EP4609136A1 - Anschlussblock für wärmetauscher und kühlvorrichtung damit - Google Patents

Anschlussblock für wärmetauscher und kühlvorrichtung damit

Info

Publication number
EP4609136A1
EP4609136A1 EP23792967.4A EP23792967A EP4609136A1 EP 4609136 A1 EP4609136 A1 EP 4609136A1 EP 23792967 A EP23792967 A EP 23792967A EP 4609136 A1 EP4609136 A1 EP 4609136A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant fluid
connection block
inlet
outlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23792967.4A
Other languages
English (en)
French (fr)
Inventor
Christophe Denoual
Frederic Tison
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Electrification SAS
Original Assignee
Valeo Systemes Thermiques SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP4609136A1 publication Critical patent/EP4609136A1/de
Pending legal-status Critical Current

Links

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
    • 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
    • F28D9/005—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 the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F28F9/0248—Arrangements for sealing connectors to header boxes
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
    • H01M10/00—Secondary cells; Manufacture thereof
    • H01M10/60—Heating or cooling; Temperature control
    • H01M10/62—Heating or cooling; Temperature control specially adapted for specific applications
    • H01M10/625—Vehicles
    • 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
    • F28D2021/0043—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for fuel cells
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • 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

Definitions

  • Connection block for heat exchanger and cooling device comprising them
  • the present invention relates to the field of thermodynamics and more precisely concerns a connection block for a heat exchanger, and a cooling device including this connection block, intended in particular to be used for cooling the components of a vehicle.
  • a heat transfer liquid such as water
  • a heat transfer liquid circuit passing through these components to be cooled.
  • the heat transfer liquid itself being cooled thanks to a heat exchanger receiving on the one hand the heat transfer liquid, and on the other hand a refrigerant fluid.
  • the refrigerant undergoes a thermodynamic cycle in a separate refrigerant circuit using, for example, a compressor, a condenser, an internal heat exchanger and an expansion member.
  • the thermal power to be dissipated to cool the electric battery is significant, for example of the order of loooo Watts.
  • the thermal power to be dissipated in the electric motor, the power electronics and the electric battery is significant and therefore requires a heat exchanger sized accordingly, called “high performance”.
  • the heat exchanger being formed of a bundle of stacked and brazed plates delimiting circulation channels of the refrigerant fluid or the heat transfer liquid, the number of plates of the heat exchanger of the electric or hybrid vehicle is all the more important as it must dissipate a high thermal power.
  • the thermal power of the electric battery to be dissipated is lower, for example of the order of 4000 Watts.
  • the efficiency of a “high performance” heat exchanger is not optimal at medium or low load, because the number of plates and the dimensioning of the channels of such a heat exchanger have been optimized for use at high load. At medium or low load, the distribution of the liquid and gas phases of the refrigerant fluid in the heat exchanger is therefore not homogeneous and is poorly efficient.
  • the vehicle components to be cooled preferably include the electric battery, the electric motor, the power electronics but also the vehicle interior.
  • connection block configured to tightly connect at least one expansion member to a heat exchanger, the connection block comprising at least:
  • connection block being characterized in that it further comprises:
  • connection block the heat exchanger can be connected to one or more expansion members without specific tubing.
  • connection block has at least as many outlets as expansion members, these outlets being directly arranged on the contact surface with the heat exchanger.
  • the connection block therefore allows the heat exchanger to receive several flows of refrigerant fluid and therefore to distribute them distinctly in one or more bodies of the heat exchanger, in order to improve the distribution, and in particular to reduce the load losses.
  • connection block has two or more ends for connecting the input of the connection block to the receiving means, depending on their arrangement, the reception means being able to include one or more reception rooms.
  • connection block and the heat exchanger are substantially flat, in the sense that it comprises at least one flat surface allowing, by brazing or welding to one side of the heat exchanger, to form watertight connections of 'on the one hand between a high pressure refrigerant fluid outlet arranged on this cheek and the refrigerant fluid inlet of the connection block, and on the other hand between each refrigerant fluid outlet of the connection block and at least one corresponding inlet of the connection block 'heat exchanger.
  • the receiving means, the passages and the branch take the form of recesses in the connection block, in the form of cylinders whose axes are parallel. These axes are preferably orthogonal to the contact surface of the connection block.
  • This production of the reception means, the passages and the branch internal to the connection block is simple to machine. It can in particular be done by drilling in the connection block, advantageously parallelepiped and compact.
  • these recesses are made in the form of straight prisms, with a height orthogonal to the contact surface of the connection block.
  • the receiving means form a first cylindrical recess orthogonal to the contact surface
  • the first passage forms a second cylindrical recess orthogonal to the contact surface
