Classifications

• • 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
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/00492—Heating, cooling or ventilating [HVAC] devices comprising regenerative heating or cooling means, e.g. heat accumulators
  • B60H1/005—Regenerative cooling means, e.g. cold accumulators
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
  • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
  • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
  • B60H1/00885—Controlling the flow of heating or cooling liquid, e.g. valves or pumps
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/32—Cooling devices
  • B60H1/3204—Cooling devices using compression
  • B60H1/3205—Control means therefor
  • B60H1/322—Control means therefor for improving the stop or idling operation of the engine
• • 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
• • 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
  • 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
  • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
• • 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
  • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
  • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
• • 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
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
  • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
  • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
  • B60H2001/00928—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising a secondary circuit
• • 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
  • 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
  • F28D2021/0091—Radiators
  • F28D2021/0096—Radiators for space heating
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
  • Y02E60/14—Thermal energy storage

Definitions

• the invention relates to a heat exchanger suitable for being part of a heating, ventilation and / or air conditioning device, in particular for a motor vehicle, comprising a multiplicity of modules stacked in a first direction. , connected to an inlet pipe and to an outlet pipe for a first fluid and suitable for circulating said first fluid.
• the heat exchanger can be, for example, an air conditioning evaporator through which a refrigerant fluid flows in order to cool the air flow and produce refrigerated air which is sent to the passenger compartment of the vehicle.
• the heat exchanger can also be a heating radiator through which a hot fluid, usually the coolant of the vehicle engine, in order to heat the air flow and produce hot air which is sent in 1 / abitacle.
• the refrigerant passes, in this order, through a compressor, a condenser, an expansion valve and an evaporator, before returning to the compressor.
• the refrigerant passed from a liquid phase or from a liquid / vapor phase to a vapor phase by receiving heat from the air flow which is thus cooled.
• a refrigerant fluid consisting of a fluorinated hydrocarbon such as that known under the designation R 134 A.
• a disadvantage of known evaporators is that their ability to • cool the air flow depends on the operation of the compressor. In other words, the air flow is no longer cooled as soon as the compressor is stopped.
• the compressor is driven by the engine and is therefore put out of operation as soon as the engine is stopped.
• the object of the invention is in particular to overcome the abovementioned drawbacks by proposing means for accumulating either - cold (by consequently yielding 'heat), or on the contrary heat, when the engine ' of the ' vehicle is running and to restore this cold or this heat in the passenger compartment when the engine is stopped.
• the invention relates in particular to a heat exchanger of the type defined in the introduction, and provides that said modules comprise two distinct series of channels suitable for receiving said first fluid and a second fluid, the second fluid being conveyed by at least a third tube.
• One of the first and second fluids is stationary in said channels, the exchanger exercising a static storage function.
• the first and second fluids circulate in said channels, the exchanger exercising a dynamic storage function.
• the first and second channels of each tube are disposed respectively on either side of an intermediate partition extending substantially perpendicular to the direction of alignment of the tubes.
• the second channels have in said direction a thickness between 1 and 5 mm.
• the tubes are connected at one of their ends to a manifold delimiting chambers for the first and second heat transfer fluids, two subsets of the first channels of the same tube opening into two different chambers and communicating with each other at the opposite end of the tube, and two subset of the second channels of the same tube also opening into two different chambers and communicating with each other at the opposite end of the tube, so as to define U-shaped paths between the respective chambers for the first and second fluids.
• the manifold comprises a profiled part having longitudinal conduits which define said chambers.
• At least one of said conduits is divided by at least one transverse partition into at least two chambers so as to define a route for the first fluid in at least four passes through the heat exchanger.
• the profiled part has first and second conduits defining the chambers which communicate with the first channels, and a third conduit disposed between them, an inlet orifice and an outlet orifice for the first fluid, arranged at a first - end of ' the manifold, communicating one with the first conduit and the other with the third conduit, and one of the first and second conduits communicating with the third conduit in the vicinity of the second end of the manifold.
