CN111788448A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
CN111788448A
CN111788448A CN201980015955.5A CN201980015955A CN111788448A CN 111788448 A CN111788448 A CN 111788448A CN 201980015955 A CN201980015955 A CN 201980015955A CN 111788448 A CN111788448 A CN 111788448A
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China
Prior art keywords
height
heat exchanger
fin
exchange medium
tubes
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CN201980015955.5A
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Chinese (zh)
Inventor
吴光宪
全泰洙
李相俊
金泽根
郑焞安
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Hanon Systems Corp
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Hanon Systems Corp
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Publication of CN111788448A publication Critical patent/CN111788448A/en
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    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • 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
    • 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
    • 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
    • F28D2021/0082—Charged air coolers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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

Abstract

The present invention relates to a heat exchanger, and more particularly, to an air-cooled intercooler for a heat exchanger capable of cooling air compressed to high temperature and high pressure by a supercharger to improve an output of an engine by an air-cooling method, in which a heat exchanger including a plurality of tubes connected at both ends to a plurality of header tanks, inner fins provided between the tubes, and outer fins interposed between the tubes is formed such that the heights of the inner fins and the outer fins are set such that a cooling performance and a pressure drop amount of a heat exchange medium can be satisfied even if the number of rows of the tubes is reduced in a predetermined core region to reduce the weight, thereby reducing the weight in a limited space, that is, a heat exchanger package, and thus saving the manufacturing cost of the heat exchanger and improving the cooling performance of the heat exchanger.

Description

Heat exchanger
Technical Field
The present invention relates to a heat exchanger, and more particularly, to an air-cooled intercooler that cools air compressed to high temperature and high pressure by a supercharger in an air-cooled manner to increase the output of an engine.
Background
An Intercooler (Intercooler) in the heat exchanger is a device that cools air compressed to high temperature and high pressure by a supercharger in order to increase the output of the engine.
The temperature of the air rapidly compressed by the supercharger is very high, its volume expands and the oxygen density decreases, so that a phenomenon occurs in which the filling efficiency in the cylinder decreases. Therefore, the intercooler cools the high-temperature air compressed by the supercharger, thereby improving the intake efficiency of the engine cylinder, improving the combustion efficiency, and improving the fuel economy.
The intercooler performing such a function may be classified into a water-cooled type and an air-cooled type according to a cooling method. Among them, the air-cooled intercooler 10 is similar in principle to the water-cooled intercooler, but is different in that the charge side air is cooled by using the outside air instead of the cooling water or water of the vehicle when cooling the intercooler through which the charge side air of high temperature and high pressure passes.
The air-cooled intercooler 10 shown in fig. 1 includes an inlet header tank 12 and an outlet header tank 13 which are formed in parallel at a predetermined distance and in which cooling air is stored and flows, a plurality of tubes 11 having both ends connected to the inlet header tank 12 and the outlet header tank 13 to form a flow passage of the cooling air, outer fins 14 interposed between the plurality of tubes 11, and inner fins 15 provided inside the tubes 11, and high-temperature and high-pressure charge-side air compressed by a supercharger passes through the tubes 11 outside the air-cooled intercooler 10 to exchange heat with the cooling air passing through the tubes 11.
However, in such an air-cooled intercooler, if the number of rows of tubes is reduced in order to reduce the cost and weight, the weight can be effectively reduced, but the cooling performance is reduced.
That is, in order to reduce the weight of the air-cooled intercooler and ensure cooling performance in a limited space, it is necessary to optimize the heights of the inner and outer fins.
Documents of the prior art
Patent document
JP 2016-023550 A(2016.02.08)
Disclosure of Invention
Technical problem
The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a heat exchanger that reduces weight and improves cooling performance in a limited space, i.e., in a heat exchanger package.
