EP1070929A2 - Evaporateur pour système de conditionnement d'air pour véhicule automobile - Google Patents

Evaporateur pour système de conditionnement d'air pour véhicule automobile Download PDF

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Publication number
EP1070929A2
EP1070929A2 EP00115565A EP00115565A EP1070929A2 EP 1070929 A2 EP1070929 A2 EP 1070929A2 EP 00115565 A EP00115565 A EP 00115565A EP 00115565 A EP00115565 A EP 00115565A EP 1070929 A2 EP1070929 A2 EP 1070929A2
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EP
European Patent Office
Prior art keywords
evaporator
collector
compartments
compartment
slots
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.)
Granted
Application number
EP00115565A
Other languages
German (de)
English (en)
Other versions
EP1070929A4 (fr
EP1070929A3 (fr
EP1070929B1 (fr
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
Publication of EP1070929A2 publication Critical patent/EP1070929A2/fr
Publication of EP1070929A4 publication Critical patent/EP1070929A4/fr
Publication of EP1070929A3 publication Critical patent/EP1070929A3/fr
Application granted granted Critical
Publication of EP1070929B1 publication Critical patent/EP1070929B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—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
    • F28F2225/08—Reinforcing means for header boxes

Definitions

  • the invention concerns an automotive air conditioning system evaporator.
  • An automotive air conditioning system heat exchanger having a longitudinally-extending collector, defining a first and a second compartment, each having a coolant inlet or respectively a coolant outlet, the collector defining plural slots each extending into both said compartments, plural pipes extending from the slots to a flow-return device, is known from US-A-5 174 373, being suitable for a condenser.
  • duplex heat exchangers where two rows of flat pipe arrays are arranged one behind the other with clearance to allow air circulation, connected with the internal heat exchange fluid via circular pipe shaped collectors, in which the collectors for these conventional duplex heat exchangers have a circular interior cross-section free from transverse sub-divisions.
  • both rows of the flat pipe array can be interconnected with one another in various ways by means of connection leads. This is also taken into account in the event of use as an evaporator.
  • both flat pipe arrays arranged behind one another in the surrounding air, are fed by different internal heat exchange fluids, e.g. on one hand by means of the cooling water in an engine cooling system and, on the other, by means of the forced air or engine oil acting as the coolant in an automotive air conditioning system.
  • the collectors are not sub-divided transversely into two successive compartments, isolated from each other by means of a longitudinal divider.
  • One embodiment of the invention provides an automotive air conditioning system evaporator with only a single row of pipes, hence a simplex evaporator which, with both manufacturing depth for the pipes in the circulating air and coolant operating pressure pre-determined, has the lowest possible dimensions from the point of view of installation volumes and wall thicknesses and, with this, also uses the minimum amount of material. Moreover, for optimisation, particular attention is to be paid to the fact that, in this type of evaporator, the interior of the collector is divided transversely into two different compartments.
  • coolant inflow and return flow to both compartments are arranged to take place concurrently whereas, in the case where there is an uneven number of flows, inflow and return flow to the same compartment can be provided, however, in association with different interior areas which, in the same compartment, are separated from each other by means of at least one transverse partition.
  • Duplex heat exchangers suffice to begin with for the requirement of the above problem definition, especially in the context of optimising the manufacturing volumes, even if both flat pipe arrays have fins passing through them (e.g. Figs. 16 and 17 of EP 0 414 433 A2).
  • an automotive air conditioning system evaporator having a longitudinally-extending collector defining a first and a second compartment, each compartment having a coolant inlet or respectively a coolant outlet, the collector defining plural slots each extending into both said compartments, the evaporator having plural pipes extending from the slots to a flow-return device, characterised in that both compartments of the collector have the shape of a rounded pipe to provide pressure stability.
  • each of the two collector compartments is rounded for stability under pressure and in the ideal case is, in addition, circular in cross-section.