  • the first cylindrical recess joins the second cylindrical recess at a portion of the connection block in which a section of the first cylindrical recess intersects a section of the second cylindrical recess, without completely covering it.
  • This characteristic of the connection block further makes it compact.
  • the reception means form a reception chamber comprising a support surface capable of receiving an inlet of said at least one expansion member and a closed volume capable of receiving a refrigerant fluid at the outlet of said at least one member relaxation, the branch connecting the bearing surface at the refrigerant fluid inlet, the first passage connecting the closed volume to the first refrigerant fluid outlet and the second passage connecting the closed volume to the second refrigerant fluid outlet.
  • the receiving chamber forms at least two watertight connections, one between the inlet of the expansion member and the branch of the connection block, the other between one or more outlets of the expansion member and the first and second passages.
  • said at least one expansion member comprises a first expansion member and a second expansion member
  • the receiving means comprise a first receiving chamber intended to receive the first expansion member and a second receiving chamber intended to receive the second expansion member, and:
  • the first receiving chamber is connected by the branch to the refrigerant fluid inlet, and by the first passage to the first refrigerant fluid outlet, and
  • the second receiving chamber is connected by the branch to the refrigerant fluid inlet, and by the second passage to the second refrigerant fluid outlet.
  • the second receiving chamber comprises a second support surface capable of receiving an inlet of the second expansion member, and a second closed volume capable of receiving a refrigerant fluid at the outlet of the second expansion member, the branch connecting the second surface d support of the second receiving chamber at the refrigerant fluid inlet, and the second passage connecting the second closed volume to the second refrigerant fluid outlet.
  • each receiving chamber is for example formed of three coaxial bores of diameter tapering from a surface opposite the contact surface, the bore of smaller diameter being configured to receive an inlet from a valve. expansion of an expansion member and to form a tight connection between the inlet of the expansion valve and the branch.
  • the shoulder between the smaller diameter bore and the intermediate diameter bore serves, for example, as a bearing surface for the inlet of the extension valve.
  • the inlet of the expansion valve is adjusted closely in the smaller diameter bore or in the branch, so as to achieve this seal.
  • the intermediate diameter drilling is configured to form a closed volume between the part of the expansion member included in the larger diameter drilling and the inlet of the expansion valve, the closed volume forming a tight connection between the outlets of the expansion valve and the first and/or second passages when the expansion member is received in the receiving chamber.
  • the contact surface of the connection block comprises a first groove forming the refrigerant fluid inlet and part of the branch, the branch comprising a first conduit starting from the first groove and opening into the first reception chamber, and a second conduit starting from the first groove and opening into the second reception chamber.
  • This first groove allows efficient distribution of the refrigerant fluid in each receiving chamber of the receiving means.
  • the contact surface comprises a second groove supplying the second refrigerant fluid outlet, configured to connect an inlet mouth of the heat exchanger to a first end of the second passage, the second passage being produced in the form of a cylindrical recess and having a second end opposite the first end and forming an opening into the second receiving chamber.
  • This second groove makes it possible to efficiently bring the refrigerant fluid from the second receiving chamber towards the inlet mouth of the heat exchanger.
  • connection block is brazed or welded to a side of the heat exchanger, an end plate of which opposite the side is itself brazed or welded to the end plate of the internal heat exchanger , the high pressure outlet manifold being connected to a pipe passing through the heat exchanger and serving the refrigerant fluid inlet of the connection block, the low pressure inlet manifold being connected to a refrigerant fluid outlet of the heat exchanger on the end plate, and
  • the heat exchanger includes:
  • a first distribution chamber serving a first body of the heat exchanger, and a first refrigerant fluid inlet opening onto the first distribution chamber
  • the first refrigerant fluid outlet of the connection block being connected to the second refrigerant inlet of the heat exchanger and the second refrigerant outlet of the connection block being connected to the first refrigerant inlet of the heat exchanger.
  • the first refrigerant fluid outlet of the connection block is connected to the first refrigerant fluid inlet of the heat exchanger and the second refrigerant fluid outlet of the connection block is connected to the second refrigerant fluid inlet of the exchanger thermal.
  • the cooling device according to the invention, the distribution of refrigerant fluid is balanced between the first body of the heat exchanger and the second body of the heat exchanger, which homogenizes this distribution and reduces pressure losses.
  • the efficiency of the heat exchanger is improved.
  • the invention makes it possible to use the first body and/or the second body depending on the thermal power to be dissipated.
  • the cooling device according to the invention also has the advantage of being compact.
  • the first body of the heat exchanger comprises for example a first plurality of plates between which are arranged first channels intended to receive a refrigerant fluid
  • the second body of the heat exchanger comprises a second plurality of plates between which are arranged second channels intended to receive the refrigerant fluid
