US20190195564A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20190195564A1
US20190195564A1 US16/220,813 US201816220813A US2019195564A1 US 20190195564 A1 US20190195564 A1 US 20190195564A1 US 201816220813 A US201816220813 A US 201816220813A US 2019195564 A1 US2019195564 A1 US 2019195564A1
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United States
Prior art keywords
tube
wall thickness
heat exchanger
width
formula
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Abandoned
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US16/220,813
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English (en)
Inventor
Hong-Young Lim
Ho Chang Sim
Sun Mi Lee
Wi Sam Jo
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.)
Hanon Systems Corp
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Hanon Systems Corp
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Filing date
Publication date
Priority claimed from KR1020180154915A external-priority patent/KR20190072413A/ko
Application filed by Hanon Systems Corp filed Critical Hanon Systems Corp
Assigned to HANON SYSTEMS reassignment HANON SYSTEMS ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JO, Wi Sam, LEE, SUN MI, LIM, HONG-YOUNG, SIM, HO CHANG
Publication of US20190195564A1 publication Critical patent/US20190195564A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—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
    • F28D2021/0084—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded

Definitions

  • the following disclosure relates to a heat exchanger, and more particularly, to a heat exchanger operated in a high-pressure environment and including a tube which is manufactured according to an extrusion method and optimized in pressure resistance and heat transfer performance.
  • a heat exchanger is a device for generating heat exchange between a working fluid and a surrounding environment such as ambient air and other fluids.
  • a widely used heat exchanger includes a flow channel through which a working fluid passes and a tube including a tube wall for heat transfer to an external medium (fin, or the like).
  • a plurality of tubes are generally arranged in parallel and fins are provided between the tubes to improve heat transfer performance.
  • the heat exchanger tubes generally each have a shape of a flat pipe, in which the fins are brazed to be coupled to the outside of the flat surfaces of the tubes, respectively.
  • Such heat exchanger tubes may be formed in a variety of ways. For example, a method of bending a thin metal plate and joining the ends is commonly used.
  • a high-pressure heat exchanger generally uses tubes formed according to an extrusion method that does not cause a joint portion.
  • An extruded tube may be easily manufactured to have a cross-section having a complicated shape, as compared with a tube manufactured in a plate bonding manner.
  • the extruded tube is easier to manufacture to have a cross-section having a complicated shape, as compared with a tube manufactured according to a plate bonding scheme.
  • a design of forming a plurality of partitions (hereinafter, referred to as ‘inner walls’) in a flow channel i.e., tube inside space
  • the area of the tube inside space in contact with a working fluid (refrigerant) is increased to increase an amount of heat transferred from the working fluid to the tube, resultantly increasing heat transfer performance.
  • a flow rate of the working fluid itself may be reduced to rather degrade heat transfer performance.
  • a design for reducing a thickness of the inner wall may be introduced. In this case, if the inner wall is too thin, the inner wall may burst due to internal pressure of the working fluid and design performance may not be realized. Also, if the thickness of the inner wall is too thin, substantial manufacturing itself is difficult.
  • Japanese Patent Laid-Open Publication No. 2007-093144 (“Heat Exchanging Tube and Heat Exchanger” published on Apr. 12, 2007) discloses a technique of limiting numerical values regarding various sizes of an extruded tube to maintain stiffness against an external impact, while ensuring heat transfer performance.
  • Japanese Patent Laid-Open Publication No. 2016-186398 (“Heat Exchanging Tube and Heat Exchanger Using the Heat Exchanging Tube” published on Oct. 27, 2016) discloses a technique regarding a shape and a size of an extruded tube capable of enhancing manufacturing characteristics, while ensuring a light weight.
  • An embodiment of the present invention is directed to providing a heat exchanger having an optimal design satisfying appropriate pressure resistance and manufacturing characteristics, as well as maximizing heat transfer performance in an internal wall thickness, an outer wall thickness, and the number of holes of an extruded tube.
  • Another embodiment of the present invention is directed to providing a heat exchanger having an optimal design formed based on a more systematic rule so as to be easily applied to tubes of various sizes.
  • a heat exchanger includes: a pair of header tanks formed in parallel and spaced apart from each other by a predetermined distance; a plurality of tubes fixed to the pair of header tanks at both ends to form a flow channel of a refrigerant; and a fin interposed between the tubes, wherein the plurality of tubes are extruded tubes, and when each tube is formed such that a tube width is greater than a tube height and a flow channel in the tube is divided into a plurality of holes formed in parallel of the tube in a width direction by a plurality of inner walls extending in a height direction of the tube, the tube width, an outer wall thickness at an end portion of the tube in the width direction, a hole width, and an inner wall thickness have a size within a range in which the following formula is satisfied:
