EP0773419B1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0773419B1
EP0773419B1 EP96118055A EP96118055A EP0773419B1 EP 0773419 B1 EP0773419 B1 EP 0773419B1 EP 96118055 A EP96118055 A EP 96118055A EP 96118055 A EP96118055 A EP 96118055A EP 0773419 B1 EP0773419 B1 EP 0773419B1
Authority
EP
European Patent Office
Prior art keywords
tubes
cooling fin
heat exchanger
core portion
cooling
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
EP96118055A
Other languages
German (de)
English (en)
Other versions
EP0773419A3 (fr
EP0773419A2 (fr
Inventor
Tatsuo Sugimoto
Yasutoshi Yamanaka
Hiroo Yamaguchi
Takaaki Sakane
Akira Uchikawa
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.)
Denso Corp
Original Assignee
Denso 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 JP29452895A external-priority patent/JP3446427B2/ja
Priority claimed from JP14608296A external-priority patent/JP3709611B2/ja
Application filed by Denso Corp filed Critical Denso Corp
Publication of EP0773419A2 publication Critical patent/EP0773419A2/fr
Publication of EP0773419A3 publication Critical patent/EP0773419A3/fr
Application granted granted Critical
Publication of EP0773419B1 publication Critical patent/EP0773419B1/fr
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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • 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
    • 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
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant
    • 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
    • F28F2215/02—Arrangements of fins common to different heat exchange sections, the fins being in contact with different heat exchange media