  • the first distribution chamber and the second distribution chamber being capable of supplying in a sealed manner relative to each other respectively a first flow rate of refrigerant fluid to the first channels and a second flow rate of refrigerant fluid to the second channels.
  • the first and second channels respectively of the first and the second body are preferably all of identical sections and lengths, and the first flow rate is preferably substantially equal to the second flow rate.
  • the first flow rate can in fact be different from the second flow rate in particular depending on different pressure losses between the first and second channels, despite an identical structure of the first and second channels.
  • the first and second distribution chambers are arranged around a pipe, the latter passing orthogonally through the plates of the first and the second plurality of plates, and the cooling device comprises a sealing barrier between the first distribution chamber and the second distribution chamber, the sealing barrier forming a angular portion of cylindrical sleeve around the pipe, and having an opening on the side of the heat exchanger.
  • the first and second distribution chambers are at least partly delimited by a first helical spiral and a second helical spiral intertwined with each other around the pipe.
  • the cooling device comprises for example a first sealing barrier between the first distribution chamber and the second body of the heat exchanger, the first sealing barrier being a spiral plug, and a second sealing barrier between the second distribution chamber and the first body of the heat exchanger, formed by a cylindrical envelope surrounding the first and second spirals facing the first channels, the cylindrical envelope comprising orifices between the first distribution chamber and each of the first channels.
  • the first and second spirals stop for example at the interface between the first channels and the second channels.
  • the first and second intertwined spirals define for example two pitches, the first distribution chamber being defined by a first of said pitches less than a second of said pitches, the second pitch defining the second chamber of distribution.
  • the capacity of the first distribution chamber is smaller than the capacity of the second distribution chamber, the number of first channels being less than the number of second channels.
  • the ratio between the number of first channels and the number of second channels and therefore between the first step and the second step, is a function of the thermal power that we wish to dissipate in the first body of the heat exchanger and in the second body of the heat exchanger, these first and second bodies being able to be powered independently.
  • the dimensioning of the first body is for example adapted to the dissipation of a low thermal power in a case of low speed driving of an electric or hybrid vehicle.
  • THE dimensioning of the second body is for example adapted to the dissipation of an average thermal power in a case of slow charging of an electric or hybrid vehicle. Used together, the first and second bodies make it possible to dissipate a high thermal power, particularly in the event of rapid charging of the electric or hybrid vehicle.
  • the first distribution chamber has a larger capacity than the second distribution chamber, the first pitch being greater than the second pitch and the number of first channels being greater than the number of second channels .
  • the number of channels of the first body and the second body are the same.
  • a plate of the heat exchanger arranged at the interface between the first body and the second body does not allow the refrigerant fluid to pass between the first body and the second body.
  • the refrigerant fluid cannot pass from the first body to the second body of the heat exchanger.
  • the cooling device according to the invention advantageously further comprises the expansion member or the first and second expansion members.
  • FIG. 1 represents a cooling device according to the invention, in a first embodiment of the invention
  • FIG. 1 represents a connection block according to the invention, in this first embodiment of the invention.
  • FIG. 4 represents a cooling device according to the invention, in a second embodiment of the invention
  • FIG. 5 represents a connection block according to the invention, in the second embodiment of the invention
  • FIG. 7 is a front view of a heat exchanger of the cooling device of Figure 1 or 4, on which the cheek of the heat exchanger has been made transparent,
  • FIG. 8 is a sectional view of the cooling device of Figure 1, in a secondary alternative embodiment of the invention.
  • FIG. 9 schematically shows a cooling device according to the invention, in a main alternative embodiment of the invention.
  • FIG. 11 represents a cooling system of an electric or hybrid vehicle comprising the cooling device of Figure 4.
  • a cooling device 1 according to the invention comprises an expansion member 6, a connection block 30 according to the invention, a heat exchanger 2, and a heat exchanger internal 4.
  • the expansion device 6 is electronically controlled.
  • the heat exchanger 2 has a heat transfer liquid inlet 26 and a heat transfer liquid outlet 28.
  • the internal heat exchanger 4 comprises a free end plate on which are arranged a high pressure inlet manifold 42 of refrigerant fluid and a low pressure outlet manifold 48 of refrigerant fluid.
  • the opposite end plate of the heat exchanger 4 is an end plate brazed to an end plate 211 of the heat exchanger 2, referenced in Figure 9.
  • an evacuation port 24 of refrigerant fluid from the heat exchanger 2 is directly in communication with a low pressure inlet manifold 46 of the heat exchanger internal 4.
  • a high pressure outlet collector 44 of the internal heat exchanger 4 communicates with a pipe 29 passing through the heat exchanger 2.
  • the pipe 29 has a first end 294 opening into an inlet 370 ( referenced in Figure 2) of refrigerant fluid from the connection block 30 while being arranged in an inlet 22 of refrigerant fluid from the heat exchanger 2.
  • the pipe 29 has a second end 292 connected to the high pressure outlet manifold 44 of the internal heat exchanger 4.
