WO2020149107A1 - 熱交換器 - Google Patents

熱交換器 Download PDF

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Publication number
WO2020149107A1
WO2020149107A1 PCT/JP2019/050342 JP2019050342W WO2020149107A1 WO 2020149107 A1 WO2020149107 A1 WO 2020149107A1 JP 2019050342 W JP2019050342 W JP 2019050342W WO 2020149107 A1 WO2020149107 A1 WO 2020149107A1
Authority
WO
WIPO (PCT)
Prior art keywords
inflow pipe
heat exchanger
tank portion
flow
tube
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.)
Ceased
Application number
PCT/JP2019/050342
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
章太 茶谷
聡也 長沢
浜田　浩
雄太 松田
直人 後藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Publication of WO2020149107A1 publication Critical patent/WO2020149107A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Definitions

  • the present disclosure relates to heat exchangers.
  • the fluid tends to flow into the tube arranged near the inflow pipe, while the fluid tends to hardly flow into the tube arranged apart from the inflow pipe. .. This is a factor that makes the flow rate distribution of a plurality of tubes uneven.
  • the heat exchanger described in Patent Document 1 below is provided with a plate-shaped member inside the inlet tank.
  • the plate-shaped member partially closes an opening at one end of a predetermined number of tubes arranged on the same side as the inflow pipe and the discharge pipe in the tube stacking direction.
  • the opening area at one end is reduced.
  • An object of the present disclosure is to provide a heat exchanger capable of reducing noise while suppressing uneven distribution of flow rate in a plurality of tubes.
  • the fluid when the fluid flows from the inflow pipe into the first tank portion, the fluid flows so as to form a predetermined angle with respect to the tube stacking direction. Therefore, at one end of the first tank portion, the fluid flows in the predetermined direction. The velocity of the fluid flowing through the region along the line increases. As a result, the velocity distribution of the fluid flowing through the one end of the first tank portion becomes uneven. Due to this bias in the velocity distribution of the fluid, the pressure loss when the fluid flows into the tube increases in the region where the velocity of the fluid is high. Therefore, it becomes difficult for the fluid to flow into the tube arranged near the one end of the first tank portion.
  • FIG. 1 is a front view showing the front structure of the heat exchanger of the first embodiment.
  • FIG. 2 is a sectional view showing a sectional structure taken along line II-II in FIG.
  • FIG. 3 is a cross-sectional view showing the cross-sectional structure of the tube of the modified example of the first embodiment.
  • FIG. 4 is a sectional view showing the sectional structure of the heat exchanger of the second embodiment.
  • FIG. 5 is sectional drawing which shows the cross-section of the heat exchanger of 3rd Embodiment.
  • FIG. 6 is a sectional view showing the sectional structure of the heat exchanger of the fourth embodiment.
  • FIG. 7 is a perspective view which shows the perspective structure of the edge part of the side plate of 4th Embodiment.
  • FIG. 1 is a front view showing the front structure of the heat exchanger of the first embodiment.
  • FIG. 2 is a sectional view showing a sectional structure taken along line II-II in FIG.
  • FIG. 3 is a cross-
  • FIG. 8 is sectional drawing which shows the cross-section of the heat exchanger of 5th Embodiment.
  • FIG. 9 is sectional drawing which shows the cross-section of the heat exchanger of 6th Embodiment.
  • FIG. 10 is sectional drawing which shows the cross-section of the heat exchanger of 7th Embodiment.
  • FIG. 11 is sectional drawing which shows the cross-section of the heat exchanger of 8th Embodiment.
  • FIG. 12: is sectional drawing which shows the cross-section of the heat exchanger of 9th Embodiment.
  • FIG. 13 is sectional drawing which shows the cross-section of the inflow pipe of 9th Embodiment.
  • FIG. 14 is a perspective view showing a perspective structure of a drift member according to the ninth embodiment.
  • the heat exchanger 10 is used, for example, as a heater core of an air conditioner mounted on a vehicle.
  • the air conditioner is a device that air-conditions the vehicle interior by blowing heated or cooled conditioned air into the vehicle interior.
  • the heat exchanger 10 is arranged in an air conditioning duct through which conditioned air flows. Inside the heat exchanger 10, engine cooling water is circulated.
  • the cooling water flowing inside the heat exchanger 10 is in a liquid single-phase state.
  • the heat exchanger 10 heats the conditioned air by the heat of the cooling water by exchanging heat between the cooling water flowing inside the heat exchanger 10 and the conditioned air flowing inside the air conditioning duct.
  • the conditioned air heated by the heat exchanger 10 is blown into the vehicle compartment through the air conditioning duct to heat the vehicle compartment.
  • the cooling water flowing inside the heat exchanger 10 corresponds to the fluid.
  • the heat exchanger 10 includes a heat exchange core portion 20, tank portions 31 and 32, and side plates 41 and 42.
  • the heat exchanger 10 is made of a metal material such as an aluminum alloy.