• the heat exchanger comprises a multiplicity of modules stacked in a first direction, each formed of three mutually joined plates, namely a first plate facing a first end of the stack, a second plate facing the second end of the stack and a third intermediate plate, the plates each extending, substantially along the same contour, in second and third directions substantially perpendicular to each other and perpendicular to the first direction, the modules being spaced from each other, in at least a middle region, so as to define therebetween intervals for the passage of an air flow in the third direction, and the plates being stamped so as to define in each module, assages for the circulation of the first and second fluids heat transfer fluids in the second direction, respectively on either side of the intermediate plate, and having, in two end regions located on either side of 'said at least one central region, apertures for allowing the different modules to receive the first and second fluids, the plates being interconnected so tight fluids around the openings, as well as at their periphery in each module.
• the passages for the circulation of the second fluid have in the first direction a thickness of between 1 and 5 mm.
• Each plate has, in a first of said end regions, first and second openings for the circulation of the first fluid in both directions respectively, and a third opening for the circulation of the second fluid in a first direction, and, in the second of said end regions, a fourth opening for the circulation of the second fluid in the second direction.
• the third opening is arranged between the first and second openings in the second direction.
• the fourth opening is extended in the second direction.
• the first plate of a module and the third plate of a neighboring module have respective bosses in mutual support in which the first and second corresponding openings are formed, the first and second openings of the second plate of said neighboring module being traversed by sealingly by the bosses of said third plate.
• the third opening of the first plate of a module is adjacent to that of the third plate of the same module and that of the second plate of a neighboring module, the latter opening being formed in a boss.
• the first plate of a module and the second plate of a neighboring module have respective bosses in mutual support in which the fourth corresponding openings are formed, the first and third plates of a module being tightly connected in a zone ring surrounding the boss of the first plate and the opening of the third plate.
• the second direction is substantially vertical, said first end region being the upper region and the second fluid flowing from bottom to top.
• the second heat transfer fluid is capable of passing from the liquid state to the solid state when it receives cold from the first heat transfer fluid and vice versa when it restores the cold.
• the second heat transfer fluid has a melting point between 0 and 10 ° C and preferably between 4 and 7 ° C.
• the second heat transfer fluid has an enthalpy of fusion of at least 150 kJ / kg.
• the second heat transfer fluid is chosen from tetradecane, paraffins, hydrated salts and eutectic mixtures.
• the exchange surface between the first and second fluids in the heat exchanger is between 0.5 and 1.5 m 2 .
• the direct exchange surface in contact with the second fluid in the heat exchanger is between 0.5 and 1.5 m 2 .
• At least part of the spaces provided in the heat exchanger for the circulation of the second fluid in thermal contact with the first fluid and / or with an air flow is lined with a highly porous heat-conducting foam, in particular graphite.
• the invention also relates to the use of a heat exchanger as defined above in a heating, ventilation and / or air conditioning device, in particular for a motor vehicle, comprising at least a first closed loop in which said heat exchanger is traversed by an air flow and in which said first fluid can circulate so as to yield heat or cold to said air flow in the heat exchanger, as well as a second closed loop in which said second fluid can circulate between said heat exchanger and a reservoir so as to receive heat or cold from the first fluid coolant in the heat exchanger to accumulate in the tank and return it to the air flow in one heat exchanger, depending on the heat or cooling produced by the first loop and the processing needs of the air flow.
• the second loop advantageously contains between 200 and 500 g of the second fluid.
• FIG. 1 is a circuit diagram of a device using an evaporator according to the invention for air conditioning the passenger compartment of a motor vehicle.
• Figure 2 is an elevational view of an evaporator according to the invention.
• FIG. 3 is a partial sectional view along the line III-III of FIG. 2.
• Figure 4 is a perspective • longitudinal section of the manifold 1 the evaporator, according to the line IV-IV of Figure 5.
• FIG. 5 is a partial view of the evaporator, in section along the line V-V in FIG. 4.
• Figure 6 is a sectional view of a variant of the manifold of one evaporator, along line VI-VI of • Figure 5.
• Figure 7 is a partial elevational view of another evaporator according to invention.
• FIG. 8 is a partial sectional view along the line VII-VIIl ' of FIG. 7.
• FIG. 9 is a partial sectional view along the line IX-IX in FIG. 7.
• Figures 10 and 11 are partial sectional views along line X-X of Figure 8, respectively of the upper part and the lower part of one evaporator.
