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WO2019058848A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2019058848A1
WO2019058848A1 PCT/JP2018/030889 JP2018030889W WO2019058848A1 WO 2019058848 A1 WO2019058848 A1 WO 2019058848A1 JP 2018030889 W JP2018030889 W JP 2018030889W WO 2019058848 A1 WO2019058848 A1 WO 2019058848A1
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WO
WIPO (PCT)
Prior art keywords
pitch
amount
extension
extension amount
rate
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/JP2018/030889
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English (en)
Japanese (ja)
Inventor
石井　裕
隆 登山
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.)
Sanden Corp
Original Assignee
Sanden Holdings 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 Sanden Holdings Corp filed Critical Sanden Holdings Corp
Publication of WO2019058848A1 publication Critical patent/WO2019058848A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F28F1/10—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
    • F28F1/24—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 and extending transversely
    • F28F1/30—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 and extending transversely the means being attachable to the 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus

Definitions

  • the present invention relates to a heat exchanger.
  • An object of the present invention is to suppress the blocking of the air passage due to frost formation and the cost increase while maintaining the heat exchange efficiency.
  • the heat exchanger is Let directions orthogonal to each other be a first direction, a second direction, and a third direction, A plurality of piping members extending in the first direction and spaced in the second direction, and through which the heat medium flows; A plurality of plate members fixed between adjacent piping members, extending in a third direction and spaced apart in the first direction; Heat exchange is performed between the heat medium flowing inside the piping member and the air flowing around the piping member and around the plate member, An area surrounded by the piping member and the plate member is a ventilation passage for flowing air in the third direction, and the plate member is an extension which is extended on the windward side relative to the ventilation passage along the third direction.
  • the surface area of the plate member is equal to or greater than the surface area when the extension amount of the extension portion is a predetermined reference amount and the pitch of the plate member is a predetermined reference pitch,
  • the time required for the air passage to be blocked by frosting is the blocking time
  • the extension amount is set based on a first change rate, which is a change rate of the closure time when the extension amount is longer than the reference amount, with respect to the closure time when the extension amount is the reference amount
  • the pitch is set based on a second change rate, which is a change rate of the closure time when the pitch is longer than the reference pitch, with respect to the closure time when the pitch is the reference pitch.
  • the surface area of the plate member is equal to or larger than the surface area when the reference amount and the reference pitch are set, and the extension amount is set according to the first change rate of the closure time.
  • the pitch is set according to the rate of change.
  • FIG. 1 is a diagram showing a heat exchanger.
  • the heat exchanger 11 functions as an evaporator in a heat pump cycle and a refrigeration circuit, such as a car air conditioner and a showcase.
  • the aluminum heat exchanger 11 includes a pair of upper and lower headers 12, a plurality of tubes 13 (pipe members), and a plurality of fins 14 (plate members).
  • the pair of headers 12 extend in the lateral direction and are spaced apart in the longitudinal direction.
  • the header 12 is formed by a cylindrical pipe whose both ends are closed, and the inside is divided by the partition wall 17 into compartments aligned in the lateral direction.
  • the upper header 12 is internally divided into a section 12A at one end in the lateral direction and a section 12B at the other end in the lateral direction, and an inlet 15 is provided in the section 12A at the one end in the lateral direction.
  • the lower header 12 is internally divided into a section 12C at one end in the lateral direction and a section 12D at the other end in the lateral direction, and a discharge port 16 is provided in the section 12D at the other end in the lateral direction.
  • Each tube 13 extends in the longitudinal direction, and the upper end and the lower end are respectively connected to the header 12 and provided at equal intervals along the lateral direction.
  • the tube 13 has a laterally thin flat shape, and both ends thereof are in communication with the inside of the header 12 and brazed to the header 12.
  • 13a to 13l are sequentially arranged from one end in the lateral direction to the other end.
  • the tube 13 d and the tube 13 e are partitioned by the partition wall 17, and in the lower header 12, the tube 13 h and the tube 13 i are partitioned by the partition wall 17.
  • Each fin 14 is fixed by brazing between adjacent tubes 13.
  • a flow path is formed by the header 12 and the tube 13, through which a refrigerant (heat medium) flows. That is, first, it flows into the section 12A on one end side in the lateral direction of the upper header 12 through the inflow port 15, is distributed to the tubes 13a to 13d, and then flows into the section 12C on one end side in the lateral direction of the lower header 12. Next, after being distributed to the tubes 13e to 13h, they flow into the section 12B on the other end side in the lateral direction in the upper header 12 and then are distributed to the tubes 13i to 13l and then to the other end side in the lateral direction on the lower header 12. It flows into the compartment 12 D and is discharged through the discharge port 16.
  • the coolant flows through each tube 13, it exchanges heat with the air flowing around the tubes 13 and the fins 14. That is, the refrigerant evaporates and evaporates to raise the temperature by heat absorption, whereby one air is cooled.
  • FIG. 2 is a view showing a tube and a fin.
  • (A) in the figure is a view of the tube 13 and the fins 14 as viewed from the windward side in the width direction.
  • the fins 14 are corrugated fins in which thin plates are formed in a rectangular wave shape. Thereby, it becomes possible to integrate and form a plurality of thin plates provided at intervals in the longitudinal direction.
  • Each region surrounded by the fins 14 and the tube 13 serves as a ventilation passage 21 for flowing air in the width direction.
  • the pitch P of the fins 14 is, for example, 1.6 mm.
  • (B) in the figure is a view of the tube 13 and the fins 14 as viewed from the longitudinal direction, and the tube 13 is shown in cross section.
  • the tube 13 is formed with a plurality of through holes 22 extending in the longitudinal direction and aligned along the width direction, and the coolant flows through the through holes 22.
  • the fin 14 is formed with an extended portion 23 extending on the windward side of the air passage 21 along the width direction.
  • the amount of extension (length) of each extension 23 is uniform.