  • Tw tube width
  • Tn outer wall thickness at end portion of tube in width direction
  • A hole width
  • B inner wall thickness
  • a plurality of louvers may be formed on the fin, and the hole width, the inner wall thickness, a louver pitch may have a size within a range in which the following formula is further satisfied:
  • A hole width
  • B inner wall thickness
  • Lp louver pitch
  • the inner wall thickness B may have a size within a range in which the following formula is further satisfied:
  • the inner wall thickness B may have a size within a range in which the following formula is further satisfied:
  • the inner wall thickness B may have a size within a range in which the following formula is further satisfied:
  • the inner wall thickness B may have a size within a range in which the following formula is further satisfied:
  • the plurality of tubes may be formed of aluminum.
  • FIG. 1 is a perspective view of a general fin-tube heat exchanger.
  • FIG. 2 is a top view of an extruded tube and a louver-pin combination.
  • FIG. 3 is a view illustrating definition of each part of an extruded tube.
  • FIGS. 4(A) and 4(B) illustrate simulation results of a relationship between hole width/inner wall thickness and burst pressure or heat transfer performance.
  • FIG. 5 illustrates simulation result of a relationship between a hole width, the number of inner wall thickness sets and heat transfer performance.
  • FIG. 6 illustrates a range of optimal design conditions for a hole width and an inner wall thickness.
  • FIG. 7(A) to 7(D) illustrate ranges of optimal design conditions under these additional conditions.
  • FIG. 8 illustrates an area of optimal design condition range smaller than the area illustrated in FIG. 6 .
  • FIG. 1 is a perspective view of a general fin-tube heat exchanger.
  • a typical fin-tube type heat exchanger 100 includes a pair of header tanks 110 formed in parallel and spaced apart from each other by a predetermined distance, a plurality of tubes 120 fixed to the pair of header tanks 110 at both ends to form a flow channel of a refrigerant, and a fin 130 interposed between the tubes 120 .
  • the tube 120 is an extruded tube, which is formed by an extrusion method and does not have a joint.
  • a plurality of louvers 135 may be formed on the fin 130
  • FIG. 2 illustrates a top view of a combination of the extruded tube and the louver.
  • the heat exchanger 100 may be a condenser, and the tube 120 may be formed of aluminum.
  • an optimal design made by more systematic rules between the sizes of each part of the tube 120 is proposed to enhance performance of heat transfer from a refrigerant to an inner wall of the tube and ensure pressure resistance and manufacturing characteristics through appropriate inner and outer wall thicknesses of the tube.
  • FIG. 3 illustrates the definition of each part of the extruded tube, in which a tube width Tw, a tube height Th, the outer wall thickness Tn at an end portion of the tube 120 in a width direction, a hole width A, and an inner wall thickness B are illustrated.
  • the tube width Tw is greater than the tube height Th, and a flow channel in the tube 120 is divided into a plurality of holes 122 formed in parallel in a width direction of the tube 120 by a plurality of inner walls 121 extending in a height direction of the tube 120 .
  • the inner wall thickness B may burst. It is known that a maximum operating pressure of the refrigerant flowing in the tube 120 is 25 kg/cm 2 .
  • safety factor is generally 3 to 4 times greater, and thus, when pressure at which the inner wall 121 bursts is burst pressure Pb, the inner wall thickness B may be determined such that the burst pressure Pb is about 85 kg/cm 2 .
  • the inner walls 121 are spaced apart from each other by a space corresponding to the hole width A, and although the inner wall thickness B is the same, pressure resistance increases as the hole width A decreases. Resultantly, pressure resistance may be determined collectively in consideration of the inner wall thickness B and the hole width A, rather than determined by only a single indicator of the inner wall thickness B.
  • the burst pressure Pb tends to decrease as the hole width A/inner wall thickness B increases.
  • the hole width A/inner wall thickness B when the burst pressure Pb corresponds to 85 kg/cm 2 (as described above) is approximately 2.5. Therefore, the hole width A/inner wall thickness B value may be determined to be larger than 2.5.
  • the pressure resistance is enhanced as the hole width A/inner wall thickness B value increases, but if this value is too large, another problem may arise. Details thereof are as follows.
  • the hole width A/inner wall thickness B value increases, it means that the inner wall thickness B decreases when the hole width A is fixed or the hole width A increases when the inner wall thickness B is fixed.
  • the hole width A excessively increases, the number of holes 122 which may be formed in the single tube 120 may decrease, and in this case, a contact sectional area between the refrigerant and the tube inner wall decreases to reduce heat transfer performance.
  • the ultimate object of the present invention is to maximize heat transfer performance, and thus, the hole width A/inner wall thickness B value must be determined within a range in which heat transfer performance does not deteriorate.
