EP1195568B1 - Echangeur de chaleur comportant plusieurs portions d'échange de chaleur - Google Patents

Echangeur de chaleur comportant plusieurs portions d'échange de chaleur Download PDF

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Publication number
EP1195568B1
EP1195568B1 EP02000277.0A EP02000277A EP1195568B1 EP 1195568 B1 EP1195568 B1 EP 1195568B1 EP 02000277 A EP02000277 A EP 02000277A EP 1195568 B1 EP1195568 B1 EP 1195568B1
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EP
European Patent Office
Prior art keywords
core portion
louver
condenser
radiator
length
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
EP02000277.0A
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German (de)
English (en)
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EP1195568A1 (fr
Inventor
Tatsuo Sugimoto
Shinobu Suzuki
Takaaki Sakane
Yasutoshi Yamanaka
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Denso Corp
Original Assignee
Denso Corp
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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
    • 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
    • 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
    • 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 invention relates to a heat exchanger according to the preamble of claim 1.
  • a heat exchanger is known from EP 0 367 078 .
  • the present invention relates to a heat exchanger in which different core portions are integrated with each other, and more particularly the present invention relates to a heat exchanger which can be effectively applied to a radiator of an automotive engine and a condenser of an automotive air conditioning apparatus.
  • an automotive air conditioning apparatus is assembled into a vehicle at 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 during vehicle assembling process. Therefore the automotive air conditioning apparatus is assembled with automotive parts in the assembling process of the vehicle at the manufacturing plant.
  • a heat exchanger in which different core portions such as a radiator and a condenser are integrated is disclosed in Japanese Patent Publication No. 3-177795 .
  • cooling fins of first core portion and second core portion are integrated with each other. These cooling fins are connected to each oval flat tube of the first and second core portions by brazing.
  • a plurality of slits are formed at the center portion between the first and second core portions for interrupting a heat transmission from a high temperature side core portion (for example, radiator core portion) to a low temperature side core portion (for example, condenser core portion).
  • a high temperature side core portion for example, radiator core portion
  • a low temperature side core portion for example, condenser core portion
  • the required heat exchanging abilities of the first core portion (condenser core portion) and the second core portion (radiator core portion) varies in accordance with the difference of engine type or vehicle type despite the required constitutions of the heat exchanger are the same.
  • the required heat exchanging abilities thereof are set by tuning fin pitches of the cooling fins respectively in accordance with the engine type or vehicle type.
  • each fin pitch cannot be designed independently respectively. Therefore, the above-described method of setting the fin pitches in the first and second core potions respectively cannot be applied to this type heat exchanger.
  • the length of the louver in one core portion, out of the first and second core portions, the required radiation amount of which is smaller than that of the other core portion is shorter than the length of the louver in the other core portion.
  • the length of the louver is short thereby decreasing the heat transfer ratio.
  • the pressure loss in the core portion decreases thereby increasing the flow amount of the external fluid.
  • the radiation amount of the core portion having a large required radiation amount increases.
  • a tilt angle of the louver in one core portion, out of the first and second core portion, the required radiation amount of which is smaller than that of the other core portion is smaller than the tilt angle of the louver in the other core portion.
  • the tilt angle of the louver is small thereby decreasing the heat transfer ratio.
  • the pressure loss in the core portion decreases thereby increasing the flow amount of the external fluid.
  • the radiation amount of the core portion having a large required radiation amount increases.
  • a condenser core portion 2 of an automotive air conditioning apparatus is used as a first core portion, and a radiator core portion 3 for cooling an engine is used as a second core portion.
  • the condenser core portion 2 is disposed at the upstream air side of the radiator core portion 3 in air flow direction and the two core portions 2, 3 are disposed in series in the air flow direction at the front-most portion of an engine compartment.
  • the structure of the heat exchanger of the first embodiment is hereinafter described with reference to FIGS. 1 through 5 .
