EP0415584A2 - Evaporateur de type empilé - Google Patents

Evaporateur de type empilé Download PDF

Info

Publication number
EP0415584A2
EP0415584A2 EP90308796A EP90308796A EP0415584A2 EP 0415584 A2 EP0415584 A2 EP 0415584A2 EP 90308796 A EP90308796 A EP 90308796A EP 90308796 A EP90308796 A EP 90308796A EP 0415584 A2 EP0415584 A2 EP 0415584A2
Authority
EP
European Patent Office
Prior art keywords
coolant
stack type
type evaporator
ribs
core
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
EP90308796A
Other languages
German (de)
English (en)
Other versions
EP0415584A3 (en
EP0415584B1 (fr
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/fr
Publication of EP0415584A3 publication Critical patent/EP0415584A3/en
Application granted granted Critical
Publication of EP0415584B1 publication Critical patent/EP0415584B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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.
  • 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.
  • the stack type evaporator in the invention comprises a delivery or inlet header at one end portion thereof and a return or outlet header at the other end portion in such a state that coolant may flow straight within each tubular element, which tubular elements comprise a plurality of ribs formed parallel with a flow direction of the coolant so that an overall pressure loss of the evaporator is decreased and heat transfer is effected uniform within a region defined between the inlet and outlet headers.
  • the 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, the pair of core plates facing each other with their ribs arranged inwardly, each tubular element further comprising an inlet header portion disposed at an end and an outlet header portion disposed at another end, wherein the ribs of each core plate extend parallel with a flow direction of the coolant and are arranged at regular intervals of distance to form a row in a direction perpendicular to the flow direction and wherein each rib protrvding from one of the paired core plates is disposed intermediate between two ribs protruding from the other core plate in the
  • 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 th 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP19900308796 1989-08-30 1990-08-09 Evaporateur de type empilé Expired - Lifetime EP0415584B1 (fr)

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 true EP0415584A2 (fr) 1991-03-06
EP0415584A3 EP0415584A3 (en) 1991-12-18
EP0415584B1 EP0415584B1 (fr) 1994-03-30

Family

ID=26444796

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900308796 Expired - Lifetime EP0415584B1 (fr) 1989-08-30 1990-08-09 Evaporateur de type empilé

Country Status (2)

Country Link
EP (1) EP0415584B1 (fr)
DE (1) DE69007709T2 (fr)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993013376A1 (fr) * 1991-12-23 1993-07-08 Ford Motor Company Limited Structure d'echangeur thermique
EP0563474A1 (fr) * 1992-04-03 1993-10-06 Showa Aluminum Corporation Evaporateur de type empilé
EP0584806A1 (fr) * 1992-08-27 1994-03-02 Mitsubishi Jukogyo Kabushiki Kaisha Echangeur de chaleur à plaques et procédé pour sa fabrication
EP0588117A1 (fr) * 1992-08-31 1994-03-23 Mitsubishi Jukogyo Kabushiki Kaisha Echangeur de chaleur à plaques
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
EP0710808A1 (fr) * 1994-11-01 1996-05-08 Nippondenso Co., Ltd. Evaporateur pour un réfrigérant
EP0807794A1 (fr) * 1993-12-28 1997-11-19 Showa Aluminum Corporation Echangeurs de chaleur à plaques
EP0724125A3 (fr) * 1995-01-27 1998-01-14 Zexel Corporation Tube plat pour échangeur de chaleur et son procédé de fabrication
FR2755217A1 (fr) * 1996-10-28 1998-04-30 Valeo Climatisation Evaporateur a plaques empilees perfectionnees pour installation de climatisation, notamment de vehicule automobile
US5800673A (en) * 1989-08-30 1998-09-01 Showa Aluminum Corporation Stack type evaporator
EP0935115A2 (fr) * 1998-02-05 1999-08-11 Denso Corporation Echangeur de chaleur fabriqué avec plusieurs plaques conductrices de chaleur
CN106610151A (zh) * 2015-10-22 2017-05-03 丹佛斯微通道换热器（嘉兴）有限公司 一种热交换器
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
CN109312993A (zh) * 2016-10-21 2019-02-05 松下知识产权经营株式会社 热交换器和使用它的制冷装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3028304A1 (de) * 1979-08-03 1981-02-19 Fuji Heavy Ind Ltd Waermeaustauscher
US4371034A (en) * 1979-08-03 1983-02-01 Hisaka Works, Limited Plate type evaporator
DE3536325A1 (de) * 1984-10-12 1986-05-07 Showa Aluminum K.K., Sakai, Osaka Waermeaustauscher
EP0271084A2 (fr) * 1986-12-11 1988-06-15 Nippondenso Co., Ltd. Evaporateur de réfrigérant

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3028304A1 (de) * 1979-08-03 1981-02-19 Fuji Heavy Ind Ltd Waermeaustauscher
US4371034A (en) * 1979-08-03 1983-02-01 Hisaka Works, Limited Plate type evaporator
DE3536325A1 (de) * 1984-10-12 1986-05-07 Showa Aluminum K.K., Sakai, Osaka Waermeaustauscher
EP0271084A2 (fr) * 1986-12-11 1988-06-15 Nippondenso Co., Ltd. Evaporateur de réfrigérant

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
AUTOMOTIVE INDUSTRIES vol. 146, no. 2, June 15, 1972, PHILADELPHIA pages 61 - 63; JAMES B. POND: 'philco-ford converts to all-aluminum evaporators ' *

Cited By (26)