• Figures 12 to 14 are front views of the three plates constituting a module of the evaporator of Figures 7 to 11.
• Figure 15 shows a replacement plate
• Figure 16 is a diagram similar to Figure 1 relating to a variant of the device.
• FIG. 1 shows a motor vehicle air conditioning device.
• This device conventionally comprises a loop of refrigerant BF in which the fluid successively passes through a compressor BF1, a condenser BF2, a reservoir or “bottle” BF3, a regulator BF4 and an evaporator BF5 having to return to the compressor.
• the device also comprises a heating loop BC in which the coolant of the driving motor M of the vehicle circulates under the action of a pump BCl, driven by the motor M, the loop BC further containing a heating radiator BC2 and BC3 solenoid valves suitable for controlling the flow of fluid in this radiator.
• An air flow represented by the arrow F successively passes through the evaporator BF5 and the radiator BC2 to be brought to a desired temperature before being introduced into the passenger compartment of the vehicle.
• the evaporator BF5 is also part of a BS loop which contains. in addition to an electric circulation pump BSl and a fluid accumulation tank BS2.
• the loop BS contains a heat transfer fluid which is capable of exchanging heat with the refrigerant fluid and with the air flow F in one evaporator BF5.
• the pump BS1 is stopped and the fluid does not circulate in the loop BS. Only the small amount of this fluid contained in the BF5 evaporator is cooled by the refrigerant, allowing rapid warming up of the evaporator.
• the pump BSl is started, so that cooled fluid circulates in the loop BS, leading to an accumulation of cold in the tank BS2 . If the engine and therefore the compressor BF1 stop, the circulation of the fluid in the loop BS continues under the action of the pump BSl, and this fluid takes over from the refrigerant to cool the air flow F by taking cold from the tank BS2.
• FIG. 2 represents an evaporator 10 according to the invention which can constitute the evaporator BF5 of FIG. 1.
• This evaporator comprises a bundle 12 formed of a multiplicity of parallel tubes 14 which alternate with corrugated spacers 16 providing surfaces of heat exchange.
• the bundle 12 is interposed between two manifolds, namely a manifold 18 placed here ' in the upper part and a manifold 20 placed here in the lower part.
• the manifold 18 is provided with an inlet pipe 22 for the coolant in the liquid phase or in the liquid / vapor phase and with an outlet pipe 24 for the coolant in the gas phase.
• the coolant enters the tube 22 as shown by the arrow F1 and exits the tube 24 as shown by the arrow F2 after having exchanged heat with an air flow which sweeps the beam 12 as shown by the arrows F on Figure 2.
• the tubes 14 have circulation channels for the refrigerant which thus exchanges heat with the air flow.
• the - refrigerant in liquid phase or in liquid / vapor phase is transformed into vapor phase by absorbing heat., This mistletoe allows to cool the air flow.
• the tubes 14 of the invention differ from the tubes of conventional evaporators in that they offer a dual function, namely to allow the circulation of the coolant, but also, according to one embodiment of the invention, the circulation fluid from the loop BS which is then a heat transfer fluid.
• the tube 14 is composed of two plate-shaped parts, namely a first part 26 in which are formed channels 28 for the circulation of the coolant and a second part 30 in which are formed channels 32 for the circulation of the heat transfer fluid.
• the plate 26 is produced by extruding a metallic material, preferably aluminum or an aluminum-based alloy.
• the part or plate 26 comprises a row of channels 28 each having a section of substantially rectangular shape and it is delimited by two large parallel faces.
• the plate 30 is also formed by extrusion of a similar metallic material and it comprises a row of channels 32 each having a generally rectangular cross section, except for the channels adjacent to the lateral edges of the plate 30.
• This plate 30 is delimited by two large parallel faces.
• One of the large faces of the plate 26 is connected to one of the large faces of the plate 30, for example by brazing to form an integral assembly.
• the corrugated spacers 16 are advantageously formed from the same metallic material as the plates.
• the channels 28 have internal dimensions and wall thicknesses chosen taking into account the nature and operating pressures of the refrigerant used.
• the channels 28 have a hydraulic diameter generally between 1 and 2 mm, the burst pressures should be around 36 bars.