  • the heat transfer coefficient h of the refrigerant side i.e., the inside of the tube
  • the hole width A/inner wall thickness B at a point where the value of the heat transfer coefficient h at the refrigerant side is maximized may be determined as a maximum value, but in this case, the degree of freedom of design may be excessively limited.
  • the hole width A/inner wall thickness B value at a point where the heat transfer coefficient (h) at the refrigerant side is about 75% of the maximum value is about 4.
  • the heat transfer coefficients h at the refrigerant side (i.e., the inside of the tube) in a general tube without an inner wall and in a tube having the hole width A/inner wall thickness B of 4 were measured and results thereof shows that the heat transfer coefficient value at the refrigerant side in the tube according to the design of the present invention was enhanced to be about 650% higher than that of the general tube. That is, the heat transfer coefficient may be enhanced sufficiently remarkably even at a point where the heat transfer coefficient value is not a maximum value, as compared with the existing case.
  • the hole width A/inner wall thickness B value may be determined to be smaller than 4.
  • the tube 120 may have a size within a range in which the following formula is satisfied:
  • the increase in the hole width A/inner wall thickness B value indicates the decrease in the inner wall thickness B when the hole width A is fixed.
  • Heat transfer performance may be enhanced as the inner wall thickness B decreases within a range in which pressure resistance is satisfied.
  • the inner wall thickness B is excessively reduced, the inner wall 121 may not be properly manufactured in the process of manufacturing the tube 120 according to an extrusion scheme. That is, in order to ensure manufacturing characteristics, the inner wall thickness B must have a value equal to or greater than a thickness that can be manufactured by general extrusion, and here, a limit value of the thickness that can be manufactured in an extruding process is known to be 0.07 to 0.10 in the extrusion process technical field. Thus, the inner wall thickness B may be determined to be greater than 0.07 which is a manufacturing limit.
  • the above-mentioned manufacturing limit is a value that may be obtained using the best equipment, materials, conditions, etc., and practically, it is not easy to realize the manufacturing limit in a practical production field of a mass production system. That is, as the inner wall thickness decreases, the inner wall may be bent or burst in the process of manufacturing or thicknesses of several inner walls may not be uniform. That is, as the inner wall thickness decreases, a defect rate increases (a pass rate decreases), and conversely, as the inner wall thickness increases, the defect rate decreases (the pass rate increases). That is, it is preferred that the inner wall thickness decreases to an appropriate level at which the pass rate is not excessively lowered. In other words, a maximum value of the inner wall thickness may be determined according to the pass rate.
  • the inner wall thickness B may be a maximum of 0.2 mm.
  • the inner wall thickness B may have a size within a range in which the following formula is satisfied:
  • the present manufacturing limit is known to be 0.07, but if the extrusion manufacturing technology develops, a less value may also be possible.
  • a minimum value of the inner wall thickness B may most preferably be 0.07.
  • the minimum value of the inner wall thickness B may be 0.1 so that the inner wall thickness may be manufactured to have a value slightly greater than the manufacturing limit.
  • a pass rate was 95% when the inner wall thickness B is 0.18 mm. From this point of view, the inner wall thickness B may have a size within a range in which the following formula is satisfied:
  • the pass rate is about 90%. From this point of view, as described above, the thickness of the inner wall is manufactured to be as thin as the manufacturing limit or ease of manufacturing is considered similarly, and the inner wall thickness B may have a size within a range in which the following formula is satisfied:
  • an outer size of the tube 120 may be determined in advance according to a required size of the heat exchanger 100 itself, or in order to replace the newly designed tube 120 of the present invention in the existing heat-exchanger, the outer size of the tube 120 may be determined in advance because it is to be the same as an outer size of the existing heat exchanger tube.
  • the outer size of the tube 120 includes the tube width Tw and the tube height Th.
  • the outer wall thickness Tn at the end of the tube 120 in the width direction may also be determined in advance (as a specific value having sufficient stiffness against the above-described collision risk). Since the tube width Tw and the outer wall thickness Tn at the end portion of the tube 120 in the width direction are determined in advance as described above, a flow channel space in the tube 120 may be designed in consideration of the tube width Tw and the outer wall thickness Tn.
  • the numbers of inner walls 121 and the holes 122 included in the flow channel space are appropriately determined in consideration of the tube width Tw, the outer wall thickness Tn at the end of the tube 120 in the width direction, and the like, to thus maximize heat transfer performance.
