US20230288146A1 - Heat exchanger for a motor vehicle - Google Patents
Heat exchanger for a motor vehicle Download PDFInfo
- Publication number
- US20230288146A1 US20230288146A1 US18/013,390 US202118013390A US2023288146A1 US 20230288146 A1 US20230288146 A1 US 20230288146A1 US 202118013390 A US202118013390 A US 202118013390A US 2023288146 A1 US2023288146 A1 US 2023288146A1
- Authority
- US
- United States
- Prior art keywords
- conduit
- heat exchanger
- heat
- chambers
- circuit
- 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
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- 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
- 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
- F28D9/0093—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
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different 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
- F28F9/0246—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
- 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
- F28F9/0246—Arrangements for connecting header boxes with flow lines
- F28F9/0256—Arrangements for coupling connectors with flow lines
-
- 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
- F28F9/0263—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry or cross-section of header box
-
- 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
- F28F9/0275—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 with multiple branch pipes
-
- 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
- F28D2021/007—Condensers
-
- 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
- F28D2021/0084—Condensers
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
The invention relates to a heat exchanger (100) for a motor vehicle, comprising a first circuit (110) comprising at least one first group of chambers (75) and one second group of chambers (76) intended to be traversed by a heat transfer fluid, and a second circuit (120) intended to be traversed by a coolant, the heat exchanger (100) being configured to implement an exchange of heat between the heat transfer fluid and the coolant, the heat exchanger (100) comprising at least one component (155) for differentiating the flow of heat transfer fluid circulating in the first group of chambers (75) from the flow of heat transfer fluid circulating in the second group of chambers (76) of the first circuit (110).
Description
- The present invention relates to the field of heat exchangers for motor vehicles. It applies for preference, although not exclusively, to the heat exchangers used in the air conditioning circuits of such vehicles.
- The present invention more particularly relates to heat exchangers which comprise a first circuit configured to carry a heat-transport liquid and a second circuit configured to carry a refrigerant fluid. More specifically, the present invention relates to such exchangers in which the second circuit comprises at least two successive passes of refrigerant fluid, and in which the first circuit comprises a plurality of chambers split into several groups of chambers. The heat exchanger is then configured to perform an exchange of heat between the heat-transport liquid circulating in at least one of the groups of chambers and the refrigerant fluid circulating in at least one of the passes of the second circuit. What is meant here by a “pass” is distinct regions of the second circuit of the heat exchanger which are configured so that the refrigerant fluid circulates successively within them. According to one particular arrangement, the passes of the second circuit may be arranged in such a way that the refrigerant fluid circulates in parallel between them.
- In such exchangers, also known as water-cooled condensers, the refrigerant fluid is admitted to a first pass of the second circuit in gaseous form and then, circulating successively through the various passes of the second circuit, in contact with the various groups of chambers of the first circuit through which chambers the heat-transport liquid circulates, it is progressively condensed until it leaves the exchanger in liquid form.
- The technical problem to which the present invention aims to propose a solution is that of the efficiency of the exchange of heat in the various passes of the second circuit, notably in those regions of the heat exchanger in which the physical-chemical conversion that is the condensing of the refrigerant fluid takes place.
- In order to increase the efficiency of such a heat exchange, a first subject of the present invention is a heat exchanger for a motor vehicle, comprising:
-
- a first circuit through which a heat-transport liquid is intended to pass and which comprises a first inlet header via which the heat-transport liquid is admitted to the first circuit and a first outlet header via which the heat-transport liquid leaves the first circuit, the first circuit comprising a plurality of chambers which are fluidically connected to the first inlet header and to the first outlet header and are split into at least a first group of chambers and a second group of chambers,
- a second circuit through which a refrigerant fluid is intended to pass and which comprises a second inlet header via which the refrigerant fluid is admitted into the heat exchanger and a second outlet header via which the refrigerant fluid leaves the heat exchanger, the second circuit comprising at least two successive passes, the heat exchanger being configured to perform an exchange of heat between the
heat-transport liquid circulating in at least one of the groups of chambers and at least one of the passes of the second circuit,
characterized in that the heat exchanger comprises at least one differentiation member for differentiating the flowrate of heat-transport liquid circulating per chamber in the first group of chambers from the flowrate of heat-transport liquid circulating per chamber in the second group of chambers of the first circuit.