  • Its operation, according to the invention also becomes correspondingly obvious, if a collector's total circular cross-section as specified in US patent 5 174 373 is compared with a collector's individual circular cross-sections according to the invention, given the two pre-requisites that both circular cross-sections of both compartments are identical and shall be measured on the same manufactured depth of the flat pipes. It then follows that, in the invention, an individual compartment's circular cross-section is about half the diameter of the circular cross-section of the complete collector as specified in US Patent 5 174 373.
  • the lowering in the circular cross-section diameter corresponds with a factor of two, as well as perhaps to lowering the wall thickness required to about half its value. In this way, savings in material requirements and costs are already achieved. Moreover, a considerable saving in the building-in height, which in any event is barely adequate behind the dashboard inside the vehicle, results.
  • coolants such as the widely employed R 134a coolant are still used for automotive air conditioning system evaporators, whose operating pressure is in the region of 10 to 30 bar.
  • natural coolants such as e.g. CO 2
  • CO 2 which are used in evaporators at operating pressures from 40 to 80 bar.
  • the evaporator as specified in the invention is equally well suited to operation with CO 2 as the coolant, as the saving in wall thickness becomes particularly and reassuringly apparent. It is even possible as of now to install the evaporator as specified in the invention using conventional coolants, without considerable cost increases or any kind of rework being required for later conversion to CO 2 operation.
  • first and second collector walls which surround both collector compartments, are made up of separate components. It could also be possible to assemble the wall respectively associated with a compartment, if necessary, even made up of several parts along the circumference depending on the type of pipe base and cover, whereas an integral design with the first and/or second wall along the circumference is also favourable.
  • An integral construction with a first circular pipe and a second circular pipe for the construction of a collector for a duplex heat exchanger is known from DE-G 91 11 412.8 U1, in particular Fig. 4 with its description.
  • the longitudinal divider between both circular cross-section compartments is already manufactured from the start as an integral component. This concept can also be transferred to the simplex evaporator as specified in the invention.
  • insert slots matched to the profile of the flat pipes in the context of the maximum permissible tolerances, are manufactured as a separate capping component, to which matching can be achieved in a much easier way than to an incorporated collector or even only to an incorporated component wall.
  • a capping component can be formed from sheet metal in a way which is much simpler and then bent appropriately. If this sheet is then also coated with solder, a solder carrier to solder the flat pipes with the collector is obtained at the same time.
  • a typical capping component formed from sheet metal, can also be manufactured without difficulty with collars extending the insert slots to the interior and/or the exterior and allowing solder to form a surface bond between the inner surface of the collars and the external surfaces of the flat pipes. Moreover, it is possible to manage the manufacture of the transverse slots in the collector itself with a lower demand for accuracy without detriment to the end result. For example, it is possible to cut in the transverse slots with a simple milling cutter following extrusion or a similar integral manufacturing process.
  • compartments in the flat pipe served by the internal heat exchange fluid shall be, as far as possible, able to use even the wall thickness region of the longitudinal divider, in a different way to US Patent 5 174 373.
  • Another solution is proposed concerning the wall thickness area of this longitudinal divider, as well as a solution regarding an extension of the transverse slot into the thickness of the actual collector wall.
  • transverse slot regions which are still opposite the actual collector wall area and/or the longitudinal divider on the front face of each flat pipe, internal recessing of the transverse slot is effected, such that uninterrupted communication between the relevant compartment in the collector and the critical flat pipe compartments mentioned can be achieved at that point.
  • Precise matching to the flat pipes is also invariably achieved by means of the capping component with its machined insert slots. It has been shown that the extremely narrow transverse slot dimensions in the collector cover, in association with the installed capping component and the inserted flat pipes, do not adversely affect collector wall thickness dimensioning requirements, as any material weakness in the collector wall is again compensated by addition of the inserted parts and the solder used.
  • Fig. 1 shows the basic construction of a dual flow automotive air conditioning system evaporator 2 as specified in the invention. It is preferable to produce the complete evaporator (or parts thereof) using aluminium or aluminium alloy such as e.g. AlMn1 and hard soldered components, for example by means of hard solder in its AlSi7-12 form.