  • a value obtained by multiplying a value, which normalizes the tube width Tw as a value obtained by subtracting the pair of outer wall thicknesses Tn from the tube width Tw, to the hole width A and the inner wall thickness B set is set to as a determination indicator (Tw(A+B)/(Tw ⁇ 2Tn)).
  • FIG. 5 illustrates simulation results of a relationship between the numbers of hole width and inner wall thickness sets and heat transfer performance.
  • the determination indicator (Tw(A+B)/(Tw ⁇ 2Tn)) increases, heat transfer performance tends to gradually increase and start to decrease at a certain point.
  • the determination indicator (Tw(A+B)/(Tw ⁇ 2Tn)) value may be determined as a value at which heat transfer performance is maximized, but in this case, the degree of freedom of design may be excessively limited.
  • a boundary value of the determination indicator (Tw(A+B)/(Tw ⁇ 2Tn)) range at the point corresponding to about 75% of the maximum value of heat transfer performance may be about 0.2/0.6.
  • the determination indicator (Tw(A+B)/(Tw ⁇ 2Tn)) value may be determined as a value within the range of 0.2 to 0.6.
  • the tube 120 may have a size within a range in which the following formula is satisfied:
  • Heat transferred from the refrigerant to the inner wall surface in the tube 120 is transferred to the outer surface of the tube 120 and finally discharged as outside air.
  • the fin 130 is provided to more efficiently transfer the heat transferred to the outer surface of the tube 120 to the outside air. That is, heat transferred to the outer surface of the tube 120 is transferred to the fin 130 so that the area in contact with the outside air is expanded to the outer surface of the tube 120 and the surface of the fin 130 , and as a result, performance of heat transfer to the outside air may be significantly improved.
  • a plurality of the louvers 135 may be formed on the fin 130 to further increase the contact area with the outside air.
  • a direction in which the louvers 135 are arranged in parallel and a direction in which the inner wall 121 and the hole 122 set are arranged in parallel are the same as a width direction of the tube 120 .
  • the amount of heat transferred from the inside of the tube 120 to the outer surface of the tube 120 is slightly larger locally at a position corresponding to the position of the inner wall 121 and is less at a position corresponding to the position of the hole 122 .
  • at least one inner wall 121 and hole 122 set is included in the width range of one louver 135 .
  • the tube 120 preferably has a size within a range in which the following formula is satisfied:
  • FIG. 6 is a graph illustrating a range of optimal design conditions for the hole width and the inner wall thickness.
  • a pair of graphs indicated by ⁇ circle around ( 1 ) ⁇ represents an upper limit value and a lower limit value of Formula 1, respectively
  • a pair of graphs indicated by ⁇ circle around ( 2 ) ⁇ represents an upper limit value and a lower limit value of Formula 2, respectively
  • a pair of graphs indicated by ⁇ circle around ( 3 ) ⁇ represents an upper limit value and a lower limit value of Formula 3, respectively.
  • the tube 120 according to the present invention may be designed to have the hole width A and the inner wall thickness B value within the optimal design condition range illustrated in FIG. 6 .
  • FIG. 7(A) ⁇ 7 (D) illustrate ranges of optimal design conditions under these additional conditions. That is, FIG. 7(A) illustrates an optimal design condition range according to Formula 2-11, FIG. 7(B) illustrates an optimal design condition range according to Formula 2-12, FIG. 7(C) illustrates an optimal design condition range according to Formula 2-21, and FIG. 7(D) illustrates the optimal design condition range according to Formula 2-22.
  • Formula 4 may be further introduced in consideration of even the louver pitch Lp.
  • the graph indicated by ⁇ circle around ( 4 ) ⁇ represents Formula 4, and an area portion formed below the graph indicated by ⁇ circle around ( 4 ) ⁇ is the design condition range according to the Formula 4.
  • the graph indicated by ⁇ circle around ( 4 ) ⁇ is located above an upper limit graph indicated by ⁇ circle around ( 3 ) ⁇ , there is no change in the optimal design area.
  • the louver pitch Lp is reduced, the graph indicated by ⁇ circle around ( 4 ) ⁇ comes below the upper limit value graph indicated by ⁇ circle around ( 3 ) ⁇ , and in this case, the area of the optimal design condition range is smaller than the area illustrated in FIG. 6 .
  • FIG. 8 Such an example is illustrated in FIG. 8 .
  • the present invention there is an effect of significantly improving performance of heat transfer from the refrigerant to the tube, as compared with the related art. More specifically, according to the present invention, performance of heat transfer from the refrigerant to the inner wall of the tube may be enhanced by increasing the contact length with the refrigerant at the internal cross-section of the tube and further increasing the sectional area of the refrigerant passage, and the inner wall and outer wall thicknesses of the tube may be optimized to ensure appropriate pressure resistance and manufacturing characteristics.
  • the present invention although an overall size of the heat exchanger or the heat exchanger tube is varied, dimensions at which heat transfer performance, pressure resistance, and manufacturing characteristics are optimized may be easily calculated. Therefore, it is possible to maximize design convenience in the process of designing a new heat exchanger or designing to improve an existing heat exchanger.

