WO2001001058A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
WO2001001058A1
WO2001001058A1 PCT/JP2000/001808 JP0001808W WO0101058A1 WO 2001001058 A1 WO2001001058 A1 WO 2001001058A1 JP 0001808 W JP0001808 W JP 0001808W WO 0101058 A1 WO0101058 A1 WO 0101058A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
tank
tube element
fin
pair
Prior art date
Application number
PCT/JP2000/001808
Other languages
English (en)
Japanese (ja)
Inventor
Kunihiko Nishishita
Original Assignee
Zexel Valeo Climate Control Corporation
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 Zexel Valeo Climate Control Corporation filed Critical Zexel Valeo Climate Control Corporation
Publication of WO2001001058A1 publication Critical patent/WO2001001058A1/fr

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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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins

Definitions

  • the present invention relates to a heat exchanger having a fin formed in a corrugated shape, which is used for a refrigeration cycle mounted on a vehicle, and particularly used as an evaporator.
  • Japanese Patent Application Laid-Open No. 7-167578 discloses a laminated heat exchanger in which the width of a fin in the ventilation direction is 50 mm or more and 65 mm or less.
  • the best fin that balances heat exchange efficiency and airflow resistance is a fin height FH of 7.0 mm or more.
  • the reference discloses that the fin is 9.0 mm or less, the fin pitch FP is 2.0 mm or more and 3.6 mm or less, and the fin thickness is 0.06 mm or more and 0.10 mm or less. .
  • the surface of the heat exchanger is coated with a corrosion-resistant film, and a hydrophilic film is further coated thereon. Then, the drainage of the condensed water adhering to the fins is reduced, and conversely, the heat exchange efficiency is reduced and the condensed water freezes, so that the fin pitch cannot be reduced.
  • an object of the present invention is to provide a heat exchanger having a reduced width without deteriorating the performance of the heat exchanger. Disclosure of the invention
  • the present invention has at least a tube element through which a refrigerant flows, and a corrugated fin disposed between the tube elements, wherein the corrugated fin has a vent portion in contact with the tube element, and one of the tube elements And a flat portion located between the vent portion in contact with the other tube element, and the flat portion includes a plurality of loops extending in a direction perpendicular to the ventilation direction.
  • the width of the heat exchanger in the ventilation direction of the air flowing through the corrugated fin is formed within a range of 30 mm or more and 57 mm or less, and
  • the louver tilt angle should be between 28 ° and 55 °.
  • the fin pitch between the bent portion contacting one of the tube elements and the next bent portion contacting the one tube element can obtain the maximum value of the above factor at about 3.8 mm, and
  • the desired condition can be satisfied in the range of about 3.0 mm or more and 5.0 mm or less, and the fin height can obtain the maximum value of the above factor in about 7.5 mm and about 5.0 mm.
  • the desired condition can be satisfied within the range of m or more and 9.5 mm or less. Further, it is desirable to set the fin height so that the interval between the tube elements is formed corresponding to the fin height.
  • a distance between an end of the louver and the tube element is in a range of about 0.2 mm or more and 1.5 mm or less.
  • the thickness of the corrugated fin is 0.09 mm or more and 0.2 mm or less.
  • the heat exchanger includes a tube element having a pair of tank portions formed at at least one end in the longitudinal direction and a refrigerant passage communicating with the tank portions, and a corrugate disposed between the tube element.
  • the present invention can be applied to the case of a stacked heat exchanger formed by alternately stacking fins.
  • the tube element may include a pair of upper tank portions formed at one longitudinal end, a pair of lower tank portions formed at the other longitudinal end, and one of the upper tank portions.
  • a double-tank heat exchanger having a first refrigerant passage communicating with one of the lower tank portions and a second refrigerant passage communicating with the other of the upper tank portion and the other of the lower ink portion may be provided.
  • the tube element may be a single-tank heat exchanger having a pair of tank portions formed at one end in the longitudinal direction and a U-shaped passage communicating the pair of tank portions.
