EP0414433A2 - Duplex-Wärmetauscher - Google Patents

Duplex-Wärmetauscher Download PDF

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Publication number
EP0414433A2
EP0414433A2 EP90308921A EP90308921A EP0414433A2 EP 0414433 A2 EP0414433 A2 EP 0414433A2 EP 90308921 A EP90308921 A EP 90308921A EP 90308921 A EP90308921 A EP 90308921A EP 0414433 A2 EP0414433 A2 EP 0414433A2
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EP
European Patent Office
Prior art keywords
heat exchanger
unit heat
coolant
duplex
heat exchangers
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
EP90308921A
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English (en)
French (fr)
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EP0414433B1 (de
EP0414433A3 (en
Inventor
Hironaka Sasaki
Hirohiki Watanabe
Tetsuya Tategami
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Showa Aluminum Can Corp
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Showa Aluminum Corp
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Publication date
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Application filed by Showa Aluminum Corp filed Critical Showa Aluminum Corp
Priority to EP94117701A priority Critical patent/EP0643278B1/de
Publication of EP0414433A2 publication Critical patent/EP0414433A2/de
Publication of EP0414433A3 publication Critical patent/EP0414433A3/en
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    • 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
    • F28D1/04—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 tubular conduits
    • F28D1/053—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 tubular conduits the conduits being straight
    • F28D1/0535—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 tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28D1/04—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 tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F28D2021/0084—Condensers
    • 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
    • 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
    • F28D2021/0089—Oil coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/12—Fins with U-shaped slots for laterally inserting conduits

Definitions

  • the invention relates to a heat exchanger, and more particularly to a duplex heat exchanger comprising two unit heat exchangers and adapted for use as the condensers or evaporators in car coolers, or for use as the oil coolers for automobiles or the likes.
  • the so-called multi-flow type heat exchanger has attracted public attention in the uses mentioned above.
  • This heat exchanger has a structure, as disclosed in Japanese Patent Publication Kokai 63-34466, such that a plurality of parallel flat tubes are connected to a pair of hollow headers at their opposite ends, respectively, with a corrugated fin interposed between one such flat tube and the next.
  • heat exchange occurs between coolant and ambient air which flows through spaces defined between the tubes while the coolant flows through a, coolant circuit composed of said flat tubes.
  • the known multi-flow type heat exchanger can be made thinner than the other known heat exchangers in its dimension in a direction of air flow, without affecting the efficiency of heat exchange. Therefore, said multi-flow type heat exchanger has proved itself better in performance than the other known heat exchangers of some types such as the serpentine type.
  • An object of the invention is therefore to provide a heat exchanger which is adapted to increase the heat transfer capacity thereof.
  • Another object is provide a heat exchanger whose heat transfer capacity can be increased without necessitating an excessively wide space.
  • a further object of the invention is to provide a heat exchanger which is so beneficially constructed that an optimal design is readily chosen for a higher efficiency of heat transfer and also for a lower loss of fluid pressure.
  • the invention aims to provide a duplex heat exchanger which, in order to achieve the abovementioned objects, comprises unit heat exchangers of the multi-flow type wherein these unit heat exchangers are disposed fore and aft in a direction of air flow.
  • the duplex heat exchanger in accordance with the present invention is characterized in that the unit heat exchangers which respectively comprise a plurality of tubes arranged parallel with each other and with a fin interposed between one of such tubes and the next, opposite ends of each tube being connected to a pair of headers in fluid connection therewith, are closely juxtaposed to each other fore and aft in the direction of air flow wherein coolant circuits of said unit heat exchangers are connected either in series or in parallel with each other.
  • coolant circuits of said unit heat exchangers are connected either in series or in parallel with each other.
  • Figs. 1 to 9 shows an embodiment in which the invention is applied to an evaporator made of aluminum-based alloy for us as a car cooler.
  • the reference symbol “H” denotes a duplex heat exchanger which comprises a forehand unit heat exchanger "A” located at an upstream side, as well as a rearward unit heat exchanger “B” located at downstream side with respect to a direction "W" of air flow.
  • the forehand unit heat exchanger "A” is composed of a plurality of horizontally disposed tubes 1 stacked in a vertical direction, of corrugated fins 2 interposed between two of such tubes adjacent to each other, and of a left-hand header 3 and a right-hand header 4.