  • the heat exchange core portion 20 is a portion that exchanges heat between the cooling water and the air.
  • the heat exchange core portion 20 includes a plurality of tubes 21 arranged in a stack at a predetermined interval in the X-axis direction in the figure, and a plurality of fins 22 arranged in a gap between adjacent tubes 21. Have In FIG. 1, only a part of the plurality of fins 22 is shown.
  • the X-axis direction is also referred to as "tube stacking direction X”. Further, one of the tube stacking directions X is referred to as "X1 direction”, and the other direction is referred to as "X2 direction”.
  • the tube 21 is an elongated pipe having an internal flow passage W10 through which cooling water flows.
  • the cross-sectional shape of the tube 21 orthogonal to the Z-axis direction is flat.
  • the tube 21 is formed so as to extend in the Z-axis direction.
  • the Z-axis direction is also referred to as “tube longitudinal direction Z”.
  • one of the tube longitudinal directions Z is referred to as "Z1 direction”
  • the other direction is referred to as Z2 direction.
  • a direction orthogonal to both the X-axis direction and the Z-axis direction is also referred to as "tube width direction Y".
  • the fins 22 are so-called corrugated fins formed by bending a thin and long metal plate into a wavy shape.
  • the bent portion of the fin 22 is fixed to the outer peripheral surface of the adjacent tubes 21 and 21 by brazing.
  • the fins 22 are provided to increase the heat transfer area of the tubes 21 and thereby increase the heat exchange efficiency between the cooling water and the air.
  • the tank portions 31 and 32 are cylindrical members formed so as to extend in the tube stacking direction X. As shown in FIG. 2, inside the first tank portion 31, an internal passage W20 through which cooling water flows is formed. One end portions 210 of the plurality of tubes 21 in the Z2 direction are connected to the first tank portion 31. One end portions 210 of the plurality of tubes 21 are arranged so as to penetrate the peripheral wall 312 of the first tank portion 31 and extend to the internal flow passage W20 of the first tank portion 31. Similarly, inside the second tank portion, an internal flow path through which cooling water flows is formed. As shown in FIG. 1, the second tank portion 32 is connected to the other end portions 211 of the plurality of tubes 21 in the Z1 direction.
  • the inflow pipe 40 is connected to the end 331 of the inflow port 33 in the X2 direction. Specifically, a flange portion 400 is formed at the tip of the inflow pipe 40.
  • the inflow pipe 40 is fixed to the end 331 of the inflow port 33 by crimping the flange portion 400 to the end 331 of the inflow port 33.
  • a seal member 50 is arranged between the outer peripheral surface of the inflow pipe 40 and the inner peripheral surface of the inflow port 33 to seal between them.
  • the side plates 41 and 42 are arranged at both ends of the heat exchange core portion 20 in the X-axis direction.
  • the respective end portions 410 and 420 of the side plates 41 and 42 in the Z2 direction are connected to the first tank portion 31.
  • the end portion 410 of the side plate 41 is arranged so as to penetrate the peripheral wall 312 of the first tank portion 31 and extend to the internal flow path W20 of the first tank portion 31.
  • the end portion 420 of the side plate 42 is also connected to the first tank portion 31.
  • the other end portions 411 and 421 of the side plates 41 and 42 in the Z1 direction are connected to the second tank portion 32.
  • the side plates 41, 42 are provided to reinforce the heat exchange core section 20.
  • the single-phase cooling water flows into the first tank portion 31 through the inflow pipe 40.
  • the cooling water that has flowed into the first tank portion 31 is distributed to each tube 21 by flowing from the one end portion 210 of each tube 21 into the internal flow path W10 of each tube 21.
  • the cooling water distributed to each tube 21 flows through the internal flow path W10 of each tube 21 toward the second tank portion 32.
  • heat is exchanged between the cooling water flowing through the internal flow passage W10 of each tube 21 and the air flowing between the adjacent tubes 21 and 21, whereby the heat of the cooling water is converted into air. It is transmitted and the air is heated.
  • the cooling water that has passed through each tube 21 is collected in the second tank portion 32 and then discharged from the discharge pipe 43.
  • the cooling water flowing from the inflow pipe 40 into the first tank portion 31 is indicated by the arrow. It flows in the direction indicated by D1, that is, in the direction forming a predetermined angle ⁇ with respect to the axis m1.
  • the flow of the cooling water from the opening 401 of the inflow pipe 40 in the direction indicated by the arrow D1 increases the speed of the cooling water flowing in the region A1 along the arrow D1 at the end portion 310 of the first tank portion 31.
  • the velocity distribution of the cooling water flowing through the end portion 310 of the first tank portion 31 becomes uneven in the tube width direction Y.
  • the actions and effects shown in the following (1) and (2) can be obtained.
  • the deviation of the flow distribution of the tubes 21 due to the position of the inflow pipe 40 can be offset, and as a result, the deviation of the flow distribution of the plurality of tubes 21 can be suppressed.