Means for solving the problems
According to the heat exchanger of the present invention for achieving the object as described above, the heat exchanger 1000 may be constituted to include: a plurality of tubes 300 forming a flow path of the first heat exchange medium; an inner fin 400 provided inside the tube 300; and outer fins 500 interposed between the tubes 300, the first heat exchange medium passing through the tubes 300 and exchanging heat with the second heat exchange medium passing through the tubes 300, wherein in the heat exchanger 1000, the height of the inner fins 400 and the height of the outer fins 500 are formed such that the discharge temperature of the first heat exchange medium after passing through the tubes 300 reaches a temperature within a specific range within a predetermined region, and the height of the inner fins 400 and the height of the outer fins 500 are formed within a range satisfying the value of the following equation 1.
[ mathematical formula 1]
[ upper limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+177.31
[ lower limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+176.71
(Hh is the height of the inner fin, Hc is the height of the outer fin)
In the heat exchanger 1000, the height of the inner fin 400 and the height of the outer fin 500 may be set such that the weight of the heat exchanger 1000 is within a specific weight range, and the height of the inner fin 400 and the height of the outer fin 500 may be set such that the pressure drop amount of the first heat exchange medium passing through the inside of the tubes 300 of the heat exchanger 1000 is equal to or less than a specific value and the pressure drop amount of the second heat exchange medium passing through the space between the tubes 300 outside the heat exchanger 1000 is equal to or less than a specific value.
The height of the inner fin 400 and the height of the outer fin 500 may be set such that the pressure drop amount of the second heat exchange medium passing through the tubes 300 outside the heat exchanger 1000 is equal to or less than a value satisfying the following equation 2.
[ mathematical formula 2]
Hh＝0.2909Hc2-2.667Hc+10.953
(Hh is the height of the inner fin, Hc is the height of the outer fin)
The height of the inner fin 400 and the height of the outer fin 500 may be set such that the pressure drop amount of the first heat exchange medium passing through the tube 300 of the heat exchanger 1000 is equal to or less than a value satisfying the following equation 3.
[ mathematical formula 3]
Hh＝0.0007Hc2+0.7321Hc+0.0466
(Hh is the height of the inner fin, Hc is the height of the outer fin)
The height of the inner fin 400 and the height of the outer fin 500 may be formed within a range in which the weight of the heat exchanger 1000 satisfies the following equation 4.
[ mathematical formula 4]
[ upper limit value]Hh＝0.5966Hc2-12.152Hc+69.271
[ lower limit value]Hh＝0.5966Hc2-12.152Hc+63.771
(Hh is the height of the inner fin, Hc is the height of the outer fin)
In addition, according to the heat exchanger of the present invention, the heat exchanger 1000 may be configured to include: a plurality of tubes 300 forming a flow path of the first heat exchange medium; an inner fin 400 provided inside the tube 300; and outer fins 500 interposed between the tubes 300, the first heat exchange medium passing through the tubes 300 and exchanging heat with the second heat exchange medium passing through the tubes 300, wherein in the heat exchanger 1000, the height of the inner fins 400 and the height of the outer fins 500 are formed such that the weight of the heat exchanger 1000 is within a specific weight range, and the height of the inner fins 400 and the height of the outer fins 500 are formed such that the pressure drop amount of the first heat exchange medium passing through the tubes 300 of the heat exchanger 1000 is equal to or less than a specific value and the pressure drop amount of the second heat exchange medium passing through the tubes 300 outside the heat exchanger 1000 is equal to or less than a specific value, in a predetermined region.
The height of the inner fin 400 and the height of the outer fin 500 may be set such that the discharge temperature of the first heat exchange medium after passing through the inside of the tube 300 reaches a temperature within a specific range.
The height of the inner fin 400 and the height of the outer fin 500 are formed within a range of values satisfying the following equation 1.
[ mathematical formula 1]
[ upper limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+177.31
[ lower limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+176.71
(Hh is the height of the inner fin, Hc is the height of the outer fin)
The height of the inner fin 400 and the height of the outer fin 500 may be set such that the pressure drop amount of the second heat exchange medium passing through the tubes 300 outside the heat exchanger 1000 is equal to or less than a value satisfying the following equation 2.