  • the amount of extension L of the fins 14 is, for example, 3 mm. There is no extension on the leeward side in the width direction of the fins 14.
  • the length of the ventilation path 21 in the width direction is, for example, 14 mm.
  • FIG. 3 is a diagram showing a reference pitch and a reference amount.
  • (A) in the figure is a view of the tube 13 and the fins 14 as viewed from the windward side in the width direction.
  • the pitch P of the fins 14 is, for example, 1.2 mm, which is taken as a reference pitch Ps.
  • (B) in the figure is a view of the tube 13 and the fins 14 as viewed from the longitudinal direction, and the tube 13 is shown in cross section.
  • the extension amount L of the fin 14 is, for example, 0 mm, which is set as a reference amount Ls. That is, one end on the windward side in the width direction in the fin 14 is unified to be flush with one end of the tube 13.
  • the pitch P and the extension amount L are set in a range in which the surface area of the fins 14 is equal to or more than the surface area when the reference amount Ls and the reference pitch Ps are adopted. Specifically, it is set in consideration of the blocking time due to frost formation.
  • the closing time is the time required for the air passage 21 to be closed due to frost formation.
  • FIG. 4 is a graph showing the occlusion time according to the amount of extension.
  • the pitch P of the fins 14 is 1.6 mm and the extension amount L is 0 mm, 3 mm, 10 mm, and 24 mm.
  • the longer the extension amount L the longer the closing time.
  • FIG. 5 is a graph showing the occlusion time according to the pitch.
  • the extension amount L of the fins 14 is 3 mm and the pitch P is 1.2 mm, 1.4 mm, and 1.6 mm. The wider the pitch P, the longer the closing time.
  • the change rate of the occlusion time when the extension amount L is longer than the reference amount Ls relative to the occlusion time when the extension amount L is the reference amount Ls is a first change rate ⁇ .
  • FIG. 6 is a graph showing the relationship between the extension amount and the first change rate.
  • the transition of the first change rate ⁇ according to the extension amount L is indicated by the characteristic line Lc1, and the characteristic line
  • Lc1 the transition of the first change rate ⁇ according to the extension amount L.
  • the extension amount L is 3 mm
  • the increase of the first change rate ⁇ is most remarkable
  • the slope of the characteristic line Lc1 is maximum when the extension amount L is in the range of 0 ⁇ L ⁇ 3.
  • the extension amount L is 10 mm, the increase in the first change rate ⁇ is suppressed, and the slope of the characteristic line Lc1 decreases.
  • the extension amount L When the extension amount L is 24 mm, the increase of the first change rate ⁇ is further suppressed, and the slope of the characteristic line Lc1 is also considerably reduced.
  • the fins 14 have a thickness of only about 0.1 mm, and easily deform when subjected to an external force. Therefore, as the extension amount L is made longer, an external force is applied at the time of manufacturing, at the time of transportation, at the time of use, and it becomes easy to cause the deformation of the fins 14. Therefore, the extension amount L is set within the range of 1 to 4 mm, preferably about 3 mm.
  • a change rate of the occlusion time when the pitch P is wider than the reference pitch Ps is set as a second change rate ⁇ with respect to the occlusion time when the pitch P is the reference pitch Ps.
  • FIG. 7 is a graph showing the relationship between the pitch and the second change rate.
  • characteristic line Lc2 transition of second change rate ⁇ according to pitch P is shown by characteristic line Lc2
  • characteristic line Lc2 is The larger the inclination with respect to the horizontal axis, the higher the effect of suppression of occlusion by widening the pitch P.
  • the second change rate ⁇ is also increased when the pitch P is 1.4 mm, but when the pitch P is 1.6 mm, the increase in the second change rate ⁇ is most significant, and the slope of the characteristic line Lc2 is
  • the pitch P is maximum in the range of 1.4 ⁇ P ⁇ 1.6.
  • the pitch P is 1.8 mm or more, the increase in the second change rate ⁇ is suppressed, and the slope of the characteristic line Lc2 decreases.
  • the pitch P is set within the range of 1.4 to 1.8 mm, preferably about 1.6 mm.
  • the reference amount Ls is 0 mm
  • the reference pitch Ps is 1.2 mm
  • the surface area of the fins 14 is equal to or more than the surface area when the reference amount Ls and the reference pitch Ps are employed. Thereby, at least the heat exchange efficiency can be maintained.
  • a first change rate ⁇ which is a change rate of the occlusion time when the extension amount L is made longer than the reference amount Ls with respect to the occlusion time when the extension amount L is the reference amount Ls, is calculated.
  • the extension amount L is set based on the one change rate ⁇ . Specifically, as shown in FIG. 6, the extension amount L is set in a range including the extension amount L when the slope of the first characteristic line Lc1 is maximum. Since the slope of the characteristic line Lc1 is maximum when the extension amount L is in the range of 0 ⁇ L ⁇ 3, the extension amount L is set within the range of 1 to 4 mm.
  • a second change rate ⁇ which is a change rate of the occlusion time when the pitch P is made longer than the reference pitch Ps with respect to the occlusion time when the pitch P is the reference pitch Ps.
  • the pitch P is set based on the change rate ⁇ . Specifically, as shown in FIG. 7, the pitch P is set in a range including the pitch P when the slope of the second characteristic line Lc2 is maximum. Since the inclination of the characteristic line Lc2 is maximum when the pitch P is in the range of 1.4 ⁇ P ⁇ 1.6, the pitch P is set within the range of 1.4 to 1.8 mm.
  • the combination of the extension amount L of the fins 14 and the pitch P can delay the time until the air passage 21 is closed. Further, since the cost increase due to the extension of the fins 14 can be offset by widening the pitch P, the cost increase can be suppressed. In fact, as a result of lengthening the extension amount L from 0 mm to 3 mm and widening the pitch P from 1.2 mm to 1.6 mm, the time until the air passage 21 is blocked while maintaining the heat exchange efficiency It has been extended by about 60% and could be realized at a conventional cost.
  • the extension amount L and the pitch P are made common to all the tubes 13a to 13l, but the invention is not limited thereto.
  • the frost formation tends to occur on the upstream side of the tubes 13a to 13l through which the refrigerant flows. Therefore, among the tubes 13a to 13l, the extension amount L is set within the range of 1 to 4 mm and the pitch P is 1.4 to 1.8 mm only with the upstream side through which the refrigerant flows, for example, only the tubes 13a to 13d. It may be set within the range.
  • the extension amount L may be set to the reference amount Ls
  • the pitch P may be set to the reference pitch Ps.
  • the header 12 extends in the lateral direction, and the tube 13 extends in the longitudinal direction.
  • the present invention is not limited thereto.
  • the header 12 extends in the longitudinal direction and the tube 13 extends in the lateral direction