  • the tubes 1 are made of an extruded profile pipe of said aluminum-based alloy.
  • the tubes 1 may be porous or perforated tubes such as "harmonica tubes” or may be made of an upset-welded pipe.
  • the corrugated fins 2 are of substantially the same width as the tubes 1 and are soldered thereto.
  • the cor­rugated fins 2 are made of the same or other aluminum-based alloy, and preferably are formed with louvers cut and raised from main bodies of the fins.
  • a cylindrical pipe made of an aluminum-based alloy and having inner and/or outer surfaces coated with a soldering agent is used to manufacture the headers 3 and 4.
  • Tube receiving apertures 5 are formed at regular intervals in a longitudinal direction of each header so that respective ends of each tube 1 are inserted in the tube receiving apertures and securedly soldered thereto.
  • Cover plates 6 are fixed to an upper end and a lower end of the left-hand header 3, and other cover plates 7 are similarly fixed to an upper end and a lower end of the right-hand header 4.
  • Side plates 8 are disposed outside of the outermost corrugated fins 2.
  • the rearward unit heat exchanger "B” comprises tubes 21, corrugated fins 22, a left-hand header 23 and a right-hand header 24 wherein tube receiving apertures 25, cover plates 26 and 27 and side plates 28 are provided in a manner similar to that in the forehand unit heat exchanger "A".
  • a distance "LB” between the left-hand and the right-hand headers in the rearward unit heat exchanger "B” is greater than a similar distance "LA” in the forehand unit heat exchanger "A”.
  • the forehand and rearward headers do not overlap each other and the depth of the duplex heat exchanger as a whole is reduced to a significant degree. This enhances compactness of the heat exchanger so that space occupied by it in the automobiles or the likes is advantageously decreased.
  • Coolant paths of the forehand unit heat exchanger "A” are connected in series to those of the rearward one "B".
  • a coolant inlet pipe 40 is connected to an upper portion of the left-hand header 23 of the rearward unit heat exchanger "B”.
  • a coolant outlet pipe 50 is connected to an upper portion of the left-hand header 3 of the forehand unit heat exchanger "A”.
  • Said left-hand headers 3 and 23 of the forehand and rearward unit heat exchangers "A" and "B” are interconnected by a joint pipe 60.
  • the reference numerals 71 and 72 in Figs. 2 and 3 denote brackets for fixing said unit heat exchangers one to another.
  • a partition plate 29 in the left-hand header 23 is located at a middle portion thereof so that said header 23 of the rearward unit heat exchanger "B" is partitioned into an upper and a lower chambers.
  • other partition plates 9 in the left-hand header 3 are positioned respectively above and below a middle portion thereof, thus partitioning said header 3 of the forehand unit heat exchanger "A” into three chambers.
  • still another partition plate 10 in the right-hand header 4 at a middle portion thereof partitions same into two chambers for the forehand unit heat exchanger "A”. Due to the partitions 29, 9 and 10, coolant flows in such a manner as illustrated in Fig.
  • Heat transfer occurs between an air flow indicated by an arrow "W" and the coolant flowing through the tubes of said unit heat exchangers "A" and “B".
  • W Air flow
  • the coolant temperature and the air flow temperature in the embodiment because the coolant is flowed from the rearward heat exchanger lying leeward to the forehand one standing to the windward.
  • the times of coolant U-turn between the groups of tubes in the forehand heat exchanger "A” is more than that in the rearward heat exchanger "B".
  • Such a structure makes less a total cross-sectional area of coolant paths in the forehand heat exchanger "A” than that in the rearward one "B” incorrespondence with a change in volume of the coolant flowing through the duplex heat exchanger employed as a condenser. It is to be noted in this connection that the coolant flowing into the rearward heat exchanger “B” is still in its gas state of a larger volume but it is gradually cooled down therein into its liquid state of a smaller volume. Therefore, the larger cross-sectional area of coolant paths in the rearward heat exchanger "B” is useful for sufficient heat transfar of the coolant in its gas state in said heat exchanger.
  • the cross-sectional area in the forehand heat exchanger "A” is set at 30 to 60 % of that in the rearward heat exchanger "B".
  • the cross-sectional area of coolant paths in the forehand heat exchanger "A” is 30 to 60 %, and more preferably 35 to of that in the rearward heat exchanger "B” in order for the duplex heat exchanger to perform efficient heat transfer under a lower pressure loss.
