EP1520146A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur

Info

Publication number
EP1520146A1
EP1520146A1 EP03740407A EP03740407A EP1520146A1 EP 1520146 A1 EP1520146 A1 EP 1520146A1 EP 03740407 A EP03740407 A EP 03740407A EP 03740407 A EP03740407 A EP 03740407A EP 1520146 A1 EP1520146 A1 EP 1520146A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
sub
blocks
exchanger according
tubes
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
EP03740407A
Other languages
German (de)
English (en)
Inventor
Walter Demuth
Martin Kotsch
Karl-Heinz Staffa
Christoph Watler
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr 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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1520146A1 publication Critical patent/EP1520146A1/fr
Ceased legal-status Critical Current

Links

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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with 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
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines

Definitions

  • the invention relates to a heat exchanger, in particular a cooler for a heating or air conditioning system of motor vehicles, according to the preamble of claim 1, 8, 9, 10 or 11.
  • a flat tube heat exchanger in particular a serpentine type condenser, with a flat tube block consisting of one or more flat tubes, which with preferably twisted end sections on the opposite or on the same tube block side in respective connection space components, i.e. Manifolds, so that if the manifolds are arranged on the same tube block side, two adjacent and parallel manifolds are provided.
  • a plurality of serpentine-shaped flat tubes can be provided, in which adjacent flat tubes are arranged adjacent to one another in the longitudinal direction of the header tubes with their inlet-side or outlet-side tube sections, the serpentines comprising a plurality of 180 ° bends. A corresponding arrangement prevents heat transfer losses, but still leaves something to be desired.
  • EP 0 414 433 discloses a duplex heat exchanger which enables a refrigerant flow in cross-countercurrent by two flat heat exchangers arranged in series, hereinafter referred to as blocks, each with two header pipes, which are connected over a large number of flat tubes. tubes are interconnected, are provided.
  • the two blocks are connected to each other by means of flanges and O-ring seals, for which purpose they have to be assembled, tensioned, soldered and connected after soldering.
  • the refrigerant is supplied to the block through which flow first occurs in an upper region, the outlet at the bottom, and when the second block flows through thereafter, the inlet can take place both at the bottom and at the top, and the outlet takes place accordingly at the top and bottom.
  • Such a duplex heat exchanger consisting of two blocks is associated with a large number of individual parts and a relatively high production outlay, so that production is expensive. Such a heat exchanger also leaves something to be desired with regard to the thermal properties.
  • a cooler for a supercritical vapor compression refrigeration cycle in which a refrigerant outlet is provided in a higher position than a refrigerant inlet in relation to a vertical direction, so that refrigerant flows from an underside to an upper side of the cooler.
  • a cooler also leaves something to be desired in terms of coolant efficiency.
  • the main idea of the invention is the surfaces of the
  • the sub-block preferably being arranged within the zone with the highest air temperature.
  • the height of the partial block through which refrigerant flows is at least as large as the height of the zone with increased air temperature.
  • the number of pipes arranged in a partial block in the horizontal direction depends on the space temperature-related air temperature zone within which the corresponding partial block is arranged.
  • the number of tubes of a partial block within a zone with a higher temperature is greater than the number of tubes of a partial block which is arranged within a zone with a lower temperature, the ratio of the number of tubes of the partial block within the zone also a higher temperature for the number of tubes of the sub-block within the zone with a lower temperature in the range from 1: 1 to 3: 1 can be selected.
  • At least two sub-blocks are arranged one behind the other and at least two sub-blocks one above the other, the sub-blocks being flowed through one after the other by the refrigerant, and the sequence of the through-flow being arbitrarily specifiable by means of structural measures.
  • the refrigerant preferably flows through at least two of the sub-blocks in countercurrent to the air flow.
  • the heat exchanger is subdivided into four sub-blocks, which are flowed through in succession, the sub-blocks flowing through first being arranged below the sub-blocks flowed through subsequently, the first and second sub-blocks as well as the third and fourth sub-blocks each being at the same height are arranged.
  • Such a heat exchanger is particularly suitable for an installation space in which, due to the installation space, a zone in a lower area a higher air temperature is present than in an upper area of the installation space.
  • the partial blocks flowed through first are arranged above the partial blocks flowed through subsequently, the first and second partial blocks and the third and fourth partial blocks each being arranged at the same height.
  • This alternative embodiment of the heat exchanger is particularly suitable for an installation space in which, due to the installation space, a zone with a higher air temperature is present in an upper region than in a lower region of the installation space.
  • the temperature of the refrigerant differs in the different sub-blocks.
  • the temperature of the refrigerant in the lower sub-blocks is higher than in the upper ones Sub-blocks, where the temperature of one or both rear sub-blocks is higher than the temperature of the corresponding front
  • the temperature of the refrigerant is higher in the upper sub-blocks than in the lower ones Sub-blocks, the temperature of one or both rear sub-blocks being higher than the temperature of the corresponding front sub-block.
  • R 134 a and carbon dioxide can be used as refrigerants.
  • carbon dioxide in a supercritical state ie if there is a pure gas flow in the heat exchanger, is suitable for a heat exchanger according to the invention.