• the channels will generally have dimensions between 0.5 and 1 mm, the burst pressures having to be around 250 bars.
• the channels 32 are intended for the circulation of the thermal accumulation fluid.
• the section of the channels 32 can have a height of the order of 3 mm for a width of the order of 1 mm, these dimensions being of course subject to variations. These dimensions and the thicknesses of the walls surrounding the channels 32 are selected 'taking also into account the constraints of pressure.
• the pressures of the heat transfer fluid are relatively low, generally less than 5 bars. The total amount of heat transfer fluid depends on the thermal energy (cold) that one seeks to transfer to the air flow to be sent into the passenger compartment.
• the manifold 18 comprises a profiled part 38 and a manifold plate 40 formed by the superposition of several plates delimiting openings or circulation passages.
• the profiled part 38 has an elongated shape and internally delimits three ducts parallel to the coolant.
• a conduit 42 extending along one side of the profiled part is divided by an attached partition 44 to form an inlet compartment 46 and an intermediate compartment 48. Opposite the conduit 42 is a conduit 50 forming a circulation compartment.
• Another conduit 52 placed between ' the conduits 42' and 50 forms an intermediate compartment.
• the inlet manifold 22 communicates as with the compartment 46, while the outlet tubing 24 communicates with the compartment 52.
• the compartment 42 and the compartment 52 are closed by a plug 54 at the end of the part 38 opposite the tubes 22 and 24, while the compartment 50 is closed at its two ends by plugs 56.
• the manifold 20 is formed by a stack of plates which delimit suitable passages (not shown) to communicate all the channels 28 on the one hand and all the channels 32 on the other hand of the same tube.
• the aforementioned passages of the collector plate 40 cooperate with passages of the profiled part 38 to establish an appropriate communication between the compartments 46, 48, 50 and the conduits 60 of the box 18 on the one hand and the channels 28 and 32 tubes on the other hand.
• the refrigerant circulates in four passes inside the evaporator. It first enters the compartment 46 to then gain the compartment 50 by borrowing the channels 28 twice (passes 1 and 2) then is conveyed to the compartment 48 by borrowing the channels 28 twice (passes 3 and 4) . From there, the fluid reaches the compartment 52 through an opening 58 formed in the partition which separates the conduits 42 and 52, in the vicinity of the plug 54. The fluid then gains the outlet 24.
• the profiled part 38 of the manifold delimits two longitudinal conduits 60 which communicate by passages 62 with the channels 32 of the tubes 14.
• the two conduits 60 make it possible to establish a communication between the channels 32 of the different tubes.
• the conduits 60 are closed at one end of the manifold and open at the other end to communicate with the rest of a secondary cold accumulation loop such as the BS loop of the figure 1.
• the manifold shown in Figure 6 differs from that of Figure 4 in two ways.
• each of -conduits, latéraux- '70, .72' - for the coolant which communicate with the channels 28 of the tubes through openings 74 is longitudinally divided by a partition 76, 78, these two partitions being offset relative to each other in the longitudinal direction of the box, from which it results in known manner, in the example of Figure 6, a ' circulation of the fluid in 6 passes instead of 4
• the median conduit 82 which is connected to the fluid inlet tubing 82, the lateral conduit 70 being connected to the outlet tubing 84, while the other lateral conduit 72 is connected to the median conduit 80 through a communication opening 86.
• conduits 88 for the fluid • accumulation similar to conduits 60 of Figure 5, which communicate with the channels 32 of the tubes through openings 90.
• These channels communicate with inlet pipes and outlet 91 at their end situated to the left of the figure, that is to say on the side of the pipes 82 and 84, and are closed by plugs 92 at the opposite end, that is to say on the side plug 94 common to conduits 72 and 80.
• FIG. 7 to 11 show an evaporator of different construction from those of Figures 2 to 6, also usable in the device of Figure 1.
• This evaporator comprises a stack of modules 100 each formed from three stamped plates.
• the partial elevational view of FIG. 7 shows some of the modules 100, those closest to the right end of the stack which carries the inlet and outlet pipes 101, 102 for the refrigerant, connected to a member expansion valve, for example a regulator 103 in the illustrated embodiment, and the inlet and outlet pipes 104, 105 for the thermal storage fluid.