- The presence of the aforesaid differentiation member results in different flow velocities for the heat-transport liquid between the groups of chambers concerned. This has the effect of differentiating the duration of the exchange of heat performed between the heat-transport liquid circulating in these groups of chambers and the refrigerant fluid circulating in the corresponding passes of the second circuit. The invention thus achieves its stated objective by notably making it possible to increase a duration of the exchange of heat between the heat-transport liquid circulating in one group of chambers in which the flowrate of this heat-transport liquid is lowest and the refrigerant fluid circulating in a pass of the second circuit in contact with this group of chambers.
- According to one particularly advantageous embodiment, each chamber is delimited by at least two plates, each plate comprising a bottom wall surrounded by a turned-up edge, the bottom wall being provided with at least one opening which at least in part delimits the first inlet header, the two plates being positioned one inside the other. Advantageously, the bottom walls of the plates delimiting the chambers of the first circuit have a substantially planar overall shape.
- The heat exchanger according to the invention is therefore made up of a stack of plates as previously described stacked in a direction of stacking substantially perpendicular to an overall main plane of extension of the bottom wall of each of these plates. This has the effect that the aforementioned first inlet header is formed of the stack of the aforesaid openings pierced in the bottom walls of the plates delimiting the chambers of the first circuit.
- The first inlet header for admitting the heat-transport liquid into the first circuit of the exchanger according to the invention therefore substantially assumes the form of a conduit extending through the heat exchanger according to the invention. According to a preferred although not exclusive embodiment, the openings formed in the bottom walls of the plates that make up the heat exchanger according to the invention are arranged in such a way that the aforesaid first inlet header extends substantially perpendicular to the bottom walls of the plates which delimit the chambers of the first circuit and, therefore, substantially parallel to the direction of stacking of the aforesaid plates.
- According to a first example of how the invention may be embodied, the first inlet header comprises a first conduit supplying the first group of chambers and a second conduit supplying the second group of chambers, the differentiation member involving a second bore section of the second conduit that is smaller than a first bore section of the first conduit. What is meant here by a bore section is the surface area of a cross section of the conduit concerned, measured in a plane substantially perpendicular to the main direction of extension thereof. The foregoing therefore means that the flowrate of heat-transport liquid circulating in the second conduit of the first inlet header is smaller than the flowrate of heat-transport liquid circulating in the first conduit of the first inlet header.
- Advantageously, according to such an example, a ratio between the second bore section of the second conduit and the first bore section of the first conduit is comprised between 0.4 and 0.8.
- More specifically, according to a first embodiment of this first example of how the invention may be embodied, the bottom walls of the at least two plates each comprise at least a first opening and a second opening, respectively constituting the first conduit and the second conduit of the first inlet header.
- According to one example of how the invention may be embodied, the second bore section is defined by at least one of the second openings formed in the plate.
- To complement this, the aforementioned first bore section and the aforementioned second bore section are respectively defined by the dimensions of at least one of the openings formed in the aforesaid plate or plates. For example, the first bore section is defined by the aforementioned first opening, and the second bore section is defined by the second opening defined hereinabove.
- According to the invention, the differentiation member is formed by at least a second opening that forms part of the second conduit.
- Alternatively, the differentiation member comprises all of the second openings of the second conduit.
- The above-defined differentiation member that differentiates the flowrate of heat-transport liquid is therefore embodied here by the difference in bore section between the first opening and the second opening. In other words again, the differentiation member corresponds to the second bore section of at least one of the second openings being smaller than the first bore section of one of the first openings.
- It must therefore be understood here that, in this example of how the heat exchanger according to the invention may be embodied, the differentiation of the flowrate of heat-transport liquid between the first conduit and the second conduit of the first inlet header is the result of the geometry of the plates that forms the first circuit and of the dimensions of the openings made in the bottom walls of these plates.
- According to one example, all of the second openings that define the second conduit of the first inlet header may have the same bore section, substantially equal to the aforementioned second bore section. The differentiation member that differentiates the flowrate of heat-transport liquid is then defined by all of the second openings that define the second conduit. In a variant, just one of the second openings that contributes to defining the second conduit has a bore section substantially equal to the aforementioned second bore section.
- In another example, the heat exchanger comprises at least one heat-transport-liquid supply unit, the supply unit being fluidically connected to the first inlet header which comprises a first conduit supplying the first group of chambers and a second conduit supplying the second group of chambers. The first conduit and the second conduit therefore together form the above-defined first inlet header. Advantageously, in such an example, the bore sections of the first conduit and of the second conduit are substantially equal.