[ mathematical formula 2]
Hh＝0.2909Hc2-2.667Hc+10.953
(Hh is the height of the inner fin, Hc is the height of the outer fin)
The height of the inner fin 400 and the height of the outer fin 500 may be set such that the pressure drop amount of the first heat exchange medium passing through the tube 300 of the heat exchanger 1000 is equal to or less than a value satisfying the following equation 3.
[ mathematical formula 3]
Hh＝0.0007Hc2+0.7321Hc+0.0466
(Hh is the height of the inner fin, Hc is the height of the outer fin)
The height of the inner fin 400 and the height of the outer fin 500 may be formed within a range in which the weight of the heat exchanger 1000 satisfies the following equation 4.
[ mathematical formula 4]
[ upper limit value]Hh＝0.5966Hc2-12.152Hc+69.271
[ lower limit value]Hh＝0.5966Hc2-12.152Hc+63.771
(Hh is the height of the inner fin, Hc is the height of the outer fin)
Effects of the invention
The heat exchanger according to the invention has the following advantages: the weight is reduced in a limited space, i.e., in a heat exchanger package, so that the manufacturing cost of the heat exchanger can be saved while the cooling performance of the heat exchanger is improved.
Drawings
Fig. 1 is a perspective view showing a conventional air-cooled intercooler.
Fig. 2 is a perspective view illustrating a heat exchanger according to an embodiment of the present invention.
Fig. 3 is a graph showing the number of rows of tubes in a heat exchanger versus cooling performance.
Fig. 4 is a graph showing the number of rows of tubes in a heat exchanger versus the weight of the heat exchanger.
Fig. 5 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the ejection temperature of the first heat exchange medium according to the present invention.
Fig. 6 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the pressure drop amount pd2 of the second heat exchange medium according to the present invention.
Fig. 7 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the pressure drop amount pd1 of the first heat exchange medium according to the present invention.
Fig. 8 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the weight of the heat exchanger according to the present invention.
Fig. 9 is a graph showing the height of the inner fin and the height of the outer fin together with the pressure drop pd1 of the first heat exchange medium, the pressure drop pd2 of the second heat exchange medium, and the weight range of the heat exchanger according to the present invention.
Fig. 10 is a graph further illustrating the cooling performance of the heat exchanger, that is, the ejection temperature of the first heat exchange medium, on the basis of fig. 9.
Fig. 11 is a graph showing the relationship of the height of the outer fin according to the present invention and the cooling performance of the heat exchanger.
FIG. 12 is a graph showing the relationship of the height of the inner fins to the ejection temperature of the first heat exchange medium according to the present invention.
Detailed Description
The heat exchanger of the present invention having the above-described configuration will be described in detail with reference to the drawings.
First, the heat exchanger according to an embodiment of the present invention may be an air-cooled intercooler as follows: a first heat exchange medium (supercharging-side air) compressed to a high temperature and a high pressure by the supercharger to increase the output of the engine passes through the inside of the tubes and exchanges heat with a second heat exchange medium (cooling-side air) passing through the outside between the tubes on the outside, whereby the first heat exchange medium can be cooled by air cooling.
Fig. 2 is a perspective view illustrating a heat exchanger according to an embodiment of the present invention.
As shown, the heat exchanger 1000 according to an embodiment of the present invention may be generally constructed with an inlet header tank 100, an outlet header tank 200, a plurality of tubes 300, an inner fin 400, and an outer fin 500.
The inlet header tank 100 is a portion forming a space capable of storing the first heat exchange medium flowing in from the supercharger inside and along which the first heat exchange medium may flow, and may be formed with an inlet pipe 110 to allow the first heat exchange medium to flow in.
The outlet header tank 200 is a portion forming a space that passes through the insides of the tubes 300 and performs heat exchange, where the first heat exchange medium may be collected and stored and may flow along the inside, and may be formed with an outlet pipe 210 to discharge the first heat exchange medium.