  • the aforementioned tubes 1 and 21 may preferably be 6 to mm in width "Wt", 1.5 to 7 mm in height "Ht”, and 1.0 mm or more in an inner height "Hp" of coolant path.
  • rne corrugated fins 2 and 22 may preferably be 6 to 16 mm in height "Hf” (that is, a distance between two adjacent tubes 1 or 21 ), and 1.6 to 4.0 mm in fin pitch "Fp". Reasons for such dimensions will be given below.
  • Tube width "Wt" less than 6 mm will make too narrow the width of the corrugated fins 2 and 22 which are interposed respectively between the two adjacent tubes 1 or 21.
  • a larger tube width above 20 mm will cause an excessively large width of said fins 2 and 22, which in turn causes an increased resistance against air flow therethrough in addition to an overweight of the condenser.
  • the range of 6 to 20 mm is desirable, and a range of 10 to 20 mm is more desirable.
  • Tube height "Ht” above 7 mm will increase the resistance of the tubes against air flow, and said height below 1.5 mm will make it difficult to obtain the inner height "Hp" of coolant path greater than 1.0 mm with a sufficient wall thickness of the tubes.
  • the range of 1.5 to 5 mm, or more particularly a range 2 to 4 mm is preferable.
  • fin height "Hf " less than 6 mm will bring about an increased pressure loss of air flow penetrating through the fins, though fin height of 16 mm or more will reduce the number of mounted fins, reducing the "fin effect" and making worse the heat transfer performance. Therefore, fin height is selected from the aforementioned range of 6 to 16 mm, or more preferably from a range of 8 to 12 mm is selected.
  • fin pitch "Fp” the air flow pressure loss increases with its value below 1.6 mm whereas heat transfer performance becomes worse with its value above 4.0 mm.
  • the most preferivelyable range is from 2.0 to 3.6 mm.
  • the most adequate dimensions are selected as to the shapes of tubes 1 and 21 and the corrugated fins 2 and 22 which give important influences on the perform­ance of condenser.
  • Selection of the dimensions of tube width, tube height, inner height of coolant path, fin height and fin pitch respectively from the ranges referred to above will provide the condenser which can be operated efficiently in an optimal manner wherein a good balance is realized between the pressure loss of coolant or airflow and the heat transfer characteristics, without being accompanied by any significant increase in the weight of condenser.
  • a second embodiment of the invention is illustrated in Fig. 10 and 11.
  • the same reference numerals are allotted to the same parts or elements as those in the first embodiment, and description of such parts or elements is not repeated here.
  • the second embodiment also is applied to a condenser and comprises a forehand heat exchanger "A" connected in series to a rearward heat exchanger "B".
  • coolant flows through the forehand heat exchanger "A” from its upper region toward its lower region, contrary to the flow direction in the first embodiment.
  • a lower chamber of a left-hand header 23 of the rearward heat exchanger "B” is brought by a joint pipe 60 into fluid communication with an upper chamber of a left-hand header 3 of the forehand heat exchanger "A".
  • coolant which enters the rearward heat heat exchanger "B" through a coolant inlet pipe 40 will make then a U-turn before it arrives at the lower chamber of said lower chamber of the left-hand header 23 and hence moves into said upper chamber of the left-hand header 3.
  • the coolant descends zigzag to the lower region of the forehand heat exchanger "A” while making U-turns therein, and is discharged from said heat exchanger "A".
  • positions of partition plates 9, 10 and 29 are determined such that cross-sectional areas of tube groups arranged in a serpentine pattern throughout the forehand and rearward heat exchangers "A" and "B” decrease gradually and stepwise in a direction from inlet toward outlet of coolant. Said cross-sectional areas depend on the numbers of tubes in the groups thereof. Said partition plates 9, 10 and 29 are disposed so as to form the tube groups consisting of thirteen, ten, eight, six, five and four pipes in said direction. Such a gradual change in the number of tubes in the second embodiment corresponds more exactly to the change in the specific volume of coolant, thus providing more efficient condenser.
  • Fin pitch "Fp A” in the forehand heat exchanger “A” is greater than fin pitch “Fp B” in the rearward heat exchanger so that. This means that heat transfer surface per unit area seen in the direction of air flow is narrower in the forehand heat exchanger “A” than that in the rearward heat exchanger “B”.