- In this example, the invention anticipates for the supply unit to comprise a first duct supplying the first conduit and a second duct supplying the second conduit of the first inlet header, the differentiation member involving a second bore section of the second duct that is smaller than a first bore section of the first duct. Advantageously, a ratio between the second bore section of the second duct and the first bore section of the first duct is comprised between 0.4 and 0.8.
- According to another example, the first heat-transport liquid circuit comprises a third group of chambers which are fluidically connected to the first conduit of the first inlet header and to the first outlet header successively to the first group of chambers, the heat-transport liquid flowrate differentiation member comprising at least a third bore section of the first conduit, positioned between the first group of chambers and the third group of chambers, the third bore section being smaller than the first bore section of the first conduit. Advantageously, a ratio between the third bore section of the first conduit and the first bore section of the first conduit is substantially comprised between 0.4 and 0.8.
- In other words, according to this example, the bore section of the first conduit according to the invention is reduced in the third group of chambers of the first circuit. This makes it possible to increase still further the residence time of the heat-transport liquid in the third group of chambers of the first circuit and, therefore, the duration and efficiency of the exchange of heat between the refrigerant fluid circulating in the second circuit and the heat-transport liquid circulating in the third group of chambers.
- According to one advantageous example, at least one of the first openings that make up the first conduit exhibits the third bore section.
- The invention thus makes it possible, through simple means such as the creation of openings of different dimensions in plates delimiting the chambers of the first circuit of a heat exchanger as has just been described, to modify the flowrate of heat-transport liquid within such an exchanger, for an increased residence time in contact with the refrigerant fluid and, therefore, for better heat-exchange efficiency. The invention thus achieves its stated objective.
- A second aspect of the invention also relates to a thermal conditioning system for a motor vehicle comprising at least one heat exchanger according to any one of the preceding features. Advantageously, in such a thermal conditioning system, the heat-transport liquid is glycol water.
- Further features, details and advantages of the invention will become more clearly apparent from reading the description, which is provided below by way of illustration and with reference to drawings in which:
-
FIG. 1 is a schematic perspective overview of one example of a thermal conditioning system according to the invention; -
FIG. 2 is a schematic view in section on a vertical and transverse plane of the heat exchanger ofFIG. 1 showing a first example of how the invention may be embodied; -
FIG. 3 is a schematic view in section on a vertical and transverse plane of the heat exchanger ofFIG. 1 showing a second example of how the invention may be embodied; -
FIG. 4 is a schematic view in section on a vertical and transverse plane of the heat exchanger ofFIG. 1 showing a third example of how the invention may be embodied. - It should first of all be noted that although the figures set out the invention in detail for implementing the invention, these figures may of course be used in order to better define the invention if necessary. It should also be noted that these figures set out only a number of examples of ways in which the invention may be embodied.
-
FIG. 1 is a schematic perspective illustration of athermal conditioning system 500 according to the invention. - Such a
thermal conditioning system 500 notably comprises aheat exchanger 100 configured to be the site of an exchange of heat between a heat-transport liquid and a refrigerant fluid both circulating within it. According to one example, the heat-transport liquid is a glycol water. The heat-transport liquid and the refrigerant fluid are not depicted in the figures. - Advantageously, the
heat exchanger 100 comprises afirst circuit 110 through which the heat-transport liquid is conveyed, and asecond circuit 120 through which the refrigerant fluid is conveyed, thefirst circuit 110 and thesecond circuit 120 being, inside theheat exchanger 100, in contact with one another in such a way that an exchange of heat between the heat-transport liquid and the refrigerant fluid can occur. - The
first circuit 110 of theheat exchanger 100 extends between a first inlet header 1 via which the heat-transport liquid is admitted to thefirst circuit 110 of theheat exchanger 100 and afirst outlet header 2 via which the heat-transport liquid leaves thefirst circuit 110 of theheat exchanger 100. - The
second circuit 120 of theheat exchanger 100 extends between asecond inlet header 3 via which the refrigerant fluid is admitted to thesecond circuit 120 of theheat exchanger 100 and a second outlet header 4 via which the refrigerant fluid leaves thesecond circuit 120 of theheat exchanger 100. - According to the example more particularly illustrated in