The pipe 300 is a portion having one end connected to the inlet header tank 100 and the other end connected to the outlet header tank 200 to form a flow path through which the first heat exchange medium can flow. In addition, the tube 300 is provided in plurality, formed long in the length direction, and may be arranged to be spaced apart from each other in the height direction. Both ends of the pipe 300 may be fixed to the header tanks 100, 200 by brazing or the like.
In this case, the inlet header tank 100, the outlet header tank 200, and the tubes 130 may be formed in various manners, and for example, a press pipe type heat exchanger in which a plurality of tubes 130 formed in a pipe shape are connected and fixed to the pipe-shaped header tanks 100 and 200 may be formed, or a stack type heat exchanger in which a header tank and a tube are integrally formed by stacking a plurality of plates may be formed.
The inner fin 400 is used to improve heat exchange efficiency, and may be disposed inside the tube 300. The inner fin 400 is formed as a corrugated fin, and may be fixed to the inner circumferential surface of the pipe 300 by brazing or the like.
The outer fin 500 serves to improve heat exchange efficiency, and may be disposed outside the tube 300. The outer fin 500 is formed as a corrugated fin, is sandwiched between adjacent tubes 300, and is fixed to the outer circumferential surface of the tube 300 by brazing or the like.
Thus, the region including the tubes 300, the inner fins 400, and the outer fins 500 disposed in the region between the inlet header tank 100 and the outlet header tank 200 can be a core portion, which is a region where most of the heat exchange is performed. Further, high-temperature supercharging-side air compressed by the supercharger, i.e., a first heat exchange medium flows into the inlet header tank 100 and flows along the inside of the tubes 300, is collected in the outlet header tank 200 and discharged, and at the same time, a second heat exchange medium, which is cooling air, flows from the front side to the rear side outside the heat exchanger 1000 so as to pass through the space between the tubes 300 of the core portion, and exchanges heat between the first heat exchange medium and the second heat exchange medium, thereby cooling the first heat exchange medium.
In this case, as shown in fig. 3, the cooling performance is reduced as the number of rows of tubes 300 in the predetermined region, that is, the core region is reduced, and as shown in fig. 4, the weight is reduced as the number of rows of tubes 300 is reduced. Therefore, if the number of rows of tubes 300 is reduced in order to reduce the weight of the heat exchanger, the cooling performance will be reduced although the weight can be reduced, and thus the design of the tubes and fins needs to be optimized in consideration of these factors.
That is, in the heat exchanger of the present invention, the height of the inner fin 400 and the height of the outer fin 500 are formed such that the weight of the heat exchanger is within a specific weight range in a predetermined region, whereby the number of rows of the tubes 300 can be determined. Further, since the height of the inner fin 400 and the height of the outer fin 500 also affect the ejection temperature of the first heat exchange medium ejected through the inside of the tube 300, which indicates the performance of the heat exchanger, the height of the inner fin 400 and the height of the outer fin 500 may be formed such that the ejection temperature of the first heat exchange medium reaches a temperature within a specific range.
Fig. 5 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the ejection temperature of the first heat exchange medium according to the present invention.
Referring to fig. 5, the heights of the inner fin 400 and the outer fin 500 may be formed in a temperature range in which the ejection temperature of the first heat exchange medium is maintained to be the lowest. That is, the height of the inner fin and the height of the outer fin may be selected in respective regions between a graph representing the upper limit value and a graph representing the lower limit value, which may be expressed by the following mathematical formula 1.
[ mathematical formula 1]
[ upper limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+177.31
[ lower limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+176.71
(Hh is the height of the inner fin, Hc is the height of the outer fin)
Thus, if the height of the outer flap is chosen to be 8.1mm, the height of the inner flap may generally be chosen in the range of 6.5mm to 7.0 mm.
Further, since the heights of the inner fin 400 and the outer fin 500 also affect the pressure drop pd1 of the first heat exchange medium passing through the inside of the tube 300 and the pressure drop pd2 of the second heat exchange medium passing through the space between the tubes 300 outside the heat exchanger 1000, it is necessary to select the heights of the inner fin and the outer fin so as to optimize the overlapped region in consideration of the ejection temperature of the first heat exchange medium, the pressure drop of the first heat exchange medium, and the pressure drop of the second heat exchange medium.