  • connection block 30 is an aluminum block, in which drillings have been made orthogonally to the contact surface 360.
  • means for receiving the expansion member 6 are formed by a reception chamber 380 produced by three coaxial holes 381, 383, 385, of diameter narrowing from the surface of the connection block 30 opposite the contact surface 360.
  • This reception chamber 380 more precisely houses a valve expansion of the expansion member 6.
  • the last bore 385 of smaller diameter of this receiving chamber is itself pierced by a branch 310 opening onto the contact surface 360 of the connection block 30, this branch 310 forming the refrigerant fluid inlet 370 of the connection block 30.
  • This branch 310 is here also a cylindrical drilling, of smaller diameter than the last drilling 385 and coaxial with it.
  • the last bore 385 of the receiving chamber 380 has a bearing surface 386, referenced in Figure 3, enclosing a periphery of the inlet of the expansion valve of the organ of expansion valve 6. This support surface 386 thus forms a tight connection between the inlet of the expansion valve of the expansion member 6, and the refrigerant fluid inlet 370 of the connection block 30.
  • the diameter of the branch 310 is identical to that of the last drilling 385.
  • the inlet of the expansion valve of the expansion member 6 is held against the shoulder between the last drilling 385 and the branch 310, to form the tight connection between the inlet of the expansion valve of the expansion member 6, and the refrigerant fluid inlet 370 of the connection block 30.
  • the refrigerant fluid leaving the expansion valve leaves this closed volume 388 via a first passage 330 provided between the cylindrical surface of the drilling 383 of intermediate diameter and a first outlet 320 of refrigerant fluid from the connection block 30, and also by a second passage 350 provided between the cylindrical surface of the drilling 383 of intermediate diameter and a second refrigerant fluid outlet 340 from the connection block 30.
  • the first passage 330 is more precisely formed by a first cylindrical drilling 322, continued by a second cylindrical drilling of smaller diameter which joins the drilling 383 of intermediate diameter of the receiving chamber 380 at the level of a portion of the connection block 30
  • first and second drillings are made orthogonally from the contact surface 360. Viewed in section through a plane parallel to the contact surface 360, the portion of the block where the first passage 330 joins the closed volume 388 of the receiving chamber 380 would therefore show the first passage 330 and the receiving chamber 380 in the form of sections round and non-empty intersection but without one being included in the other.
  • the distance between the axis of revolution of the second drilling of the first passage 330 and the axis of revolution of the drilling 383 of intermediate diameter of the receiving chamber 380 is less than the sum of the radii of the cylinders formed through these holes.
  • the second passage 350 is made symmetrically to the first passage 330 with respect to a plane orthogonal to the contact surface 360 passing through a diameter of the cylindrical drilling forming the branch 310 of the connection block 30.
  • Figure 3 also shows the flows followed by a refrigerant fluid FR inside the connection block 30.
  • the refrigerant fluid FR at the outlet of the pipe 29 arrives at high pressure at the inlet 370 of the connection block 30 and enters into the expansion valve of the expansion member 6. After expansion in this valve, the refrigerant fluid FR arrives from the outlets of this valve at low pressure in the closed volume 388 and leaves this closed volume 388 via the first passage 330 and through the second passage 350 to the respective outlets 320 and 340 of the connection block 30.
  • connection block 30 makes it possible to send the low pressure refrigerant fluid FR into the intake mouth 22 via two separate inlets, that is to say a first inlet 221 and a second inlet 223, respectively supplying a first body 25 of the heat exchanger 2 and a second body 27 of the heat exchanger 2, as illustrated in Figure 8.
  • This separation of the fluid FR refrigerant in two separate flows allows better control the pressure losses inside the heat exchanger 2 as will be explained below in relation to this figure 8.
  • a cooling device 10 in a second embodiment of the invention illustrated in Figure 4, comprises a first expansion member 64, a second expansion member 62, a connection block 3 according to the invention as well as the heat exchanger 2 and the internal heat exchanger 4 of the first embodiment of the invention.
  • the connection block 3 comprises a contact surface 36 (referenced in Figure 5) brazed to the cheek 251 of the heat exchanger 2, which is assembled with the internal heat exchanger 4 as in the first embodiment of the invention.
  • the expansion members 62 and 64 are electronically controlled. Alternatively they are thermally controlled.
  • Connection block 3 has many characteristics similar to those of connection block 30 and will therefore be less detailed than this one.
  • the valves of the first and second expansion members 64 and 62 are inserted in the receiving means of the connection block 3, shown in Figure 5, these receiving means comprising a first receiving chamber 38 housing the expansion valve of the first expansion member 64 and a second receiving chamber 39 housing the expansion valve of the second expansion member 62.
  • These chambers are made in three cylindrical holes in a manner similar to the chamber 380 of the connection block 30
  • the respective expansion valves of the expansion members 64, 62 are arranged in the same way.
  • the refrigerant fluid inlet 37 FR of the connection block 3 is formed by a first groove 31 dug on the contact surface 36.
  • the last bore of smaller diameter of the receiving chamber 38 is itself pierced by a first conduit 312 cylindrical opening into the first groove 31.
  • the last bore of smaller diameter of the reception chamber 39 is itself pierced by a second cylindrical conduit 314 opening into the first groove 31.