Definitions

  • the present invention relates to a heat exchanger according to the preamble of claim 1.
  • a heat exchanger of that kind is disclosed in EP 677 716.
  • this known heat exchanger only the ends of the fins are connected, whereby a single clearance at the intermediate portion between the connecting portions is formed.
  • This long, single clearance provides a flimsy structure which could have the tendency to contact somewhere in the centre when the fins are assembled with the tubes.
  • the present invention particularly relates to a heat exchanger in which different core portions are integrated with each other, and more particularly the present invention can be effectively applied to an integration of a radiator of an engine which is a driving source of a vehicle and a condenser of an automotive air conditioning apparatus.
  • an automotive air conditioning apparatus is assembled into a vehicle in a car dealer or the like after the vehicle has been completed. Recently, however, the automotive air conditioning apparatus is generally installed in the vehicle when the vehicle is completed, and therefore the automotive air conditioning apparatus is assembled with automotive parts in the assembling steps of the vehicle at the manufacturing plant.
  • cooling fins of first core portion and second core portion are integrated with each other, and a slit shaped recess portion is formed in a zigzag shape in a height direction of the integrated cooling, and a heat transmitting passage for transmitting heat is meanderingly formed so as to prolong the heat transmitting passage.
  • the heat transmitting passage is prolonged so that heat transmitted from the radiator to the condenser is suppressed, however, the heat transmission cannot be interrupted completely.
  • it is necessary to decide the capacity of the condenser core portion by considering the decrease of the heat exchange efficiency.
  • a plurality of folded portions of corrugated first and second cooling fins are formed between a pair of adjacent connecting portions for connecting the first and second cooling fins.
  • the connecting portions may be formed in each flat portion of the first and second cooling fins. Therefore, total cross sectional areas of the plurality of connecting portions which is a cross sectional area of heat transmitting passage of heat transmitted between the two cooling fins can be reduced. Thus, the heat transmitting amount between the two cooling fins can be reduced, so that the heat transmitting between the two cooling fins can be effectively interrupted.
  • the cross sectional area of the heat transmitting passage is reduced so that the heat transmitting between the two cooling fins is interrupted.
  • the distance between the two cooling fins can be suppressed from increasing.
  • the heat exchanger can be suppressed from being large-sized, and the heat transmitting between the two cooling fins can be effectively interrupted.
  • the connecting portion has a portion in parallel with a longitudinal direction of the first and second cooling fins, and a length (E) of the portion being equal to 5% or less of a length (F) between each pair of the adjacent connecting portions when the first and second cooling fins are unfolded. Therefore, the deterioration percentages of the heat exchange efficiency of the first cooling fin can be suppressed less than 2%.
  • the first cooling fin is projected from the first tubes to the second tubes side with a projection length being in a range of 1.7 - 7.0 mm. Therefore, radiating amount of the first tube and the first cooling fin can be increased over about 2 %.
  • the projection length Lc of the first cooling fin and the connection ratio (E/F) the deterioration amount with providing the connecting portion can be offset by the increase of the radiating amount with projecting the first cooling fin.
  • the second cooling fin is projected from the second tube toward the first tube side, the projection length (Lr) is equal to 5.0 mm or less. Therefore, the size of the heat exchanger can be prevented from being large-sized, and the heat exchange efficiency can be prevented from decreasing. Further, because the cooling fins are integrally formed through the connecting portions, the manufacturing cost of the two cooling fins can be reduced so that the manufacturing cost of the heat exchanger can be reduced.
  • a partition member is located at end portions of the first core portion and second core portion. By the partition member, air bypassing the first core portion does not flow through the clearance between the first cooling fin and the second cool fin, so that a duct effect can be obtained.
  • the distance between the first cooling fin and the second cooling fin is equal to 5.0 mm or less. Therefore, the air flow resistance becomes larger, so that the duct effect can be obtained.
  • a condenser core portion of an automotive air conditioning apparatus is used as a first core portion
  • a radiator core portion for cooling an engine is used as a second core portion.