  • FIG. 1 is a front view showing a heat exchanger according to an embodiment of the present invention, which is a one-tank stacked heat exchanger, and (b) of FIG. 1 is a side view thereof.
  • FIG. 2 (a) is a front view showing the fin height Fh of the fin
  • FIG. 2 (b) is a cross-sectional view thereof
  • FIG. 3 is the fin lever angle.
  • FIG. 4 is a schematic side view showing the fin pitch Fp, the fin height Fp, and the distance Dr between the end of the lever and the top of the vent.
  • Fig. 5 is a characteristic diagram showing the relationship between the louver angle Ra and the heat exchanger capacity Fa, and Fig.
  • FIG. 6 is a graph showing the relationship between the fin pitch Fp and the heat exchanger capacity Fa.
  • FIG. 7 is a characteristic diagram showing a relationship between the fin height Fh and the heat exchanger capacity Fa
  • FIG. 8 is a ventilation direction of the heat exchanger.
  • Width Cw and heat exchanger capacity F a A characteristic diagram showing the relationship
  • FIG. 9 is a heat exchanger according to the embodiment of the present invention, is a perspective view showing a laminated heat exchanger of the two-tank.
  • the heat exchanger 1 shown in FIGS. 1 (a) and 1 (b) is a one-tank laminated heat exchanger, and includes a pair of tank portions 2 and 2 formed at one longitudinal end, and the pair of tank portions. It is composed of a plurality of tube elements 4 each including a refrigerant passage portion 3 communicating with each other, and a corrugated fin 5 disposed between the refrigerant passage portions 3 of the tube element 4.
  • end plates 6 and 6 are disposed at both ends of the tube element 4 and the fin 5 in the stacking direction, and are located substantially at the center in the stacking direction.
  • the tube element 4 ′ is formed by connecting the tank portion 2 in the laminating direction. It has a blind tank section 2 'that divides one of the pair of tank groups 7, 7 into two tank blocks 7A, 7B.
  • an inlet-side mounting portion 8 for mounting a refrigerant inflow pipe (not shown) is formed extending from the tank portion 2 along the direction of air flow.
  • an outlet-side mounting portion 9 for mounting a refrigerant outflow pipe (not shown) is formed extending from the tank portion 2 along the direction of air flow.
  • the refrigerant flowing into the tank block 7A from the inflow pipe mounted on the inlet-side mounting portion 8 flows through the refrigerant flow path 3 into the tank group 7 on the other side, and flows through the tank group 7.
  • the refrigerant having moved through the other tank group 7 passes through the refrigerant flow path 3 and moves to the tank block 7B, and flows out to the refrigerant outflow pipe mounted on the outlet side mounting portion 9. It is.
  • the width Cw in the ventilation direction is within the range of 30 mm or more and 57 mm or less in order to save the space of the air conditioner itself and the space of the vehicle itself. It is desired to be formed. And, in the present embodiment, the width C w of the heat exchanger 1 is formed as 40 mm.
  • the fins 5 are connected to the vent portions 1 la and 11 b which are in contact with the refrigerant flow path portion 3 of the tube element 4 and to one of the tube elements 4. It has a flat portion 12 located between the contacting vent portion 11a and the vent portion 11b contacting the other tube element 4, and corresponds to a portion between the refrigerant flow passage portions 3 of the adjacent tube elements 4.
  • the fin 5 has a predetermined fin height Fh and a fin bit Fp between the vertices of the vent portion 11a to be in contact with the one tube element 4.
  • the fin 5 is formed with a plurality of loopers 10 extending vertically in the ventilation direction, which are cut and raised in order in the ventilation direction, and the air passing along the fins 5 is transmitted to the looper 10.
  • the fins 5 can pass along the fins 5 so as to intersect, so increasing the inclination angle (louver angle) Ra of the louver with respect to the flat portion 12 of the fins 5 can increase the heat exchange capacity.
  • the angle Ra is increased, the ventilation resistance is increased and the heat exchange capacity is reduced.
  • heat exchanger capacity Fa cooling performance / ventilation resistance
  • the characteristic diagram showing the relationship between the louver angle Ra and the heat exchanger capacity F a obtained by the experiment is shown in Fig. 5, and the maximum value is obtained when the louver angle Ra is approximately 42 °. It turns out that it becomes ability. Then, the range where the maximum capacity is 80% or more when the maximum capacity is 100% is defined as an appropriate range Ras of the louver angle Ra.
