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US20010003310A1 - Flat tube evaporator with vertical flat tubes for motor vehicles - Google Patents

Flat tube evaporator with vertical flat tubes for motor vehicles Download PDF

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Publication number
US20010003310A1
US20010003310A1 US09/214,484 US21448499A US2001003310A1 US 20010003310 A1 US20010003310 A1 US 20010003310A1 US 21448499 A US21448499 A US 21448499A US 2001003310 A1 US2001003310 A1 US 2001003310A1
Authority
US
United States
Prior art keywords
flat
zig zag
flat tubes
flat tube
heat exchange
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.)
Abandoned
Application number
US09/214,484
Other languages
English (en)
Inventor
Roland Haussmann
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.)
Valeo Klimatechnik GmbH and Co KG
Original Assignee
Valeo Klimatechnik GmbH and Co KG
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 Valeo Klimatechnik GmbH and Co KG filed Critical Valeo Klimatechnik GmbH and Co KG
Assigned to VALEO KLIMATECHNIK GMBH & CO., KG reassignment VALEO KLIMATECHNIK GMBH & CO., KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAUSSMANN, ROY
Assigned to VALEO KLIMATECHNIK GMBH & CO., KG reassignment VALEO KLIMATECHNIK GMBH & CO., KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAUSSMANN, ROLAND
Publication of US20010003310A1 publication Critical patent/US20010003310A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/14—Collecting or removing condensed and defrost water; Drip trays
    • 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
    • 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
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/04—Reinforcing means for conduits