  • the condenser core portion is disposed at an upstream air side of the radiator core portion in air flow direction and the two core portions are disposed in series in the air flow direction at a front-most portion of an engine compartment.
  • FIG. 1 is a partial enlarged cross-sectional view (along line B-B of FIG. 2) of a heat exchanger 1 of the present invention.
  • a condenser core portion 2 and a radiator core portion 3 are disposed in series in the air flow direction so as to form predetermined clearances 46 between each pair of a condenser tube 21 and a radiator tube 31 described later to interrupt heat transmission.
  • the condenser core portion 2 includes flat shaped condenser tubes 21 which are refrigerant passages and corrugated (wave-shaped) cooling fins 22 in which a plurality of folded portions 22a brazed to the condenser tube 21 are formed.
  • the radiator core portion 3 has a similar structure with the condenser core portion 2.
  • the radiator core portion 3 includes the radiator tubes 31 disposed in parallel with the condenser tubes 21 and radiator cooling fins 32.
  • the tubes 21 and 31 and the cooling fins 22 and 32 are alternately laminated and are brazed to each other.
  • a plurality of louvers 22b and 32b are formed in the two cooling fins 22 and 32 to facilitate heat exchange, the two cooling fins 22 and 23 are integrally formed with the louvers 22b and 32b by a roller forming method or the like.
  • a plurality of connecting portions 45 are formed between the two cooling fins 22 and 32.
  • opposite end portions 22d and 32d which are vertical to the longitudinal direction of the two tubes 21 and 31 formed end portions of the two cooling fins 22 and 32 are connected to each other.
  • a plurality of folded portions 22a and 32a (five to ten folded portions in the first embodiment) of the two cooling fins 22 and 32 are formed between one of the plurality of connecting portions 45 and the other connecting portion 45.
  • connection ratio E/F connection ratio
  • the connecting portions 45 are formed on plane portions 22c and 32c of the two cooling fins 22 and 32 as shown in FIGS. 1 and 7.
  • the two cooling fins 22 and 32 are projected toward the clearance 46 as shown in FIG. 1.
  • a projection length Lc projected from the condenser tube 21 toward the clearance 46 and a projection length Lr projected from the radiator tube 31 toward the clearance 46 will be described later.
  • Side plates 23 and 33 are reinforcement member of the two heat exchanger core portions 2 and 3, the side plates 23 and 33 are respectively disposed in two end portions of the two heat exchanger core portions as shown in FIG. 2.
  • the side plates 23 and 33 are integrally formed from a sheet of aluminum plate to a general U-shape in cross-sections.
  • a connecting portion 4 for connecting the side plate 23 and the side plate 33 is formed in two end portions of the longitudinal direction of the two side plates 23 and 33.
  • a Z-shaped bent portion 41 of the side plate 23 and a Z-shaped bent portion 42 of the side plate 33 are connected to each other at a top end portion 43 so that the connecting portion 4 is formed.
  • the width of the connecting portion 4 is set to be small enough as compared with the dimension of the side plate 23 or 33 in the longitudinal direction. Further, a recess portion is formed in the top end portion 43 of the connecting portion 4 to reduce a thickness of the plate wall of the connecting portion 4.
  • first header tank 34 for distributing cooling water to each the radiator tube 31 is disposed at an end side without having the side plate 33.
  • the front shape of first header tank 34 is nearly a triangular, the cross-sectional shape is ellipsoid as shown in FIG. 3.
  • the large-diameter of the ellipsoid becomes smaller along the oblique line of the triangular, further, becomes equal (a circle) to the small-diameter of the ellipsoid at the top side of the oblique line.
  • An inlet 35 of cooling water flowing to the radiator is formed at a bottom side of the first header tank 34 having a nearly triangular.
  • a pipe 35a for connecting a pipe (not shown) of cooling water is brazed to the inlet 35.
  • second header tank 36 for receiving the cooling water having been heat-exchanged is disposed in an opposite end of the first header tank 34, the second header tank 36 has a similar shape with the first header tank 34. As shown in FIG. 2, the second header tank 36 and the first header tank 34 are point-symmetrical with reference to the center of the radiator core portion 3. Further, an outlet 37 for discharging the cooling water is formed at the bottom side of the second header tank 36. With the tubes and the cooling fins and the like, a pipe 35 for connecting the pipe (not shown) of cooling water is brazed to the outlet 37. As shown in FIG. 2, the inlet 35 and the outlet 37 of the radiator are directed toward the paper side in FIG. 2.