  • the proper range Ras is in the range from 28 ° to 55 ° according to the characteristic diagram shown in FIG.
  • the relationship between the fin pitch Fp and the heat exchanger capacity Fa obtained by an experiment is shown in FIG. 6, in which the fin pitch Fp is about 4.0 mm. It can be seen that the maximum capacity is obtained at the time. Assuming that the range in which the heat exchanger capacity Fa is 80% or more of the maximum is the appropriate range Fps of the fine pitch Fp, as in the case described above, the appropriate range Fps is as shown in FIG. According to the characteristic diagram shown by, it is 3.0 mm or more and 5.0 mm or less.
  • Fig. 7 shows that the maximum capacity is obtained when the fin height Fh is about 7.5 mm.
  • the appropriate range Fhs of the fin height Fh As in the case described above, the appropriate range Fhs is as shown in Fig. 6. According to the characteristic diagram, it becomes 5.0mm or more and 9.5mm or less.
  • the fin plate thickness Ft is preferably as thin as possible in a cost-like manner.
  • the fin plate thickness Ft needs to be more than a predetermined value. It is desirable to set it within the range of 09 mm or more and 0.2 mm or less.
  • the distance D r between the end of the louver 10 formed in the fin 5 and the top of the fin vents 11 a and 11 b is not less than 0.2 mm and not more than 1.5 mm It is desirable.
  • the distance Dr in this range, the drainage of the fin can be improved and the fin strength when the fin is formed in a corrugated shape can be maintained. Further, the joining property by brazing between the fin 5 and the tube element 4 can be improved.
  • the width Cw in the ventilation direction was set to 40 mm, but as shown in Fig. 8, the width in the ventilation direction was within the range of 30 mm to 57 mm. With the heat exchanger set to, the various appropriate ranges described above could be obtained.
  • a heat exchanger 30 shown in FIG. 9 shows another embodiment of the above-described heat exchanger 1, and the shape of the fin 5 and the shape of the louver 10 are the same as those of the heat exchanger 1. What can be used.
  • the heat exchanger 30 includes a pair of upper tank portions 31 and 32 formed at one longitudinal end and a pair of lower tank portions 33 and 3 formed at the other longitudinal end. 4, a first refrigerant flow path 35 communicating between one upper tank section 31 and one lower ink section 33, and a first refrigerant path 35 communicating with the other upper tank section 32 and the other lower tank section.
  • a plurality of tube elements 37 having a second refrigerant flow path 36 are provided, and the fins 5 satisfying the above-described conditions are arranged between the tube elements 37.
  • the width of the heat exchanger 30 along the ventilation direction can be formed to be 30 mm or more and 57 mm or less.
  • Reference numerals 44 are end plates disposed at both ends in the stacking direction.
  • the heat exchanger 30 is composed of four tank groups 38, 39, 40, 41 each having the tank sections 31, 32, 33, 34 communicating with each other in the stacking direction. It has.
  • a refrigerant inlet pipe 42 is connected to a first tank group 38 composed of one upper tank part 31 and a refrigerant outlet pipe is connected to a fourth sunset group 41 composed of the other upper tank part 32. 4 3 is communicated.
  • a second tank group 39 composed of one lower tank part 33 and a third tank group 40 composed of the other lower tank part 34 are formed at the end of the second tank group 39.
  • the opening 45, the bypass flow path 44, and the opening 46 formed at the end of the third tank group 40 communicate with each other.
  • the refrigerant flowing from the refrigerant inlet pipe 42 flows from the first tank group 38 to the first refrigerant flow path 35, flows to the second tank group 39, and flows into the bypass flow path. It flows into the third tank group 40 via the section 44, passes through the second refrigerant flow path 35, flows into the fourth tank group 41, and flows out from the refrigerant outlet pipe 43. Is what it is. Industrial applicability
  • the louver angle is set to 28 ° or more and 55 ° or less.
  • the fin pitch 3.0 mm or more Since the capacity of the heat exchanger can be maintained at a predetermined level or more even when the thickness is 0 mm or less, the drainage of the fins can be improved while maintaining the performance of the heat exchanger.

