of the fourteenth and fifteenth ones near a coolant outlet. Similarly, the passages through the openings 101 d are closed between the lower header portions 101 b of the tenth and eleventh tubular elements. such a local closing of the passages causes the coolant flowing into the evaporator through an inlet pipe 103 via an inlet header 103 a to advance zigzag changing its flow direction at every boundary between adjacent groups of the tubular elements, before it flows out of the evaporator through an outlet pipe 104 via an outlet header 104 a .
  • the tubular element 101 are constructed, as is in the first embodiment, by facing two dish-like core plates 106 to each other and by soldering them integral with each other. Ribs 107 protruding from the inner surfaces of the core plates 106 and arranged at regular intervals longitudinally of the plates form coolant paths 101 c which extend straight within each tubular element 101, from an upper header portion 101 a to a lower header portion 101 b .
  • Upper and lower expanded portions 109 of the core plates 106 are of an elliptical shape, as shown in Figs. 5, 8 and 9, which allows three rows of coolant-flowing openings 101 d to be formed therethrough.
  • Lugs 109 b which are formed corresponding to the recesses 109 a are engaged therewith to provide additional soldered surfaces which will improve the pressure resistance of the upper and lower header portions 101 a and 101 b so as to withstand well the pressure of coolant.
  • Protrusions 106 b on the surfaces of the core plates 106 are used to place the corrugated fin members 102 in position.
  • the protrusions 106 b are located adjacent to but more inwardly than the expanded portions 109 and are arranged between the ribs 107 as well as outside of the outermost rib 107 in such a state as forming rows.
  • the upper and lower rows of the protrusions 106 b support as shown in Fig. 11 the upper and lower ends of the corrugated fin members 102, respectively, when the tubular elements 101 and the fin members 102 are temporarily assembled to alternate with each other before they are soldered.
  • Such gaps will function as draining gaps 125 after all the integral parts of the evaporator are bonded to each other in one and single operation by, for example, the soldering method.
  • the inner width of the expanded portions 109 is preferably made substantially the same as that of a flat pipe portion 108.
  • Side walls 121 which cover the portions 108 and 109 continuously extend straight from the inside of the flat pipe portion 108 towards the upper and lower header portions 101 a and 101 b whereby all of the coolant paths 101 c including the outermost one are straight fluid connection with the header portions 101 a and 101 b .
  • the side plates 105 have a plurality of inner channels 128 which are formed by, for instance, the pressing of metal sheet to extend vertically and parallel with each other.
  • Such inner channels 128 provide vertical drain ducts 129 between the side plate 105 and the corrugated fin member 102.
  • heat transfer takes place between the stream of coolant and the stream of air, the former entering the evaporator through the inlet pipe 103 to flow through the evaporator and leave it through the outlet pipe 104, while the latter is flowing through air paths defined in the corrugated fin members 102 disposed between two tubular elements 101 or between one tubular element 101 and the side plate 105.
  • the heat of the air stream is absorbed by the evaporator so that a considerable amount of condensed water will be produced in the air paths between two tubular elements 101 or between the outermost tubular element 101 and the side plate 105, or such condensed water will enter the air paths.
  • drain ducts 126 (Fig. 10) which are defined between the outer surface of tubular elements and the corrugated fin members 102 due to recesses formed by the ribs 107. Then, the condensed water will be discharged to the outer bottom surface and the lower header portions 101 b .
  • Depth "D2" of the inner channels 128 is designed such that the amount of condensed water can smoothly flow, and may preferably be set at 0.5 mm or more.
  • the inner channels 128 are formed by corrugation of the side plates 105 so that rigidity thereof is increased. Therefore, load can be uniformly imparted to the entire width of a temporary assembly consisting of the side plates 105 and pairs of the alternating tubular elements 101 and fin members 102, the pairs being interposed between the side plates 105 in "banding" state before the soldering process.
  • the increased rigidity can make thinner the side plates 105 to about 0.5 mm, whose thickness has been about 1.6 mm in the known evaporators.
  • the lowermost portions of the side plates 105 are pressed to be header supporting tongues 130 which abut the end surfaces of the lower header portions 101 b .
  • the inner channels 128 extend across the tongues 130, continuously from the main portions of the side plates. This structure of the end plates not only ensures the drainage of condensed water but also increases the mechanical strength at the outer surfaces of lower header portions 101 b of the outermost tubular elements 101, to which portions 101 b neither the header 103 a nor the header 103 b is attached after all of the evaporator parts are made rigidly integral with each other.