  • the first header tank 24 distributes refrigerant in the condenser core portion 2 into each the condenser tube 21, and the body of the first header tank 24 is cylindrically formed as shown in FIG. 3.
  • the first header tank 24 of the condenser is disposed to have a predetermined clearance with the second header tank 36 of the radiator. Further, a joint 26a for connecting a refrigerant pipe (not shown) is brazed to the body of the first header tank 24, and an outlet 26 of refrigerant is formed in the joint 26a.
  • a second header tank 25 of the condenser for receiving the refrigerant having been heat-exchanged is disposed in an opposite end of the first header tank 24 of the condenser, the second header tank 25 is disposed to have a predetermined clearance with the first header tank 34 of the radiator.
  • the body of the second header tank 25 is cylindrically formed.
  • a joint 27a for connecting a refrigerant pipe (not shown) is brazed to the body of the second header tank 25, an outlet 27 of refrigerant is formed in the joint 27a.
  • the inlet 27 and the outlet 26 of the condenser are directed toward the paper side in FIG. 2.
  • the radiating area of the two cooling fins 22 and 32 becomes larger so that radiating amount becomes larger.
  • the radiating amount is not increased so much with increasing the projection lengths Lc and Lr. That is, as shown in FIG. 4, in the condenser core portion 2, when the projection length Lc of the cooling fin 22 is equal to 4.0 mm or more, the increase percentage of the radiating amount is saturated.
  • the radiator core portion 3 when the projection length Lr of the cooling fin 32 is equal to 7.0 mm or more, the increase percentage of the radiating amount is saturated.
  • the above-described examinations shows numerical analytic results in a corrugated cooling fin having the louvers by a finite element method when a pitch of the louver is 1.0 mm, an angle of the louver is 23°, a height of the cooling fin is 8.0 mm, the clearance distance L formed between the two tubes 21 and 31 is 10.0 mm and the fixed speed of air flowing from a side of the condenser core portion 2 is 2.0 m/sec.
  • the inventors have experimented a number of numerical analytic tests under various calculated conditions in addition to the above calculated conditions.
  • the clearance distance L is in a range of 4.0 - 10.0 mm, it turns out that the increase percentage of radiating amount and the air flow resistance do not depend on the thickness and the height of the cooling fin, however, nearly have functional relationship with the projection lengths Lc and Lr as shown in FIGS. 4, 5 and 10.
  • connection ratio E/F of the two cooling fins 22 and 23 will be described.
  • connection ratio E/F becomes larger, the connecting portion 4 of the two cooling fins 22 and 32 becomes larger, and therefore an amount of heat transmitted from radiator core portion 3 to condenser core portion 2 is increased so that the heat exchange efficiency of the condenser core portion 2 is deteriorated.
  • the inventors have examined and studied the relationship between the deterioration amount of the heat exchange efficiency of the condenser core portion 2 and the connection ratio E/F quantitatively, and the results are shown in FIG. 9. As shown in FIG. 9, the deterioration amount of the heat exchange efficiency of the condenser core portion 2 is nearly linearly increased when the connection ratio E/F becomes large. Further, it also turns out that the deterioration percentages of the heat exchange efficiency of the condenser core portion 2 can be suppressed less than 5% when the connection ratio E/F is equal to 0.1 or less.
  • the deterioration percentages of the condenser of vertical line in FIG. 9 are calculated by dividing the difference between the heat exchange amounts without having the connecting portion 45 (two core portions 2 and 3 are completely separated) and the heat exchange amounts with having the connecting portion 45 with the heat exchange amounts without having the connecting portion 45.
  • the connection ratio E/F is, the smaller the heat transmitting amount is, as shown in FIG. 9.
  • the projection length Lc of the cooling fin 22 of the condenser core portion 2 is made large until a specified size so that the increase percentage of the radiating amount can be improved.
  • the projection length Lc of the cooling fin 22 and the connection ratio E/F are suitably selected so that the deterioration amount of the condenser with the connecting portion can be offset by the increase of the radiating amount with projecting the cooling fin 22. Because the cooling fin 22 is projected toward the clearance 46 side between the two core portions 2 and 3, the shape of the heat exchanger 1 can be prevented from being large-sized.
  • the projection length Lc is about 1.7 mm
  • the connection ratio E/F is about 0.05. That is, because the connection ratio E/F is about 0.05, the deterioration amount is about 2%.
  • the projection length Lc is about 1.7 mm, so that the radiating amount of the condenser core portion 2 increases about 2%.