FIG. 1 , theheat exchanger 100 comprises asupply unit 5 via which the heat-transport liquid enters the above-defined first inlet header 1. Thesupply unit 5 is therefore fluidically connected to the first inlet header 1. According to this example, theheat exchanger 100 also comprises anoutlet unit 50 fluidically connected to thefirst outlet header 2 and via which the heat-transport liquid leaves theheat exchanger 100. - The refrigerant fluid, admitted to the
heat exchanger 100 in essentially gaseous form, is progressively condensed as it passes through theheat exchanger 100 through an exchange of heat with the heat-transport liquid, until it leaves theheat exchanger 100 in essentially liquid form. In one particularly advantageous configuration, the refrigerant fluid in liquid form is received and stored in acondensation bottle 200 arranged near theheat exchanger 100. Advantageously, and to increase the efficiency of the exchange of heat between the heat-transport liquid and the refrigerant fluid, the latter makes a plurality of passes through thesecond circuit 120, successively in contact with different regions of thefirst circuit 110. The various distinct regions of thesecond circuit 120, through which regions the refrigerant fluid successively circulates will, in what follows, be referred to by the term “passes” of thesecond circuit 120 of theheat exchanger 100. -
FIG. 2 schematically illustrates, in section on a vertical and transverse plane A visible inFIG. 1 , aheat exchanger 100 according to a first example of how the invention may be embodied. -
FIG. 2 again shows the above-defined first inlet header 1, configured to admit the heat-transport liquid into thefirst circuit 110 of theheat exchanger 100. ThisFIG. 2 also again shows thesupply unit 5 as previously defined, configured to allow the heat-transport liquid to enter thefirst circuit 110. - With reference to
FIG. 2 , theheat exchanger 100 is formed of a stack of N plates 6 a, . . . 6 i, 6 j, . . . 6 n, stacked in a direction of stacking E arbitrarily referred to in what follows as the vertical direction V of theheat exchanger 100 and indicated by the axis V inFIG. 2 . It should be noted that the vertical direction V of theheat exchanger 100 can be anything with reference to a vertical direction of a motor vehicle in which a thermal conditioning system as previously described and comprising theheat exchanger 100 is placed. - As shown in
FIG. 2 , each plate 6 a, . . . , 6 i, 6 j, . . . 6 n, of theheat exchanger 100 is formed of a bottom wall 60 a, . . . , 60 i, 60 j, . . . 60 n the overall shape of which is substantially planar, surrounded by a turned-up edge 61 a, . . . 61 i, 61 j, . . . 61 n, of which the dimensions, measured perpendicular to the main plane of extension of the bottom wall 60 a, . . . , 60 i, 60 j, . . . , 60 n, are small relative to the dimensions of this wall. Only two plates 6 i, 6 j, theirbottom walls 60 i, 60 j, and their turned-upedges 61 i, 61 j, have been identified inFIG. 2 . According to the example illustrated inFIG. 2 , the bottom walls 60 a, . . . , 60 i, 60 j, . . . 60 n are substantially perpendicular to the above-defined vertical direction V of theheat exchanger 100, and are substantially parallel to a plane P defined by a longitudinal direction L and a transverse direction T, which are respectively arbitrarily referred to as the longitudinal direction and as the transverse direction of theheat exchanger 100. - In the
heat exchanger 100 according to the invention, the plates 6 a, . . . , 6 i, 6 j, . . . 6 n pairwise delimit chambers 7 a, . . . 7 i, 7 j, . . . , 7 n of thefirst circuit 110 of theheat exchanger 100, which is to say chambers configured to convey the heat-transport liquid within theheat exchanger 100. Only one chamber 7 i, delimited by the plates 6 i, 6 j, is depicted inFIG. 2 . The spaces defined between the chambers 7 a, . . . , 7 i, 7 j, . . . , 7 n together partially form the second circuit of theheat exchanger 100, in which circuit the refrigerant fluid circulates in contact with the chambers 7 a, . . . , 7 i, 7 j, . . . , 71 n of thefirst circuit 110. It must be appreciated here that the bottom walls 60 a, . . . , 60 i, 60 j, . . . , 60 n, of substantially planar overall shape, have reliefs so that when the corresponding plates 6 a, . . . , 6 i, 6 j, . . . , 6 n are stacked in the aforementioned vertical direction V, these walls between them form different volumes respectively corresponding at least in part to thesecond circuit 120 of theheat exchanger 100 or to chambers 7 a, . . . , 7 i, 7 j, . . . , 7 n of thefirst circuit 110. - Advantageously, each bottom wall 60 a, . . . , 60 i, 60 j, . . . , 60 n comprises at least one opening 62 a, . . . , 62 i, 62 j, . . . , 62 n which at least partly delimits the first inlet header 1. The first inlet header 1 of the
first circuit 110 thus extends substantially over the entirety of the dimension of theheat exchanger 100 in the above-defined vertical direction V thereof, and is formed of the stack of the aforesaid openings 62 a, . . . , 62 i, 62 j, . . . , 62 n. - Advantageously, the chambers 7 a, . . . , 7 i, 7 j, . . . , 7 n of the