  • the reception chambers 38, 39 are fluidly connected to the refrigerant fluid inlet 37 of the connection block 3 by the same internal branch of the connection block 3, this branch being formed by the first groove 31 and by conduits 312, 314 orthogonal to the contact surface 36 which extend the ends of the first groove 31.
  • a bearing surface 382 (referenced in Figure 6) of the last bore of smaller diameter of the first or second receiving chamber 38, 39 forms a tight connection between the inlet respective of the expansion valve of the first or second expansion member 64, 62 and respectively the first or second conduit 312, 314, therefore between the inlets of these expansion valves and the inlet 37 of the connection block 3 .
  • the first reception chamber 38 is connected to a first outlet 32 only of the connection block 3, by a first passage 33.
  • the first passage 33 is produced in the same way as the first passage 330.
  • This seal is achieved by the tight insertion of this expansion valve into the first receiving chamber 38, in the same way as in the first embodiment of the invention.
  • the first passage 33 is formed by a first cylindrical recess 326 followed by a second cylindrical recess of smaller diameter.
  • the first cylindrical recess 326 is arranged opposite the second refrigerant fluid inlet 223 of the heat exchanger 2.
  • the second receiving chamber 39 is connected to a second outlet 34 only of the connection block 3, by a second passage 35.
  • the second passage 35 is made in the same way as the second passage 350. In particular it receives the fluid FR refrigerant leaving the valve expansion of the second expansion member 62, in a sealed manner thanks to a closed volume included between this expansion valve and the intermediate diameter drilling of the second receiving chamber 39.
  • a second groove is made on the exchange surface 36 of the connection block 3. A first end of this second groove opens into the second passage 35, and a second end of this second groove is arranged opposite the first refrigerant fluid inlet 221 of the heat exchanger 2. Thus the second refrigerant fluid outlet 34 of the connection block 3 is formed through this second groove.
  • This second embodiment therefore makes it possible to distinctly control a first flow of low-pressure refrigerant fluid arriving at the first inlet 221 of refrigerant fluid of the heat exchanger 2, a second flow of low-pressure refrigerant fluid arriving at the second refrigerant fluid inlet 223 of the heat exchanger 2.
  • the first flow is controlled by the second expansion member 62 while the second flow is controlled by the first expansion member 64.
  • the refrigerant fluid flows FR in the connection block 3 are illustrated in dotted lines in Figures 5 and 6.
  • Figure 7 shows a part of the heat exchanger 2 at the level of the portion of the cheek 251 of the heat exchanger in contact with the contact surface 36 or 360 of the connection block 3 or 30.
  • the cheek 251 has been made transparent, only orifices 222 and 224 of this cheek 251 corresponding respectively to the first inlet 221 and to the second inlet 223 of refrigerant fluid of the heat exchanger 2 being represented.
  • In this figure therefore appear in multiple lines the sealing edges of the channels of the heat exchanger 2 as well as in relief of the flow disruptors of a first channel of the heat exchanger 2.
  • the first end 294 of the pipe 29 is arranged in the center of the inlet mouth 22 of the heat exchanger 2. This first end 294 projects from the cheek 251 of the heat exchanger 2, so as to insert into the cylindrical bore forming the branch 310 of the connection block 30, or into the first groove 31 of the connection block 3, without touching the bottom of the first groove 31 so as to that the refrigerant fluid circulates towards the first conduit 312 and towards the second conduit 314.
  • the first refrigerant fluid outlet 32, 320 FR of the connection block 3, 30 is placed opposite the orifice 224 of the cheek 251 so as to supply the second refrigerant fluid inlet 223 of the heat exchanger 2, and the second refrigerant fluid outlet 34, 340 FR of the connection block 3, 30 is placed opposite the orifice 222 of the cheek 251 so as to supply the first refrigerant fluid inlet 221 of the heat exchanger 2.
  • inlet sealing means are arranged at the level of the inlet mouth 22.
  • the inlet mouth 22 is itself the end of an inlet collector 23 passing through the heat exchanger 2, this inlet collector 23 being surrounded at least in part by a cylindrical envelope 235 making it possible to serve the first body 25 and the second body 27 of the heat exchanger 2 in a sealed manner.
  • the inlet collector 23 comprises a first distribution chamber 231 supplied by the first inlet 221 and serving the first body 25 of the heat exchanger 2, and a second distribution chamber 233 supplied by the second inlet 223 and serving the second body 27 of the heat exchanger 2.
  • the first and second distribution chambers 231 and 233 are arranged around the line 29, as detailed below.
  • the inlet sealing means comprise the cheek 251 of the heat exchanger 2, as well as the walls of an angular portion of cylindrical sleeve 238 around the pipe 29 forming the first chamber of distribution 231. These walls oriented axially, that is to say in the direction of main extension of the pipe 29, are pressed against the cheek 251.
  • first flow of refrigerant fluid FR coming from the second outlet 34, 340 of the connection block 3, 30 enters the orifice 222 of the cheek 251 and is located in the angular portion of cylindrical sleeve 238, sealed with respect to the second distribution chamber 233 supplied by the second flow of refrigerant fluid FR coming from of the first output 32, 320 of the connection block 3, 30.
  • the inlet sealing means visible in Figure 7 comprise the cheek 251 of the heat exchanger 2, the cylindrical envelope 235 as well as a first spiral plug 225 initiating the wall of the first spiral 234 and s 'extending axially towards the cheek 251, and a second spiral plug 227 initiating the wall of the second spiral 236 and extending axially towards the cheek 251.