  • the deterioration amount of the condenser is offset by projecting the cooling fin.
  • the projection length is suitably selected by the thickness, the shape and material, the louvers 22b and 32b and the like of the cooling fins 22 and 32.
  • the projection length is preferably in a range of 1.7 - 7.0 mm.
  • the length Ls of the clearance 47 between the two cooling fins 22 and 32 may be a length in which the heat transmission is effectively interrupted, more specifically, the length Ls of the clearance 47 is about in a range of 0.5 - 2.0 mm. In the first embodiment, the length Ls of the clearance between the two cooling fins is about 0.5 mm, the clearance distance L between the two tubes 21 and 31 is about 4.0 mm.
  • the cooling fin 32 of the radiator core portion 3 is also projected toward the condenser core portion side 2, the radiating amount is increased in the radiator core portion 3 as shown in FIG. 11.
  • the shape of the heat exchanger 1 can be prevented from being large-sized, the radiating amount can be increased in the radiator core portion 3.
  • the projection length Lr of the cooling fin 32 is about 1.8 mm, the increase percentage of the radiating amount of the cooling fin 32 is about 5 %.
  • the projection lengths Lc and Lr are suitably selected respectively, so that the radiating capacity of the condenser core portion 2 and the radiating capacity of the radiator core portion 3 can be easily controlled.
  • a desired design can be easily modified without a large design change of the heat exchanger.
  • a plurality of folded portions 22a and 32a (5-10 folded portions, in the first embodiment) are formed between one of the connected portion 45 and the other connected portion 45 of the plurality of connected portions 45, total cross sectional areas of the plurality of connecting portions 45 which is a cross sectional area of heat transmitting passage of heat transmitted between the two cooling fins 23 and 32 can be made smaller.
  • the heat transmitting amount between the two cooling fins 22 and 32 can be made smaller, so that the heat transmitting between the two cooling fins 23 and 32 can be effectively interrupted.
  • the cross sectional area of the heat transmitting passage is made smaller so that the heat transmitting between the two cooling fins 22 and 32 is interrupted.
  • the distance between the two cooling fins 22 and 32 can be decreased.
  • the increase of the size of the heat exchanger 1 is controlled, and the heat transmitting between the two cooling fins 22 and 32 can be effectively interrupted.
  • cooling fins 22 and 32 are integrally formed, the manufacturing cost of the two cooling fins 22 and 32 can be decreased, and as a result, the manufacturing cost of the heat exchanger 1 can be decreased.
  • the heat exchange efficiency of an automotive heat exchanger is improved in view of a vehicle design concept in recent years, in which a space of a passenger compartment is expanded by downsizing an engine compartment.
  • the side plates 23 and 33 in FIG. 1 are integrated (hereinafter, the integrated side plate is simply referred to as side plate (partition member) 50.) and the clearance 46 between the two core portions 2 and 3 is closed so that an amount of air passing through the condenser core portion 2 is increased.
  • the equipment in the engine compartment are closely disposed to the extent that the equipment can be fixed or maintained by a serviceman, similarly, the radiator core portion 3 is disposed closely to the other equipment.
  • the radiator core portion 3 is installed at the front side of the vehicle (the engine compartment) as shown in FIGS. 13 and 14. Further, it is not limited to the second embodiment, the radiator core portion 3 is usually so disposed that air flowing from front side of a vehicle toward the engine compartment effectively join together into the radiator core portion 3.
  • clearances (distance) between the radiator core portion 3 and the other equipment which are closely disposed to the radiator core portion 3 and clearances between the radiator core portion 3 and reinforcing members of the vehicle such as upper reinforcing member (upper cross member) 100 and lower reinforcing member (lower cross member) 101 are made smaller, so that it has a construction (layout) in which air flowing from the front side of vehicle into the engine compartment does not directly flow toward the downstream side by bypassing the radiator core portion 3.
  • air flowing from the front side of a vehicle toward the engine compartment flows so as to join together into the radiator core portion 3 as approaching the radiator core. portion 3. Therefore, when the condenser core portion 2 is located at an upstream air side of the radiator core portion 3, air flowing from the front side of a vehicle toward the engine compartment is divided into two air flows including one air flow bypassing the condenser core portions 2 and passing through the radiator core portion 3 from the clearance 46 between the condenser core portion 2 and radiator core portion 3, and the other air flow straightly passing through the two core portions 2 and 3.