* 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
US5514248A (en) * 1990-08-20 1996-05-07 Showa Aluminum Corporation Stack type evaporator
US5470431A (en) * 1990-08-20 1995-11-28 Showa Aluminum Corp. Stack type evaporator
WO1993013376A1 (fr) * 1991-12-23 1993-07-08 Ford Motor Company Limited Structure d'echangeur thermique
EP0563474A1 (fr) * 1992-04-03 1993-10-06 Showa Aluminum Corporation Evaporateur de type empilé
AU656429B2 (en) * 1992-04-03 1995-02-02 Showa Denko Kabushiki Kaisha Stack type evaporator
EP0584806A1 (fr) * 1992-08-27 1994-03-02 Mitsubishi Jukogyo Kabushiki Kaisha Echangeur de chaleur à plaques et procédé pour sa fabrication
US5417280A (en) * 1992-08-27 1995-05-23 Mitsubishi Jukogyo Kabushiki Kaisha Stacked heat exchanger and method of manufacturing the same
EP0709640A3 (fr) * 1992-08-31 1997-10-29 Mitsubishi Heavy Ind Ltd Echangeur de chaleur à plaques
EP0709640A2 (fr) * 1992-08-31 1996-05-01 Mitsubishi Jukogyo Kabushiki Kaisha Echangeur de chaleur à plaques
AU676116B2 (en) * 1992-08-31 1997-02-27 Mitsubishi Jukogyo Kabushiki Kaisha Stacked heat exchanger
EP0588117A1 (fr) * 1992-08-31 1994-03-23 Mitsubishi Jukogyo Kabushiki Kaisha Echangeur de chaleur à plaques
EP0807794A1 (fr) * 1993-12-28 1997-11-19 Showa Aluminum Corporation Echangeurs de chaleur à plaques
US5810077A (en) * 1993-12-28 1998-09-22 Showa Aluminum Corporation Layered heat exchanger
US5678422A (en) * 1994-11-01 1997-10-21 Nippondenso Co., Ltd. Refrigerant evaporator
EP0710808A1 (fr) * 1994-11-01 1996-05-08 Nippondenso Co., Ltd. Evaporateur pour un réfrigérant
EP0724125A3 (fr) * 1995-01-27 1998-01-14 Zexel Corporation Tube plat pour échangeur de chaleur et son procédé de fabrication
DE19746772B4 (de) * 1996-10-28 2007-01-25 Valeo Climatisation Verdampfer mit verbessertem Plattenpaket für eine Klimaanlage, insbesondere von Kraftfahrzeugen
FR2755217A1 (fr) * 1996-10-28 1998-04-30 Valeo Climatisation Evaporateur a plaques empilees perfectionnees pour installation de climatisation, notamment de vehicule automobile
DE19746772A1 (de) * 1996-10-28 1998-04-30 Valeo Climatisation Verdampfer mit verbessertem Plattenpaket für eine Klimaanlage, insbesondere von Kraftfahrzeugen
EP0935115A2 (fr) * 1998-02-05 1999-08-11 Denso Corporation Echangeur de chaleur fabriqué avec plusieurs plaques conductrices de chaleur
EP0935115A3 (fr) * 1998-02-05 2000-03-29 Denso Corporation Echangeur de chaleur fabriqué avec plusieurs plaques conductrices de chaleur
CN106610151A (zh) * 2015-10-22 2017-05-03 丹佛斯微通道换热器（嘉兴）有限公司 一种热交换器
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
CN109312993A (zh) * 2016-10-21 2019-02-05 松下知识产权经营株式会社 热交换器和使用它的制冷装置
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

Also Published As

Publication number Publication date
DE69007709T2 (de) 1994-07-14
EP0415584A3 (en) 1991-12-18
DE69007709D1 (de) 1994-05-05
EP0415584B1 (fr) 1994-03-30

Similar Documents

Publication Publication Date Title
US5152337A (en) Stack type evaporator
EP0234942B1 (fr) Echangeur de chaleur à plaques
AU668403B2 (en) Stacked heat exchanger
EP0415584B1 (fr) Evaporateur de type empilé
US6273183B1 (en) Heat exchanger turbulizers with interrupted convolutions
US4712612A (en) Horizontal stack type evaporator
US5125453A (en) Heat exchanger structure
CA1313183C (fr) Echangeur de chaleur a plaques
CA1064902A (fr) Echangeur de chaleur
US6938685B2 (en) Heat exchanger
US4958681A (en) Heat exchanger with bypass channel louvered fins
JP2007518053A (ja) 熱交換器およびその熱交換モジュール
US11624565B2 (en) Header box and heat exchanger
US4699209A (en) Heat exchanger design for cryogenic reboiler or condenser service
KR100414852B1 (ko) 열교환기용냉매유통관
JPH07167578A (ja) 積層型熱交換器
US5373895A (en) Heat exchanger
JPS63271099A (ja) 熱交換器
CA2214255C (fr) Agitateurs d'echangeur de chaleur avec enroulements interrompus
US1993872A (en) Radiator core
JP2602788Y2 (ja) 積層型エバポレータの素子
JPS63243688A (ja) 凝縮器
JP2533197B2 (ja) 空気調和機用積層型蒸発器
EP0769669A1 (fr) Echangeur de chaleur
JPS63161393A (ja) 凝縮器

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB

17P Request for examination filed

Effective date: 19920305

17Q First examination report despatched

Effective date: 19921016

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REF Corresponds to:

Ref document number: 69007709

Country of ref document: DE

Date of ref document: 19940505

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

REG Reference to a national code

Ref country code: FR

Ref legal event code: TQ

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

Ref country code: DE

Payment date: 20080821

Year of fee payment: 19

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

Ref country code: FR

Payment date: 20080818

Year of fee payment: 19

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

Ref country code: GB

Payment date: 20080820

Year of fee payment: 19

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

Effective date: 20090809

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100430

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

Ref country code: DE

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

Effective date: 20100302

Ref country code: FR

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

Effective date: 20090831

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

Ref country code: GB

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

Effective date: 20090809