  • FIG. 1 is a partial enlarged cross-sectional view 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 in which a plural refrigerant passages are formed, 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, in which a single refrigerant passage is formed, disposed in parallel with the condenser tubes 21 and radiator cooling fins 32.
  • the tubes 21 and 31 and the cooling fins 22, 32 are alternately laminated and are brazed to each other.
  • a plurality of louvers 220 and 320 are formed in the two cooling fins 22, 32 to facilitate heat exchange.
  • the two cooling fins 22, 23 and a plurality of connecting portions 45 are integrally formed with the louvers 220, 320 by a roller forming method or the like.
  • the connecting portions 45 are formed between the two cooling fins 22, 32 for connecting the two cooling fins 22, 23. At both sides of the connecting portion 45, adiabatic slits 47 are provided for interrupting heat transmission from the radiator core portion 3 to the condenser core portion 2.
  • the width of the connecting portion 45 is set to be smaller enough than the height of the cooling fins 22, 32 (the distance between a pair of adjacent flat tubes 21, 31) to suppress the heat transmission from the radiator core portion 3 to the condenser core portion 2.
  • Side plates 23, 33 are reinforcement member of the two heat exchanging core portions 2, 3.
  • the side plates 23, 33 are respectively disposed in upper and lower end portions of the two heat exchanging core portions 2, 3 as shown in FIG. 2 .
  • the side plates 23, 33 are integrally formed from a sheet of aluminum plate to a general U-shape in cross section.
  • Connecting portions 4 for connecting the side plate 23 and the side plate 33 are formed in two end portions of the longitudinal direction of the two side plates 23, 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 to suppress the heat transmission. Further, a recess portion is formed in the top end portion 43 of the connecting portion 4 to reduce the thickness of the plate wall of the connecting portion 4.
  • first header tank 34 for distributing cooling water to each radiator tube 31 is disposed at an end (left end) side of the radiator core portion 3.
  • the front shape of first header tank 34 is nearly a triangular, the cross-sectional shape is ellipsoid as shown in FIG. 3 .
  • An inlet 35 of cooling water flowing to the radiator is formed at an upper side of the first header tank 34 having a nearly triangular shape.
  • a pipe 35a for connecting a pipe (not shown) of cooling water is brazed to the inlet 35.
  • a second header tank 36 for receiving the cooling water having been heat-exchanged is disposed in an opposite end (right end) of the first header tank 34.
  • the second header tank 36 has a similar shape with the first header tank 34.
  • 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.
  • 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 37a for connecting the pipe (not shown) of cooling water is brazed to the outlet 37.
  • a first header tank 24 is disposed at an end side of the condenser core portion 2 for distributing the refrigerant into each 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.
  • a joint 26a for connecting a refrigerant pipe (not shown) is brazed to the body of the first header tank 24, and an inlet 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 at an opposite end of the first header tank 24 of the condenser core portion 2.
  • 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 width Lc of the condenser cooling fin 22 and the width Lr of the radiator cooling fin 32 have the same length as the width of the tubes 21, 31 in the cross sectional longitudinal direction thereof.
  • the widths Lc, Lr are the dimension of the cooling fins 22, 32 along the cross sectionally longitudinal direction of the tubes 21, 31 (air flow direction) .
  • the louver 220 of the condenser cooling fin 22 is constructed by a first louver group 221, a second louver group 222, and a turning louver 223 arranged between both louver groups 221, 222.
  • the turning louver 223 turns the air flow.
  • the first louver group 221 and the second louver group 222 tilt toward the opposite side to each other.
  • a first louver group 321, a second louver group 322, and a turning louver 323 are provided in the radiator cooling fin 32.
  • each first and second louver groups 221, 222 has three louvers 220.
  • each first and second louver groups 321, 322 has five louvers 320.
  • the ratio of the Nc and Lc in the condenser cooling fin 22 (Nc/Lc) and the ratio of the Nr and Lr in the radiator cooling fin 32 (Nr/Lr) satisfy the following relation: Nc / Lc ⁇ Nr / Lr .
  • the condenser cooling fin 22 has six louvers although ten louvers can be provided thereon if desired. Therefore, the area of air introducing portions 224, 225 provided in front and rear of the louvers 220 can be wide relative to the area where the louvers 220 are formed.
  • a gas phase refrigerant flowing out of a compressor flows into the first header tank 24 through the refrigerant inlet 26.
  • the gas phase refrigerant flows in the condenser tubes 21 from the right side to the left side in FIGS. 2 and 3 while being heat exchanged with the cooling air to be condensed.
