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
  • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
  • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with 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
  • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
  • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
  • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow 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
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
  • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
  • F28D9/0056—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the 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
  • F28D2021/0082—Charged air coolers

Definitions

• Stacked plate charge air coolers are known, as mentioned above, in which each plate guides the cooling liquid in a circuit forming several passes of identical section and inside which the coolant circulates according to a orthogonal direction to the supercharging air flow. Between each pass, the coolant changes direction of flow. While traveling through the circuit, the temperature of the coolant increases, which causes a variation of its physical properties (in particular its density, its viscosity). However, when the physical properties of the coolant change, the pressure drop also changes. In existing solutions, the widths of the passes are identical within the same circuit and does not adapt to the evolution of the pressure losses mentioned above, which has the effect of degrading the performance of the exchanger.
• the pressure losses can indeed contribute positively to the heat efficiency of the exchanger because it is known that the greater the pressure loss, the more the flow flow can be turbulent mode, which is favorable to heat exchange, at least to a certain extent.
• the pumps used for the circulation of coolant have limited characteristics, in order to avoid too much penalize the energy consumption taken from the engine of the vehicle.
• the invention thus relates to a plate intended to allow a heat exchange between a first and a second fluid flowing in contact with the plate, said plate being configured to define a circuit comprising several successive passes in which the first fluid flows in one direction. flow by changing flow direction from one pass to another, each of the passes having a passage section of the first fluid.
• the passage section of a pass is larger than the passage section of another pass, called downstream, located downstream of the upstream pass in the direction of flow of the first fluid. in the circuit.
• the first fluid circulates through passes whose passage section decreases which has the effect of accompanying the change in pressure losses due to the increase in temperature.
• the coefficient of pressure loss can then be kept relatively constant along the circuit.
• the first fluid corresponds to a coolant and the second fluid corresponds to the charge air.
• said plate comprises an initial pass and a final pass and the pass passage sections decrease by one pass. the other since the initial pass to the final pass. They decrease, for example, linearly or proportionally.
• the passage section of the initial pass is between 40 and 60% larger than the passage section of the final pass.
• said plate comprises four passes, said first pass, second pass, third pass and fourth pass, the first pass being connected to an input of the circuit, the second pass being connected to the first pass, the third pass being connected to the second pass and the fourth pass being connected on the one hand to the third pass and on the other hand to an output of the circuit.
• the passage section then decreases from the first pass until the fourth pass.
• the passage section of the first pass is between 5 and 15% larger than the passage section of the second pass.
• the passage section of the second pass is between 20 and 40% larger than the passage section of the third pass.
• the passage section of the third pass is between 5 and 15% larger than the passage section of the fourth pass.
• the distance between edges defining the first pass is between 30 and 35 mm
• the distance between edges defining the second pass is between 27 and 32 mm
• the distance between edges defining the third pass is between between 22 and 25 mm and / or the distance between edges defining the fourth pass is between 20 and 23 mm.
• the borders defining a pass are, in particular, parallel to each other so that the passage section of a pass is constant.
• the passage section is measured in a plane perpendicular to an extension plane of the plate.
• the passes comprise disruptors of the fluid flow.
• the invention also relates to a heat exchanger, in particular intended for a motor vehicle, comprising plates as defined above, at least two of said plates being stacked one on the other in a pair of plates so that the circuit one of the two plates mirrors the circuit of the other of the two plates. It is understood here that two plates forming a pair of plates are stacked one on the other so that their circuit together form a circulation channel of the first fluid.