  • the first and second spiral plugs 225 and 227 sealingly separate the respective inlets 221 and 223 of the first and second distribution chambers 231 and 233.
  • the first inlet 221 of the first distribution chamber 231 is thus delimited axially on the one hand by a foiled portion 251 comprising the orifice 222 corresponding to this first inlet 221, and on the other hand by the second helical spiral 236, radially d on the one hand by the cylindrical envelope 235 and on the other hand by the pipe 29, and angularly by the second spiral plug 227 initiating the wall of the second spiral 236.
  • the first spiral plug 225 angularly prevents the first flow from joining the second distribution chamber 233 over the axial length of the first spiral plug 225, the first flow being forced, in this first inlet 221, to flow axially between the first spiral cap 225 and the wall of the second spiral 236, that is to say is forced to engage between a surface of the wall of the first spiral 234, and a surface of the wall of the second spiral 236, defining the first distribution chamber 231.
  • the second inlet 223 of the second distribution chamber 233 is delimited axially on the one hand by a cheek portion 251 comprising the orifice 224 corresponding to this second inlet 223, and on the other hand by the first helical spiral 234 , radially on the one hand by the cylindrical envelope 235 and on the other hand by the pipe 29, and angularly by the first spiral plug 225 initiating the wall of the first spiral 234.
  • the second spiral plug 227 angularly prevents the second flow from joining the first distribution chamber 231 over the axial length of the second spiral plug 227, the second flow being forced, in this second inlet 223, to flow axially between the second spiral plug 227 and the wall of the first spiral 234, that is to say is forced to engage between another surface of the wall of the second spiral 236, and another surface the wall of the first spiral 234 , defining the second distribution chamber 233.
  • connection block 30 In the section of a part of the cooling device 1 shown in Figure 8, illustrating this secondary alternative embodiment of the invention with the connection block 30, the first and second flows of refrigerant fluid FR leaving the expansion valve 6 to reach respectively the first inlet 221 and the second inlet 223 of the intake mouth 22, are represented by arrows.
  • this secondary embodiment can also be used with connection block 3.
  • one of the plates 254 of the bundle of plates forming the heat exchanger 2 and located between the first body 25 of the heat exchanger 2 and the second body 27 of the heat exchanger 2 tightly surrounds the inlet collector 23 in order to prevent the refrigerant fluid from passing from the first body 25 to the second body 27 outside the inlet collector 23.
  • Figure 9 now schematically describes the path of the refrigerant fluid and a heat transfer liquid H2O in the heat exchanger 2.
  • the heat exchanger 2 is formed from a bundle of plates brazed together and between which channels are formed.
  • the bundle of plates more precisely forms an alternation of channels intended for the refrigerant fluid FR and channels intended for the heat transfer liquid H2O.
  • the refrigerant fluid FR and the heat transfer liquid H2O enter the heat exchanger 2 via respectively the refrigerant fluid inlet collector 23 of the heat exchanger 2 and the heat transfer liquid H2O inlet 26 of the heat exchanger 2.
  • the inlet collector 23 comprises the intake mouth 22 of refrigerant fluid FR.
  • Passages between the plates allow the refrigerant fluid FR and the heat transfer liquid H2O to be evacuated through respectively the outlet 24 of the heat exchanger 2 and the heat transfer liquid outlet 28 of the heat exchanger 2.
  • the plate bundle of heat exchanger 2 includes:
  • the heat exchanger 2 only has two first channels and two second channels.
  • the heat exchanger 2 according to the invention generally comprises many more first and second channels.
  • a first refrigerant fluid channel FR is formed between the plates 251 and 252, another first refrigerant fluid channel FR is formed between the plates 253 and 254.
  • a heat transfer liquid channel is formed between the plates 252 and 253 and another heat transfer liquid channel is formed between the plates 254 and 271.
  • a second refrigerant fluid channel FR is formed between the plates 271 and 272, another second refrigerant fluid channel FR is formed between the plates 273 and 274.
  • a heat transfer liquid channel H2O is formed between the plates 272 and 273 and another channel of heat transfer liquid is formed between the plates 274 and the end plate 211 of the heat exchanger 2 from which the evacuation port 24 exits.
  • the refrigerant fluid FR or the heat transfer liquid H2O is shown arriving in the channel in a solid arrow and leaving, after a U-shaped path in the channel, in a dotted arrow towards the evacuation mouth 24 or the liquid outlet 28 H2O heat carrier.
  • the refrigerant fluid FR leaving the expansion member 6, or the first and second expansion members 64, 62 is separated into two streams.
  • the first flow is brought to the first inlet 221 of the inlet mouth 22, serving the first distribution chamber 231 of the first flow of refrigerant fluid FR in the first body 25 of the heat exchanger 2.
  • the second flow is brought to the second inlet 223 of the intake mouth 22, serving the second chamber 233 for distributing the second flow of refrigerant fluid FR in the second body 27 of the heat exchanger 2.
  • the first flow is distributed by the first distribution chamber 231 to the first channels in a sealed manner with respect to the distribution of the second flow by the second distribution chamber 233 to the second channels.
  • the inlet collector 23 is able to ensure the supply of a first flow rate to the first channels and a second flow rate to the second channels, of substantially identical values, which homogenizes the distribution of the refrigerant fluid FR in the heat exchanger 2.
  • only the first body of the heat exchanger or the second body of the heat exchanger 2 is optionally used. In this case only the first flow or the second flow is sent to the heat exchanger 2.