  • aluminium or aluminium alloy such as e.g. AlMn1
  • hard soldered components for example by means of hard solder in its AlSi7-12 form.
  • Evaporator 2 has a flat pipe array 20, interconnected by means of zigzag fins 21 (Fig. 4) for heat transfer purposes.
  • each flat pipe 20 on the outside of the array is fitted with a zigzag fin, which can be followed externally by a metal finishing sheet (not illustrated), which can form part of a framework for the array. It is preferable to effect the heat transfer connection at the same time by hard soldering the zigzag fins 21 to the flat pipes 20 and, if necessary, to each metal finishing sheet.
  • the flat pipes 20 are set in the array substantially at equal intervals and, when installed in the automotive air conditioning system, mainly arranged vertically in the diagram layer portrayed in Fig. 1.
  • the surrounding air is circulated mainly as an external heat exchange medium in the horizontal plane as shown in the diagram layer in Fig. 1 as specified by the double line arrows in Fig. 5 and Fig. 5a.
  • the coolant acting as the internal heat exchange medium is fed as a dual flow through each individual flat pipe 20, in which the arrows depicted in Fig. 1 indicate the two flows 22 and 24, namely Flow 22 on the inflow side with the downward pointing arrow in Fig. 1 and Flow 24 on the outflow side with the upward pointing arrow in Fig. 1.
  • a plurality or multiplicity of channels 26 is formed over the full cross-section length of each individual flat pipe 20 over which the two flows are divided, e.g. at any given time, an identical number of channels 26 is assigned to each flow 22 or 24.
  • a collector 4 which is extended outwards at an angle of 90° to the flat pipes 20 (compare Figs. 4 to 5a); in its transverse direction (diagram layer in Figs. 1 to 3a), the collector 4 is divided into two compartments 8 and 10, which are completely, or at least to a considerable degree, separated from each other by means of an intermediate partition 12.
  • the collector cover 6 forms a pipe base or contributes to its formation.
  • the collector cover 6 is divided over its length, in the dimension in which the flat pipe array 20 is divided, mainly at equally spaced intervals, by transverse slots 18 which are common to both compartments 8 and 10, into which each flat pipe 20 in the flat pipe array 20 engages its same nominated end 23 for the purpose of sealing it.
  • This end 23 of the flat pipe 20 is therefore, just as with transverse slot 18, common to both compartments 8 and 10.
  • the front faces of the ends 23 of the flat pipes 20 are at the same time aligned over the length of both the individual flat pipe 20 and the collector 4.
  • a return flow device 28 which switches the first flow 22 to the second flow 24 in each individual flat pipe 20.
  • a return flow device 28 There are numerous design options for such a return flow device 28. Without any limitation as to generality, this is shaped in Fig. 1 as bowl 30 which, with its sidewall 31, is crimped as specified in Fig. 1, holding fast the exterior of each flat tube 2.
  • each flat pipe 20 can be associated with an individual bowl 30. It is also possible to interconnect such bowls or build up the appropriate bowl shaped return flow structure into a single integral component. Essentially, its function is the return of the two flows 22 and 24 in each flat tube 20.
  • evaporator 2 the coolant used as the internal heat exchange fluid is fed as an opposing cross-flow with respect to the direction of flow of the surrounding air.
  • Figs. 5 and 5a in which the direction of flow of the coolant is illustrated with the horizontally aligned double walled arrows.
  • the collector 4 coolant inlet 14 and the collector 4 coolant outlet 16 are formed at any given time on a front facing sealing wall 15 or 17 of the collector 4, e.g. as illustrated, as an external connection nipple on a disc shaped sealing wall 15 or 17, which is enclosed securely in the collector cover 6.
  • inlet 14 and outlet 16 are associated at the same time with the same sealing wall 15 whereas, in the design form specified in Fig. 5a, inlet 14 is associated with a sealing wall 15 and outlet 16 is associated with another sealing wall 17.
  • inlet 14 leads into compartment 10, facing away from the direction of flow of the coolant and outlet 16 issues from compartment 8, facing towards the circulating surrounding air.
  • both compartments 8 and 10 at any given time are divided into two sub-compartments 50 and 52 or 54 and 56 by means of a transverse partition 9 in which, in the case of Fig. 5, inlet 14 is extended through transverse partition 9 into compartment 10 via an intermediate pipe connection 13.
  • Fig. 1 The basic principle of using the coolant to produce the flow through evaporator 2 is depicted in Fig. 1.