  • Such different fin pitches “Fp A “ and “Fp B” is effective to improve heat transfer efficiency, without increasing air flow pressure loss. It is recommended to adopt a value of 1.07 to 1.8 as a ratio of "Fp A “ to "Fp B ". A ratio less than 1.07 will result in a greater pressure loss of air flow and a lower efficiency of heat radiation.
  • a ratio higher than 1.8 however will likewise result in an insufficient heat radiation efficiency, apart from an enough decrease in the pressure loss.
  • a narrower range of the ratio from 1.1 to 1.6 is more preferable. Even in a case wherein the core sizes of the forehand and rearward heat exchangers are the same, the ratio should fall within the range of 1.07 to 1.8, and more desirably within the range of 1.1 to 1.6 for the same reason as mentioned above.
  • a third embodiment also is applied to a condenser shown in Figs. 12 and 13 and comprising a forehand heat exchanger "A" which is connected in series to a rearward heat exchanger “B” and is of the same size as the former.
  • Headers, tubes and corrugated fins in the third embodiment are respectively of the same structures and are given the same reference numerals as those in the first embodiment, so that description thereof is not repeated.
  • joint blocks are utilized to connect the heat exchangers "A" and "B” into fluid communication with each other.
  • a male joint block 80 is welded or otherwise attached to a lowermost portion of a left-hand header 3 in the forehand heat exchanger "A”.
  • the male joint block 80 has a lug 81 protruding from an inner side, and a coolant passage 82 is formed through the lug 81 so as to be in fluid connection with the left-hand header 3.
  • a female joint block 90 is fixed to a lowermost portion of the left-hand header 23 in the rearward heat exchanger "B".
  • An aperture 91 is formed at inner side of and through the female joint block so as to be likewise in fluid connection with the left-hand header 23.
  • the lug 81 is engaged with the aperture 91, the inner sides of the blocks thereby being brought into close contact with each other. Then a bolt 100 is inserted through a hole 83 of the male block 80 into an internally-threaded hole 92 of the female block 90. In this way, the coolant paths of the forehand and rearward heat exchangers "A" and "B" are connected in series. Further, fixed to an uppermost portion of the rearward heat exchanger "B" is an inlet block 110 having a hole.
  • a pipe attaching block 120 which has a lug 121 and an attached inlet pipe 130 is mounted to the inlet block 110, by engaging the lug 121 with the hole of the inlet block, and is fastened thereto by means of a bolt 140.
  • an outlet block 150 having a hole 151 is fixed to an uppermost portion of the left-hand header 3 in the forehand heat exchanger "A".
  • a pipe attaching block 160 which has a lug 161 and an attached outlet pipe 170 is mounted to the outlet block 150, by engaging the lug 161 with the hole 151 of the outlet block, and is fastened thereto by means of a bolt 180.
  • connection system as using the joint blocks and other blocks as in this embodiment is advantageous in that the forehand and rearward unit heat exchangers can be separately manufactured and inspected for coolant leakage. Assembly of the two unit heat exchangers into a duplex heat exchanger is easily carried out at a final step in the manufacture process whereby workshop operations and productivity are improved.
  • Figs. 14 and 15 show a fourth embodiment also applied to a condenser.
  • This embodiment is different from the first embodiment in that a forehand and a rearward heat exchangers "A" and "B" of the same shape and the same dimension are connected parallel with each other.
  • a bifurcate inlet pipe 190 for coolant is attached to upper portions of left-hand headers 3 and 23 of the respective heat exchangers "A" and "B".
  • a bifurcate outlet pipe 200 is connected to bottoms of said left-hand headers 3 and 23.
  • a partition plate 9 is secured in the left-hand header 3 at its middle portion, for the forehand heat exchanger, while two partition plates 29 are secured in the left-hand header 23 respectively at its upper and lower portions.
  • partition plate (not shown ) is similarly secured in a right-hand header 24 at its middle portion.
  • Those partition plates cause coolant which enter the heat exchangers "A” and "B” through the bifurcate inlet pipe 190 to make a U-turn within the forehand heat exchanger "A” and to make three U-turns within the rearward heat exchanger "B".