first circuit 110 are organized into mutually independent groups of chambers, through which groups the heat-transport liquid circulates successively. For example, the chambers 7 a, . . . , 7 i, 7 j, . . . , 7 n of thefirst circuit 110 are organized into a first group ofchambers 75 and a second group ofchambers 76, each group ofchambers heat exchanger 100, in contact with a pass, as defined hereinabove, of thesecond circuit 120 of theheat exchanger 100. In other words, the first group ofchambers 75 is in contact with a first pass, not depicted, of thesecond circuit 120, and the second group ofchambers 76 is in contact with a second pass, not depicted, of thesecond circuit 120 and distinct from the first pass. The first group ofchambers 75 and the second group ofchambers 76 are indicated schematically inFIG. 2 . - According to the first example of how the invention may be embodied, which is illustrated in
FIG. 2 , the inlet header 1 comprises a first conduit 10 and a second conduit 11. - As shown by
FIG. 2 , the first conduit 10 extends substantially over the entirety of the dimension of theheat exchanger 100 in the above-defined vertical direction V thereof. According to the invention, the second conduit 11 extends substantially over half of the dimension of theheat exchanger 100 in the vertical direction V thereof. Moreover, as shown inFIG. 2 , the first conduit 10 is formed of the stack, in the vertical direction V of theheat exchanger 100, of first openings 63 a, . . . , 63 i, 63 j, . . . , 63 n, arranged in the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n, of theheat exchanger 100, and the second conduit 11 is formed of the stack, in the vertical direction V of theheat exchanger 100, of second openings 64 a, . . . , 64 i, 64 j, . . . , 64 n, arranged in the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n, of theheat exchanger 100. - In other words, according to the example illustrated in
FIG. 2 , the bottom wall 60 a, . . . , 60 i, 60 j, . . . , 60 n, of each plate 6 a, . . . , 6 i, 6 j, . . . , 6 n, that makes up theheat exchanger 100, is pierced with at least a first opening 63 a, . . . , 63 i, 63 j, . . . , 63 n and with at least a second opening 64 a, . . . , 64 i, 64 j, . . . , 64 n, which openings together respectively define the first conduit 10 and the second conduit 11 of the first inlet header 1. - According to the invention, the first conduit 10 of the first inlet header 1 is configured to supply heat-transport liquid to the above-defined first group of
chambers 75, and the second conduit 11 of the first inlet header 1 is configured to supply heat-transport liquid to the above-defined second group ofchambers 76. - Moreover, the invention plans for a
first bore section 150 of the first conduit 10 to be greater than the second bore section 160 of the second conduit 11, the bore section being defined here in a plane substantially perpendicular to the main direction of extension of the conduit concerned. More specifically, the invention plans for a ratio between the second bore section 160 and thefirst bore section 150 to be comprised between 0.4 and 0.8. - It should be noted that, according to the first example of how the invention may be embodied, illustrated more particularly in
FIG. 2 , thesupply unit 5 comprises, on the one hand, afirst duct 50 fluidically connected to the first conduit 10 of the first inlet header 1 and, on the other hand, asecond duct 51 fluidically connected to the second conduit 11 of the first inlet header 1. - According to the example more particularly illustrated in
FIG. 2 , the first conduit 10 and the second conduit 11 each have a substantially cylindrical shape, with the axis of elongation substantially parallel to the above-defined vertical direction V of theheat exchanger 100. According to such an example, thebore sections 150, 160 may be represented by the diameters of the first conduit 10 and of the second conduit 11, respectively, these being measured perpendicular to the vertical direction V of theheat exchanger 100. More generally, thebore sections 150, 160 are to be understood as meaning the surface-areas of a projection of the first conduit 10 and of the second conduit 11 respectively on to a plane perpendicular to the vertical direction V of theheat exchanger 100. - It will be appreciated from the foregoing that the
first bore section 150 is defined by at least one of the first openings 63 a, . . . , 63 i, 63 j, . . . , 63 n of the first conduit 10 and that the second bore section 160 as defined by at least one of the second openings 64 a, . . . , 64 i, 64 j, . . . , 64 n formed in the plate 6 a, . . . , 6 i, 6 j, . . . , 6 n. - It then follows from the foregoing that, in the
thermal system 500 according to the invention, as illustrated inFIG. 1 , the flowrate of heat-transport liquid circulating in the second conduit 11 is lower than the flowrate of heat-transport liquid circulating in the first conduit 10. The above-defined second bore section 160, which is smaller than thefirst bore section 150, therefore forms a differentiating member 155 differentiating the flowrate of heat-transport liquid within theheat exchanger 100. - Stated differently, the flowrate differentiating member 155 that differentiates the flowrate of the heat-transport liquid is formed here by at least one of the second openings 64 a, . . . , 64 i, 64 j, . . . , 64 n contributing to defining the second conduit 11 of the first inlet header 1, which has the second bore section 160 smaller than the
first bore section 150 of the first conduit 10 of the first inlet header 1. - It will be appreciated from the foregoing that the differentiating member 155 is formed by one of the second openings 64 a, . . . , 64 i, 64 j, . . . , 64 n of the second conduit 11. Alternatively, the differentiating member may be defined by all of the second openings 64 a, . . . , 64 i, 64 j, . . . , 64 n of the second conduit 11.