Definitions

  • the invention relates to a flat tube evaporator, preferably of aluminum or an aluminum alloy, for motor vehicle air conditioning equipments with the features of the preamble of claim 1 .
  • a flat tube evaporator is for example known from U.S. Pat. No. 4,350,025.
  • the T-shaped projections to the end regions of the flat tubes increase the amount of material necessary and the structural depth of the flat tube evaporator and necessitate an expensive manufacture technology.
  • the projections freely projecting from the zig zag fins cannot take up and drain humidity which adheres within the region of the zig zag fins as drops and thus cannot reach the water flow gutters arranged behind the zig zag fins with respect to the flow direction thereof from the external heat exchange fluid.
  • the object underlying the present invention is to achieve an efficient water drain function from the zig zag fins with a simple manufacture technology without necessitating an additional amount of material or a greater structural depth.
  • the further embodiment according to claim 2 is especially interesting when the ribbing by means of the zig zag fins comprises limbs relatively narrowly adjacent to one another. Namely, it has shown that then on the one hand the shaping according to claim 2 in the manufacture of the flat tube evaporator is still relatively easy and that on the other hand the relatively narrow distance between the limbs of the zig zag fins adjacent to the water flow gutter leads to the fact that humidity automatically accumulates at this narrow part, gradually increases and becomes a major accumulation and finally, when it has increased to reach to the condensation water flow gutter, can be drained to this gutter essentially without residues. This further opposes to an entraining of humidity in the flow direction by means of the incoming flow of the external heat exchange fluid.
  • the flow gutters are provided in the region of the fins, where the condensation water accumulates.
  • Such flow gutters are disturbing at the connection ends of the flat tubes where a soldering or brazing, e.g. with a tube bottom, is effected.
  • claim 3 provides to do without the indentation in the brazed region which can form the water flow gutter.
  • the T-profile web provided therein had to be separately cut off, which requires a complicated finishing, for example by sawing out of the piece or milling off.
  • the same effect can be easily achieved by not additionally forming from the beginning the indentation in the end regions of the flat tubes when cutting them off the coil.
  • FIG. 1 shows a perspective view of a flat tube evaporator, in which the longitudinal extension of the flat tubes 2 is vertical;
  • FIG. 2 shows a cross-section in the flow direction of the external heat exchange fluid through a section of the block arrangement of flat tubes and zig zag fins with a detailed representation at the rear end of the representation of FIG. 2, seen in the flow direction of the external heat exchange fluid;
  • FIG. 3 shows in an enlarged scale a plan view on a zig zag fin internested between two adjacent flat tubes with a view into the flow direction of the external heat exchange fluid.
  • the flat tube evaporator represented in FIG. 1 has a double-flow design and is embodied as an evaporator of a refrigerant circulation.
  • the flat tube evaporator comprises the following general design:
  • a major number of typically twenty to thirty flat tubes 2 which extend vertically, is arranged at constant distances to each other and with aligned front sides 4 . Between the flat sides 6 of the flat tubes, a zig zag fin 8 each is internested in a sandwiched fashion. Similarly, a zig zag fin 8 each is furthermore arranged at the two outer surfaces 4 of the outer flat tubes.
  • Each flat tube comprises internal reinforcing webs 10 , which division off chambers 12 in the flat tube acting as continuous ducts. Depending on the structural depth, a number of the chambers or ducts 12 of ten to thirty is typical.
  • a refrigerant such as preferably fluorohydrocarbon, serves as internal heat exchange medium which enters the heat exchanger via a supply line 14 and exits the heat exchanger via an outlet line 16 .
  • the supply line 14 comes from the liquefier thereof.
  • the outlet line 16 leads to the condensor of the refrigerant circulation.
  • a distribution of the refrigerant on the inlet side is effected from the supply line 14 to the individual flat tubes by a so-called distributor.
  • the refrigerant On the outlet side, the refrigerant is supplied as a whole to the outlet line 16 .
  • both functions are combined in a common header 18 .
  • This header 18 is then arranged at a front side 4 of the flat tubes 2 , while at the other front side 4 of the flat tubes 2 , a flow reverse takes place only between each of the flows, here for example in common deflection header 22 according to FIG. 1.
  • the multi-flow design means at least one flow reverse in the region of the individual ducts formed by the chambers 12 in each flat tube 2 .
  • the deflection header 22 does then not need any further intermediate chamber subdivision, it is only necessary that a single deflection function is guaranteed.
  • the deflection header 22 in the deflection header 22 at least one parting wall is necessary, so that for example in case of a four-flow design, a double simple deflection in the respective deflection header 22 is effected.
  • the number of parting walls optionally has to be increased.
  • the header 18 is composed of a tube bottom 26 and a cap 28 , wherein optionally further parts for constructing the header 18 can be provided.
  • the header 18 requires at least a two-chamber design which separates an inlet side from the outlet side.
  • the chamber subdivision comprises at least one flat web in form of a longitudinal web 32 , which separates the inlet region in the header 18 communicating with the supply line 14 from an outlet chamber 34 continuously extending longitudinally of the header 18 and communicating with the outlet line 16 .
  • the supply of the refrigerant on the side of the inlet to all flat tubes 2 has to be as steady as possible.
  • the supplied refrigerant can be supplied to each individual flat tube 2 by a so-called distributor.
  • the supply is effected to adjacent groups of flat tubes 2 , in which at least some groups comprise a number of flat tubes higher than one, wherein the number of flat tubes 2 per group can also vary.
  • An own inlet chamber is assigned to each group of flat tubes 2 , which chamber directly communicates with the respective group of the flat tubes 2 .
  • the own inlet chambers are divisioned off from one another in the chamber subdivision by crosswise webs designed as flat webs.
  • the crosswise webs depart at a right angle only from one side of each of the longitudinal webs 32 .
  • the supply line 14 communicates with each of the individual inlet chambers via an own supply line 44 extending in the header 18 , the design of which can vary, e.g. coordinated in a tube.
  • the block of flat tubes 2 and zig zag fins 8 is laterally terminated by a side sheet metal 36 in contact with each of the outer zig zag fins, such that the side sheet metals 36 form an outer frame for the outer air flowing against the heat exchanger block according to arrow 6 in FIG. 2.
  • the flat tubes 2 , the zig zag fins 8 , the tube bottom 26 and the cap 28 of the header together with the optionally provided chamber subdivision as well as the side sheet metals 36 of the heat exchanger consist, as well as conveniently the supply line 14 and the outlet line 16 , of aluminum and/or an aluminum alloy and are brazed including the sections of the line connections adjacent to the heat exchanger to form the finished evaporator.
  • the supply line 14 and the outlet line 16 which can pass over into the header 18 via corresponding connecting sleeves, are connected to two respective connecting sleeves of a thermostatically controlled block valve.
  • this valve comprises two further connecting sleeves at the side of the inlet and of the outlet.
  • the tube bottom 26 and the cap 28 are formed of sheet metal pre-coated with solder or braze, respectively.
  • the free edge of the cap engages the tube bottom 26 with an overlap at least on one side.
  • the special arrangement of a zig zag fin 4 at a right angle to the flow direction of the external heat exchange fluid 9 is represented with a view in the flow direction.
  • the individual limbs 38 of the zig zag fin extend here in the flow direction of the arrow 9 of the external heat exchange fluid and are connected via rounded apexes 40 in the continuation direction of the zig zag fin, i.e. in the vertical direction.
  • Each of the apexes 40 are fixed by brazing zones 42 at the adjacent flat side of the adjacent flat tube 2 .
  • the arrangement and the embodiment of the limb 38 and the apex 40 are selected such that the free flow cross-section for the external heat exchange fluid according to arrow 9 is greater within the turn of the apexes 40 than in the region of the free distance 44 of two apexes 40 adajacent to the same flat tube 2 .
  • the space 46 between adjacent limbs 38 of the zig zag fin 8 has a narrower design in the region of the free distance 44 than adjacent to the apex 40 . This leads to the fact that in the region of the narrow gap defined by each of the free distances 44 under the influence of surface tensions, capillary depositions 48 from humidity entrained by the external heat exchange fluid can occur.
  • depositions 48 of liquid accumulate at the rear ends of the width extension of the zig zag fin 8 or the limbs thereof 38 , respectively, seen in the flow direction of the external heat exchange fluid according to arrow 9 .
  • a water flow gutter 50 vertically and continuously extending downwards is designed at each of the two adjacent flat tubes 2 .
  • the respective vertical water flow gutter 50 is designed by a vertical indentation 60 at the flat side of the contiguous flat tube 2 facing the adjacent zig zag fin, wherein the indentation can be conveniently effected at the wall surface of a duct 12 .
  • the indentation 60 in question can also be effected in the last duct 12 of the respective flat tube 2 , seen in the flow direction of the external heat exchange fluid according to arrow 9
  • FIG. 2 shows that likewise the water flow gutter can be designed in a preceding duct, here in the last but one duct seen in the mentioned flow direction.
  • each of these indentations faces a free distance 44 each between adjacent limbs 38 of the zig zag fin.
  • connection ends 62 of the flat tubes 2 are kept free from the respective indentation 60 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US09/214,484 1997-05-07 1998-05-05 Flat tube evaporator with vertical flat tubes for motor vehicles Abandoned US20010003310A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19719263.7 1997-05-07
DE19719263A DE19719263C2 (de) 1997-05-07 1997-05-07 Flachrohrverdampfer mit vertikaler Längserstreckungsrichtung der Flachrohre bei Kraftfahrzeugen