• the -modules 100 are in mutual contact.
• each module has the same substantially rectangular outline, 'and each have a peripheral edge 111 situated in a plane perpendicular to the stacking direction, c that is, the left-right direction in Figure 7.
• the plates 108, 110 and 109 shown separately in Figures 12 to 14 respectively, are arranged in this order from left to right of Figures 7 to 11.
• the peripheral edges 111 of the three plates are mutually joined and tightly brazed to fluids.
• the outlet pipe 105 of the accumulation fluid is connected to the upper end region of the modules, at half the width of the latter, while the inlet and outlet pipes 101, 102 of the coolant are connected in the same upper region, laterally on either side of the pipe 105. It is advantageous that the inlet and outlet pipes 104, 105 of the " accumulation fluid " are located respectively at the lower part and at the upper part of the exchanger so as to eliminate the residual gases.
• each of the pipes 101 and 102, the plate 108 of a module and the plate 110 of the neighboring module are stamped to form respective bosses 112, 113 whose plane vertices 114, 115 are in mutual support and are pierced with open-. res 116, 117 in coincidence.
• the flat vertices 114, 115 are tightly brazed together around the openings 116, 117 'so as to form, through the stack, longitudinal conduits 118, 119. connected respectively to the pipes 101 and 102 ..
• Opposite the tubing 104 for entering the accumulation fluid as can be seen more particularly in FIG.
• the plate 108 of a module and the plate 109 of a neighboring module have respective bosses 120, 121 of which the flat vertices 122, 123 are applied one against the other and are pierced with coincident openings 124, 125 around which they are brazed together in a fluid-tight manner.
• These bosses define a longitudinal duct 126 in communication with the pipe 104, openings 127 being formed in the plates 110 to ensure the continuity of this duct.
• the plates 108 and 110 of each module extend in the planes of their respective peripheral edges 111, and the plate 109 of a module has a boss 128, the flat top 129 of which bears on the plate 110 of the neighboring module, the top 129 and the plates 108 and 110 having respective coincident openings 130, 131 and 132 around which they are brazed together fluid tight.
• the bosses 128 delimit a longitudinal duct 133 communicating with the pipe 105. In the middle region of the height of the modules, as can be seen in FIGS.
• the plates 108 and 110 generally extend in planes parallel to the planes from their peripheral edges 111, and spaced from one another. However, these plates are brazed together in a sealed manner in a zone 134 (FIG. 11) situated immediately above the duct 126 and extending over the entire width of the module, up to the vertical sides of the edges 111, and also along a vertical center line corresponding to the ridges of respective ribs 140 (FIG. 9) formed by stamping, which connects to the upper sides of the peripheral edges 111 and extends up to a certain distance above the area 134.
• a zone 134 (FIG. 11) situated immediately above the duct 126 and extending over the entire width of the module, up to the vertical sides of the edges 111, and also along a vertical center line corresponding to the ridges of respective ribs 140 (FIG. 9) formed by stamping, which connects to the upper sides of the peripheral edges 111 and extends up to a certain distance above the area 134.
• the plates 108 and 110 define - therefore between them a U-shaped path between the conduits 118 and 119, the branches 137, 138 of which are located on either side other ribs 140 and are connected to each other between the lower end thereof and the zone 134.
• the bosses 120, 121 and the associated openings are advantageously elongated horizontally and can extend over the almost the entire width of one evaporator.
• each module extends, over its entire surface area with the exception of the peripheral edge 111 and the bosses 121 and 128, along a plane parallel to the plane of its peripheral edge, and spaced from the plate 110.
• the bosses 121 and 128 are formed from this planar part 135, and the bosses 113 pass through air-tight openings 136 formed therein.
• the flat part 135 defines with the plate 110 a space 139 allowing a vertical path from bottom to top for the accumulation fluid from the conduit 126 to the conduit 133, allowing this fluid to circulate without emission of noise due to degassing and without problem of oil retention.
• a spacer can be provided in space 139 to promote heat exchange.
• Figure 15 shows a plate 109a which can be used as a replacement for plate 109 in the stack of Figures 7 to 11, without other changes.
• the elements of this plate similar to the corresponding elements of the plate 109 are designated by the same reference signs.
