EP1859217A1 - Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules - Google Patents

Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules

Info

Publication number
EP1859217A1
EP1859217A1 EP06706543A EP06706543A EP1859217A1 EP 1859217 A1 EP1859217 A1 EP 1859217A1 EP 06706543 A EP06706543 A EP 06706543A EP 06706543 A EP06706543 A EP 06706543A EP 1859217 A1 EP1859217 A1 EP 1859217A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
supply line
line
coolant
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.)
Withdrawn
Application number
EP06706543A
Other languages
German (de)
English (en)
Inventor
Gottfried DÜRR
Frederik GÖTZ
Michael Kranich
Karl-Heinz Staffa
Christoph Walter
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 EP1859217A1 publication Critical patent/EP1859217A1/fr
Withdrawn legal-status Critical Current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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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
    • 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
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • 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

Definitions

  • Heat exchangers in particular evaporators of a motor vehicle
  • the invention relates to a heat exchanger according to the preamble of claim 1.
  • EP 1 459 026 A1 describes an evaporator for a motor vehicle air conditioning system, in which a number of flow paths for a coolant each open into a collecting area constructed from a plurality of plates.
  • the term Kählkar is used synonymously for refrigerants, such as CO 2 , R134a, etc.
  • the coolant is supplied to the collecting area via a supply line which extends over substantially the entire length of the heat exchanger, wherein periodically spaced connecting holes between feed and Collection area are provided.
  • the feed of the evaporator with coolant on its high pressure side thus takes place substantially parallel over the entire length.
  • the effective lead length i. the length of the supply line over which coolant flows in the longitudinal direction of the heat exchanger
  • the length of the heat exchanger through which the coolant flows allows the formation of even very long heat exchangers without phase separation of the coolant already taking place in the region of the supply line.
  • the effective supply line length is preferably no greater than half the effective length of the collecting region, whereby the improvement achieved is particularly pronounced.
  • a circulating line connected to the collecting area wherein coolant enters the circulating line from a first subset of flow paths and exits from the circulating line into a second subset of flow paths.
  • Supply line, discharge line or circulation line have a separating element, by means of which at least two sections of the relevant line coolant-tight separated from each other.
  • lines can be used in multiple ways, such as a supply line and at the same time as a circulation line, so that particularly space-saving and cost-effective versions are possible.
  • the collecting area has a plurality of plate elements, through the stacking of which the collecting area is at least partially buildable.
  • the supply line is advantageously connected to an upper plate element of the collecting region, wherein a plurality of respectively corresponding openings are provided in the upper plate element and in the supply line. This allows a simple connection of supply and collection area.
  • At least one opening of supply line and upper plate element opens into at least two flow paths, whereby the number of openings can be reduced.
  • exactly one opening of supply line and upper plate element can be assigned to exactly one flow path, which leads to a particularly secure fixing of the supply line because of the larger number of openings.
  • a plate-shaped distributor element is provided in the collecting region, wherein the coolant can be distributed to the plurality of flow paths by means of a plurality of apertures provided in the distributor element.
  • a link-like shaped distribution element not only a simple construction of the collecting region of plates is made possible, but also a simple distribution of the coolant through the shape of the openings to the individual flow paths. The distribution can be done individually in parallel or sequentially.
  • a lower plate member has a plurality of openings, wherein the flow paths are defined in the region of the openings on the lower plate member. This allows a particularly cost-effective and at the same time safe connection of the flow paths to the collecting area, for example by means of soldering.
  • At least one of the flow paths is formed as a U-shaped flat tube with a plurality of chambers, whereby a large common surface of coolant and flow path is provided cost-effective and pressure-resistant.
  • the plurality of flow paths are grouped into a number of sections, each section having at least one flow path, wherein the sections are arranged side by side in the longitudinal direction of the heat exchanger and wherein between at least two of the sections to an intermediate collection of the coolant suitable volume is provided.
  • the number of sections is a total of two. Alternatively, however, the number of sections may also have a different number, in particular a larger even number or an odd number greater than or equal to three.