  • the coolant which has entered compartment 8, as specified in the design depicted in Fig. 1, is routed to the appropriate flat pipe 20 along the first flow 22 by means of the first halves of the channels 26, then switched to the return flow device 28 and routed in the opposite direction back to compartment 6 through the second halves of the channels 26. If this direction of flow is provided over the entire length of the evaporator, Fig. 1 with an opposing cross-flow taken as a basis is to be a pre-requisite for flow of the surrounding air on the right hand side in the diagram layer. In preferred development, however, it can even be provided by means of a type of flow as specified in Figs. 5 and 6, by way of example.
  • a corresponding progressive flow is effected along collector 4 from inlet 14 to outlet 16; first from inlet 14 into sub-compartment 50, from this via the associated or common flat pipes 20 into sub-compartment 54. From here, via the associated or common flat pipes 20 into sub-compartment 52 and finally from here via the associated or common flat pipes 20 into sub-compartment 56, which is connected to outlet 16.
  • each collector 4 is common to all evaporator 2 design forms: in developing the conventional design, namely for the collector cover 6 to be formed as a rounded shape for stability under pressure, this concept is applied to both walls 32 and 34 of the first compartment 8 as well as the second compartment 10 of the collector cover. Correspondingly, both walls 32 and 34 are each rounded for stability under pressure, or respectively even rounded to a circular shape in the design examples.
  • Figure 2 also shows the purest form of one limiting case, in which both walls 32 and 34 are formed as a single integral component 44, which, moreover, even incorporates the intermediate partition 12 between both compartments 8 and 10.
  • the intermediate partition 12 narrows, in addition tapering in the direction of the adjacent ends 23 of the flat pipes 20.
  • the top of this narrow taper can, in addition, depending on the requirement, be formed as a wedge shape running towards a tip or be more or less flattened after the style of the narrow face on a flat crosspiece.
  • Figure 2a also shows the other limiting case, where both walls 32 and 34 are respectively formed as a single integral component, in which both components, i.e. walls 32 and 34, are linked by a further component inset separately as longitudinal divider 36, in this case in the form of a flat material crosspiece 38, which for its part forms the intermediate partition 12 between compartments 8 and 10.
  • the exterior profile of both walls 32 and 34 can remain completely rounded - in which case extreme deviations from the circular shape are possible - both flat sides of the further component are present in case 2a, hence, preferably opposite the flat material crosspiece 38, the flange type flattened sections 40 of a plinth shaped exterior attachment 41 set in the installation between both walls 32 and 34.
  • Figs. 3 and 3a show a favoured mix between the two limiting cases cited. From the limiting case in Fig. 2, it is assumed in addition that both walls 32 and 34 are formed from a single integral component 44.
  • this further component 48 is enclosed securely, i.e. in general hard soldered, on the outside, in a longitudinal slot 46 between both rounding bends of the first and second walls 32 and 34, to the side of collector 4 facing away from the array of flat pipes 20.
  • the first alternative is illustrated in the design forms in Figs. 1 and 3 using a longitudinal divider 36 inserted as a separate component, but could also be correspondingly embodied with the intermediate partition 12 incorporated in the integral component 44 as specified in Fig. 2, particularly in the configuration tapering to a tip.
  • the intermediate partition 12 engages as if it were a flow in a channel 26a which is not used and is, in addition, anchored securely between its two channel walls.
  • this channel 26a used appropriately only to divide the flow, has a narrower channel width than the remaining channels 26 of each flat pipe 20 unless this is essential. However, as a result of this narrower dimensioning the manufacturing depth of evaporator 2 is kept proportionately small.
  • a minimum manufacturing depth is obtained by following the alternative as specified in Figs 2, 2a and 3a.
  • the intermediate partition 12 which can be formed with an integral component 44 as specified in Fig. 2 or shaped as a separate component as specified in Figs. 2a and 3a, works in concert with the outside edge 58 of a completely standard intermediate partition 60 between channels 26 of each flat pipe 20 acting in a flow-like manner. In this way, the separation is achieved in a flow-like manner with no additional manufacturing depth being required.
  • Figs. 3, 3a and 4 show the following:
  • the first and second walls 32 and 34 of the collector cover 6 are formed as the integral component 44, which, in the form depicted, can be manufactured as an impact extruded component.