• the plate 109a differs from the plate 109 by the presence of two ribs formed by stamping from the flat part 135 and the vertices of which are brazed in a sealed manner to the plate 110 of the same module.
• a first rib has a horizontal region 143 which connects to the peripheral edge 111 on one of the vertical sides of the plate (on the right in the figure), immediately below the openings 136, followed by an elbow 144 and a vertical region 145 which extends down to the vicinity of the boss 121.
• the second rib has a region 146 which extends substantially horizontally and connects to the peripheral edge 111 on the opposite side of the plate (on the left on the figure), immediately above the boss 121, followed by an elbow 147 and a vertical region 148 which extends upwards to the vicinity of the openings 136.
• the lower end of the region 145 and the upper end of the region 148 are located opposite the regions 146 and 143 respectively.
• the ribs 143-148 delimit with the peripheral edge 111 an S-shaped path for the second fluid comprising from the conduit 126 a first branch, ascending between the right side of the plate and the rib 146-148, a second descending branch between the two ribs and a third ascending branch r between the left side of the plate and the rib 143-145 and leading to the conduit 133, the regions 145 and 148 being arranged so that these three branches are substantially the same width. Furthermore, the region 146 widens upwards towards the left side of the plate so as to form a rounding at the transition between the second and third branches of the path.
• exchanger described can be used both with a static storage fluid and with a circulating storage fluid.
• the number of passes into an evaporator according to the invention can be other than 4 and 6, and may be any even number 2n, n being a number 'any integer.
• the thermal storage fluid described above as a heat transfer fluid, can also be a fluid with change of phase, that is to say a fluid whose . melting point is between 0 ° C and 10 ° C.
• the phase change fluid can consist of water, but this has the drawback that this water expands when it goes from the liquid state to the solid state and that it can generate icing phenomena.
• phase change fluids whose melting temperature is between 4 ° C and 7 ° C.
• materials from the paraffin family especially exemplary 'one designated under the trade name of the RT5 RUBITHERM society.
• An advantageous material is a paraffin having a density equal to 0.8. It is preferred to use phase change materials having a transformation enthalpy greater than or equal to 150 kJ / kg.
• the melting temperature will be greater than 0 ° C in order to avoid icing problems and above all not to penalize the thermodynamic cycle too much by too low a low pressure.
• the melting temperature will preferably be less than 10 ° C to allow obtaining, by recovery of the accumulated energy, sufficiently low temperatures to meet the constraints, comfort.
• the total quantity of heat-transfer fluid contained in the loop BS of FIG. 1 depends on the thermal energy which one seeks to transfer to the air flow F during the periods of stopping of the engine M. Studies have shown that the duration of these periods is, in most cases, less than 30 seconds. If you want to bring the air from 25 ° C and 40% relative humidity upstream of the evaporator to 10 ° C and .100% relative humidity downstream of the evaporator, the calorific power required for a flow 350 kg / h is approximately 1500, an energy of 45,000 J to be transferred in 30 seconds. This energy is provided by fusion 300 g of phase change material having a melting enthalpy of 150 kj / kg. Generally, the amount of phase change material can be between 200 and 500 g.
• the heat exchange surface between the refrigerant and the phase change material, and between the phase change material and the air flow, provided for example by the inserts 16 and 107 described above, is advantageously between 0.5 and 1.5 m 2 .
• FIG. 16 the same elements as in FIG. 1, designated by the same references, except that the letter "f" is added after the letter "S" in the reference of the cold accumulation loop, which becomes BSf, and in those of the components of this loop.
• the device of FIG. 16 differs from that of FIG. 1 by the addition of a heat accumulation loop BSc associated with the radiator BC2 and analogous to the loop BSf, therefore therefore comprising, in addition to the radiator, an electric circulation pump.
• BScl and an accumulation tank BSc2 for a heat transfer fluid which is capable of exchanging heat with the cooling fluid and with the air flow F in the radiator BC2.
• the invention could also not use a cold accumulation loop associated with an evaporator, and use only a heat accumulation loop associated with a radiator such as BC2.

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• 2003
  • 2003-10-21 FR FR0312291A patent/FR2861166B1/fr not_active Expired - Fee Related
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