  • the condensed liquid phase refrigerant is collected in the second header tank 25 and flows out of the condenser core portion 2 through the refrigerant outlet 27.
  • a hot engine coolant flows from an engine into the first header tank 34 through the engine coolant inlet 35.
  • the engine coolant flows in the radiator tube 31 from the left side to the right side in FIGS. 2 and 3 while being heat exchanged with the cooling air to be cooled.
  • the cooled engine coolant is collected in the second header tank 36 and flows out of the radiator core portion 3 through the engine coolant outlet 37.
  • the heat transmitting ratio and the air flow resistance decrease in accordance with a decrease in the number of the louvers 220, 320.
  • louvers are provided although ten louvers can be provided thereon if desired. While, in the radiator cooling fin 32, ten louvers are provided by using the most of the space thereof.
  • the heat transfer ratio in the condenser core potion 2 decreases in accordance with the decreasing the number of the louvers 220.
  • the heat transmitting ability of the condenser core portion 2 decreases.
  • the air flow resistance in the condenser core portion 2 decreases thereby increasing the amount of the cooling air passing through the radiator core portion 3.
  • the heat transmitting ability of the radiator core portion 3 increases.
  • ten louvers 220 are provided by making the most of the space thereof. While, in the radiator cooling fin 32, six louvers 320 are provided although ten louvers can be provided thereon if desired. That is, the relation: (Nc/Lc) > (Nr/Lr) is satisfied. Thereby, the radiation amount in the radiator core portion 3 decreases, while the radiation amount in the condenser core portion 2 increases with the air flow amount increasing.
  • FIG. 7 shows the relations between the number of louvers decreasing ratio and the performance ratios of the core portions 2, 3 under the condition that air flow speed of the cooling air is constant.
  • the number of louvers decreasing ratio is defined as a ratio of the number of louvers decreased relative to the number of louvers which can be provided within the predetermined fin width Lc, Lr.
  • the number of louvers decreasing ratio is 40%.
  • the number of louvers decreasing ratio is 40%.
  • a projection portion 326 is formed at the air upstream side end (the end facing the condenser core portion 2) of the radiator cooling fin 32.
  • This projection portion 320 protruses from the end of the radiator tube 31 toward the air upstream side. Thereby, the number of louvers Nr in the radiator cooling fin 32 is increased more than that in the first embodiment.
  • the radiator cooling fin 32 has twelve louvers 320.
  • a radiation amount difference between in the condenser core portion 2 and in the radiator core portion 3 is expanded more than in the first embodiment.
  • the condenser cooling fin 22 has six louvers in spite of ten louvers can be provided thereon if making the most of the space thereof.
  • the louver pitch Lpc of the louver 220 is set to be wider than the louver pitch Lpr of the louver 320.
  • the louver pitch Lpc is defined as a distance between a pair of adjacent louvers 220, 320. This distance is same as the length of each louver 220, 320 in the air flow direction.
  • the louver pitch in the condenser cooling fin 22 is set to be wider than in the first embodiment.
  • the length of the air introducing portions 224, 225 (L1+L2) can be decreased more than in the first embodiment.
  • the area L3 where the louvers 220 are formed is partial to the center portion of the condenser cooling fin 22.
  • the air flowing along the tilted surface of the louvers 220 is collected in the center portion of the cooling fin 22, and the reduction ratio of the heat transmitting ratio can be made remarkable.
  • the louver pitch Lpc is set to be larger than in the first embodiment, the air flowing along the tilted surface of the louvers 220 is spread entirely.
  • the reduction ratio of the heat transmitting ratio can be decreased.
  • the fin width Lc of the condenser cooling fin 22 is smaller than the width Ltc of the condenser oval flat tube 21. While, in the radiator cooling fin 32, the fin width Lr is same as the width Ltr of the radiator oval flat tube 31. Here, the width Ltc of the condenser tube 21 is same as the width Ltr of the radiator tube 31.
  • L F denotes a width of an entire fin constructed by the condenser cooling fin 22 and the radiator cooling fin 32, and L denotes the distance between both ends of both oval flat tubes 21, 31 (the width of the heat exchanger).
  • the radiation area in the condenser core portion 2 decreases thereby decreasing the radiation amount.
  • the air flow resistance in the condenser core portion 2 decreases thereby increasing the air flow amount passing through these heat exchanging core portions 2, 3. Consequently, the radiation amount in the radiator core portion 3 increases.
  • the fin width Lr of the radiator cooling fin 32 is smaller than the width Ltr of the radiator oval flat tube 31. While, in the condenser cooling fin 22, the fin width Lc is same as the width Ltc of the condenser oval flat tube 21. Here, the width Ltc of the condenser tube 21 is same as the width Ltr of the radiator tube 31.