  • the collector cover 6 is provided in its centre with the longitudinal slot 46, into which the longitudinal divider 36 can be pushed from the outside.
  • the longitudinal divider 36 is provided with a coating of solder for soldering to the front face 62 of the flat pipes 20 and sealing of the longitudinal slot 46, protruding externally from the collector cover 6 to ensure adequate solder provision.
  • a capping component 64 is attached externally to the collector cover 6 in the area of the transverse slots 18.
  • This capping component 64 is first placed on the collector cover 6 with as few solder slots as possible.
  • existing collars from housing slots 72 in the capping component 64 for each flat pipe 20, showing internally, are pressed into the transverse slot 46 of the collector 4 if necessary.
  • the soldering of the capping component 64 is effected, together with further soldered connections, in a continuous process oven using the so-called "One-Shot" method.
  • AlSi 7-12 a non-corrosive fluoridic flowing material, is used as the hard solder for choice. Hard soldering is effected at a temperature of 600 - 610°C.
  • the former is first pressed into a device in the collector cover 6 and then, by folding both longitudinal edges 68 over a securing ridge 70 on the collector cover 6, is fastened to this.
  • a direct housing slot 72 is formed in the capping component 64, together with the collar 66, into which the end 23 of the flat pipe 20 is inserted.
  • Collar 66 is matched both to the dimensions of the flat pipe 20 and to the external profile of collector 4. In this way, gas-tight soldering of the capping component 64 with the collector cover 6 is achieved on the one hand and, on the other, the collar 66 of the capping component 64 is also connected with the ends of the flat pipes 20 in a gas-tight fashion.
  • the pipe division i.e. the spacings along the collector cover 6 of the flat pipes 20, is normally 6-15 mm
  • the transverse slots 18 in the collector cover 6 must only be put in during the abovementioned cycle; in this way, the pressure sealing of the collector cover 6 is only slightly disturbed when the transverse slots 18 are milled.
  • the transverse slot 18 in the collector cover 6 is recessed opposite the front face of the flat pipe 20. Guaranteed sealing between the first and second compartments 8 or 10 of the collector cover 6 is achieved by means of a longitudinal divider 56, the thickness of which does not depend on the internal overpressure in the collector cover 6, but merely on the difference in pressure between the first and second compartments 8 or 10, or is to be dimensioned, as the need arises, from the point of view of its technical production.
  • the thickness of the first or second wall 32 or 34 for any given instance must be 2.5 mm, whereas the solder coated longitudinal divider 36 can be manufactured with a thickness of less than 0.2 mm. To achieve problem free mounting and provide sufficient solder as well as being capable of meeting tolerances, however, it should have a wall thickness of about 1 - 1.5 mm.
  • the longitudinal divider 36 is pressed into a channel 26a in the flat pipe 20, which is not used for continuous flow, for the purpose of sealing against the front face 62 of the flat pipe 20.
  • the longitudinal divider 36 provides a seal directly against an intermediate partition 60 between the adjacent channels 26 which provides a longitudinal path in the flat pipe 20, so as to avoid blocking the channels 26 completely.
  • the transverse slot 18 in the collector cover 6 is recessed opposite the front face 62 of the flat pipe 20 by the distance 74, so that, at this point, both external channels 26b of the flat pipe 20 are not also closed off by the collector cover 6, but linked to provide flow between the first or second compartment 8 or 10.
  • the capping cover 64 is continuously soldered to the long side of the transverse slot 18 as specified in Fig. 3 by means of the internally mounted collar 66, in the case of Fig.
  • the capping component 64 must withstand the full evaporator 2 operating pressure on both front faces of the transverse slot 18. Because of transverse slot 18's small width, (2 ⁇ the thickness of the capping component 64 plus the flat pipe thickness) of only 3 - 4 mm, however, the thickness of the capping component 64 amounts to 1 - 1.5 mm.
  • the extruded or seamlessly drawn collector cover 6 provides a framework which copes with operating pressures and provides the pressure strengths required. As a result of the production process and its shape, it can already produce the pressure strength safety required, without being further affected by the Nocolok soldering process and variations in the evaporator production process.
  • the capping component 64 provides the soldering material required. Furthermore, in the capping component 64, the minimum tolerances in the housing slots 72 of less than 0.2 mm required for soldering, as with the transverse slots 18 in the collector cover 6, can be produced more cost effectively by pressing, stamping and rolling.