• FIG. 1 is a perspective view exploding exploded heat exchanger according to the invention comprising four-pass plates;
• FIG. 2 is a top view of a plate comprising four passes, for identifying the differences of sections of passages of the different passes according to the invention.
• the invention relates to a heat exchanger 1 allowing a heat exchange between a fluid to be cooled, in particular a gas G, and a coolant C. It could be a cooler of supercharging air in which a flow of compressed air for supplying a heat engine, for example a motor vehicle engine, is cooled by a coolant, especially a mixture of water and glycol.
• the exchanger 1 comprises a heat exchange beam 2 consisting of a stack of plates 4 between them determining alternating circuits 6, 8 for the fluid to be cooled and for the cooling liquid.
• the beam here is of generally parallelepipedal shape and has an exit face 10 and a face opposite inlet, not visible, the fluid to be cooled. It is completed on both sides of the stack of a plate, said upper, 12 and a plate, said lower, 14.
• the exchanger 1 may also include a housing 5 in which the beam 2 is located. It guides the fluid to be cooled between the plates of the inlet face to the exit face 10 of the bundle 2. It consists here of two lateral walls 18, each coming against the edges 16, 16 'of the side plates 4, 12 14, of an upper wall 20, coming into contact with the upper plate 12 and a lower wall 22, coming into contact with the lower plate 14.
• the upper wall 20 may be provided with orifices 24, 26 allowing the passage, at the outlet and at the inlet, of the coolant C in the bundle 2.
• the exchanger 1 may further comprise nozzles 28, 30 for outlet and / or inlet of the cooling liquid communicating with said orifices 24, 26 provided in the housing.
• the various components of the exchanger are, for example, aluminum or aluminum alloy. They are, in particular, soldered to each other.
• Each plate 4, 12, 14 comprises, for example, a bottom 31, substantially plane, surrounded by a peripheral edge 32 terminated by a flat portion 34, for brazing the plates together.
• the coolant circuit 8 is defined, on the one hand, by said peripheral rim 32 and, on the other hand, by one or more edges 60, 60 ', for example made from material of the bottom 31 of the plate.
• the plates 4, 12, 14 are grouped in pairs and assembled by their flats 34 and / or the edges 60, 60 '.
• the circuit of an upper plate 4 and a lower plate 4 of the same pair of plates complement each other to form a circulation channel for the coolant C.
• the plates 4 are stacked in pairs so that the coolant circuit C 8 of one of the two plates is vis-à-vis the coolant circuit 8 C of the other of the two plates of the same pair to form the circulation channel coolant C.
• Circuits 6 for circulation fluid to be cooled are provided between two plates 4 vis-à-vis two pairs of adjacent plates 4.
• top 12 and bottom 14 plates of the stack are assembled with the top and bottom walls 22 of the housing to define a coolant flow channel.
• the plates 4, 12, 14 have, for example, the general shape of an elongated rectangle having two long sides and two short sides, each plate having two bosses 38, a first of the bosses 38 having an inlet 42 of the circulation channel 8 coolant C and the other bosses 38 having an outlet 40 of the coolant circulation channel C.
• the bosses 38 are located along the same small side of the plate 4, 12, 14. They are here pierced with a hole 50 for the passage of coolant C and are intended to come into contact with the bosses 38 of the an adjacent plate 4 for respectively forming an inlet manifold 44, and an outlet manifold, not visible, for the coolant C.
• the inlet manifold 44 opens, for example, into the inlet manifold 30 through the inlet port 26 of the housing and / or the outlet manifold opens, for example, into the outlet pipe 28 through the outlet 24 of the housing.
• the cooling fluid enters the beam through the inlet pipe 30 and is distributed between the plates 4 in the circuits 8 for circulating coolant through the inlet manifold 44. It flows into the circuits 8 flow of coolant C from their inputs 42 to their outputs 40 where it enters the outlet manifold. It then leaves the exchanger through the outlet pipe 30.
• the bosses 38 of two pairs of plates 4 between them determine the height of the circulating circuits 6 for the fluid to be cooled.
• An inlet manifold and an outlet manifold may be adapted to the periphery of the housing to bring and evacuate the fluid to be cooled.
• the exchanger may also comprise secondary exchange surfaces, for example corrugated disturbers reported between the plates 4 in the circulation circuits 6 of the fluid to be cooled G. These disrupters can disrupt the flow of the fluid to be cooled G to improve the heat exchange between the two fluids.