Fig. 6 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the pressure drop amount pd2 of the second heat exchange medium according to the present invention.
Referring to fig. 6, as the height of the outer fin increases, the pressure drop amount of the second heat exchange medium becomes smaller, but the critical (maximum) value of the allowable pressure drop amount pd2 may be about 2 kPa. This can be expressed by the following mathematical formula 2, and the height of the inner fin and the height of the outer fin can be selected in the corresponding region below the critical line of the pressure drop amount in the graph.
[ mathematical formula 2]
Hh＝0.2909Hc2-2.667Hc+10.953
(Hh is the height of the inner fin, Hc is the height of the outer fin)
Fig. 7 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the pressure drop amount pd1 of the first heat exchange medium according to the present invention.
Referring to fig. 7, as the height of the inner fin increases, the pressure drop of the first heat exchange medium becomes smaller, but the critical (maximum) value of the suggested pressure drop pd1 may be about 2 kPa. This can be expressed by the following mathematical formula 3, and the height of the inner fin and the height of the outer fin can be selected in the corresponding region above the critical line of the pressure drop amount in the graph.
[ mathematical formula 3]
Hh＝0.0007Hc2+0.7321Hc+0.0466
(Hh is the height of the inner fin, Hc is the height of the outer fin)
Further, the weight of the heat exchanger is reduced as the heights of the inner fin 400 and the outer fin 500 are increased, but the height of the inner fin and the height of the outer fin need to be formed within a certain weight range in consideration of the cooling performance of the heat exchanger.
Fig. 8 is a graph showing the relationship of the height of the inner fin, the height of the outer fin, and the weight of the heat exchanger according to the present invention.
Referring to fig. 8, as the height of the inner fin and the height of the outer fin increase, the weight of the heat exchanger decreases, and the height of the inner fin 400 and the height of the outer fin 500 may be formed within a certain weight range. That is, the heights of the inner and outer fins may be selected in respective regions between a graph representing the upper limit value and a graph representing the lower limit value, which may be expressed by the following mathematical formula 4.
[ mathematical formula 4]
[ upper limit value]Hh＝0.5966Hc2-12.152Hc+69.271
[ lower limit value]Hh＝0.5966Hc2-12.152Hc+63.771
(Hh is the height of the inner fin, Hc is the height of the outer fin)
Fig. 9 is a graph showing the height of the inner fin and the height of the outer fin together with the pressure drop pd1 of the first heat exchange medium, the pressure drop pd2 of the second heat exchange medium, and the weight range of the heat exchanger according to the present invention.
Referring to fig. 9, the heights of the inner fins and the heights of the outer fins corresponding to the inner region enclosed by four lines in the graph may be optimal values in consideration of the pressure drop amount of the heat exchange medium and the weight of the heat exchanger.
Fig. 10 is a graph further illustrating the cooling performance of the heat exchanger, that is, the ejection temperature of the first heat exchange medium, on the basis of fig. 9.
Referring to fig. 10, in the graph, the height of the inner fin and the height of the outer fin corresponding to the inner region surrounded by the line indicating the weight range of the heat exchanger and the line indicating the range of the ejection temperature of the first heat exchange medium may be optimal values of the height of the inner fin and the height of the outer fin in consideration of the pressure drop amount of the heat exchange medium, the weight of the heat exchanger, and the cooling performance of the heat exchanger. Thus the optimum height of the outer flap may be 7.5mm to 9.0mm and the optimum height of the inner flap may be 5.6mm to 8.6 mm.
Fig. 11 is a graph showing the relationship of the height of the outer fin according to the present invention and the cooling performance of the heat exchanger.
In fig. 11, the vertical axis represents an index indicating the cooling performance of the heat exchanger, and is a value indicating the outlet temperature of the heat exchanger, and the lower the numerical value, the higher the cooling performance. Thereby, further defined as an area where the cooling performance of the heat exchanger is high, the height of the outer fin may be formed to be 7.5mm to 8.5 mm.