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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)
EP20000115565 1999-07-20 2000-07-19 Evaporateur pour système de conditionnement d'air pour véhicule automobile Expired - Lifetime EP1070929B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19933913 1999-07-20
DE1999133913 DE19933913C2 (de) 1999-07-20 1999-07-20 Verdampfer einer Kraftfahrzeugklimaanlage

Publications (4)

Publication Number Publication Date
EP1070929A2 true EP1070929A2 (fr) 2001-01-24
EP1070929A4 EP1070929A4 (fr) 2001-09-24
EP1070929A3 EP1070929A3 (fr) 2001-11-14
EP1070929B1 EP1070929B1 (fr) 2009-01-07

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ID=7915368

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000115565 Expired - Lifetime EP1070929B1 (fr) 1999-07-20 2000-07-19 Evaporateur pour système de conditionnement d'air pour véhicule automobile

Country Status (3)

Country Link
EP (1) EP1070929B1 (fr)
DE (1) DE19933913C2 (fr)
ES (1) ES2319610T3 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003054467A1 (fr) * 2001-12-21 2003-07-03 Behr Gmbh & Co. Echangeur thermique notamment destine a un vehicule
WO2004029533A1 (fr) * 2002-09-18 2004-04-08 Behr Gmbh & Co. Echangeur thermique, notamment evaporateur
EP1439365A2 (fr) * 2003-01-15 2004-07-21 Lg Electronics Inc. Echangeur de chaleur
EP1452814A1 (fr) * 2001-11-08 2004-09-01 Zexel Valeo Climate Control Corporation Echangeur thermique et tube pour echangeur thermique
WO2005015110A1 (fr) * 2003-08-07 2005-02-17 Norsk Hydro Asa Echangeur de chaleur comprenant deux collecteurs
WO2005031236A2 (fr) * 2003-09-26 2005-04-07 Valeo Climatisation Echangeur de chaleur ameliore
US7000690B2 (en) 2001-10-06 2006-02-21 Behr Gmbh & Co. Heat exchanger for a motor vehicle
EP1460364A3 (fr) * 2003-03-19 2011-09-21 Calsonic Kansei UK Limited Echangeurs de chaleur pour véhicule automobile
JP2013134016A (ja) * 2011-12-27 2013-07-08 Daikin Industries Ltd 熱交換器
CN103277945A (zh) * 2013-05-27 2013-09-04 扬州杰信车用空调有限公司 客车蒸发器
CN104930758A (zh) * 2015-06-18 2015-09-23 安徽江淮松芝空调有限公司 平行流式车用空调蒸发器
CN105020941A (zh) * 2015-06-18 2015-11-04 安徽江淮松芝空调有限公司 平行流式车用空调散热器
EP3009780B2 (fr) † 2014-10-17 2023-10-18 Mahle International GmbH Fluide caloporteur