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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)
  • Air-Conditioning For Vehicles (AREA)

Abstract

[Problème] Empêcher une augmentation des coûts et la fermeture d'un conduit d'air provoquée par la formation de givre, tout en maintenant l'efficacité d'échange de chaleur. [Solution] La surface d'ailettes (14) est égale ou supérieure à la surface obtenue lorsque la quantité d'extension (L) est fixée à une quantité de référence (Ls), et le pas (P) est fixé à un pas de référence (Ps). En outre, la quantité d'extension (L) est définie sur la base d'un premier rapport de changement (α), c'est-à-dire le rapport de changement du temps de fermeture lorsque la quantité d'extension (L) est plus longue que la quantité de référence (Ls) au temps de fermeture lorsque la quantité d'extension (L) est la quantité de référence (Ls). De plus, le pas (P) est défini sur la base d'un second rapport de changement (β), c'est-à-dire le rapport de changement du temps de fermeture lorsque le pas (P) est plus long que le pas de référence (Ps) au temps de fermeture lorsque le pas (P) est le pas de référence (Ps).
PCT/JP2018/030889 2017-09-19 2018-08-22 Échangeur de chaleur Ceased WO2019058848A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-178918 2017-09-19
JP2017178918A JP2019052824A (ja) 2017-09-19 2017-09-19 熱交換器

Publications (1)

Publication Number Publication Date
WO2019058848A1 true WO2019058848A1 (fr) 2019-03-28

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PCT/JP2018/030889 Ceased WO2019058848A1 (fr) 2017-09-19 2018-08-22 Échangeur de chaleur

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JP (1) JP2019052824A (fr)
WO (1) WO2019058848A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06221787A (ja) * 1993-01-29 1994-08-12 Nippondenso Co Ltd 熱交換器
JPH0829016A (ja) * 1994-07-19 1996-02-02 Nippondenso Co Ltd ヒートポンプ用室外熱交換器
JP2012163323A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
WO2013008464A1 (fr) * 2011-07-14 2013-01-17 パナソニック株式会社 Échangeur de chaleur d'extérieur et climatiseur destiné à un véhicule

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06221787A (ja) * 1993-01-29 1994-08-12 Nippondenso Co Ltd 熱交換器
JPH0829016A (ja) * 1994-07-19 1996-02-02 Nippondenso Co Ltd ヒートポンプ用室外熱交換器
JP2012163323A (ja) * 2011-01-21 2012-08-30 Daikin Industries Ltd 熱交換器および空気調和機
WO2013008464A1 (fr) * 2011-07-14 2013-01-17 パナソニック株式会社 Échangeur de chaleur d'extérieur et climatiseur destiné à un véhicule

Also Published As

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JP2019052824A (ja) 2019-04-04

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