  • the first distribution chamber 231 is formed by the walls of the angular portion of cylindrical sleeve 238 around the pipe 29, this angular portion of cylindrical sleeve 238 is extending axially from the cheek 251 of the heat exchanger 2 to one end of the first channels at the interface with the second body 27 of the heat exchanger 2, but not beyond.
  • the walls of the angular portion of cylindrical sleeve 238 are closed and sealed except:
  • orifices 237 are arranged on the angular portion of cylindrical sleeve 238 facing the first channels, so that the refrigerant fluid FR circulates from the first distribution chamber 231 towards the first channels.
  • the base of the angular portion of cylindrical sleeve 238 located between the first channels and the second channels forms a sealing barrier between the first channels and the second channels.
  • the second distribution chamber 233 is delimited by the cylindrical envelope 235 present all around the pipe 29, except at the level of the angular portion of cylindrical sleeve 238 which delimits the first distribution chamber 231.
  • the cylindrical envelope 235 is waterproof except :
  • orifices 239 are arranged on this portion of the cylindrical envelope 235 so that the refrigerant fluid FR circulates from the second distribution chamber 233 towards the second channels.
  • Figure 10 illustrates the secondary embodiment of the invention, in which the distribution chambers 231 and 233 are each formed by a volume included between the walls of the first helical spiral 234 and the second helical spiral 236 intertwined around the pipeline 29.
  • Spirals 234 and 236 extend radially into the inlets of the first and second channels.
  • These spirals are preferably ribs extending radially around the pipe 29 and made of material with the pipe 29.
  • the inlet collector 23 comprises a first sealing barrier 232 between the first distribution chamber 231 and the second body 27, produced , in this variant embodiment of the invention, in the form of a spiral plug located between the spirals 234 and 236 and blocking the passage of the first flow of refrigerant fluid FR. So the first flow cannot reach the second channels.
  • the cylindrical envelope 235 forms a second sealing barrier 235 between the second distribution chamber 233 and the first body 25, tightly enclosing, in a sealed manner, the spirals 234 and 236.
  • This cylindrical envelope 235 blocks the passage of the second flow in the first channels.
  • Orifices 230 in the cylindrical envelope 235 nevertheless allow the passage of the first flow in the first channels.
  • the cylindrical envelope 235 extends for example axially from the cheek 251 of the heat exchanger 2 to one end of the first channels at the interface with the second body 27 of heat exchanger 2, but not beyond. If, on the contrary, the cylindrical envelope 235 extends axially from the cheek 251 to the level of the second end 292 of the pipe 29 connected to the high pressure outlet collector 44 of the internal heat exchanger 4, then orifices similar to the orifices 239 are for example arranged in the cylindrical envelope 235 to allow the passage of the second flow in the second channels.
  • the cylindrical envelope 235 is alternatively replaced by a helical envelope covering only the gap between the first helical wall 234 and the second helical wall 236 which delimits the second distribution chamber 233, and extending axially only from the cheek 251 of the heat exchanger 2 to one end of the first channels at the interface with the second body 27 of the heat exchanger 2.
  • FIG. 11 now illustrates a use of the connection block 3 according to the invention and of the cooling device according to the invention, in a cooling system of an electric or hybrid vehicle.
  • the vehicle comprises an electric battery 84, power electronics 86 and an electric machine 82, these components being cooled by a circuit of H2O heat transfer liquid, for example water, the circulation of which is ensured by a pump 80.
  • H2O heat transfer liquid for example water
  • the liquid heat transfer H2O enters the heat exchanger 2 via the heat transfer liquid inlet 26, and leaves the heat exchanger 2 via the heat transfer liquid outlet 28, being cooled.
  • This cooling takes place in contact with the refrigerant fluid FR also circulating in the heat exchanger 2, in a separate refrigerant fluid circuit.
  • This low pressure branch of the refrigerant fluid FR in the heat exchanger internal 4 makes it possible to cool a high pressure branch of the refrigerant fluid circuit FR as described below.
  • the refrigerant fluid FR compressed by the compressor 7 is then condensed by a condenser 9.
  • a part of the condensed refrigerant fluid FR is directed towards an expansion member 11 then evaporated in an evaporator 5 of an air conditioning system of the vehicle interior .
  • Another part of the condensed FR refrigerant fluid is sent into the high pressure inlet manifold 42 of the internal heat exchanger 4, and leaves the internal heat exchanger 4 via the high pressure outlet manifold 44 of the exchanger internal heat exchanger 4.
  • This high pressure branch of the refrigerant circuit FR is cooled in the internal heat exchanger 4 by the low pressure branch of the refrigerant circuit mentioned above.
  • the refrigerant fluid FR arriving from the high pressure outlet manifold 44 is then expanded by the first and second expansion members 64 and 62, then enters the refrigerant fluid intake mouth 22 of the heat exchanger 2 passing through the connection block 3, to cool the H2O heat transfer liquid also passing through the heat exchanger 2.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Electrochemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP23792967.4A 2022-10-26 2023-10-18 Anschlussblock für wärmetauscher und kühlvorrichtung damit Pending EP4609136A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR2211143A FR3141516B1 (fr) 2022-10-26 2022-10-26 Bloc de connexion pour échangeur thermique et dispositif de refroidissement les comportant
PCT/EP2023/079027 WO2024088855A1 (fr) 2022-10-26 2023-10-18 Bloc de connexion pour échangeur thermique et dispositif de refroidissement les comportant