  • the radiation amount in the radiator core portion 3 decreases.
  • the air flow resistance in the radiator core portion 3 decreases thereby increasing the air flow amount passing through these heat exchanging core portions 2, 3. Consequently, the radiation amount in the condenser core portion 2 increases,
  • FIG. 12 is a graph showing the experimented results based on the fifth and the sixth embodiments.
  • the graph shows relations between the ratio of the fin width Lc, Lr to the tube width Ltc, Ltr (Lc/Ltc, Lr/Ltr) and the radiation performance ratio of the condenser core portion 2 and the radiator core portion 3.
  • the experimented results are under the condition that the air flow speed is constant.
  • the fin width Lc or Lr when the fin width Lc or Lr is set to 80% of the tube widths Ltc, Ltr in one of the condenser core portion 2 and the radiator core portion 3, the radiation amount in this core portion decreases by about 10% and the pressure loss therein decreases by about 20%. In this way, as the pressure loss decreases in one core portion, the flow amount of the air passing through these core portions increases thereby increasing the radiation amount in the other core portion by about 3%. Further, as is understood from FIG. 12 , it is necessary to set the fin width Lc, Lr to 80% or less of the tube width Ltc, Ltr.
  • the length L T of the flat turning surface 223a, 323a of the turning louver 223, 323 is set to be three times or more as the louver pitch Lp.
  • the length of the flat turning surface 223a, 323a is set to be about 5.5 times as the louver pitch Lp.
  • the object of the seventh embodiment is to suppress the reduction of heat transfer ratio in the cooling fin 22, 32.
  • FIGS. 14 and 15 show a first and a second comparison examples being compared with the seventh embodiment.
  • the first and second comparison examples are all the same except for the number of louvers 220, 320.
  • FIG. 17 shows the relations between the length L T and the performance ratio of the core portion 2, 3 under the condition that the air flow speed is constant.
  • the length L T is expressed as a multiple of the louver pitch Lp.
  • the heat transfer ratio and the pressure loss ratio of the fin increase as the length L T becomes large, and are saturated as the length L T is more than 3 ⁇ Lp. Therefore, it is preferable to set the length L T to be three times or more as the louver pitch Lp.
  • the heat transfer ratio of the fin increases in accordance with that the length L T of the flat turning surface 223a, 323a becomes large because the following reason. That is, as the length L T becomes large, the flow speed of the air passing through the second louver group 222, 322 which is disposed at the air downstream side of the turning louver 223, 323 recovers. Thus, the air passes through the second louver group 222, 322 at high speed.
  • the length L T of the flat turning surface 223a, 323a of the turning louver 223, 323 is set to be three times or more as the louver pitch Lp.
  • the axis of abscissa denotes the cross sectional shape of the fin in the comparison example shown in FIG. 14B in the air flow direction.
  • the axis of abscissa denotes the cross sectional shape of the fin in the seventh embodiment shown in FIG. 13B in the air flow direction.
  • the turning louver 223, 323 is formed into a V-shape, i.e., the turning louver 223, 323 has no flat turning surface.
  • the flow speed of the air passing through the second louver group 222, 322 does not recover and is still low. Therefore, as denoted by 1 in FIG. 18A , the heat transfer ratio in the second louver group 222, 322 is lower than that in the first louver group 221, 321.
  • the length L T of the flat turning surface 223a, 323a is set to be 5.5 times as the louver pitch Lp. That is, the length L T is large enough to make the speed of the air passing through the second louver group 222, 322 recover.
  • the heat transfer ratio in the second louver group 222, 322 is approximately the same as in the first louver group 221, 321 as denoted by 2 in FIG. 18B .
  • the length L T of the flat turning surface 223a, 323a in one cooling fin in which the number of louvers is smaller than that in the other cooling fin is set to be longer than the length Li of the air introducing portion 224, 324 disposed at the air upstream side of the louvers 220, 320 for making the flow speed of the air passing through the second louver group 222, 322 recover.
  • a length (cut length) Ec of the condenser louver 220 and a length (cut length) Er of the radiator louver 320 are set to be different from each other.
  • the length Ec, Er is defined as a length of the louver 220, 320 in a direction perpendicular to the air flow direction, and influences the heat transfer ratio and the air flow resistance.
  • the length Ec of the condenser louver 220 is set to be shorter than the length Er of the radiator louver 320 for improving the performance of the radiator core portion 3.