• Each plate 4, 12, 14 for example comprises corrugations 52 arranged in the circuits 8 for circulating coolant C. These corrugations 52 extend between the pockets 38 constituting the inlet manifold and the outlet manifold 44 of the liquid C and the second longitudinal end of the plates 4, 12, 14.
• the corrugations 52 are, for example, derived from the bottom material 31 of the plates 4, 12, 14, in particular by stamping the plates 4, 12, 14.
• the circuit 8 defined by the plates 4, 12, 14 makes it possible to guide the cooling liquid C in a number n of successive passes, here four, in which the liquid flows between the inlet 42 and the outlet 40 of the circuit 8. Two adjacent passes are separated, for example, by the borders 32, 60, 60 'of the plates 4, 12, 14.
• the passes are arranged parallel to each other in an extension direction, here the long side of the plates. They may be provided in series one after the other.
• the borders 60, 60 ' are thus oriented along the long side of the plates 4 to define a cooling coil circulation in each of the passes of each of the circulation circuits 8 of the cooling liquid C.
• Some 60 of the borders extend from the edge 16 provided with the bosses 38 to the opposite edge 16 'while leaving a passage so that the fluid can flow from the pass located from one side of the edge 60 to the other passes. They alternate with borders 60 'extending from the edge 16' opposite that 16 provided with the bosses 38 to the edge 1 6 provided with the bosses 38 while leaving a passage for the fluid to flow from the pass located on one side of the edge 60 'to another.
• first pass 71 or initial pass 71, extending from the inlet 40 to the edge 16 'opposite to that 1 6 provided with bosses 38; a second pass 72 connected to the first and extending from the edge 1 'opposed to the edge 16 provided with the bosses 38 to the edge 1 6 provided with the bosses 38; a third pass 73 connected to the second pass and extending from the edge 1 6 provided with the bosses 38 to the edge 1 6 'opposite that 1 6 provided with the bosses 38; and a fourth pass 74 connected on the one hand to the third pass 73 and on the other hand to the outlet 42 so that it extends from the edge 16 'opposite the edge 16 provided with the bosses 38 to the edge 1 6 provided with the bosses 38.
• a plate according to the invention is shown in Figure 2.
• Such a plate has a length L in the direction of extension of the passes and a width I in a direction D orthogonal to the direction of extension of the passes.
• the direction D thus corresponds to the direction of flow of the fluid to be cooled.
• each pass has a width In corresponding to the distance along the direction D between two edges 32, 60, 60 'defining this pass.
• the first pass 71 has a width 11, the second passes 72 a width 12, the third passes a width 13 and the fourth passes 74 a width 14.
• the passage section of a pass is larger than the passage section of another pass, called downstream, located downstream of the upstream pass in the direction of flow of the liquid of cooling in the circuit 8 for circulation of the coolant.
• the section of passage of a pass is defined by its width multiplied by the height of the borders 32, 60, 60 'which define it.
• the borders 32, 60, 60 ' being here substantially parallel to each other and of identical height, the comparison of the widths of passes is equivalent in the following description to a comparison of the passage sections of each pass.
• the width of the first pass 71 is between 5 and 15% larger than the width 1 2 of the second pass 72.
• the width l 2 of the second pass is here between 20 and 40% greater than the width l 3 of the third pass 73.
• the width l 3 of the third pass 73 is for example between 5 and 15% greater than the width l 4 of the fourth pass 74.
• the width of the initial pass, here the first pass 71, is between 40 and 60% greater than the width of the final pass, here the fourth pass 74.
• the plate width I of the plate 4, 12, 14 is, in particular, equal to 120 mm and its length L is, for example, equal to 200 mm.
• the width of the first pass 71 is in particular between 30 and 35 mm
• the width 1 2 of the second pass 72 is, for example, between 27 and 32 mm
• the width l 3 of the third pass 73 is in particular between 22 and 25 mm
• the width l 4 of the fourth pass 74 is advantageously between 20 and 23 mm.

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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)

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• 2011
  • 2011-10-04 FR FR1158951A patent/FR2980840A1/fr not_active Withdrawn
• 2012
  • 2012-10-02 EP EP12769647.4A patent/EP2764314A1/de not_active Withdrawn
  • 2012-10-02 US US14/349,474 patent/US20140246179A1/en not_active Abandoned
  • 2012-10-02 KR KR1020147011761A patent/KR20140089529A/ko not_active Application Discontinuation
  • 2012-10-02 CN CN201280059742.0A patent/CN103988042A/zh active Pending
  • 2012-10-02 WO PCT/EP2012/069504 patent/WO2013050396A1/fr active Application Filing

Non-Patent Citations (1)

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