Claims (12)

  1. Stapelverdampfer mit vielen plattenförmigen Röhrenelementen (1) bestimmter Dicke , die Seite an Seite in Richtung der Dicke mit einem Kühlrippenglied (2) gestapelt sind, das zwischen zwei solchen Röhrenelementen angeordnet ist und sich jeweils aus einem Paar napfförmiger Kernplatten (6) zusammensetzt, die mit vielen, aus einem flachen Körper (8) herausragenden Rippen (7) versehen und an ihren Rändern aneinander derart befestigt sind, daß Kühlmittelwege gebildet werden, wobei sich die Kernplatten mit ihren innen angeordneten Rippen gegenüberliegen, dadurch gekennzeichnet, daß jedes Röhrenelement (101) an dem einen Ende einen Eingangswasserkastenteil (1a) und an dem anderen Ende einen Ausgangswasserkastenteil (1b) aufweist, daß die Rippen (7) jeder Kernplatte (6) parallel zur Kühlmittelströmungsrichtung verlaufen und in regelmäßigen Abstandsintervallen derart angeordnet sind, daß sie eine Reihe in senkrecht zur Strömungsrichtung stehender Richtung bilden, daß jede von einer der gepaarten Kernplatten (6) herausragende Rippe (7) in der Mitte zwischen zwei aus der anderen Kernplatte (6) des Paars herausragenden Rippen (7) derart angeordnet ist, daß Endflächen der Rippen (7) der einen Kernplatte (6) abwechselnd mit dem flachen Körper (8) der anderen Kernplatte (6) des Paars verbunden sind, wobei die Kühlmittelwege parallel zueinander und vom Eingangswasserkastenteil (1a) gerade zum Ausgangswasserkastenteil (1b ) verlaufen, und daß ferner die Rippen (7) an den Seitenflächen der Röhrenelemente Außenflächen besitzen, die jeweils viele, oben offene, rinnenartige, von einem Ende der Röhrenelemente zum anderen Ende führende Entwässerungskanäle (126) bilden, wobei das auf der Seitenfläche jedes Röhrenelements kondensierte Wasser durch die am anderen Ende zu entleerenden Entwässerungskanäle fließt, so daß das Auftreten eines Wassertropfenflugvorgangs wirksam verhindert wird.
  2. Stapelverdampfer nach Anspruch 1, dadurch gekennzeichnet, daß die Röhrenelemente (1) vertikal angeordnet und Seite an Seite in horizontaler Richtung gestapelt sind.
  3. Stapelverdampfer nach Anspruch 1, dadurch gekennzeichnet, daß die Kernplatten (6) durch Pressen eines Metallblechs gefertigt sind, das ein Kernmaterial aus einer Aluminiumlegierung aufweist und dessen Vorderfläche und Rückfläche mit einem Lötmittel nach dem Plattierungsverfahren überzogen sind.
  4. Stapelverdampfer nach Anspruch 1, dadurch gekennzeichnet, daß die Kernplatten (6) an ihren Enden mit elliptischen Aufweitteilen (9) ausgestattet sind, die Rückenteile mit einer Reihe von Kühlmittelfließöffnungen aufweisen.
  5. Stapelverdampfer nach Anspruch 4, dadurch gekennzeichnet, daß die Aufweitteile (9) der einen Kernplatte (6) an ihren Außenflächen Ausnehmungen aufweisen, die zwischen den Kühlmittelfließöffnungen liegen und die an entsprechende Vorsprünge der anderen Kernplatte angepaßt und mit diesen verbunden sind.
  6. Stapelverdampfer nach Anspruch 1, dadurch gekennzeichnet, daß die Kernplatten (6) Dorne aufweisen, die die Positionen der oberen und unteren Endfläche der gewellten Kühlrippenglieder festlegen.
  7. Stapelverdampfer nach Anspruch 4, dadurch gekennzeichnet, daß die Kernplatten (6) so ausgebildet sind, daß die Aufweitteile dieselbe Innenbreite wie die flachen Röhrenteile haben, wobei alle Kühlmittelwege einschließlich des äußersten Kühlmittelweges in gerader Fluidverbindung mit der Innenseite der Wasserkastenteile (1a, 1b) stehen.
  8. Stapelverdampfer nach Anspruch 1, dadurch gekennzeichnet, daß die Rippen (7) an ihren Enden weiter als an ihren Mittelteilen sind, wobei die Kühlmittelwege in der Nähe der Eingangswasserkastenteile (1a) und der Ausgangswasserkastenteile (1b) verengt sind.
  9. Stapelverdampfer nach Anspruch 1, dadurch gekennzeichnet, daß die Rippen (7) eine Breite aufweisen, die in den Bereich von zweimal der Dicke der Kernplatten fällt.
  10. Stapelverdampfer nach Anspruch 1, dadurch gekennzeichnet, daß eines der Kühlrippenglieder (102) außerhalb jedes äußersten Röhrenelements (101) angeordnet ist und daß eine vertikale Innenkanäle aufweisende Seitenplatte (105) an der Außenseite eines Kühlrippenglieds (102) angeordnet ist, wobei Entwässerungsführungen (129) längs den Innenkanälen (128) zwischen der Seitenplatte (105) und einem Kühlrippenglied (102) vorgesehen sind.
  11. Stapelverdampfer nach Anspruch 10, dadurch gekennzeichnet, daß die Innenkanäle (128) parallel zueinander verlaufen.
  12. Stapelverdampfer nach Anspruch 10 oder 11, dadurch gekennzeichnet, daß die Innenkanäle (128) eine Tiefe von o,5mm oder mehr haben.
EP19900308796 1989-08-30 1990-08-09 Stapelverdampfer Expired - Lifetime EP0415584B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP1223685A JP2533197B2 (ja) 1989-08-30 1989-08-30 空気調和機用積層型蒸発器
JP223685/89 1989-08-30
JP104291/90 1990-04-18
JP10429190A JPH043861A (ja) 1990-04-18 1990-04-18 積層型蒸発器