  • FIG. 16 is a graph showing the experimented results. The increase percentages are shown by percentages based on a standard distance in which an average distance between the two tubes 21 and 31 is 20 mm.
  • the radiator core portion 3 is located at a downstream air side of the condenser core portion 2, and a cooling fan 51 is located at downstream air side of the radiator core portion 3.
  • the clearance 46 is closed so that the duct effect can be obtained.
  • FIG. 17 shows the relationship between the distance L and the increase percentage of the heat exchange of the condenser core portion 2.
  • the smaller the distance L is, that is, the closer the distance L approaches zero the higher the heat exchange percentage of the condenser core portion 2 becomes.
  • connection ratio E/F is made as large as possible in view of manufacture for the cooling fin.
  • connection ratio E/F when the connection ratio E/F is made large, the heat exchange of the condenser core portion 2 is decreased as described above, so that it is not preferable that the connection ratio E/F is excessively made large.
  • connection ratio E/F is equal to 0.1 or less
  • the deterioration percentage of the condenser is 5% (refer to FIG. 9). Therefore, when the increase percentage of the heat exchange will be increased to 10% by the duct effect, even if the projection length (deviated amount) Lc is -1.5 mm (when the projection length Lc is -1.5 mm, the radiating amount of the condenser core portion 2 is deteriorated by about 5%, refer to FIG. 6), the deterioration percentages of the radiating amount of the condenser core portion 2 can be offset.
  • connection ratio E/F is appropriately equal to 0.1 or less.
  • the projection length (deviated amount) Lc may be in a range of 5.0 - 7.0 mm.
  • the clearance 46 between the two core portions 2 and 3 is closed by a partition plate or the like described later.
  • the length Ls of the clearance 47 between the two cooling fins 22 and 32 is made small to a proper value so that the duct effect can be obtained without closing the clearance 46 by the side plate 50 or the partition plate described later.
  • the length Ls of the clearance 47 between the two cooling fins 22 and 32 will be described.
  • the inventors have experimented on the comparison between the amount of air passing through the condenser core portion 2 of the automotive heat exchanger in which the length Ls of the clearance 47 between the two cooling fins 22 and 32 is zero and the amount of air passing through the condenser core portion 2 of the automotive heat exchanger in which the clearance 46 between the two core portions 2 and 3 is closed. As a result, the inventors have confirmed that the two air amounts are nearly equal. Thus, by making the length Ls of the clearance 47 between the two cooling fins 22 and 32 smaller, the duct effect can be obtained.
  • the amount of air passing through the condenser core portion 2 with the duct effect is not influenced by the distance L between the two tubes 21 and 31, however, is influenced by the length Ls of the clearance 47 between the two cooling fins 22 and 32.
  • the experimental results shown in FIGS. 16 and 17 may be considered as that the graphs respectively show the relationships between the length Ls of the clearance 47 and the increase percentage of the amount of air passing through the condenser core portion 2 and the relationship between the length Ls of the clearance 47 and the increase percentage of the heat exchange of the condenser core portion 2.
  • the inventors have compared the merit of the duct effect by decreasing the length Ls of the clearance 47 with the demerit by increasing the air flow resistance. As a result, it is preferable that the length Ls of the clearance 47 is equal to 5.0 mm or less (0 ⁇ Ls ⁇ 5). Further, when the improvement of the increase percentage of the heat exchange with the duct effect is considered, the projection length (deviated amount) Lc may be in a range of -1.0 - 7.0 mm.
  • the present invention can be embodied.
  • the clearances 47 may be formed in the width direction alternately so as to overlap with each other. Further, the clearance 47 may be slantingly formed so that the longitudinal direction of the clearance 47 has a predetermined angle with reference to the longitudinal direction of the cooling fin.
  • the cooling fins 22 and 32 are projected toward only the clearance 46 side.
  • the cooling fins can be projected to a side of opposing the clearance 46.
  • the clearance 46 is closed by the side plate 50.
  • a partition plate for closing the clearance 46 may be assembled into the two side plates 23 and 33 without integrating the two side plates 23 and 33.
  • the partition plate is formed by a member having a small heat exchange efficiency such as resin.
  • the wall thickness corresponding to the portion of the clearance 46 may be made thinner than the other portion.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (13)