  • a flow of at least two of the four sub-blocks with refrigerant preferably takes place in a cross-countercurrent to the air. Cross-countercurrent operation results in more effective heat transfer.
  • a diagonal deflection is provided between the second sub-block and the third sub-block, so that cross-countercurrent operation takes place in all sub-blocks.
  • the diagonal deflection is preferably formed by means of a one-piece transition flange which is connected to two manifolds, namely to the manifold assigned to the second sub-block and to the third sub-block.
  • a tube in particular a flat tube, is preferably provided in the region of the diagonal deflection, through which refrigerant does not flow or only flows minimally, whereby the heat transfer is decoupled.
  • the tubes connecting the collecting tubes in the area where the heat transfer takes place are preferably formed by flat tubes, the flat tubes being twisted in the vicinity of the collecting tubes and on the side of the heat exchanger opposite the collecting tubes before and after a 180 ° bending point by 90 °.
  • the sub-blocks are closed on both sides by manifolds, wherein at least two sub-areas on at least one side can also be terminated by a common manifold.
  • the air flowing through the heat exchanger preferably comes into contact with two or more areas with different temperatures, the maximum air temperature difference between the air inlet and outlet being less than half the temperature difference between the refrigerant inlet and the refrigerant outlet, carbon dioxide being used as the refrigerant in supercritical operation , Temperatures are around 150 ° C at the refrigerant inlet and around 50 ° C at the outlet.
  • the tubes arranged essentially in the horizontal direction are preferably thermally separated from one another, for example by an air gap.
  • the individual partial blocks are preferably also thermally separated from one another.
  • the header tubes are preferably also essentially thermally decoupled. There is only thermal contact on the diagonal deflection and, depending on the version, also on the connecting flanges.
  • the cooling fins arranged between the tubes are preferably also thermally decoupled. This is achieved, for example, in that each sub-block has its own cooling fins.
  • Figure 1 is a front view of a flat tube heat exchanger according to the embodiment.
  • FIG. 2 shows a section through the flat tube heat exchanger from FIG. 1 along line II-II in FIG. 1;
  • FIGs 1 and 2 show a cooler 1 serving as a flat tube heat exchanger for a heating or air conditioning system of a motor vehicle, which is part of a refrigerant circuit, not shown, and is used to pass a refrigerant, in particular CO 2 , with the aid of which the cooler 1 flows Cool air.
  • a refrigerant in particular CO 2
  • the air flow is symbolic by one of shown on the left on the radiator 1 arrow.
  • the CO 2 is usually present as a pure gas flow, temperatures of around 150 ° C. being present at inlet 2 in cooler 1.
  • the coolant is cooled in the cooler 1, so that there are 3 temperatures at 50 ° C. at the outlet.
  • the cooler 1 is divided into 2 ⁇ 2 sub-blocks, which are referred to below as T1, T2, T3 and T4.
  • the sub-blocks T1 and T2 are arranged in the installed state within a zone 4 with a higher air temperature and below the sub-blocks T3 and T4.
  • the height h of the two sub-blocks T1, T2, which are arranged within zone 4 with the higher air temperature, is greater than the height H of zone 4 with increased air temperature, the value of the air temperature in zone 4 being greater than the air temperature in the remaining areas of the installation space of the cooler 1.
  • a manifold S1, S2, S3, S4 is connected to each sub-block, two manifolds S1, S2 and S3, S4 being arranged at the corresponding height of the sub-blocks T1, T2 or T3, T4 are.
  • a plurality of flat pipes 5 are arranged between the collecting pipes S1 and S2 as well as S3 and S4, through which the refrigerant can pass from a collecting pipe S1 or S3 to the neighboring collecting pipe S2 or S4, which is why the flat pipes 5 have a U-shaped course. They are twisted by 90 ° in a known manner in the vicinity of the respective manifold S1, S2, S3, S4. Ribs (not shown) are arranged between the flat tubes 5, which support the heat exchange.
  • ribs can be divided into two, ie. H. the sub-blocks T1 and T2 or T3 and T4 arranged one behind the other each have their own ribs. However, it is also possible to thermally decouple the ribs of the partial blocks by means of slots.
  • a diagonal reversal 6 from partial block T2 to partial block T3 is provided, as indicated in FIG. 2 by an arrow drawn in the cooler 1.
  • a transition flange 7, as shown in FIGS. 3 to 6, is provided between the two manifolds S2 and S3, the zone of the flat tube 5 ', which lies on the boundary of the two sub-blocks T2, T3, is used by the partitions of the two collecting pipes S2 and S3 are offset by a transverse division.
  • the middle flat tube 5 ' is thus "short-circuited” and hardly flows through, at most as a result of a small pressure difference that occurs between the two header tubes S2 and S3 due to the low throttling effect in the transition flange 7.
  • the flat tube 5' which has no or only minimal flow has the As a side effect, thermal decoupling is achieved between the sub-blocks T1 and T3 or T2 and T4
  • the transition flange 7 is usually designed as a component together with the two partition walls and is soldered when the cooler 1 is soldered.
  • manifolds S1 and S2 or S3 and S4 are connected to each other at inlet 2 and outlet 3 via a connector 9, as shown in FIGS. 7 to 9, so that refrigerant can also get directly into manifold S2 can flow directly out of the collecting pipe S3.
  • the refrigerant is collected after the partial blocks T1 and T2 or T3 and T4 have been flowed through, in separately formed collecting pipes S1, S3 or S2, S4.
  • the thermal coupling of the sub-blocks T1 and T2 or T3 and T4 via the one-piece ribs can be reduced by slitting the rib or by any other suitable measure.
  • the sub-blocks T1, T2 are divided into sub-blocks T3, T4 50:50, but the division should preferably be degressive, i.e. for example, 60:40 or 70:30, because, as with the condenser, the outlet density is higher and thus the volume flow is lower than at the inlet.
  • the gas cooler also serves as a capacitor in subcritical operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