- Because of the presence of this differentiating member 155, the residence time that the heat-transport liquid spends in the second group of
chambers 76, which is supplied with heat-transport liquid by the second conduit 11, is longer than the residence time that the heat-transport liquid spends in the first group ofchambers 75 which is supplied with heat-transport liquid by the first conduit 10. The duration of the exchange of heat between the heat-transport liquid circulating in the second group ofchambers 76 and the refrigerant fluid is therefore longer than the duration of the exchange of heat between the heat-transport liquid circulating in the first group ofchambers 75 and the refrigerant fluid. This then results in greater effectiveness of the exchange of heat that takes place between the heat-transport liquid circulating in the second group ofchambers 76 and the refrigerant fluid circulating in the pass, as defined hereinabove, that is in contact with the second group ofchambers 76 in theheat exchanger 100. -
FIG. 3 schematically illustrates, in section on the vertical and transverse plane A visible inFIG. 1 , a second example of how aheat exchanger 100 according to the invention may be embodied. - This figure again shows the
heat exchanger 100, the first inlet header 1 and the first conduit 10 and second conduit 11 of the first inlet header 1. ThisFIG. 3 also again shows two plates 6 i, 6 j of theheat exchanger 100 and a chamber 7 i of thefirst circuit 110 of theexchanger 100, which chamber is delimited by the aforesaid plates 6 i, 6 j. As in the example illustrated inFIG. 2 , the second bore section 160 of the second conduit 11 is smaller than thefirst bore section 150 of the first conduit 10. Likewise, in the same way as in the example illustrated byFIG. 2 , theheat exchanger 100 comprises thesupply unit 5, which comprises thefirst duct 50 fluidically connected to the first conduit 10 of the first inlet header 1, and thesecond duct 51 fluidically connected to the second conduit 11 of the first inlet header 1. - In the variant illustrated by
FIG. 3 , at least one of the first openings 63 i′, 63 j′ that contribute to defining, in the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n, the first conduit 10, has a third bore section 170 smaller than thefirst bore section 150 of the first conduit 10. - In other words, in this variant, the first conduit 10 of the first inlet header 1 comprises a
first portion 10 a of which a bore section is substantially equal to the aforementionedfirst bore section 150, and asecond portion 10 b of which a bore section is smaller than the aforesaidfirst bore section 150 and substantially equal, to within the manufacturing tolerances, to the aforementioned third bore section 170. According to the invention, a ratio between the bore section 170 and thefirst bore section 150 is comprised between 0.4 and 0.8. - According to various embodiments of the invention, just one or several of the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n that form the
second portion 10 b of the first conduit 10 has a first opening 63 i′, 63 j′ of which the bore section is substantially equal to the aforementioned third bore section 170. In other words, according to various embodiments of the invention, just one of the first openings 63 i′, 63 j′ arranged in the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n that form thesecond portion 10 b of the first conduit 10 has a bore section equal to the third bore section 170, or several, or even all, of the first openings 63 i′, 63 j′ arranged in the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n that form thesecond portion 10 b of the first conduit 10 have a bore section equal to the third bore section 170. - Advantageously, the chambers 7 i, . . . , 7 n delimited by the plates 6 i, . . . , 6 n in which the first opening or openings 63 i′, 63 j′ having the third bore section 170 are arranged together form a third group of chambers 77 of the
first circuit 110 of theheat exchanger 100, which group finds itself in contact, in theheat exchanger 100, with a third pass of thesecond circuit 120 of this heat exchanger. It will then be appreciated that thefirst circuit 110 comprises the third group of chambers 77 which is fluidically connected to the first conduit 10 of the first inlet header 1, successively with the first group ofchambers 75, and that the third bore section 170 of the first conduit 10, which bore section is located between the first group ofchambers 75 and the third group of chambers 77, forms part of the above-defined differentiating member 155. - It then follows from the foregoing that, within the thermal system, the flowrate of heat-transport liquid circulating in the second group of
chambers 76, and the flowrate of heat-transport liquid circulating in the third group of chambers 77, are reduced in comparison with the flowrate of heat-transport liquid circulating in the first group ofchambers 75. - In one example, the invention may make provision, on the one hand, for the first group of
chambers 75 of thefirst circuit 110 of theheat exchanger 100 to be in contact with a first pass of thesecond circuit 120, in which pass the refrigerant fluid circulates in essentially gaseous form and, on the other hand, for the second group ofchambers 76 of thefirst circuit 110 of theheat exchanger 100 to be in contact with a second pass of thesecond circuit 120, in which pass the refrigerant fluid passes in the liquid state, and for the third group of chambers 77 of thefirst circuit 110 of theheat exchanger 100 to be in contact with a third pass of thesecond circuit 120, in which pass the refrigerant fluid circulates in liquid form and is supercooled by the heat-transport liquid, the temperature of the refrigerant fluid in the liquid state being lowered below its saturation temperature. -
FIG. 4 schematically illustrates, in section on the vertical and transverse plane A visible inFIG. 1 , a third example of how the invention may be embodied. This figure more specifically illustrates the above-definedsupply unit 5 of theheat exchanger 100 according to the invention, as well as the above-describedfirst duct 50 andsecond duct 51 of thissupply unit 5. - According to the example more particularly illustrated by
FIG. 4 , the invention makes provision for the above-defined differentiating member 155 to be formed on thefirst duct 50 fluidically connected to the first conduit 10 of the first inlet header 1, and by thesecond duct 51 of thesupply unit 5 fluidically connected to the second conduit 11 of the first inlet header 1. - More specifically, according to this example, the invention makes provision for the
first duct 50 of thesupply unit 5 to have afirst bore section 500, and for thesecond duct 51 to have a second bore section 510, thefirst bore section 500 of thefirst duct 50 being greater than thesecond bore section 500 of thesecond duct 51. A ratio between thesecond bore section 500 of thesecond duct 51 and thefirst bore section 500 of thefirst duct 50 is comprised between 0.4 and 0.8. - It will be appreciated here that the differentiating member 155 is formed by the second bore section 160 of the
second duct 51 being smaller than thefirst bore section 500 of thefirst duct 50. The differentiating member is therefore indeed here supported by thesupply unit 5 rather than, as in the preceding examples, being arranged actually within the openings 62 a, . . . , 62 i, 62 j, . . . 62 n of the plates 6 a, . . . , 6 i, 6 j, . . . 6 n. - Such an arrangement offers an advantage in terms of cost, in so far as the advantages of the invention can be combined with a standardization of all of the plates 6 a, . . . , 6 i, 6 j, . . . 6 n that form the
heat exchanger 100. Specifically, there is then no longer any need to differentiate the manufacture of the various sets of plates having different openings delimiting the different conduits of the first inlet header 1, since the differentiating of flowrate between the aforesaid conduits is performed upstream of the heat exchange zone, as the heat-transport liquid enters the inlet header 1 made up of the above-described conduits 10, 11. Such an arrangement furthermore reduces the risks of errors of assembly during the stacking of the various sets of plates 6 a, . . . , 6 i, 6 j, . . . 6 n having openings 63 a, . . . , 63 i, 63 j, . . . , 63 n, 64 a, . . . , 64 i, 64 j, . . . , 64 n of which the geometric characteristics differ according to whether they are intended to delimit the aforementioned first conduit 10 or the aforementioned second conduit 11 of thefirst circuit 110. - Whatever the variant considered, the invention makes it possible, using simple means, to differentiate the flowrate of heat-transport liquid between various regions of the
first circuit 110 of theheat exchanger 100, so as to differentiate the duration of the exchange of heat performed between this heat-transport liquid and the refrigerant fluid circulating in thesecond circuit 120 of theheat exchanger 100 and thus increase the efficiency of this exchange in predefined regions of theheat exchanger 100. - It should be noted that this differentiation of the flowrate of the heat-transport liquid within the
heat exchanger 100 of athermal system 500 like the one illustrated inFIG. 1 is the result solely of the geometry of the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n which make up theheat exchanger 100 and, notably, of the dimensions of the openings which, pierced in these plates, delimit therein the first inlet header 1 via which the heat-transport liquid is admitted to thefirst circuit 110 of theheat exchanger 100. - According to one method of manufacture in which the plates 6 a, . . . , 6 i, 6 j, . . . , 6 n are, for example, produced by pressing a thin sheet, implementation of the invention therefore proves to be extremely simple and very low in cost insofar as it requires nothing more than a change to the dimensions of one or more of the openings made in these plates in order to delimit the first inlet header 1.