  1. Echangeur de chaleur comprenant :
    une pluralité de premières tubulures (21) dans lesquelles s'écoule un premier réfrigérant ;
    une première ailette de refroidissement ondulée (22), dans laquelle une pluralité de parties repliées (22a) est formée en continu, ladite première ailette de refroidissement ondulée (22) étant disposée entre des premières tubulures adjacentes (21) ;
    une pluralité de seconde tubulures (31) dans lesquelles s'écoule un second réfrigérant, lesdites secondes tubulures (31) étant disposées en parallèle avec lesdites premières tubulures (21) ;
    une seconde ailette de refroidissement ondulée (32), dans laquelle une pluralité de parties repliées (32a) est formée en continu, ladite seconde ailette de refroidissement ondulée (32) étant disposée entre des secondes tubulures (31) adjacentes ; et
    une pluralité de parties de raccord (45) destinée à raccorder une partie d'extrémité latérale en regard de la seconde ailette de refroidissement adjacente (32) de ladite première ailette de refroidissement (22) et une partie d'extrémité latérale en regard de la première ailette de refroidissement adjacente (22) de ladite seconde ailette de refroidissement (32),
    caractérisé en ce que ladite pluralité de parties de raccord (45) définit une pluralité de débattements disposés entre ladite première ailette de refroidissement ondulée (22) et ladite seconde ailette de refroidissement ondulée (32),
    dans lequel au moins deux desdites parties repliées (22a, 32a) desdites première et seconde ailettes de refroidissement ondulées (22, 32) sont formées entre des parties de raccord adjacentes (45).
  2. Echangeur de chaleur selon la revendication 1, dans lequel chacune desdites première et seconde ailettes de refroidissement (22, 32) comprend une partie plate (22c, 32c) formée entre les parties repliées adjacentes (22a, 32a), et
    lesdites parties de raccord (45) sont formées entre chaque paire de ladite partie plate (22a) de ladite première ailette de refroidissement (22) et ladite partie plate (32a) de ladite seconde ailette de refroidissement (32).
  3. Echangeur de chaleur selon la revendication 1 ou 2, dans lequel une direction longitudinale desdits débattements traverse une direction de nervure desdites parties repliées (22a, 32a) selon un angle prédéterminé, lesdits débattements étant formés en fente et définis de sorte à traverser une pluralité desdites parties repliées (22a, 32a).
  4. Echangeur de chaleur selon la revendication 1, dans lequel lesdites premières tubulures (21) sont utilisées pour des tubulures de condenseur (21) d'une partie centrale de condenseur (2) afin de condenser un réfrigérant d'un condenseur en vue de former un cycle de réfrigération,
    lesdites secondes tubulures (31) sont utilisées pour des tubulures de radiateur (31) d'une partie centrale de radiateur (3) d'un radiateur destiné au refroidissement d'un moteur d'automobile, et
    ladite partie centrale de condenseur (2) est disposée au niveau d'un côté air amont de ladite partie centrale de radiateur (3).
  5. Echangeur de chaleur selon la revendication 1, dans lequel ledit échangeur de chaleur est un échangeur de chaleur d'automobile pour refroidissement de l'eau dans un moteur et d'un réfrigérant d'un appareil de climatisation employant un cycle de réfrigération, ledit échangeur de chaleur d'automobile est disposé au niveau de la partie frontale du véhicule, dans laquelle ledit réfrigérant pendant ledit cycle s'écoule dans la pluralité de premières tubulures (21), l'eau servant dudit second réfrigérant s'écoule dans la pluralité de secondes tubulures (31), lesdites secondes tubulures (31) étant disposées au niveau d'un côté air aval desdites premières tubulures (21), comprenant, en outre,
    une première partie centrale (2) incluant ladite première ailette de refroidissement (22) et lesdites premières tubulures (21) ;
    une seconde partie centrale (3) incluant ladite seconde ailette de refroidissement (32) et lesdites secondes tubulures (31) ; et
    un élément de cloisonnement (50) disposé aux parties d'extrémité de ladite première partie centrale (2) et de ladite seconde partie centrale (3) pour empêcher l'air de contourner ladite première partie centrale (2) de s'écouler à travers ledit débattement entre ladite première ailette de refroidissement (22) et ladite seconde ailette de refroidissement (32).
  6. Echangeur de chaleur selon la revendication 5, dans lequel ledit élément de cloisonnement (50) est formé d'une plaque latérale (50) qui est un élément de renfort de ladite première partie centrale (2) et de ladite seconde partie centrale (3).
  7. Echangeur de chaleur selon la revendication 1, dans lequel ledit échangeur de chaleur est un échangeur de chaleur d'automobile pour refroidissement de l'eau d'un moteur et d'un réfrigérant d'un appareil de climatisation employant un cycle de réfrigération, ledit échangeur de chaleur d'automobile est disposé au niveau d'un côté frontal du véhicule dans lequel :
    ledit réfrigérant pendant ledit cycle s'écoule dans la pluralité de premières tubulures (21),
    l'eau servant dudit second réfrigérant, s'écoule dans la pluralité de secondes tubulures (31), lesdites secondes tubulures (31) étant disposées au niveau d'un côté air aval desdites premières tubulures (21) comprenant, en outre,
    une première partie centrale (2) incluant ladite première ailette de refroidissement (22) et lesdites premières tubulures (21) ;
    une seconde partie centrale (3) incluant ladite seconde ailette de refroidissement (32) et lesdites secondes tubulures (3) ; et
    dans lequel ledit débattement entre ladite première ailette de refroidissement (22) et ladite ailette de refroidissement (32) a une distance (Ls) qui est égale à 5, 0 mm ou moins.
  8. Echangeur de chaleur selon l'une des revendications 5 à 7, dans lequel une partie d'extrémité de ladite première ailette de refroidissement (22) disposée au niveau dudit côté de seconde tubulure (31) est déviée suivant une direction allant vers la droite de ladite première tubulure (21) vers ladite seconde tubulure (31) dans une gamme de -1,5 à 7, 0 mm d'une position standard dans laquelle une partie d'extrémité de ladite première tubulure (21) est disposée au niveau du côté de ladite seconde tubulure (31).
  9. Echangeur de chaleur selon la revendication 5, dans lequel
    ladite seconde ailette de refroidissement (32) est projetée de ladite seconde tubulure (31) vers le côté de ladite première tubulure (21) avec une longueur de projection qui est égale à 8, 0 mm ou moins.
  10. Echangeur de chaleur selon l'une des revendications précédentes, dans lequel lesdites parties de raccord (45) comprennent une partie en parallèle avec une direction longitudinale desdites premières et secondes ailettes de refroidissement (22, 32), une longueur de ladite partie étant égale à 5 % ou moins d'une longueur entre chaque paire des parties de raccord (45) adjacentes lorsque lesdites premières et secondes ailettes de refroidissement (22, 32) sont dépliées.
  11. Echangeur de chaleur selon l'une des revendications précédentes, dans lequel lesdites parties de raccord (45) comprennent une partie en parallèle avec une direction longitudinale desdites premières et secondes ailettes de refroidissement ondulées (22, 32), une longueur de ladite partie étant égale à 10 % ou moins d'une longueur entre chaque paire des parties de raccord (45) adjacentes lorsque lesdites premières et secondes ailettes de refroidissement (22, 32) sont dépliées.
  12. Echangeur de chaleur selon la revendication 10, dans lequel ladite première ailette de refroidissement (22) est projetée desdites premières tubulures (21) vers lesdites secondes tubulures (31) avec une longueur de projection étant située dans une gamme de 1, 7 à 7, 0 mm.
  13. Echangeur de chaleur selon la revendication 12, dans lequel ladite seconde ailette de refroidissement (32) est projetée desdites secondes tubulures (31) vers lesdites premières tubulures (21) avec une longueur de projection étant égale à 5, 0 mm ou moins.
EP96118055A 1995-11-13 1996-11-11 Echangeur de chaleur Expired - Lifetime EP0773419B1 (fr)