  • the coolant is collected into lower chambers of the left-hand headers 3 and 23 before it leaves this duplex heat exchanger through the bifurcate outlet pipe 200.
  • the coolant is caused to make U-turn more times in the rearward heat exchanger "B” than in the forehand heat exchanger "A” because a total length of coolant flow paths is to be greater for the rearward heat exchanger "B” which lies leeward and is thus of a lesser efficiency of heat transfer. A good balance between the heat transfer efficiency of the two heat exchangers is assured in this manner in the fourth embodiment.
  • Figs. 16 and 17 show a fifth embodiment in which wide corrugated fins 210 extend from a forehand heat exchanger "A” to a rearward heat exchanger “B” so as to span them.
  • This structure provides direct connection between cores of said heat exchangers "A” and “B”, thereby improving their heat transfer efficiencies as a whole.
  • Mechanical strength of connection is also enhanced so that only one of the heat exchangers need be secured to a body of automobile. This reduces the number of parts necessary for mounting this duplex heat exchanger to automobiles or the likes, and thereby improves productivity of the heat exchanger.
  • Figs. 18 and 19 show a sixth embodiment which is applied to an evaporator for car coolers.
  • tubes of a forehand heat exchanger "A” as well as tubes of a rearward heat exchanger “B” are vertical and parallelly arranged in a right-to-left direction.
  • Upper headers 3 and 23 and lower headers 4 and 24 disposed horizontally.
  • a bifurcate inlet pipe 220 for coolant is connected to left ends of the upper headers 3 and 23.
  • a bifurcate outlet pipe 230 is connected to right ends of the lower headers 4 and 24, coolant paths of the two heat exchangers "A" and "B” thereby running parallel with each other.
  • Coolant flows into the heat exchangers "A” and “B” through the inlet pipe 220, descends to the lower headers 4 and 24, and then flows out of the heat exchangers through the outlet pipe 230.
  • fin pitch "Fp B” of corrugated fins 22 in the rearward heat exchanger “B” is made greater than that "Fp A " in the forehand heat exchanger "A”.
  • Such a greater fin pitch "Fp B " in the rearward heat exchanger prevents the so-called water-drop-flying which would otherwise be caused by air flow forcing toward a cabin of the automobile such condensed water that is retained between the fins in the rearward heat exchanger due to the capillary phenomenon.
  • Some partition plates may be fixed inside the upper and lower headers to cause coolant to meander along zigzag paths.
  • Three unit heat exchangers "A", "B” and “C” as shown in Fig. 20 may be combined though two unit heat exchangers are arranged fore and aft in the first to sixth embodiments. Further, four or more unit heat exchangers may be combined in the invention.
  • the duplex heat exchanger in invention is constructed such that the fins are each interposed between two adjacent tubes each having ends respectively connected to the hollow headers in fluid connection therewith.
  • a plurality of the unit heat exchangers are aligned with each other in the direction of air flow, and the coolant paths of said heat exchangers are connected in series or parallel with each other. Therefore, the capacity of heat transfer can be increased for the duplex heat exchanger as whole because each unit heat exchanger contributes to the heat transfer therein.
  • Such a combination of two or more unit heat exchangers provides a higher degree of freedom in selecting the number and/or location of the partition plates in order to form a desired coolant flow circuit.
  • an optimal design of the duplex heat exchanger can be employed for a higher heat transfer efficiency and for a lower pressure loss which are indispensable to a good heat exchanger.

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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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP90308921A 1989-08-23 1990-08-14 Duplex-Wärmetauscher Expired - Lifetime EP0414433B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
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JP1217959A JP3030036B2 (ja) 1989-08-23 1989-08-23 複式熱交換器
JP217959/89 1989-08-23

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EP0414433A2 true EP0414433A2 (de) 1991-02-27
EP0414433A3 EP0414433A3 (en) 1991-05-08
EP0414433B1 EP0414433B1 (de) 1995-05-24

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DE (2) DE69019633T2 (de)

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FR2681419A1 (fr) * 1991-09-13 1993-03-19 Behr Gmbh & Co Echangeur de chaleur a faisceau tubulaire comportant plusieurs circuits de fluides.
FR2682160A1 (fr) * 1991-10-07 1993-04-09 Renault Vehicules Ind Systeme de refroidissement pour moteur a combustion interne comportant deux parties distinctes de radiateur.