Publications (1)

Publication Number Publication Date
EP4609136A1 true EP4609136A1 (de) 2025-09-03

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EP23792967.4A Pending EP4609136A1 (de) 2022-10-26 2023-10-18 Anschlussblock für wärmetauscher und kühlvorrichtung damit

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EP (1) EP4609136A1 (de)
CN (1) CN120051664A (de)
FR (1) FR3141516B1 (de)
WO (1) WO2024088855A1 (de)

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Publication number Priority date Publication date Assignee Title
FR3164779A1 (fr) * 2024-07-17 2026-01-23 Valeo Systemes Thermiques Bloc de connexion d’un échangeur de chaleur amélioré

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010012869A1 (de) * 2009-03-26 2010-09-30 Modine Manufacturing Co., Racine Wärmetauschermodul
FR3006754B1 (fr) * 2013-06-07 2015-06-26 Valeo Systemes Thermiques Module de connexion, echangeur thermique, et ensemble d'echange thermique correspondant
JP6571047B2 (ja) * 2016-06-21 2019-09-04 株式会社ヴァレオジャパン 内部熱交換器及びそれを備える車両用空調装置の冷凍サイクル
CN109699183B (zh) * 2016-07-11 2021-01-15 达纳加拿大公司 具有双内部阀的热交换器
EP3683522B1 (de) * 2017-09-11 2022-10-26 Zhejiang Sanhua Intelligent Controls Co., Ltd. Fluidsteueranordnung
KR102440596B1 (ko) * 2017-11-28 2022-09-05 현대자동차 주식회사 차량용 열교환기
FR3102552B1 (fr) * 2019-10-29 2022-07-29 Valeo Systemes Thermiques Dispositif d’échange d’énergie calorifique comportant deux échangeurs de chaleur à plaques

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WO2024088855A1 (fr) 2024-05-02
FR3141516A1 (fr) 2024-05-03
CN120051664A (zh) 2025-05-27
FR3141516B1 (fr) 2024-11-22

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