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DE10315371A1 (de) * 2003-04-03 2004-10-14 Behr Gmbh & Co. Kg Wärmeübertrager
DE102004028652A1 (de) * 2004-06-15 2006-01-12 Behr Gmbh & Co. Kg Wärmeübertrager in Ganzmetall-, vorzugsweise Ganzaluminium-Bauweise
DE102005058769B4 (de) 2005-12-09 2016-11-03 Modine Manufacturing Co. Ladeluftkühler

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US7000690B2 (en) 2001-10-06 2006-02-21 Behr Gmbh & Co. Heat exchanger for a motor vehicle
US7234515B2 (en) 2001-10-06 2007-06-26 Behr Gmbh & Co. Heat exchanger for a motor vehicle
EP1452814A4 (fr) * 2001-11-08 2008-09-10 Zexel Valeo Climate Contr Corp Echangeur thermique et tube pour echangeur thermique
EP1452814A1 (fr) * 2001-11-08 2004-09-01 Zexel Valeo Climate Control Corporation Echangeur thermique et tube pour echangeur thermique
WO2003054467A1 (fr) * 2001-12-21 2003-07-03 Behr Gmbh & Co. Echangeur thermique notamment destine a un vehicule
US7650935B2 (en) 2001-12-21 2010-01-26 Behr Gmbh & Co. Kg Heat exchanger, particularly for a motor vehicle
WO2004029533A1 (fr) * 2002-09-18 2004-04-08 Behr Gmbh & Co. Echangeur thermique, notamment evaporateur
EP1439365A2 (fr) * 2003-01-15 2004-07-21 Lg Electronics Inc. Echangeur de chaleur
EP1460364A3 (fr) * 2003-03-19 2011-09-21 Calsonic Kansei UK Limited Echangeurs de chaleur pour véhicule automobile
WO2005015110A1 (fr) * 2003-08-07 2005-02-17 Norsk Hydro Asa Echangeur de chaleur comprenant deux collecteurs
WO2005031236A3 (fr) * 2003-09-26 2005-06-23 Valeo Climatisation Echangeur de chaleur ameliore
WO2005031236A2 (fr) * 2003-09-26 2005-04-07 Valeo Climatisation Echangeur de chaleur ameliore
JP2013134016A (ja) * 2011-12-27 2013-07-08 Daikin Industries Ltd 熱交換器
CN103277945A (zh) * 2013-05-27 2013-09-04 扬州杰信车用空调有限公司 客车蒸发器
EP3009780B2 (fr) † 2014-10-17 2023-10-18 Mahle International GmbH Fluide caloporteur
CN104930758A (zh) * 2015-06-18 2015-09-23 安徽江淮松芝空调有限公司 平行流式车用空调蒸发器
CN105020941A (zh) * 2015-06-18 2015-11-04 安徽江淮松芝空调有限公司 平行流式车用空调散热器

Also Published As

Publication number Publication date
ES2319610T3 (es) 2009-05-11
EP1070929A4 (fr) 2001-09-24
DE19933913A1 (de) 2001-02-01
EP1070929A3 (fr) 2001-11-14
DE19933913C2 (de) 2003-07-17
EP1070929B1 (fr) 2009-01-07

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