  • the heat exchanger is an evaporator of a motor vehicle air conditioning system, wherein the coolant is carbon dioxide (R 744).
  • the coolant is carbon dioxide (R 744).
  • Carbon dioxide is particularly critical in terms of the problems addressed in the prior art and also requires high pressures, which harmonizes particularly well with the proposed solutions.
  • R 134a is the Combination of a conventional coolant such as R 134a with a heat exchanger according to the invention due to its good properties in terms of manufacturing costs and size advantageous.
  • the supply line is laid over substantially the entire length of the heat exchanger. This may be appropriate depending on space requirements. It is essential in the context of the invention that the effective length of the supply line, ie the length over which coolant enters the collecting area, remains limited.
  • At least the supply line or the discharge line has a flattening (301b), wherein the flattening is soldered flat with the collecting area.
  • a secure and tight fixing of the line at the collecting area is given in a simple manner.
  • at least the supply line or the discharge has a substantially D-shaped cross-section. This cross section can be achieved by reworking a cost-effective circular tube or by extrusion or other known per se.
  • the cross-section of at least the lead or the lead outside the area of the sheet soldering is substantially circular.
  • standard tubes can be used, which are less expensive than cables with a special cross section, at least outside the areal soldering.
  • the part with a D-shaped cross section may in particular be welded to the part with a circular cross section. But it can also be formed by flattening a completely round tube, so that circular part and D-shaped part have formed a uniform tube before the production of the lines.
  • At least the supply line or the discharge line has a shape which cooperates in a form-fitting manner with a formation of the collecting area for the purpose of positioning the supply line or discharge line, wherein the formation does not allow the passage of coolant.
  • the supply line or the discharge line has a plurality of openings which are aligned with a plurality of openings of the collecting area for the purpose of passage of coolant, the openings not interacting in a form-fitting manner.
  • At least the supply line or the discharge openings for the purpose of the coolant passage which are made by means of bore or materialwegikider punching.
  • the supply line and / or the discharge have perforations (301a) for the purpose of passing through the coolant, which are produced by punching without material removal. Although this generally reduces the line cross-section at this point, there is a particularly high level of security against dissolving material residues which may enter the coolant during later operation of the heat exchanger.
  • Fig. 1 shows a plan view of a first embodiment of a heat exchanger from the front.
  • Fig. 2 shows a plan view of the heat exchanger of FIG. 1 from above.
  • Fig. 3 shows a plan view of the heat exchanger of Fig. 1 from the side.
  • Fig. 4 shows a sectional view through the heat exchanger of Fig. 1 in the region of a supply line.
  • 5 shows a sectional view through the heat exchanger of Fig. 1 in the region of a derivative.
  • FIG. 6 shows a sectional view through the heat exchanger of FIG. 1 in FIG.
  • FIG. 7 shows a plan view of a distributor plate of the heat exchanger of FIG. 1.
  • FIG. 8 shows a plan view and a side view of an upper plate member of the heat exchanger of FIG. 1.
  • FIG. 9 shows a plan view of a lower plate element of the heat exchanger from FIG. 1.
  • FIG. 10 shows a sectional view of a flat tube of the heat exchanger from FIG. 1.
  • FIG. 11 shows a plan view of a distributor plate of a heat exchanger according to a second exemplary embodiment.
  • Fig. 12 shows an upper plate member of the second embodiment corresponding to the distributor plate of Fig. 11.
  • Fig. 13 shows a schematic representation of the principle of operation of the first and the second embodiment
  • FIGS. 14 to 36 each show a schematic representation of the functional principle of a heat exchanger according to the invention according to a first to correspondingly twenty-third modification.
  • FIG. 37 shows a top view of a third embodiment of a heat exchanger from the front.
  • FIG. 38 shows a plan view of the heat exchanger of FIG. 37 from above.
  • FIG. 38 shows a plan view of the heat exchanger of FIG. 37 from above.
  • Fig. 39 shows a plan view of the heat exchanger of Fig. 37 from the side.
  • FIG. 40 shows a scale-oriented plan view of a distributor plate of the heat exchanger of FIG. 37.
  • FIG. 40 shows a scale-oriented plan view of a distributor plate of the heat exchanger of FIG. 37.
  • FIG. 41 is a plan view and a side sectional view taken along line AA of an upper plate member of the heat exchanger of FIG. 37;
  • FIG. FIG. 42 is a plan view, a sectional view taken along the line A - A of the plan view, and a front end view of a lead of the heat exchanger of FIG. 37.
  • FIG. 43 shows a modification of the supply line from FIG. 42 in a sectional view and in a detailed view with a punching tool.
  • the heat exchanger according to the first embodiment is an evaporator for an automotive air conditioning system and comprises a tubular inlet 1 and a tubular outlet 2. Both lines 1, 2 are parallel to each other in a longitudinal direction of the evaporator above a collecting area extending over the entire evaporator length 3 arranged. Beyond the collecting area 3 lead 1 and 2 discharge are continued to a common flange 4, via which they are connected to the other air conditioning system of the vehicle (not shown). In the area of continuations 1a, 2a between collecting area 3 and flange plate 4, the lines have a number of kinks and bends, whereby they are adapted to the individual geometry of the installation space in the vehicle. As supply line 1 and discharge line 2 in the sense of the invention, therefore, only those sections of the lines are defined in which they are arranged directly on the evaporator.
  • a circulation line 5 is arranged above the collection area 3 at this and extends over the entire length of the evaporator.
  • the circulation line 5 is designed as a tube section which is closed at its two ends and has approximately the same diameter as the supply line 1 and the discharge line 2. However, the diameters of the supply line, discharge line and circulation line can also have different diameters.
  • each of the flat tubes 6 has a plurality of chambers or channels 6a (see cross section through one of the flat tube legs in FIG. 10).
  • the chambers 6a of each of the flat tubes 6 together forms a flow path or is arranged hydraulically in parallel. In the direction of the cooling air flow, that is to say perpendicular to the plane of the drawing according to FIG. 1, there are thus in each case two flow paths in each flat tube in depth one behind the other.
  • the total of twenty flat tubes 6 are with their forty ends respectively in recesses 7a of a lower plate member 7 (see FIG. 9) inserted and soldered there.
  • a central, extending in the longitudinal direction web 7b of the plate member 7 separates the two groups of chambers 6a from each other.
  • a distributor plate 8 (see FIG. 7) is placed flat on the lower end plate 7 and soldered flatly, but at least along closed marginal lines with it.
  • the distributor plate 8 has a number of slot-like openings 8 a, which are partially aligned with the openings 7 a of the lower end plate 7 and thus with the end faces of the flat tubes 6.
  • Out of alignment portions of the apertures, e.g. H-shaped openings 8b of the distributor plate 8 are provided to connect different flow paths with each other.
  • the H-shaped openings shown in this case each connect two adjacent flat tubes 6 or four flow paths with each other.
  • the plate member 9 has a number of circular openings 9a made by punching each on the same side. By punching formed on the side facing away from the distributor plate in each case a protruding collar 9b (see side view of the plate member in Fig. 9), by means of which the supply line 1, 2 discharge line and 5 are particularly easy to attach. As can be seen from the scale drawing in FIG. 8, the holes 9a have different widths in groups on, so that the various pressures and coolant densities in the evaporator is taken into account.
  • the tubular lines 1, 2 and 5 are each provided with bores which correspond to the above-described punches 9 a of the upper plate element 9.
  • the lines 1, 2, 5 are thus attached to the collar 9b and soldered coolant-tight, whereby at the same time a mechanically secure connection between collecting area and line 1, 2, 5 is made.
  • the distances of the furthest holes result in an effective length of the respective line 1, 2, 5.
  • An effective in terms of heat exchange evaporator length is useful as the largest distance between two flow paths defined in the longitudinal direction of the evaporator. It follows that in the present embodiment, the effective length of the feed line 1 is less than 40% of the effective evaporator length.
  • the evaporator is supplied under high pressure from the liquid and gaseous phase of a coolant, which in the present case is carbon dioxide (R 744).
  • a coolant which in the present case is carbon dioxide (R 744).
  • the coolant enters through the punches 9a or holes of the supply line into a first group of eight flow paths.
  • a transfer to the eight corresponding opposing flow paths takes place in the H-shaped apertures, each with a first and a subsequently traversed flow path belonging to the same flat tube ("in-depth transfer"), after passing 16 of the evaporator's total of forty flow paths
  • the coolant enters through approximately larger holes in the circulation line 5.
  • the circulation line 5 has the function of an intermediate collector, so that the coolant of the different flow paths is remixed. at the same time flows to the left as shown in FIG. 1, wherein the flow velocity with respect to the supply line 1 is already significantly increased. By demixing related problems have already been significantly reduced at this point.
  • the remaining twelve flat tubes form a second group or a second section of a total of twenty-four flow paths 6.
  • the higher number of flow paths of the second section is taken into account in the circulating line 5, which is to be regarded as isobar, in that the diameter of the punches 9a of the second section is smaller than the diameter of the eight punches of the first section (see FIGS. 8 and 6). , However, the diameter of the punches may also have a different relative ratio.
  • the fully vaporized and expanded coolant from a particularly large twelve punches enters the discharge, in order to be fed from there to the wider refrigeration cycle.
  • the flat tubes 6 are flowed around during the above-described operation of cooling air, which is subsequently used for air conditioning of a vehicle interior.
  • the second preferred embodiment according to FIG. 11 and FIG. 12 differs from the first example only in the formation of the punches 9a 'and their corresponding holes in the lines 1, 2, 6 and in the shape of the distributor plate 8'.
  • some of the openings 9a ' are each formed so that two flow paths 6a are each directly charged with coolant through a single bore.
  • two flow paths are still flowed through per section of the evaporator, for which likewise H-shaped throughflows are used. Breaks 8a 'are responsible for the transition between the flow paths.
  • the effective lead length is slightly less than half the effective total length of the evaporator, as shown by the corresponding maximum bore spacing of lead 1 and longitudinal evaporator.
  • FIGS. 14 to 36 In order to clarify the scope of the inventive concept, twenty-three modifications according to FIGS. 14 to 36 will be described below. These are only the conceptual arrangement of supply line, discharge line and possibly further circulating lines. Outlets of coolant from a line are each symbolized by a crossed circle, whereas entries are each symbolized by a dotted circle. Flow paths for the coolant are symbolized by connecting lines between the lines.
  • Fig. 14 shows a modification according to the principle of the two embodiments described in detail with a feed line, a drain, a circulation line and two sections of flow paths, wherein the second section has twice the number of flow paths.
  • Fig. 15 shows the modification of Fig. 14 with supply and discharge on opposite sides.
  • Fig. 16 shows the modification of Fig. 15 with two equal sections.
  • Fig. 17 shows a modification with three sections, wherein a second circulating line is provided for feeding the third section.
  • Fig. 18 shows the modification of Fig. 17 with shortened circulation lines.
  • Fig. 19 shows a modification with three sections, wherein in each case a circulation line is formed by means of separating a portion of the supply line and the discharge line by a coolant-tight separating element.
  • Fig. 20 shows a modification with three sections and a separate circulation pipe, wherein the discharge has a separating element for the separation of another circulation pipe and leads away in the opposite direction to the supply line from the evaporator.
  • Fig. 21 shows a modification with three sections and two separate circulation tubes, wherein supply and discharge are arranged on the same side.
  • Fig. 22 shows a similar to Fig. 21 modification with short circulation lines.
  • FIG. 23 shows a modification with three sections, a separate circulating line and separating elements in the supply line and discharge line, with the supply line and the discharge leading away in opposite directions.
  • FIG. 24 shows a modification with five sections, wherein two separate circulating lines, each having a separating element, are provided for generating virtually four circulating lines.
  • Fig. 25 shows a solution for five sections with a total of three parallel lines, which is realized by corresponding separating elements in the supply line and circulation line.
  • Fig. 26 shows a solution with four parallel lines and five sections, wherein additional separating elements are provided.
  • Fig. 27 shows a modification with four sections, wherein three conduits are provided and continue supply and discharge opposite.
  • the solution is in principle expandable to 6 or more even-numbered sections.
  • Fig. 28 shows a modification with four or more even-numbered sections, wherein supply and discharge are provided by means of separating elements in the same conduit and vorrt only one circulation line.
  • FIG. 29 shows the modification from FIG. 28 with only two sections and thus only one separating element between the feed line and the discharge line.
  • Fig. 30 shows a solution having four or more sections in a supply line, a mutual discharge line and a circulation line.
  • Fig. 31 shows a variant in which supply and discharge have their connections in the longitudinal direction in the middle and are continued perpendicular to the longitudinal direction. There are two sections and one circulation line.
  • FIG. 32 shows a variant of FIG. 29 with asymmetrical division of the sections and at the evaporator ends in each case angled infeed and outfeed.
  • Fig. 33 shows the variant of Fig. 32 with separate pipes for supply and discharge, so that no separator is required.
  • FIG. 34 shows the variant from FIG. 33 with feed and discharge continued in the opposite direction relative to the flow of air.
  • FIG. 35 shows a variant with two sections, in which the first section is distributed in half with respect to the individual flow paths on the end regions of the evaporator, the second section being between the two subgroups of flow paths of the first section is located. This allows a fine adjustment to a distribution of the air flow.