Abstract

L'invention porte sur un échangeur de chaleur dont la largeur est comprise entre 30 mm et 57 mm ou moins,, dans le sens de ventilation, et qui est capable d'éliminer de des défauts tels que, lorsque l'angle d'un aérateur à lattes formé dans une ailette varie, afin d'augmenter le rendement thermique, grâce à une meilleure performance de refroidissement, lorsque l'angle de l'aérateur à ailettes augmente, on obtient une grande résistance de ventilation. Ce qui fait que, sur la base d'une expérimentation, pour obtenir une relation entre l'angle de l'aérateur à lattes et un facteur (capacité de l'échangeur de chaleur) indiqué par la performance de refroidissement/résistance de ventilation obtenues par la variation de l'angle de l'aérateur à ailettes, la valeur maximale du facteur peut être obtenue lorsque l'angle d'inclinaison par rapport à un sens de ventilation de l'aérateur à ailettes avoisine les 42°, et un angle approprié pour faire face aux exigences (approximativement 80 % de la valeur maximale) est compris entre 28° ou plus et 55° ou moins.
PCT/JP2000/001808 1999-06-30 2000-03-24 Echangeur de chaleur WO2001001058A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11/184555 1999-06-30
JP11184555A JP2001012883A (ja) 1999-06-30 1999-06-30 熱交換器

Publications (1)

Publication Number Publication Date
WO2001001058A1 true WO2001001058A1 (fr) 2001-01-04

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PCT/JP2000/001808 WO2001001058A1 (fr) 1999-06-30 2000-03-24 Echangeur de chaleur

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WO (1) WO2001001058A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102636070A (zh) * 2012-04-28 2012-08-15 上海交通大学 低热阻低流阻组合式强化换热翅片及其制造方法
US8945884B2 (en) 2000-12-11 2015-02-03 Life Technologies Corporation Methods and compositions for synthesis of nucleic acid molecules using multiplerecognition sites

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100918782B1 (ko) * 2002-05-17 2009-09-23 한라공조주식회사 열교환기용 핀
DE10235038A1 (de) * 2002-07-31 2004-02-12 Behr Gmbh & Co. Flachrohr-Wärmeübertrager

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6146756B2 (fr) * 1978-11-21 1986-10-15 Nippon Denso Co
JPS63163788A (ja) * 1986-12-26 1988-07-07 Matsushita Refrig Co 熱交換器
JPH05106985A (ja) * 1991-10-18 1993-04-27 Nippondenso Co Ltd コルゲートルーバフイン型熱交換器
EP0650023A1 (fr) * 1993-10-22 1995-04-26 Zexel Corporation Echangeur de chaleur à plusieurs tubes
JPH10220983A (ja) * 1997-02-05 1998-08-21 Denso Corp 積層型熱交換器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6146756B2 (fr) * 1978-11-21 1986-10-15 Nippon Denso Co
JPS63163788A (ja) * 1986-12-26 1988-07-07 Matsushita Refrig Co 熱交換器
JPH05106985A (ja) * 1991-10-18 1993-04-27 Nippondenso Co Ltd コルゲートルーバフイン型熱交換器
EP0650023A1 (fr) * 1993-10-22 1995-04-26 Zexel Corporation Echangeur de chaleur à plusieurs tubes
JPH10220983A (ja) * 1997-02-05 1998-08-21 Denso Corp 積層型熱交換器

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9309520B2 (en) 2000-08-21 2016-04-12 Life Technologies Corporation Methods and compositions for synthesis of nucleic acid molecules using multiple recognition sites
US8945884B2 (en) 2000-12-11 2015-02-03 Life Technologies Corporation Methods and compositions for synthesis of nucleic acid molecules using multiplerecognition sites
CN102636070A (zh) * 2012-04-28 2012-08-15 上海交通大学 低热阻低流阻组合式强化换热翅片及其制造方法

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