  • the one end portion 210 of the tube 21 is not closed, and therefore, as compared with the structure in which one end portion of the tube is closed like the conventional heat exchanger, the inside of the tube 21 is Disturbance does not easily occur in the flow of cooling water. Therefore, it is possible to reduce noise.
  • the pressure loss of the cooling water flowing through the flow passages W11 and W12 of the tube 21 becomes larger than that of the tube having no partition wall 212. Therefore, as the flow velocity of the cooling water flowing through the inside of the first tank portion 31 becomes faster, it becomes more difficult for the cooling water to flow into the flow passages W11 and W12 of each tube 21. Inside the first tank portion 31, the flow velocity of the cooling water is highest near the opening 401 of the inflow pipe 40. By using the tube 21 as shown in FIG. 3, it becomes more difficult for the cooling water to flow into the tube 21 arranged near the opening 401 of the inflow pipe 40, and thus each tube caused by the position of the inflow pipe 40. It is possible to further alleviate the bias in the flow distribution of 21.
  • a drift portion 404 is formed in the middle of the inflow pipe 40.
  • the uneven flow portion 404 is formed so as to be bent in the inflow pipe 40, and includes a portion formed to partially narrow the flow passage cross-sectional area of the inflow pipe 40. With such a drift portion 404, the flow direction of the cooling water flowing inside the inflow pipe 40 can be changed.
  • a drift structure 313 is provided on the peripheral wall 312 of the first tank portion 31.
  • the non-uniform flow structure 313 has a structure in which a part of the peripheral wall 312 of the first tank portion 31 is deformed so as to be recessed inward. Due to this non-uniform flow structure 313, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 becomes difficult to flow in the portion where the non-uniform flow structure 313 is provided, and becomes easy to flow in the part where the non-uniform flow structure 313 is not provided. .. Thereby, it is possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 so as to form a predetermined angle ⁇ with respect to the tube stacking direction X.
  • the inflow pipe 40 in order to allow the cooling water to flow from the inflow pipe 40 into the first tank portion 31 at a predetermined angle ⁇ with respect to the tube stacking direction X, the inflow pipe 40 is inclined and attached to the first tank portion 31. Specifically, the inflow pipe 40 is attached to the first tank portion 31 so that its central axis m2 is inclined with respect to the tube stacking direction X. As a result, as shown by the arrow D1 in FIG. 9, it is possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 at a predetermined angle ⁇ with respect to the tube stacking direction X. ..
  • the inflow pipe 40 is attached to the first tank portion 31 at an eccentric position. That is, the inflow pipe 40 is attached to the first tank portion 31 such that the central axis m2 thereof deviates from the central axis m1 of the first tank portion 31.
  • the arrow D1 in FIG. 10 it is possible to flow the cooling water from the inflow pipe 40 into the first tank portion 31 at a predetermined angle ⁇ with respect to the tube stacking direction X. ..
  • the inflow pipe 40 is attached to the side surface of the first tank portion 31. Specifically, the inflow pipe 40 is attached to the side surface of the first tank portion 31 located in the tube width direction Y. According to such a structure, the cooling water flowing from the inflow pipe 40 into the first tank portion 31 flows so as to be substantially orthogonal to the tube stacking direction X. That is, the angle ⁇ in FIG. 11 is approximately 90 degrees.
  • the drift member 70 is provided inside the first tank portion 31.
  • the drift member 70 is a member formed in a cylindrical shape around the axis m1.
  • the drift member 70 has a through hole 71 formed at a position displaced from the central axis m1.
  • the inflow pipe 40 forms a predetermined angle ⁇ with respect to the tube stacking direction X, as indicated by an arrow D1 in FIG. It is possible to allow the cooling water to flow into the first tank portion 31.
  • each embodiment can also be implemented in the following forms.
  • any fluid other than cooling water can be adopted as the fluid flowing through the heat exchanger 10.
  • the present disclosure is not limited to the above specific examples.
  • a person skilled in the art appropriately modified the above-described specific examples is also included in the scope of the present disclosure as long as the features of the present disclosure are provided.
  • Each element included in each of the above-described specific examples, and the arrangement, conditions, shape, and the like thereof are not limited to those illustrated, and can be appropriately changed.
  • the respective elements included in the above-described specific examples can be appropriately combined as long as there is no technical contradiction.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
PCT/JP2019/050342 2019-01-15 2019-12-23 熱交換器 Ceased WO2020149107A1 (ja)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019-004396 2019-01-15
JP2019004396A JP7006626B2 (ja) 2019-01-15 2019-01-15 熱交換器