  • the performance of the condenser core portion 2 is decreased by shortening the length length Ec of the condenser louver 220, the air resistance is decreased by shortening the length Ec of the condenser louver 220 thereby increasing the air flow amount. Therefore, the performance of the radiator core portion 3 is improved.
  • the fin height Hf of the cooling fin 22, 32 (distance between a pair of adjacent tubes) is 8mm, the length Er of the radiator louver 320 is 7mm, and the length Ec of the condenser louver 220 is 5mm.
  • the length Er of the radiator louver 320 is set to be shorter than the length Ec of the condenser louver 220 for improving the performance of the condenser core portion 2
  • the projection portion 326 described in FIG. 8A is provided at the air upstream side end of the radiator cooling fin 32, and a projection portion 327 facing the projection portion 326 is provided at the air downstream side end of the condenser cooling fin 22 also.
  • the number of condenser louvers 220 in the second louver group 222 and the number of radiator louvers 320 in the first louver group 321 are increased.
  • the length Ec of the condenser louver 220 is set to be shorter than the length Er of the radiator louver 320.
  • FIG. 22 is a graph showing relations between the length of the louver in the first through third embodiments according to the invention and the performance of the core portion under the condition that the flow speed of the air passing through the core portion is constant.
  • the louver length ratio placed on the axis of abscissa is a ratio of the louver length which is shortened intently (for example, condenser louver length Ec in the eighth embodiment) to the louver length which is defined by the fin height Hf (for example, radiator louver length Er in the eighth embodiment),
  • louver length ratio is defined as follows: Louver length which is shortened intensity / Louver length which is defined by a fin height .
  • the louver length ratio when the louver length ratio is set to be 50%, the radiation amount in the core portion in which the louver length is shorten decreases by about 10%, and the pressure loss therein decreases by about 30%. By this, pressure loss decreases by about 30%, the radiation amount in the core portion in which the louver length is defined by the fin height is improved by about 5%.
  • a tilt angle ⁇ c of the condenser louver 220 and a tilt angle 0 r of the radiator louver 320 are set to be different from each other.
  • the tilt angles ⁇ c, ⁇ r influence the heat transfer ratio and the air flow resistance.
  • the tilt angle ⁇ c of the condenser louver 220 is set to be smaller than the tilt angle ⁇ r of the radiator louver 320 for improving the radiation performance of the radiator core portion 3.
  • the performance of the condenser core portion 2 decreases by reducing the tilt angle ⁇ c of the condenser louver 220
  • the air resistance decreases by reducing the tilt angle ⁇ c of the condenser louver 220 thereby increasing the air flow amount. Therefore, the performance of the radiator core portion 3 is improved.
  • the tilt angle ⁇ c of the condenser louver 220 is 18°
  • the tilt angle ⁇ r of the radiator louver 320 is 25°.
  • the tilt angle ⁇ r of the radiator louver 320 is set to be smaller than the tilt angle ⁇ c of the condenser louver 220 for improving the performance of the condenser core portion 2.
  • the projection portion 326 described in FIG. 21 is provided at the air upstream side end of the radiator cooling fin 32, and a projection portion 327 facing the projection portion 326 is provided at the air downstream side end of condenser cooling fin 22 also.
  • the number of condenser louvers 220 in the second louver group 222 and the number of radiator louvers 321 in the first louver group 322 are increased.
  • the tilt angle ⁇ c of the condenser louver 220 is set to be larger than the tilt angle ⁇ r of the radiator louver 320.
  • FIG. 26 is a graph showing relations between the tilted angle of the louver in the eleventh through thirteenth embodiments and the performance of the core portion under the condition that the flow speed of the air passing through the core portion is constant.
  • a louver tilt angle reduction ratio which is placed on the axis of abscissa is defined as a ratio of the tile-angle reduced intently to the common tilt-angle for attaining a high heat transfer ratio.
  • louver tilt angle reduction ratio is defined as follows: tile - angle reduced intently / common tilt - angle for attaining a high heat transfer ratio ⁇ 100.
  • the radiation amount in the core portion in which the tilt-angle is reduced decreases by about 10%, and the pressure loss therein decreases by about 25%.
  • the radiation amount in the core portion in which the tile-angle of the louver is the common angle for attaining the high heat transfer ratio is improved about 4%.
  • the present invention is applied to the heat exchanger in which the condenser core portion 2 and the radiator core portion 3 are integrated.
  • the present invention can be applied to various heat exchangers in which two heat exchanging core portions, to carry out heat exchanges between two kinds of fluid and the air, are integrated.