EP0563471A1 (de) * 1992-03-31 1993-10-06 Modine Manufacturing Company Verdampfer
DE9400687U1 (de) * 1994-01-17 1995-05-18 Thermal-Werke, Wärme-, Kälte-, Klimatechnik GmbH, 68766 Hockenheim Verdampfer für Klimaanlagen in Kraftfahrzeugen mit Mehrkammerflachrohren
EP0657315A1 (de) * 1993-11-26 1995-06-14 IVECO FIAT S.p.A. Klimaanlage für Nutzfahrzeuge
EP0754579A2 (de) * 1995-07-20 1997-01-22 Nippondenso Co., Ltd. Fahrzeugwärmetauscher
US5622219A (en) * 1994-10-24 1997-04-22 Modine Manufacturing Company High efficiency, small volume evaporator for a refrigerant
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EP0702200A3 (de) * 1994-09-16 1998-04-08 Sanyo Electric Co., Ltd. Wärmeaustauscher und mit demselben ausgestattete Kühleinrichtung
WO1998050745A1 (de) 1997-05-07 1998-11-12 Valeo Klimatechnik Gmbh & Co. Kg Zweiflutiger und in luftrichtung einreihiger hartverlöteter flachrohrverdampfer für eine kraftfahrzeugklimaanlage
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US5379834A (en) * 1991-05-31 1995-01-10 Showa Aluminum Corporation Heat exchanger
EP0516413A1 (de) * 1991-05-31 1992-12-02 Showa Aluminum Corporation Wärmetauscher
FR2681419A1 (fr) * 1991-09-13 1993-03-19 Behr Gmbh & Co Echangeur de chaleur a faisceau tubulaire comportant plusieurs circuits de fluides.
FR2682160A1 (fr) * 1991-10-07 1993-04-09 Renault Vehicules Ind Systeme de refroidissement pour moteur a combustion interne comportant deux parties distinctes de radiateur.
EP0563471A1 (de) * 1992-03-31 1993-10-06 Modine Manufacturing Company Verdampfer
EP0657315A1 (de) * 1993-11-26 1995-06-14 IVECO FIAT S.p.A. Klimaanlage für Nutzfahrzeuge
DE9400687U1 (de) * 1994-01-17 1995-05-18 Thermal-Werke, Wärme-, Kälte-, Klimatechnik GmbH, 68766 Hockenheim Verdampfer für Klimaanlagen in Kraftfahrzeugen mit Mehrkammerflachrohren
EP0677716B1 (de) * 1994-04-12 1999-01-07 Showa Aluminum Corporation Doppelwärmetauscher in Stapelbauweise
EP0702200A3 (de) * 1994-09-16 1998-04-08 Sanyo Electric Co., Ltd. Wärmeaustauscher und mit demselben ausgestattete Kühleinrichtung
US5622219A (en) * 1994-10-24 1997-04-22 Modine Manufacturing Company High efficiency, small volume evaporator for a refrigerant
US5685366A (en) * 1994-10-24 1997-11-11 Modine Manufacturing High efficiency, small volume evaporator for a refrigerant
US5901782A (en) * 1994-10-24 1999-05-11 Modine Manufacturing Co. High efficiency, small volume evaporator for a refrigerant
EP0754579A2 (de) * 1995-07-20 1997-01-22 Nippondenso Co., Ltd. Fahrzeugwärmetauscher
EP0754579A3 (de) * 1995-07-20 1999-01-27 Denso Corporation Fahrzeugwärmetauscher
EP0769665A3 (de) * 1995-10-20 1998-01-28 Denso Corporation Kältemittelverdampfer mit gleichmässiger Temperatur der Ausblasluft
US7392837B2 (en) 1996-08-12 2008-07-01 Calsonic Kansei Corporation Integral-type heat exchanger
WO1998050745A1 (de) 1997-05-07 1998-11-12 Valeo Klimatechnik Gmbh & Co. Kg Zweiflutiger und in luftrichtung einreihiger hartverlöteter flachrohrverdampfer für eine kraftfahrzeugklimaanlage
DE19719252C2 (de) * 1997-05-07 2002-10-31 Valeo Klimatech Gmbh & Co Kg Zweiflutiger und in Luftrichtung einreihiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage
DE19719252A1 (de) * 1997-05-07 1998-11-12 Valeo Klimatech Gmbh & Co Kg Zweiflutiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage
DE19758886B4 (de) * 1997-05-07 2017-09-21 Valeo Klimatechnik Gmbh & Co. Kg Zweiflutiger und in Luftrichtung einreihiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage
EP1070929A2 (de) 1999-07-20 2001-01-24 Valeo Klimatechnik GmbH Verdampfer für Kraftfahrzeug-Klimaanlage
WO2001061263A1 (fr) * 2000-02-15 2001-08-23 Zexel Valeo Climate Control Corporation Echangeur thermique
DE10241635A1 (de) * 2001-10-02 2004-02-05 Behr Gmbh & Co. Flachrohr-Wärmeübertrager sowie Herstellungsverfahren hierfür
WO2003040640A1 (fr) * 2001-11-08 2003-05-15 Zexel Valeo Climate Control Corporation Echangeur thermique et tube pour echangeur thermique
EP1331463A2 (de) * 2002-01-25 2003-07-30 Calsonic Kansei Corporation Integrierter Wärmetauscher und Verfahren zu dessen Herstellung
EP1331463A3 (de) * 2002-01-25 2006-07-12 Calsonic Kansei Corporation Integrierter Wärmetauscher und Verfahren zu dessen Herstellung
WO2004053411A1 (de) * 2002-12-10 2004-06-24 Behr Gmbh & Co. Kg Wärmeübertrager
WO2005050115A1 (de) * 2003-10-24 2005-06-02 Behr Gmbh & Co. Kg Vorrichtung zum austausch von wärme
WO2005066565A1 (de) * 2004-01-12 2005-07-21 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für überkritischen kältekreislauf
WO2005075913A1 (de) * 2004-02-04 2005-08-18 Behr Gmbh & Co. Kg Vorrichtung zum austausch von wärme und verfahren zur herstellung einer derartigen vorrichtung
EP1568960A2 (de) * 2004-02-24 2005-08-31 Behr GmbH & Co. KG Wärmeübertrager mit Seitenteilen
EP1568960A3 (de) * 2004-02-24 2010-09-15 Behr GmbH & Co. KG Wärmeübertrager mit Seitenteilen
WO2005100895A1 (de) * 2004-04-13 2005-10-27 Behr Gmbh & Co. Kg Wärmeübertrager für kraftfahrzeuge
EP1881288A1 (de) * 2006-07-21 2008-01-23 Modine Manufacturing Company Rohr-Rippen-Block-Wärmetauscher mit Verbindungs- bzw. Anschlussblöcken
US8091617B2 (en) 2006-07-21 2012-01-10 Modine Manufacturing Company Heat exchanger
EP2430385B1 (de) * 2009-05-11 2016-07-13 MAHLE Behr GmbH & Co. KG Heizkörper für ein kraftfahrzeug mit einer brennkraftmaschine
DE202010000951U1 (de) 2010-01-22 2010-04-22 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Gaskühler für Klimaanlagen in Kraftfahrzeugen
WO2012041441A2 (fr) 2010-09-30 2012-04-05 Valeo Systems Thermiques Echangeur de chaleur pour vehicule automobile.
CN103471439A (zh) * 2013-09-18 2013-12-25 无锡马山永红换热器有限公司 组合式冷却器
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US10477771B2 (en) * 2015-09-15 2019-11-19 Cnh Industrial America Llc Agricultural harvester having a header based heat exchanger
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Also Published As

Publication number Publication date
AU637807B2 (en) 1993-06-10
EP0414433B1 (de) 1995-05-24
EP0643278B1 (de) 1997-07-09
DE69019633D1 (de) 1995-06-29
DE69031047T2 (de) 1998-02-05
DE69031047D1 (de) 1997-08-14
ATE155233T1 (de) 1997-07-15
DE69019633T2 (de) 1995-11-30
CA2023499A1 (en) 1991-02-24
JPH0384395A (ja) 1991-04-09
ATE123138T1 (de) 1995-06-15
EP0643278A2 (de) 1995-03-15
EP0414433A3 (en) 1991-05-08
EP0643278A3 (de) 1995-05-24
JP3030036B2 (ja) 2000-04-10
AU6122990A (en) 1991-02-28
CA2023499C (en) 2002-10-29

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