L'invention concerne un échangeur de chaleur, en particulier un radiateur pour une installation de chauffage ou de climatisation de véhicules automobiles servant à refroidir un réfrigérant. Ledit échangeur de chaleur (1) est traversé par de l'air, comprend des tuyaux collecteurs (S1, S2, S3, S4) ainsi que plusieurs tuyaux (5) s'étendant de manière sensiblement horizontale et est divisé en plusieurs blocs partiels (T1, T2, T3, T4). Selon l'invention, les surfaces de ces blocs partiels sont conditionnées par la taille de zones elles-mêmes conditionnées par l'espace disponible, présentant différentes températures d'air, dans l'espace d'installation de l'échangeur de chaleur. Le bloc partiel traversé en premier par un réfrigérant est disposé dans une zone conditionnée par l'espace disponible, présentant une température d'air plus élevée, de préférence dans la zone présentant la température d'air la plus élevée.
EP03740407A 2002-07-03 2003-07-03 Echangeur de chaleur Ceased EP1520146A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10229973A DE10229973A1 (de) 2002-07-03 2002-07-03 Wärmeübertrager
DE10229973 2002-07-03
PCT/EP2003/007102 WO2004005826A1 (fr) 2002-07-03 2003-07-03 Echangeur de chaleur

Publications (1)

Publication Number Publication Date
EP1520146A1 true EP1520146A1 (fr) 2005-04-06

Family

ID=29796142

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03740407A Ceased EP1520146A1 (fr) 2002-07-03 2003-07-03 Echangeur de chaleur

Country Status (9)

Country Link
US (1) US7650934B2 (fr)
EP (1) EP1520146A1 (fr)
JP (1) JP2005531748A (fr)
CN (1) CN100374807C (fr)
AU (1) AU2003281285A1 (fr)
BR (1) BR0305261A (fr)
DE (1) DE10229973A1 (fr)
WO (1) WO2004005826A1 (fr)
ZA (1) ZA200402528B (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004042308A1 (fr) * 2002-11-07 2004-05-21 Behr Gmbh & Co. Kg Echangeur de chaleur
DE102004018317A1 (de) * 2004-04-13 2005-11-03 Behr Gmbh & Co. Kg Wärmeübertrager für Kraftfahrzeuge
DE102007007233A1 (de) 2007-02-14 2008-09-25 Behr Gmbh & Co. Kg Vorrichtung, insbesondere Kraftfahzeuge, mit einem Wärmeübertrager
US10767937B2 (en) 2011-10-19 2020-09-08 Carrier Corporation Flattened tube finned heat exchanger and fabrication method
CN115451748A (zh) * 2021-06-09 2022-12-09 浙江盾安热工科技有限公司 扁管及换热器

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US3835920A (en) * 1972-02-22 1974-09-17 Gen Motors Corp Compact fluid heat exchanger
FR2571485B1 (fr) * 1984-08-22 1987-02-13 Valeo Echangeur de chaleur, en particulier radiateur d'un circuit de refroidissement de moteur de vehicule automobile
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JP3030036B2 (ja) 1989-08-23 2000-04-10 昭和アルミニウム株式会社 複式熱交換器
JPH04115257U (ja) 1991-03-15 1992-10-13 サンデン株式会社 熱交換器
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US5355947A (en) * 1993-10-25 1994-10-18 Chrysler Corporation Heat exchanger having flow control insert
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EP0845648B1 (fr) * 1996-11-27 2002-01-30 Behr GmbH & Co. Echangeur de chaleur à tubes plats, en particulier condenseur de type à serpentin
JPH11325784A (ja) 1998-03-16 1999-11-26 Denso Corp 熱交換器
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Also Published As

Publication number Publication date
WO2004005826A1 (fr) 2004-01-15
US20050006072A1 (en) 2005-01-13
US7650934B2 (en) 2010-01-26
DE10229973A1 (de) 2004-01-29
CN1592839A (zh) 2005-03-09
ZA200402528B (en) 2004-11-26
AU2003281285A1 (en) 2004-01-23
BR0305261A (pt) 2004-10-05
CN100374807C (zh) 2008-03-12
JP2005531748A (ja) 2005-10-20

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