Claims (3)

  1. Echangeur de chaleur (1) comprenant :
    une première partie de noyau (2) destinée à effectuer un échange de chaleur entre un premier fluide et un fluide externe, ladite première partie de noyau (2) comportant une pluralité de premiers tubes (21) à travers lesquels le premier fluide s'écoule et une première ailette de refroidissement (22) ayant des fentes multiples (220) disposées entre chaque dite paire de premiers tubes adjacents (21) ; et
    une deuxième partie de noyau (3) disposée de manière à effectuer un échange de chaleur entre un deuxième fluide et le fluide externe, ladite deuxième partie de noyau (3) comportant une pluralité de deuxièmes tubes (31) à travers lesquels le deuxième fluide s'écoule et une deuxième ailette de refroidissement (32) ayant des fentes multiples (320) disposées entre chaque dite paire de deuxièmes tubes adjacents (31) ; dans lequel
    ladite première partie de noyau (2) et ladite deuxième partie de noyau (3) sont disposées en parallèle avec un espace prédéterminé (46) entre elles,
    ladite première ailette de refroidissement (22) et ladite deuxième ailette de refroidissement (23) sont intégrées par une partie de raccordement (45),
    caractérisé en ce que
    une longueur de ladite fente dans une partie de noyau, parmi lesdites première et deuxième parties de noyau, dont une quantité de rayonnement requise est inférieure à celle de l'autre partie de noyau, est plus courte qu'une longueur de ladite fente dans l'autre partie de noyau, et
    dans lequel la longueur de ladite fente dans une partie de noyau, ayant une quantité de rayonnement requise inférieure à celle dans l'autre partie de noyau, est plus courte que 50% de la longueur de ladite fente dans l'autre partie de noyau.
  2. Echangeur de chaleur (1) selon la revendication 1, dans lequel un angle d'inclinaison de ladite fente dans ladite partie de noyau, parmi lesdites première et deuxième parties de noyau, dont la quantité de rayonnement requise est inférieure à celle de l'autre partie de noyau, est plus petit qu'un angle d'inclinaison de ladite fente dans l'autre partie de noyau.
  3. Echangeur de chaleur (1) selon la revendication 1, dans lequel ladite première partie de noyau (2) est une partie de noyau de condenseur (2) pour condenser un réfrigérant d'un condenseur afin de former un cycle de réfrigération,
    ladite deuxième partie de noyau (3) est une partie de noyau de radiateur (3) pour refroidir un liquide de refroidissement de moteur d'un moteur d'automobile,
    ledit fluide externe est un air de refroidissement permettant de condenser le réfrigérant et de refroidir le liquide de refroidissement de moteur, et
    ladite partie de noyau de condenseur (2) est disposée au niveau d'un côté amont d'air de ladite partie de noyau de radiateur (3).
EP02000277.0A 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur Expired - Lifetime EP1195568B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP06323797A JP3855346B2 (ja) 1997-03-17 1997-03-17 熱交換器
JP6323797 1997-03-17
EP19980104696 EP0866298B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP19980104696 Division EP0866298B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur

Publications (2)

Publication Number Publication Date
EP1195568A1 EP1195568A1 (fr) 2002-04-10
EP1195568B1 true EP1195568B1 (fr) 2014-02-12

Family

ID=13223422

Family Applications (4)

Application Number Title Priority Date Filing Date
EP02000277.0A Expired - Lifetime EP1195568B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur
EP02000275.4A Expired - Lifetime EP1195566B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur
EP02000276A Expired - Lifetime EP1195567B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur
EP19980104696 Expired - Lifetime EP0866298B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur

Family Applications After (3)

Application Number Title Priority Date Filing Date
EP02000275.4A Expired - Lifetime EP1195566B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur
EP02000276A Expired - Lifetime EP1195567B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur
EP19980104696 Expired - Lifetime EP0866298B1 (fr) 1997-03-17 1998-03-16 Echangeur de chaleur comportant plusieurs portions d'échange de chaleur

Country Status (3)

Country Link
EP (4) EP1195568B1 (fr)
JP (1) JP3855346B2 (fr)
DE (1) DE69814717T2 (fr)

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JP4117429B2 (ja) * 1999-02-01 2008-07-16 株式会社デンソー 熱交換器用フィン
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JP4207331B2 (ja) * 1999-09-29 2009-01-14 株式会社デンソー 複式熱交換器
JP4599732B2 (ja) * 2000-03-16 2010-12-15 株式会社デンソー 複式熱交換器の製造方法
US6561264B2 (en) 2000-03-16 2003-05-13 Denso Corporation Compound heat exhanger having cooling fins introducing different heat exhanging performances within heat exchanging core portion
GB2372560A (en) 2001-02-24 2002-08-28 Llanelli Radiators Ltd Heat exchanger system
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DE10235038A1 (de) * 2002-07-31 2004-02-12 Behr Gmbh & Co. Flachrohr-Wärmeübertrager
JP4037241B2 (ja) 2002-10-24 2008-01-23 カルソニックカンセイ株式会社 コルゲートフィン
JP5563162B2 (ja) * 2011-07-14 2014-07-30 パナソニック株式会社 室外熱交換器および車両用空調装置
JP6050995B2 (ja) * 2012-09-18 2016-12-21 株式会社ケーヒン・サーマル・テクノロジー エバポレータ
JP5853948B2 (ja) * 2012-12-27 2016-02-09 株式会社デンソー 熱交換器
JP6354198B2 (ja) * 2014-02-21 2018-07-11 いすゞ自動車株式会社 ラジエータ
JP6687967B2 (ja) 2014-03-24 2020-04-28 株式会社デンソー 熱交換器
DE102015226577A1 (de) * 2015-12-22 2017-06-22 Mahle International Gmbh Blechteil mit einer Kiemen aufweisenden Rippenstruktur eines Wärmeübertragers sowie Herstellungsverfahren
JP2020034236A (ja) * 2018-08-30 2020-03-05 株式会社ティラド コルゲートフィンおよびその製造方法
WO2020239120A1 (fr) * 2019-05-31 2020-12-03 杭州三花微通道换热器有限公司 Tube plat, échangeur de chaleur à canaux multiples et système de réfrigération de climatisation
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Also Published As

Publication number Publication date
JP3855346B2 (ja) 2006-12-06
EP0866298A3 (fr) 1999-06-16
EP1195566A1 (fr) 2002-04-10
EP0866298A2 (fr) 1998-09-23
DE69814717T2 (de) 2004-03-18
EP0866298B1 (fr) 2003-05-21
JPH10253276A (ja) 1998-09-25
EP1195567B1 (fr) 2011-08-24
EP1195566B1 (fr) 2014-01-08
DE69814717D1 (de) 2003-06-26
EP1195567A1 (fr) 2002-04-10
EP1195568A1 (fr) 2002-04-10

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