Publications (1)

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WO2020149107A1 true WO2020149107A1 (ja) 2020-07-23

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005308386A (ja) * 2004-03-23 2005-11-04 Showa Denko Kk 熱交換器
JP2009008277A (ja) * 2007-06-26 2009-01-15 Showa Denko Kk 熱交換器およびその製造方法
JP2010223508A (ja) * 2009-03-24 2010-10-07 Tokyo Radiator Mfg Co Ltd 車両用エンジンのインタークーラ
WO2018055826A1 (ja) * 2016-09-23 2018-03-29 東芝キヤリア株式会社 熱交換器及び冷凍サイクル装置
JP2018105509A (ja) * 2015-04-28 2018-07-05 株式会社デンソー 熱交換器
WO2018221751A1 (ja) * 2018-07-03 2018-12-06 株式会社小松製作所 熱交換器

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6414504B2 (ja) * 2015-04-14 2018-10-31 株式会社デンソー 熱交換器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005308386A (ja) * 2004-03-23 2005-11-04 Showa Denko Kk 熱交換器
JP2009008277A (ja) * 2007-06-26 2009-01-15 Showa Denko Kk 熱交換器およびその製造方法
JP2010223508A (ja) * 2009-03-24 2010-10-07 Tokyo Radiator Mfg Co Ltd 車両用エンジンのインタークーラ
JP2018105509A (ja) * 2015-04-28 2018-07-05 株式会社デンソー 熱交換器
WO2018055826A1 (ja) * 2016-09-23 2018-03-29 東芝キヤリア株式会社 熱交換器及び冷凍サイクル装置
WO2018221751A1 (ja) * 2018-07-03 2018-12-06 株式会社小松製作所 熱交換器

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JP2020112322A (ja) 2020-07-27
JP7006626B2 (ja) 2022-01-24

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