FIG. 12 is a graph showing the relationship of the height of the inner fins to the ejection temperature of the first heat exchange medium according to the present invention.
As shown in the drawing, further defined as an area where the ejection temperature of the first heat exchange medium can be maintained to be the lowest, the height of the inner fin may be formed to be 6.5mm to 7.5 mm.
The present invention is not limited to the above-described embodiments, and various application ranges are possible, and those skilled in the art can make various modifications without departing from the spirit of the present invention claimed in the claims.
Description of the reference numerals
1000: heat exchanger
100: inlet header tank
110: inlet pipe
200: outlet water collecting tank
210: outlet duct
300: pipe
400: inner fin
500: exterior fin

Claims (11)

1. A heat exchanger (1000) is constituted to include: a plurality of tubes (300) forming a flow path for the first heat exchange medium; an inner fin (400) provided inside the tube (300); and outer fins (500) sandwiched between the tubes (300), wherein the first heat exchange medium passes through the inside of the tubes (300) and exchanges heat with a second heat exchange medium passing between the tubes (300), the heat exchanger being characterized in that,
in the heat exchanger (1000), the height of the inner fin (400) and the height of the outer fin (500) are formed so that the discharge temperature of the first heat exchange medium after passing through the inside of the tube (300) reaches a temperature within a specific range in a predetermined region,
the height of the inner fin (400) and the height of the outer fin (500) are formed within a range of values satisfying the following mathematical formula 1,
[ mathematical formula 1]
[ upper limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+177.31
[ lower limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+176.71，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
2. The heat exchanger of claim 1,
in the heat exchanger (1000), the height of the inner fin (400) and the height of the outer fin (500) are formed so that the weight of the heat exchanger (1000) is within a specific weight range,
the height of the inner fin (400) and the height of the outer fin (500) are formed such that the pressure drop amount of the first heat exchange medium passing through the inside of the tubes (300) of the heat exchanger (1000) is a specific value or less and the pressure drop amount of the second heat exchange medium passing through the space between the tubes (300) outside of the heat exchanger (1000) is a specific value or less.
3. The heat exchanger of claim 2,
the height of the inner fin (400) and the height of the outer fin (500) are formed such that the pressure drop of the second heat exchange medium passing between the tubes (300) outside the heat exchanger (1000) is equal to or less than a value satisfying the following equation 2,
[ mathematical formula 2]
Hh＝0.2909Hc2-2.667Hc+10.953，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
4. The heat exchanger of claim 2,
the height of the inner fin (400) and the height of the outer fin (500) are formed so that the pressure drop amount of the first heat exchange medium passing through the tube (300) of the heat exchanger (1000) is equal to or less than a value satisfying the following equation 3,
[ mathematical formula 3]
Hh＝0.0007Hc2+0.7321Hc+0.0466，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
5. The heat exchanger of claim 2,
the height of the inner fin (400) and the height of the outer fin (500) are formed within a range where the weight of the heat exchanger (1000) satisfies the following equation 4,
[ mathematical formula 4]
[ upper limit value]Hh＝0.5966Hc2-12.152Hc+69.271
[ lower limit value]Hh＝0.5966Hc2-12.152Hc+63.771，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
6. A heat exchanger (1000) is constituted to include: a plurality of tubes (300) forming a flow path for the first heat exchange medium; an inner fin (400) provided inside the tube (300); and outer fins (500) sandwiched between the tubes (300), wherein the first heat exchange medium passes through the inside of the tubes (300) and exchanges heat with a second heat exchange medium passing between the tubes (300), the heat exchanger being characterized in that,
in the heat exchanger (1000), the height of the inner fin (400) and the height of the outer fin (500) are formed so that the weight of the heat exchanger (1000) is within a specific weight range in a predetermined region,
the height of the inner fin (400) and the height of the outer fin (500) are formed such that the pressure drop amount of the first heat exchange medium passing through the inside of the tubes (300) of the heat exchanger (1000) is a specific value or less and the pressure drop amount of the second heat exchange medium passing through the space between the tubes (300) outside of the heat exchanger (1000) is a specific value or less.