Publications (1)

Publication Number Publication Date
US20010003310A1 true US20010003310A1 (en) 2001-06-14

Family

ID=7828871

Family Applications (1)

Application Number Title Priority Date Filing Date
US09/214,484 Abandoned US20010003310A1 (en) 1997-05-07 1998-05-05 Flat tube evaporator with vertical flat tubes for motor vehicles

Country Status (6)

Country Link
US (1) US20010003310A1 (pt)
EP (1) EP0910778B1 (pt)
CN (1) CN1225713A (pt)
BR (1) BR9804884A (pt)
DE (1) DE19719263C2 (pt)
WO (1) WO1998050741A1 (pt)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110203308A1 (en) * 2008-01-17 2011-08-25 Robert Hong-Leung Chiang Heat exchanger including multiple tube distributor

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100906769B1 (ko) * 2002-01-31 2009-07-10 한라공조주식회사 오뚜기형 유로를 갖는 열교환기용 튜브 및 이를 이용한열교환기
FR2867845B1 (fr) * 2004-03-16 2007-04-20 Valeo Climatisation Tubes d'echangeur de chaleur favorisant le drainage des condensats
CN100432579C (zh) * 2004-07-05 2008-11-12 昭和电工株式会社 蒸发器
CN102052807B (zh) * 2011-01-26 2012-11-28 西安交通大学 一种冷凝器
CN112455360B (zh) * 2020-11-30 2022-03-11 奇瑞汽车股份有限公司 膨胀胶块的排水部件和膨胀胶块

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4350025A (en) * 1980-04-18 1982-09-21 Nissan Motor Company, Limited Refrigerant evaporator

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4621685A (en) * 1983-09-12 1986-11-11 Diesel Kiki Co., Ltd. Heat exchanger comprising condensed moisture drainage means
JPH0823477B2 (ja) * 1987-08-09 1996-03-06 日本電装株式会社 積層型熱交換器
US4829780A (en) * 1988-01-28 1989-05-16 Modine Manufacturing Company Evaporator with improved condensate collection
AU668403B2 (en) * 1992-08-31 1996-05-02 Mitsubishi Jukogyo Kabushiki Kaisha Stacked heat exchanger
US5622219A (en) * 1994-10-24 1997-04-22 Modine Manufacturing Company High efficiency, small volume evaporator for a refrigerant
KR100261006B1 (ko) * 1996-07-03 2000-07-01 오타 유다카 열교환기용 편평튜우브

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4350025A (en) * 1980-04-18 1982-09-21 Nissan Motor Company, Limited Refrigerant evaporator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110203308A1 (en) * 2008-01-17 2011-08-25 Robert Hong-Leung Chiang Heat exchanger including multiple tube distributor

Also Published As

Publication number Publication date
CN1225713A (zh) 1999-08-11
BR9804884A (pt) 1999-08-31
DE19719263A1 (de) 1998-11-12
DE19719263C2 (de) 2002-04-25
EP0910778A1 (de) 1999-04-28
EP0910778B1 (de) 2003-07-16
WO1998050741A1 (de) 1998-11-12

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Legal Events

Date Code Title Description
AS Assignment

Owner name: VALEO KLIMATECHNIK GMBH & CO., KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HAUSSMANN, ROY;REEL/FRAME:010187/0548

Effective date: 19981222

AS Assignment

Owner name: VALEO KLIMATECHNIK GMBH & CO., KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HAUSSMANN, ROLAND;REEL/FRAME:010401/0129

Effective date: 19981222

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION