EP2633255B1 - Wärmetauscher mit seitlicher flüssigkeitszufuhr - Google Patents

Wärmetauscher mit seitlicher flüssigkeitszufuhr Download PDF

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Publication number
EP2633255B1
EP2633255B1 EP11771201.8A EP11771201A EP2633255B1 EP 2633255 B1 EP2633255 B1 EP 2633255B1 EP 11771201 A EP11771201 A EP 11771201A EP 2633255 B1 EP2633255 B1 EP 2633255B1
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EP
European Patent Office
Prior art keywords
heat exchanger
outlet
inlet
impression
duct
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EP11771201.8A
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English (en)
French (fr)
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EP2633255A1 (de
Inventor
Sylvain Moreau
François Busson
Mohamed Ibrahimi
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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Publication of EP2633255A1 publication Critical patent/EP2633255A1/de
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
    • 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
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels

Definitions

  • the invention relates to the field of heat exchangers, especially for motor vehicles.
  • a plate heat exchanger has an intake pipe and an evacuation pipe forming part of a fluid circulation circuit considered, at least one connecting part of which extends in the direction of longitudinal stacking. Such an arrangement has a large size.
  • the invention is particularly applicable to evaporators intended for air-conditioning installations, in which the fluid circulating within the exchanger body is a refrigerant which enters the liquid phase and exits in the gas phase after heat exchange with a flow of gas.
  • the known heat exchangers are not optimized, especially in terms of dimensions.
  • the invention particularly aims to overcome the aforementioned drawbacks of known heat exchangers. It aims in particular to achieve a heat exchanger of the aforementioned type having a small footprint in the longitudinal stacking direction of the tubes.
  • the invention also aims to provide such a heat exchanger having an optimized pressure drop and which is particularly suitable as an evaporator for a motor vehicle air conditioning installation.
  • the invention proposes for this purpose a heat exchanger comprising an assembly of tubes, for example constituted by an assembly of plates, stacked in a longitudinal stacking direction to form a heat exchanger body for the circulation of a first fluid, comprising a connection device arranged at one end of the exchanger body in the longitudinal stacking direction.
  • the connecting device comprises an end plate and a cover adapted to be assembled together to jointly define an inlet channel and an outlet channel, respectively, for the admission of the fluid into the exchanger body and the evacuation of the fluid from the exchanger body.
  • the inlet channel and the outlet channel open in a transverse direction substantially perpendicular to the longitudinal stacking direction.
  • the input channel and the output channel are of generally bent shape.
  • the end plate has a stamped portion having a first input pattern and a first output pattern.
  • the cover has a second input cavity and a second output cavity.
  • the first input cavity cooperates with the second input cavity to define the input channel
  • the first output cavity cooperates with the second input cavity.
  • Output fingerprint to set the output channel.
  • the inlet channel and the outlet channel each have cross sections essentially defined by the second inlet cavity and the second outlet cavity of the lid.
  • the first input pattern and the first output pattern are of reduced depth less than a substantial depth of the second input pattern and the second pattern of output.
  • the reduced depth of the first input pattern and the first input pattern is less than 1 mm, preferably less than 0.5 mm, and the substantial depth of the second input pattern and the second pattern output is less than 10 mm, preferably less than 8 mm.
  • the outlet channel has a first end opening into the exchanger body and a second end opening outwardly of the exchanger body.
  • the outlet channel has a hydraulic diameter, in any intermediate region between the first end and the second end, between a first value of hydraulic diameter at the first end of the outlet channel and a second value of hydraulic diameter at the second end of the output channel.
  • the value of the hydraulic diameter of the outlet channel increases from the first value of hydraulic diameter at the first end of the outlet channel to the second hydraulic diameter value at the second end of the outlet channel.
  • the first value of the hydraulic diameter is between 10.5 mm and 11 mm, preferably 10.8 mm, and / or the second value of the hydraulic diameter is between 15 mm and 16 mm, preferably 15.6 mm. mm.
  • the outlet channel has an internal width, considered in an assembly plane of the end plate and the cover, which is greater than an internal width of the inlet channel, considered in the same plane of 'assembly.
  • the internal width of the outlet channel is between 14.5 mm and 16.8 mm, preferably close to 16 mm.
  • a stamped reservoir is interposed between the end plate and an adjacent plate of the heat exchanger body, opposite the lid, to ensure fluid communication with the inlet channel and the flow channel. exit.
  • the size of the input and output channels, considered in the stacking direction, is thus reduced. Such a reduction in size is particularly desired in the case of air conditioning evaporators for motor vehicles whose plate width, which corresponds substantially to the thickness of the exchanger body, is less than or equal to 40 mm.
  • the end plate and the cover thus form two specific components that can be assembled on a heat exchanger body known elsewhere.
  • FIG. 1 represents a heat exchanger 10, in a perspective view, which, in the example, constitutes an evaporator for a motor vehicle air conditioning installation.
  • the heat exchanger 10 comprises, for example, an assembly of plates 12 stacked in pairs in a longitudinal stacking direction, or first direction x, to form an exchanger body 14 delimiting internal tubes for the circulation of a fluid, preferably a refrigerant or refrigerant.
  • the plates 12 are respectively formed from a stamped metal sheet, for example made of aluminum alloy, having respective assembly edges intended to be joined together, in particular by brazing, to define first circulation channels of a first fluid.
  • the first circulation channels of the first fluid in particular the refrigerant or refrigerant, alternate with circulation passages for a second fluid, preferably air, which externally scans the exchanger body 14, as represented by the arrow A on the figure 1 .
  • the plates 12 comprise a first end boss 16 and a second end boss 18.
  • Each first end boss 16 of a plate 12 is intended to be assembled with the first end boss 16 of a plate 12 adjacent, in particular by brazing.
  • each second end boss 18 of a plate 12 is intended to be assembled with the second end boss 18 of an adjacent plate 12, in particular by brazing.
  • the first end bosses 16, located in the upper part on the figure 1 according to the embodiment, are each provided with two openings (not visible on the figure 1 ) allowing to define internally two circulation ducts (not visible on the figure 1 ) extending parallel to the longitudinal stacking direction of the plates 12.
  • the second end bosses 18 are made in an analogous manner and also make it possible to define two other circulation ducts internally.
  • the circulation ducts made by the openings of the first end bosses 16 and the second bosses end 18 make it possible to ensure fluid communication between the plates 12 for circulation in one or more passes.
  • corrugated spacers forming heat exchange fins are disposed between two pairs of adjacent plates 12, in the space between the first end bosses 16 and the second end bosses 18 respectively of the pairs of plates. 12, in the circulation passages for the second fluid to increase the heat exchange surface, between the first fluid, preferably the refrigerant or refrigerant, and the second fluid, preferably air.
  • the exchanger body 14 is provided, at one of its ends, in the longitudinal stacking direction, with a connection device 19 comprising an end plate 20, or input / output plate 20.
  • the end plate 20 is a specific plate, whose structure is different from the plates 12 forming the plate assembly 12 stacked in pairs to form a heat exchanger body 14.
  • the end plate 20 is assembled against the plate 12 located at the end of the exchanger body 14, in the longitudinal stacking direction.
  • connection device 19 also comprises a lid 22, advantageously obtained by stamping, to delimit together with the end plate 20 an inlet channel 24 and an outlet channel 26.
  • the inlet channel 24 and the outlet channel 26 are of generally bent shape.
  • the inlet channel 24 and the outlet channel 26 open internally into the exchanger body 14 and externally from the same side of the exchanger body 14 for admission and evacuation of the first fluid, as shown respectively by arrows F1 and F2.
  • the inlet channel 24 and the outlet channel 26 open in a transverse direction y substantially perpendicular to the longitudinal stacking direction x.
  • a regulator at the border of a compartment dedicated to the engine and a compartment of cockpit, and the arrangement of the evaporator in the compartment compartment, according to an orientation in which its exchange surface extends perpendicularly to the direction of flow of air, such an orientation of the channels 24 and 26 tends to arrange the latter substantially to the right of the expander.
  • the connecting means thus making it possible to link the heat exchanger to the expander is more direct, which also leads to a reduction in the pressure drop in each of the tubes of said connecting means.
  • the longitudinal stacking direction x forms with the transverse direction y and a vertical direction z a direct dihedron.
  • the inlet channel 24 and the outlet channel 26 communicate respectively with the two circulation ducts. delimited inside the exchanger body 14 through the openings of the first end bosses 16.
  • Figures 2 to 4 present, respectively, an assembled perspective view, in exploded perspective and in plan of the end plate 20.
  • Figures 2 to 4 therefore have the structure of the end plate 20 and the cover 22.
  • the end plate 20 is made by stamping a metal strip, for example aluminum alloy.
  • the end plate 20 has a wall 28 of generally rectangular shape, advantageously having a ribbed structure, terminated at one end (in the lower part according to the figure 2 ) by an outgrowth 29 coming to bear against the second end boss 18 of the adjacent plate 12 to close the circulation ducts defined by the respective openings of the second end bosses 18.
  • the end plate 20 has a stamped portion 30 adapted to define, together with the lid 22, the inlet channel 24 and the outlet channel 26.
  • the stamped portion 30 has a first input cavity 32 helping to define the input channel 24 and a first output cavity 34 helping to define the output channel 26.
  • the end plate 20 also has an inlet opening 36 and an outlet opening 38, as shown on the figure 3 , formed through the stamped portion 30 to ensure fluid communication with the circulation ducts made by the openings of the first end bosses 16 and second end bosses 18 defined inside the exchanger body 14.
  • the first input cavity 32 and the first output cavity 34 each have substantially the shape of an arc.
  • the first input cavity 32 externally surrounds the first output cavity 34 on substantially a quarter circle, as shown on the Figures 2 to 4 .
  • connection device 19 also comprises a reservoir 40, advantageously stamped.
  • the reservoir 40 has substantially the shape of the first end boss 16 of the plate 12.
  • the reservoir 40 is interposed between the end plate 20 and the plate 12 located at the end of the exchanger body 14 in the longitudinal stacking direction.
  • the reservoir 40 is arranged opposite the cover 22 with respect to the wall 28 of the end plate 20 of the connection device 19.
  • the reservoir 40 is intended to ensure fluid communication between the exchanger body 14 and the input channel 24 and the output channel 26.
  • the reservoir 40 is provided with an inlet opening 42 and an outlet opening 44.
  • the inlet opening 42 and the outlet opening 44 are respectively located in alignment with the inlet opening. 36 and the outlet opening 38 of the end plate 20, as shown on the figure 3 .
  • the cover 22 has a second inlet cavity 46 and a second outlet cavity 48, advantageously of substantial depth.
  • the second entrance footprint 46 and the second output fingerprint 48 are intended to come, respectively, opposite the first input fingerprint 32 and the first output fingerprint 34 to define the input channel 24 and the output channel 26 .
  • the second input cavity 46 and the second output cavity 48 also have a substantially circular arc shape.
  • the second input cavity 46 externally surrounds the second output cavity 48 on substantially a quarter circle.
  • the input channel 24 and the output channel 26 each have a substantially arcuate shape, as shown in FIGS. Figures 2 to 4 .
  • the inlet channel 24 externally surrounds the outlet channel 26 on substantially a quarter circle as seen on the Figures 1 to 4 .
  • Any input or output imprint that defines a path having an arcuate curvature advantageously makes it possible to reduce the pressure drop of the fluid flowing in the connection device 19.
  • such an arcuate design of the fingerprints of the connection arrangement advantageously provides a significant reduction of the pressure drop upstream and downstream of the body 14 of the exchanger 10, with respect to the direction of flow of the fluid.
  • connection device 19 is therefore composed, at least, of the end plate 20 and the cover 22.
  • connection device 19 may also be composed of the reservoir 40 for communication with the exchanger body 14.
  • the first input fingerprint 32 and the first output fingerprint 34, on the one hand, and the second input fingerprint 46 and the second output fingerprint 48, on the other hand, help to define the print channel. 24 and the outlet channel 26 after assembly of the stamped portion 30 of the end plate 20 and the cover 22, and, alternatively, the reservoir 40.
  • the second inlet cavity 46 and the second outlet cavity 48 are of substantial depth with respect to the first inlet cavity 32 and the first outlet cavity 34, which have a reduced depth.
  • the first input fingerprint 32 and the first output fingerprint 34 have a stamping depth less than the stamping depth of the second input fingerprint 46 and the second print fingerprint 48.
  • the inlet channel 24 and the outlet channel 26 have internal cross-sections which are essentially defined by the second inlet indentation 46 and the second outlet recess 48 of the cover 22. therefore, the end plate 20 has a smaller footprint than the cover 22, in the longitudinal stacking direction.
  • reduced depth is also meant the fact that the depth of stamping can be practically zero, at least locally, the inlet channel 24 and the outlet channel 26 being then defined mainly by the second imprint 46 and the second outlet cavity 48 of the cover 22.
  • connection device 19 by the reduced depth of the first inlet cavity 32 and the first outlet cavity 34, does not impinge on the passage section, constituted by the circulation passages, for the second fluid passing through the exchanger body 14.
  • the inlet channel 24 and the outlet channel 26 have an evolving internal cross-section, as presented by the Figures 5 to 7 which are sectional views along the lines VV, VI-VI and VII-VII respectively of the figure 4 .
  • first inlet recess 32 and the first outlet recess 34 of the embossed portion 30 of the end plate 20 are delimited respectively by a first inlet bottom wall 50 and a first outlet bottom wall 52 having a substantially flat profile and connected to a first junction wall 54 of generally flat shape which constitutes the wall 28 of the end plate 20.
  • the first inlet cavity 32 and the first outlet cavity 34 have respective depths P 1 and P 2 , which can be equal or different.
  • the second inlet cavity 46 and the second outlet cavity 48 of the cover 22 are delimited respectively by a second inlet bottom wall 56 and a second outlet bottom wall 58.
  • the second inlet bottom wall 56 and the second outlet bottom wall 58 are substantially semicircular profile, connected to a second connecting wall 60 forming the cover 22.
  • the second inlet cavity 46 and the second outlet cavity 48 have respective depths P 3 and P 4 , which can be equal or different.
  • the first junction wall 54 and the second junction wall 60 are adapted to be assembled along a plane of junction for assembly, in particular by brazing.
  • the respective depths P 1 and P 2 of the first input cavity 32 and of the first output cavity 34 are typically less than 1 mm, preferably 0.5 mm, in particular for plates having a width L, in the transverse direction y, of the order of 35 to 40 mm.
  • the respective depths P 3 and P 4 of the second inlet cavity 46 and of the second outlet cavity 48 of the cover 22 are typically less than 10 mm, preferably less than 8 mm, for plates having the width L of the order of 35 to 40 mm.
  • the width L corresponds to the thickness of the exchanger body 14.
  • the cup of the figure 5 is made in the region where the inlet channel 24 and the outlet channel 26 open internally into the exchanger body 14. It can be noted, by way of example, that the depths P 1 and P 2 of the first cavity of FIG. In this region, the inlet 32 and the first outlet cavity 34 are zero. Thus, at this section, the cross section of the inlet channel 24 and the outlet channel 26 is essentially formed by the second inlet cavity 46 and the second outlet cavity 48 of the cover 22.
  • the first inlet cavity 32 and the first outlet cavity 34 of the end plate 20 terminate respectively with a first inlet half-collar 62 and a first outlet half-collar 64.
  • the second input fingerprint 46 and the second output fingerprint 48 of the cover 22 is terminating respectively with a second input half-collar 66 and a second output half-collar 68.
  • the collars for the inlet channel 24 and the outlet channel 26 are respectively surrounded by an inlet nozzle 70 and an outlet nozzle 72.
  • the inlet nozzle 70 and the nozzle of output 72 are made in the form of stepped sleeves.
  • the inlet nozzle 70 and the outlet nozzle 72 make it possible to connect the heat exchanger 10 to a circulation circuit of the first fluid, not shown.
  • the inlet tips 70 and outlet 72 are substantially tubular rings.
  • the outer diameter of each ring comprises a first tubular section extended by a second tubular section.
  • the outer diameter of the second tubular section is larger than the diameter of the first tubular section, thereby forming a shoulder.
  • the free end of the second tubular section comprises a flange.
  • the flange and the second tubular section comprise means for fixing and locking in rotation of each endpiece on the associated channel 70 or 72.
  • Such means for fixing and locking in rotation is formed by two notches extending over the entire thickness of the flange and extending over a portion of the second tubular section.
  • Each notch is shaped in order to cooperate by complementarity of form with a set of walls of junction 54, 60 formed on the plate and the cover defining the channels 70, 72.
  • the notches extend in a median plane to the tips 70, 72.
  • each of the end pieces 70, 72 on the previously assembled plate and cover allows perfect positioning of each of the inlet and outlet channels that come from the plate and the cover. To do this, the tips thus fitted ensure a contact and a compression of the plate and the lid, which promotes the brazing of these two parts.
  • such a design makes it possible to increase the rigidity and the tightness of the constituent parts of the connection device 19. It also turns out that the use of such end pieces mounted on the plate 20 and the cover 22 generates, compared to known solutions, increased manufacturing quality according to which games and manufacturing and assembly tolerances are reduced.
  • the first fluid flowing in the heat exchanger 10 is a refrigerant or refrigerant with phase change, the inlet channel 24 being intended for the admission of the first fluid in the liquid phase and the outlet channel 26 at the evacuation of the first fluid in the vapor phase.
  • the present invention aims to optimize the pressure drop or the internal pressure drop, in particular in the outlet channel 26.
  • the connection device structure 19 described above allows such an optimization precisely by dimensioning the hydraulic diameter of the outlet channel 26 between the heat exchanger body 14 and the outlet nozzle 72.
  • A is the area of the passage section of the tube, and P is the "wet" perimeter of the passage section of the tube.
  • the outlet channel 26 has a first end 74 opening into the exchanger body 14 and a second end 76 opening outwardly of the exchanger body 14, at the outlet end 72.
  • the outlet channel 26 has a hydraulic diameter Dh which, in any intermediate region between the first end 74 and the second end 76, has a value between a first hydraulic diameter value Dh 1 at the first end 74 and a second value of hydraulic diameter Dh 2 at the second end 76.
  • the value of the hydraulic diameter Dh of the outlet channel 26 increases from the first value of hydraulic diameter Dh 1 to the second value of hydraulic diameter Dh 2 .
  • the outlet channel 26 has an internal width Ls, considered in an assembly plane of the end plate 20 and the cover 22.
  • the internal width Ls is greater than an internal width Le of the duct. 24, considered in the assembly plane of the end plate 20 and the cover 22.
  • the internal width Ls of the outlet channel 26 is between 14.5 mm and 16.8 mm, preferably close to 16 mm.
  • the value of the hydraulic diameter Dh of the outlet channel 26 increases progressively from the first first value Dh 1 of between 10 mm and 11 mm, in particular equal to 10.8 mm, at the first end 74 until at the second first value Dh 2 between 15 mm and 16 mm, in particular equal to 15.6 mm, at the second end 76.
  • the width L of the plates 12, corresponding to the thickness of the exchanger body 14 in the transverse direction y is 38 mm
  • the width Ls of the outlet channel 26 is 16 mm
  • the width The input channel 24 is 10 mm.
  • Such an arrangement corresponds respectively to 42% and 26% of the thickness of the heat exchanger 10.
  • the depths P 1 and P 2 are equal to 0.4 mm.
  • the invention thus makes it possible to optimize the size of the heat exchanger 10 in the direction of longitudinal stacking x, which is particularly important for evaporators of air conditioning installations of a motor vehicle with lateral feed. Indeed, the space devoted to such evaporators is restricted and it is necessary to limit this congestion. This is particularly the case for evaporators whose thickness is less than or equal to 40 mm.
  • the invention also makes it possible to optimize the hydraulic diameter of the outlet channel 26, as mentioned above.
  • Another additional advantage of the invention is that the end plate 20 and the cover 22 can be assembled on a standard exchanger body 14.
  • the exchanger body 14 can be used for both lateral feed exchangers according to the present invention as well as for end feed exchangers.
  • the same assembly process and the same tooling can be used.
  • the components of the heat exchanger 10 are then brazed together in a single operation.
  • the present invention also finds an application for heat exchangers whose exchanger body consists of tubes, regardless of whether they are made from a plate assembly, by folding or any other method.

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  • 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)

Claims (17)

  1. Wärmetauscher (10), umfassend eine Anordnung von Innenrohren, die in einer Stapellängsrichtung (x) gestapelt sind, um einen Tauscherkörper (14) zu bilden, der für die Zirkulation eines ersten Fluids bestimmt ist, umfassend eine Verbindungsvorrichtung (19), die an einem Ende des Tauscherkörpers (14) in der Stapellängsrichtung (x) angeordnet ist,
    wobei die Verbindungsvorrichtung (19) eine Endplatte (20) und eine Abdeckung (22) aufweist, die geeignet sind, zusammengefügt zu werden, um gemeinsam jeweils einen Eintrittskanal (24) und einen Austrittskanal (26) für das Einlassen des Fluids in den Tauscherkörper (14) und das Ableiten des Fluids aus dem Tauscherkörper (14) zu begrenzen, dadurch gekennzeichnet, dass der Eintrittskanal (24) und der Austrittskanal (26) in einer Querrichtung (y), die im Wesentlichen senkrecht zu der Stapellängsrichtung (x) ist, münden.
  2. Wärmetauscher (10) nach Anspruch 1, wobei der Eintrittskanal (24) und der Austrittskanal (26) von im Wesentlichen abgewinkelter Form sind.
  3. Wärmetauscher (10) nach einem der vorhergehenden Ansprüche, wobei die Endplatte (20) einen vertieften Teil (30) aufweist, der eine erste Eintrittsvertiefung (32) und eine erste Austrittsvertiefung (34) aufweist.
  4. Wärmetauscher (10) nach einem der vorhergehenden Ansprüche, wobei die Abdeckung (22) eine zweite Eintrittsvertiefung (46) und eine zweite Austrittsvertiefung (48) aufweist.
  5. Wärmetauscher (10) nach Anspruch 3 und 4, wobei die erste Eintrittsvertiefung (32) mit der zweiten Eintrittsvertiefung (46) zusammenwirkt, um den Eintrittskanal (24) zu definieren, und die erste Austrittsvertiefung (34) mit der zweiten Austrittsvertiefung (48) zusammenwirkt, um den Austrittskanal (26) zu definieren.
  6. Wärmetauscher (10) nach Anspruch 5, wobei der Eintrittskanal (24) und der Austrittskanal (26) jeweils Querschnitte aufweisen, die im Wesentlichen durch die zweite Eintrittsvertiefung (46) und die zweite Austrittsvertiefung (48) der Abdeckung (22) definiert sind.
  7. Wärmetauscher (10) nach einem der Ansprüche 3 bis 6, wobei die erste Eintrittsvertiefung (32) und die erste Austrittsvertiefung (34) von einer reduzierten Tiefe (P1, P2) sind, die niedriger als eine wesentliche Tiefe (P3, P4) der zweiten Eintrittsvertiefung (46) und der zweiten Austrittsvertiefung (48) sind.
  8. Wärmetauscher (10) nach Anspruch 7, wobei die reduzierte Tiefe (P1, P2) der ersten Eintrittsvertiefung (32) und die erste Eintrittsvertiefung (34) niedriger als 1 mm, vorzugsweise niedriger als 0,5 mm ist.
  9. Wärmetauscher (10) nach Anspruch 7 oder 8, wobei die wesentliche Tiefe (P3, P4) der zweiten Eintrittsvertiefung (46) und die zweite Eintrittsvertiefung (48) niedriger als 10 mm, vorzugsweise niedriger als 8 mm ist.
  10. Wärmetauscher (10) nach einem der vorhergehenden Ansprüche, wobei der Austrittskanal (26) ein erstes Ende (74), das in den Tauscherkörper (14) mündet, und ein zweites Ende (76) aufweist, das außerhalb des Tauscherkörpers (14) mündet, und dadurch, dass der Austrittskanal (26) einen hydraulischen Durchmesser (Dh) im gesamten Zwischenbereich zwischen dem ersten Ende (74) und dem zweiten Ende (76) aufweist, der zwischen einem ersten Wert des hydraulischen Durchmessers (Dh1) an dem ersten Ende (74) des Austrittskanals (26) und einem zweiten Wert des hydraulischen Durchmessers (Dh2) an dem zweiten Ende (76) des Austrittskanals (26) inbegriffen ist.
  11. Wärmetauscher (10) nach Anspruch 10, wobei der Wert des hydraulischen Durchmessers (Dh) des Austrittskanals (26) von dem ersten Wert des hydraulischen Durchmessers (Dh1) an dem ersten Ende (74) des Austrittskanals (26) bis zu dem zweiten Wert des hydraulischen Durchmessers (Dh2) an dem zweiten Ende (76) des Austrittskanals (26) zunimmt.
  12. Wärmetauscher (10) nach Anspruch 11, wobei der erste Wert des hydraulischen Durchmessers (Dh1) zwischen 10,5 mm und 11 mm, vorzugsweise 10,8 mm beträgt.
  13. Wärmetauscher (10) nach Anspruch 11 oder 13, wobei der zweite Wert des hydraulischen Durchmessers (Dh2) zwischen 15 mm und 16 mm, vorzugsweise 15,6 mm beträgt.
  14. Wärmetauscher (10) nach einem der vorhergehenden Ansprüche, wobei der Austrittskanal (26) eine innere Länge (Ls), in einer Zusammenbauebene der Endplatte (20) und der Abdeckung (22) betrachtet, aufweist, die größer als eine innere Breite (Le) des Eintrittskanals (24), in der gleichen Zusammenbauebene betrachtet, ist.
  15. Wärmetauscher (10) nach Anspruch 14, wobei die innere Breite (Ls) des Austrittskanals (26) zwischen 14,5 mm und 16,8, vorzugsweise etwa 16 mm beträgt.
  16. Wärmetauscher (10) nach einem der vorhergehenden Ansprüche, wobei die Innenrohre aus einer Anordnung von Platten (12) gebildet sind.
  17. Wärmetauscher (10) nach Anspruch 16, wobei ein vertiefter Behälter (40) zwischen der Endplatte (20) und einer benachbarten Platte (12) des Tauscherkörpers (14) gegenüberliegend von der Abdeckung (22) angeordnet ist, um eine Fluidkommunikation mit dem Eintrittskanal (24) und dem Austrittskanal (26) zu gewährleisten.
EP11771201.8A 2010-10-25 2011-10-21 Wärmetauscher mit seitlicher flüssigkeitszufuhr Active EP2633255B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1004183A FR2966581B1 (fr) 2010-10-25 2010-10-25 Echangeur de chaleur avec alimentation en fluide laterale
PCT/EP2011/068472 WO2012055790A1 (fr) 2010-10-25 2011-10-21 Echangeur de chaleur avec alimentation en fluide latérale.

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EP2633255B1 true EP2633255B1 (de) 2018-09-12

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FR3018601B1 (fr) * 2014-03-12 2018-04-27 Valeo Systemes Thermiques Dispositif de connexion pour echangeur de chaleur et echangeur de chaleur equipe dudit dispositif de connexion
JP6358848B2 (ja) * 2014-05-15 2018-07-18 株式会社ケーヒン・サーマル・テクノロジー エバポレータ
US10906380B2 (en) * 2016-03-11 2021-02-02 Marelli Cabin Comfort Japan Corporation Evaporator with cold storage function

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JPH06331297A (ja) * 1993-05-20 1994-11-29 Zexel Corp 熱交換器
JPH0933187A (ja) * 1995-07-19 1997-02-07 Showa Alum Corp 積層型熱交換器
JPH10288475A (ja) * 1997-04-15 1998-10-27 Zexel Corp 積層型熱交換器
JP2001021286A (ja) * 1999-07-08 2001-01-26 Zexel Valeo Climate Control Corp 熱交換器
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EP2633255A1 (de) 2013-09-04
JP2013540252A (ja) 2013-10-31
JP5887352B2 (ja) 2016-03-16
FR2966581B1 (fr) 2014-12-26
WO2012055790A1 (fr) 2012-05-03
US20130312942A1 (en) 2013-11-28
US9829255B2 (en) 2017-11-28
FR2966581A1 (fr) 2012-04-27
MX2013004612A (es) 2013-07-03
MX353963B (es) 2018-02-06

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