  • FIG. 36 shows an arrangement modified from FIG. 35, in which subgroups of flow paths of the second section are respectively arranged at the evaporator ends.
  • the subgroups are a-symmetrically distributed for more accurate adaptation, with only one flow path at one end and three flow paths of the second section at the other end.
  • the feed line 301 is laid almost over the entire housing length of the heat exchanger and arranged between a discharge line 302 and a circulation line 305.
  • the effective length Lz of the feed line results as a maximum distance of a total of five in the feed direction successively arranged openings 301a, via which the refrigerant enters the heat exchanger.
  • An effective length Ls of a collecting region 303 results from a maximum distance between two flow paths in the longitudinal direction of the heat exchanger.
  • the effective supply line length Lz is approximately 43% of the effective evaporator length Ls.
  • the drawings Fig. 37 to Fig. 43 are each in scale.
  • the collecting region 303 is constructed analogously to the first exemplary embodiments of an upper plate element 309, a distributor plate 308 and a lower plate element 307 for receiving flat tubes 306.
  • the distributor plate 308 differs in the exact arrangement of their openings 308a from the previous embodiments, but works on the same principle.
  • the plate elements 307, 308, 309 are soldered flat on their abutting surfaces.
  • the lower plate member corresponds to that of the first embodiment. Overlaying the drawings in FIGS. 40 and 41 results directly in the intended flow paths of the coolant within the heat exchanger. Just as in the previous embodiments are in accordance with the decreasing pressure, the openings in the Lines and running in the upper plate member 309 in the course of the flow path of the coolant increasingly larger.
  • the supply line 301, the discharge line 302 and the circulation line 305 each have a flattening 301 b in the area of their contact with an upper plate element 309, so that the lines have a D-shaped cross section over this section (see FIGS. 39, 42 ). Outside the contact area, supply line 301 and discharge line 302 are circular in cross section.
  • the lines 301, 302, 305 in the region of the flattening 301b perforations 301c which correspond with embossed elevations 309b of the upper plate member 309. Since the elevations 309b do not provide a passage for the refrigerant (see FIG. 41), the engagement of the elevations 309b in the perforations 301c, ie the positive engagement of corresponding formations, merely serves to position and retain the lines 301, 302, 305 in FIG During the production of the heat exchanger. In this case, the upper side of the upper plate element 309 is plated flat with solder.
  • the openings 301a have no burrs or excess material residues. This can be achieved by drilling or usually more cost-effective punching and subsequent deburring and removal of the punched-out material. This can be done using compressed air, for example. In general, there remains a certain risk of loose burrs or material remnants that are not completely removed, which could later enter the refrigeration cycle.
  • the line 301 is therefore punched by means of a suitable tool 310 without removal of material, that is to say in a material-preserving manner, in order to produce the openings 301a, 301b. In this case, the removed from the opening material 301 d of the conduit wall is disposed within the conduit and firmly connected to the rest of the wall.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne un échangeur thermique, en particulier un évaporateur d'une installation de climatisation pour véhicules, comprenant une pluralité de passages d'écoulement, chacun présentant au moins un tube (6) à plusieurs canaux, à travers lesquels passe le liquide de refroidissement, comprenant une ligne d'entrée (1) et une ligne de sortie (2) utilisée pour alimenter et évacuer le liquide de refroidissement vers et à partir de l'échangeur thermique, comprenant au moins une région de collecte (3), certaines parties étant reliées à la pluralité de passages d'écoulement. L'air refroidi peut alors passer à travers l'échangeur thermique dans un sens transversal de manière à refroidir le liquide de refroidissement, l'échangeur thermique présentant une longueur structurelle supérieure dans un sens longitudinal, sensiblement perpendiculaire au sens transversal, à longueur du sens transversal, et la ligne d'entrée (1) est placée, de manière à être orientée dans le sens longitudinal, sur la région de collecte (3), tout en étant reliée à l'échangeur thermique. La ligne d'entrée comprend, dans la région de liaison avec la région de collecte, une longueur de ligne d'entrée efficace dans le sens longitudinal, cette dernière étant considérablement inférieure à la longueur totale efficace de la région de collecte (3).
EP06706543A 2005-03-07 2006-02-01 Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules Withdrawn EP1859217A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005010849 2005-03-07
PCT/EP2006/000861 WO2006094583A1 (fr) 2005-03-07 2006-02-01 Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules

Publications (1)

Publication Number Publication Date
EP1859217A1 true EP1859217A1 (fr) 2007-11-28

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EP06706543A Withdrawn EP1859217A1 (fr) 2005-03-07 2006-02-01 Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules

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EP (1) EP1859217A1 (fr)
JP (1) JP2008531976A (fr)
WO (1) WO2006094583A1 (fr)

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CN103983126B (zh) * 2014-05-28 2016-08-24 丹佛斯微通道换热器（嘉兴）有限公司 换热器
EP3534091B1 (fr) * 2016-10-26 2021-10-06 Mitsubishi Electric Corporation Distributeur et échangeur de chaleur
DE102017219182A1 (de) * 2017-10-26 2019-05-02 Mahle International Gmbh Wärmeübertrager

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3017272B2 (ja) * 1990-11-07 2000-03-06 株式会社ゼクセル 熱交換器
JPH05346297A (ja) * 1992-06-15 1993-12-27 Nippon Light Metal Co Ltd 熱交換器
US5622219A (en) * 1994-10-24 1997-04-22 Modine Manufacturing Company High efficiency, small volume evaporator for a refrigerant
JP3023546B2 (ja) * 1996-12-04 2000-03-21 ゴールド工業株式会社 熱交換器のエレメント
DE10149507A1 (de) * 2001-10-06 2003-04-10 Behr Gmbh & Co Wärmetauscher, insbesondere Flachrohr-Wärmetauscher eines Kraftfahrzeugs
DE50212972D1 (de) * 2001-12-21 2008-12-11 Behr Gmbh & Co Kg Wärmeübertrager, insbesondere für ein kraftfahrzeug
JP3960233B2 (ja) * 2002-04-03 2007-08-15 株式会社デンソー 熱交換器
JP4212306B2 (ja) * 2002-06-18 2009-01-21 株式会社日本クライメイトシステムズ 熱交換器のパイプ取付構造
FR2847973B1 (fr) * 2002-11-29 2006-01-27 Valeo Climatisation Echangeur de chaleur a inertie thermique pour circuit de fluide caloporteur, notamment de vehicule automobile.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006094583A1 *

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