Publications (3)

Publication Number Publication Date
EP0415584A2 EP0415584A2 (de) 1991-03-06
EP0415584A3 EP0415584A3 (en) 1991-12-18
EP0415584B1 true EP0415584B1 (de) 1994-03-30

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EP19900308796 Expired - Lifetime EP0415584B1 (de) 1989-08-30 1990-08-09 Stapelverdampfer

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EP (1) EP0415584B1 (de)
DE (1) DE69007709T2 (de)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5800673A (en) * 1989-08-30 1998-09-01 Showa Aluminum Corporation Stack type evaporator
US5470431A (en) * 1990-08-20 1995-11-28 Showa Aluminum Corp. Stack type evaporator
US5514248A (en) * 1990-08-20 1996-05-07 Showa Aluminum Corporation Stack type evaporator
US5125453A (en) * 1991-12-23 1992-06-30 Ford Motor Company Heat exchanger structure
CA2075686C (en) * 1992-04-03 2003-02-11 Nobuyuki Okuda Stack type evaporator
KR0143540B1 (ko) * 1992-08-27 1998-08-01 코오노 미찌아끼 편평튜브와 물결형휜을 교호로 적층해서 이루어진 적층형 열교환기 및 그 제조방법
AU668403B2 (en) * 1992-08-31 1996-05-02 Mitsubishi Jukogyo Kabushiki Kaisha Stacked heat exchanger
KR100353020B1 (ko) * 1993-12-28 2003-01-10 쇼와 덴코 가부시키가이샤 적층형열교환기
JPH08136086A (ja) * 1994-11-01 1996-05-31 Nippondenso Co Ltd 冷媒蒸発器
JPH08200977A (ja) * 1995-01-27 1996-08-09 Zexel Corp 熱交換器用偏平チューブ及びその製造方法
FR2755217B1 (fr) * 1996-10-28 1999-01-08 Valeo Climatisation Evaporateur a plaques empilees perfectionnees pour installation de climatisation, notamment de vehicule automobile
DE69816260T2 (de) * 1998-02-05 2004-06-03 Denso Corp., Kariya Mit mehreren wärmeleitenden Platten ausgeführter Wärmetauscher
CN106610151B (zh) * 2015-10-22 2019-05-07 丹佛斯微通道换热器（嘉兴）有限公司 一种热交换器
JP2018066534A (ja) * 2016-10-21 2018-04-26 パナソニックＩｐマネジメント株式会社 熱交換器およびそれを用いた冷凍システム
CN107014230A (zh) * 2017-03-30 2017-08-04 贵州永红航空机械有限责任公司 一种内部折流式多流程板翅式散热器

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* Cited by examiner, † Cited by third party
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US4371034A (en) * 1979-08-03 1983-02-01 Hisaka Works, Limited Plate type evaporator
JPS5623700A (en) * 1979-08-03 1981-03-06 Fuji Heavy Ind Ltd Heat exchanger
US4712612A (en) * 1984-10-12 1987-12-15 Showa Aluminum Kabushiki Kaisha Horizontal stack type evaporator
JP2646580B2 (ja) * 1986-12-11 1997-08-27 株式会社デンソー 冷媒蒸発器

Also Published As

Publication number Publication date
EP0415584A3 (en) 1991-12-18
DE69007709D1 (de) 1994-05-05
DE69007709T2 (de) 1994-07-14
EP0415584A2 (de) 1991-03-06

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