7. The heat exchanger of claim 6,
the height of the inner fin (400) and the height of the outer fin (500) are formed such that the discharge temperature of the first heat exchange medium after passing through the inside of the tube (300) reaches a temperature within a specific range.
8. The heat exchanger of claim 7,
the height of the inner fin (400) and the height of the outer fin (500) are formed within a range of values satisfying the following mathematical formula 1,
[ mathematical formula 1]
[ upper limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+177.31
[ lower limit value]Hh＝-0.3049Hc3+7.7969Hc2-64.17Hc+176.71，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
9. The heat exchanger of claim 6,
the height of the inner fin (400) and the height of the outer fin (500) are formed such that the pressure drop of the second heat exchange medium passing between the tubes (300) outside the heat exchanger (1000) is equal to or less than a value satisfying the following equation 2,
[ mathematical formula 2]
Hh＝0.2909Hc2-2.667Hc+10.953，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
10. The heat exchanger of claim 6,
the height of the inner fin (400) and the height of the outer fin (500) are formed so that the pressure drop amount of the first heat exchange medium passing through the tube (300) of the heat exchanger (1000) is equal to or less than a value satisfying the following equation 3,
[ mathematical formula 3]
Hh＝0.0007Hc2+0.7321Hc+0.0466，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
11. The heat exchanger of claim 6,
the height of the inner fin (400) and the height of the outer fin (500) are formed within a range where the weight of the heat exchanger (1000) satisfies the following equation 4,
[ mathematical formula 4]
[ upper limit value]Hh＝0.5966Hc2-12.152Hc+69.271
[ lower limit value]Hh＝0.5966Hc2-12.152Hc+63.771，
Where Hh is the height of the inner fin and Hc is the height of the outer fin.
CN201980015955.5A 2018-04-17 2019-03-27 Heat exchanger Pending CN111788448A (en)

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KR1020180044310A KR102450813B1 (en) 2018-04-17 2018-04-17 Heat exchanger
KR10-2018-0044310 2018-04-17
PCT/KR2019/003542 WO2019203467A1 (en) 2018-04-17 2019-03-27 Heat exchanger

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2576197B2 (en) * 1988-06-29 1997-01-29 日本電装株式会社 Heat exchanger
KR20060031261A (en) * 2004-10-08 2006-04-12 한라공조주식회사 Lamination-type heater for an air conditioning system of a car
CN1975123A (en) * 2005-11-29 2007-06-06 株式会社电装 Intercooler
CN103575140A (en) * 2012-07-19 2014-02-12 格伦格斯有限公司 Compact type aluminum heat exchanger with welding pipe for power electronic equipment and battery cooling
KR101427430B1 (en) * 2008-06-02 2014-08-08 한라비스테온공조 주식회사 Heat exchanger for vehicle

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012201710A1 (en) * 2011-02-14 2012-08-16 Denso Corporation heat exchangers
JP6481275B2 (en) 2014-07-16 2019-03-13 いすゞ自動車株式会社 Corrugated fin heat exchanger

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2576197B2 (en) * 1988-06-29 1997-01-29 日本電装株式会社 Heat exchanger
KR20060031261A (en) * 2004-10-08 2006-04-12 한라공조주식회사 Lamination-type heater for an air conditioning system of a car
CN1975123A (en) * 2005-11-29 2007-06-06 株式会社电装 Intercooler
KR101427430B1 (en) * 2008-06-02 2014-08-08 한라비스테온공조 주식회사 Heat exchanger for vehicle
CN103575140A (en) * 2012-07-19 2014-02-12 格伦格斯有限公司 Compact type aluminum heat exchanger with welding pipe for power electronic equipment and battery cooling

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Application publication date: 20201016