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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)
US16/220,813 2017-12-15 2018-12-14 Heat exchanger Abandoned US20190195564A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR20170172756 2017-12-15
KR10-2017-0172756 2017-12-15
KR10-2018-0154915 2018-12-05
KR1020180154915A KR20190072413A (ko) 2017-12-15 2018-12-05 열교환기

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US20190195564A1 true US20190195564A1 (en) 2019-06-27

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DE (1) DE102018131871A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11226161B2 (en) * 2017-12-21 2022-01-18 Hanon Systems Heat exchanger

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003148888A (ja) * 2001-11-15 2003-05-21 Sanden Corp オイルクーラ
US20030094267A1 (en) * 2001-11-19 2003-05-22 Young Darryl Leigh Multi-edge folded louvered fin for heat exchanger
US20040069477A1 (en) * 2000-11-24 2004-04-15 Naoki Nishikawa Heat exchanger tube and heat exchanger
US20070071920A1 (en) * 2005-09-29 2007-03-29 Denso Corporation Heat exchanger tube and heat exchanger

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016186398A (ja) 2015-03-27 2016-10-27 株式会社ケーヒン・サーマル・テクノロジー 熱交換器用チューブ及び該熱交換器用チューブの用いられた熱交換器

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040069477A1 (en) * 2000-11-24 2004-04-15 Naoki Nishikawa Heat exchanger tube and heat exchanger
JP2003148888A (ja) * 2001-11-15 2003-05-21 Sanden Corp オイルクーラ
US20030094267A1 (en) * 2001-11-19 2003-05-22 Young Darryl Leigh Multi-edge folded louvered fin for heat exchanger
US20070071920A1 (en) * 2005-09-29 2007-03-29 Denso Corporation Heat exchanger tube and heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11226161B2 (en) * 2017-12-21 2022-01-18 Hanon Systems Heat exchanger

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