Applications Claiming Priority (9)

Application Number Priority Date Filing Date Title
JP294528/95 1995-11-13
JP29452895A JP3446427B2 (ja) 1995-11-13 1995-11-13 熱交換器
JP29452895 1995-11-13
JP32760495 1995-12-15
JP327604/95 1995-12-15
JP32760495 1995-12-15
JP146082/96 1996-06-07
JP14608296 1996-06-07
JP14608296A JP3709611B2 (ja) 1995-12-15 1996-06-07 熱交換器

Publications (3)

Publication Number Publication Date
EP0773419A2 EP0773419A2 (fr) 1997-05-14
EP0773419A3 EP0773419A3 (fr) 1998-08-19
EP0773419B1 true EP0773419B1 (fr) 2003-02-05

Family

ID=27319091

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96118055A Expired - Lifetime EP0773419B1 (fr) 1995-11-13 1996-11-11 Echangeur de chaleur

Country Status (4)

Country Link
EP (1) EP0773419B1 (fr)
KR (1) KR100268098B1 (fr)
CN (1) CN1149380C (fr)
DE (1) DE69626085T2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8196646B2 (en) 2008-12-15 2012-06-12 Delphi Technologies, Inc. Heat exchanger assembly

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Publication number Priority date Publication date Assignee Title
EP0825404B2 (fr) 1996-08-12 2008-04-16 Calsonic Kansei Corporation Echangeurs de chaleur combinés
JP4019113B2 (ja) * 1997-11-13 2007-12-12 株式会社ティラド 一体型熱交換器のフィンとその製造方法
FR2786259B1 (fr) * 1998-11-20 2001-02-02 Valeo Thermique Moteur Sa Echangeur de chaleur combine, en particulier pour vehicule automobile
JP3625259B2 (ja) * 1999-07-19 2005-03-02 株式会社ゼクセルヴァレオクライメートコントロール 熱交換器
JP4281175B2 (ja) * 1999-09-29 2009-06-17 株式会社デンソー 複式熱交換器
US20030106677A1 (en) * 2001-12-12 2003-06-12 Stephen Memory Split fin for a heat exchanger
KR20030092711A (ko) * 2002-05-31 2003-12-06 한라공조주식회사 일체형 열교환기
DE10342241A1 (de) 2003-09-11 2005-04-07 Behr Gmbh & Co. Kg Wärmetauscher
DE102006017434B4 (de) * 2005-08-04 2020-03-12 Hanon Systems Mehrflutiger Wärmeübertrager
JP2007170987A (ja) * 2005-12-22 2007-07-05 Keyence Corp 接触式変位計
JP5920175B2 (ja) * 2012-11-13 2016-05-18 株式会社デンソー 熱交換器
EP3580505A4 (fr) * 2017-02-13 2020-12-16 Evapco, Inc. Condenseur de trajet de fluide à multiple sections transversales
JP7346958B2 (ja) * 2018-07-25 2023-09-20 株式会社デンソー 熱交換器
CN109405621A (zh) * 2018-08-30 2019-03-01 纳百川控股有限公司 水箱翅片

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JPS5680698A (en) * 1979-11-30 1981-07-02 Nippon Denso Co Ltd Heat exchanger
JPH0645155Y2 (ja) * 1988-10-24 1994-11-16 サンデン株式会社 熱交換器
JP2786702B2 (ja) * 1989-12-07 1998-08-13 昭和アルミニウム株式会社 複式一体型熱交換器
ES2127472T3 (es) * 1994-04-12 1999-04-16 Showa Aluminum Corp Intercambiador de calor duplex de tipo apilado.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8196646B2 (en) 2008-12-15 2012-06-12 Delphi Technologies, Inc. Heat exchanger assembly

Also Published As

Publication number Publication date
DE69626085D1 (de) 2003-03-13
DE69626085T2 (de) 2003-11-13
KR970028428A (ko) 1997-06-24
CN1149380C (zh) 2004-05-12
EP0773419A3 (fr) 1998-08-19
KR100268098B1 (ko) 2000-10-16
EP0773419A2 (fr) 1997-05-14
CN1159567A (zh) 1997-09-17

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