- The invention as has just been described nevertheless is not limited to the exclusively described and illustrated means and configurations, and is also applicable to all equivalent means or configurations and to any combination of such means or configurations.
Claims (11)
1. A heat exchanger for a motor vehicle comprising:
a first circuit through which a heat-transport liquid is intended to pass and which comprises a first inlet header via which the heat-transport liquid is admitted to the first circuit and a first outlet header via which the heat-transport liquid leaves the first circuit,
the first circuit comprising a plurality of chambers which are fluidically connected to the first inlet header and to the first outlet header and are split into at least a first group of chambers and a second group of chambers; and
a second circuit through which a refrigerant fluid is configured to pass and which comprises a second inlet header via which the refrigerant fluid is admitted into the heat exchanger and a second outlet header via which the refrigerant fluid leaves the heat exchanger, the second circuit comprising at least two successive passes,
the heat exchanger being configured to perform an exchange of heat between the heat-transport liquid circulating in at least one of the groups of chambers and at least one of the passes of the second circuit,
wherein the heat exchanger comprises at least one differentiation member for differentiating the per-chamber flowrate of heat-transport liquid circulating in the first group of chambers from the per-chamber flowrate of heat-transport liquid circulating in the second group of chambers of the first circuit.
2. The heat exchanger as claimed in claim 1 , wherein each chamber is delimited by at least two plates, each plate comprising a bottom wall surrounded by a turned-up edge, the bottom wall being provided with at least one opening which at least in part delimits the first inlet header, the two plates being positioned one inside the other.
3. The heat exchanger as claimed in claim 1 , wherein the first inlet header comprises a first conduit supplying the first group of chambers and a second conduit supplying the second group of chambers, the differentiation member involving a second bore section of the second conduit that is smaller than a first bore section of the first conduit.
4. The heat exchanger as claimed in claim 3 , wherein a ratio between the second bore section of the second conduit and the first bore section of the first conduit is comprised between 0.4 and 0.8.
5. The heat exchanger as claimed in claim 2 , wherein the bottom walls of the at least two plates each comprise at least a first opening and a second opening, which respectively make up the first conduit and the second conduit of the first inlet header.
6. The heat exchanger as claimed in claim 4 , wherein the differentiation member is formed of at least a second opening that makes up the second conduit.
7. The heat exchanger as claimed in claim 5 , wherein the differentiation member comprises all of the second openings of the second conduit.
7. The heat exchanger as claimed in claim 1 , comprising at least one heat-transport-liquid supply unit, the supply unit being fluidically connected to the first inlet header which comprises a first conduit supplying the first group of chambers and a second conduit supplying the second group of chambers.
8. The heat exchanger as claimed in claim 7 , wherein the supply unit comprises a first duct supplying the first conduit and a second duct supplying the second conduit of the first inlet header, the differentiation member involving a second bore section of the second duct that is smaller than a first bore section of the first duct.
9. The heat exchanger as claimed in claim 3 , wherein the first heat-transport liquid circuit comprises a third group of chambers which are fluidically connected to the first conduit of the first inlet header and to the first outlet header successively to the first group of chambers, the heat-transport liquid flowrate differentiation member comprising at least a third bore section of the first conduit, positioned between the first group of chambers and the third group of chambers, the third bore section being smaller than the first bore section of the first conduit.
10. A thermal conditioning system for a motor vehicle comprising at least one heat exchanger as claimed in claim 1 .
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR2006807A FR3111971B1 (en) | 2020-06-29 | 2020-06-29 | Motor vehicle heat exchanger |
FR2006807 | 2020-06-29 | ||
PCT/EP2021/066457 WO2022002617A1 (en) | 2020-06-29 | 2021-06-17 | Heat exchanger for a motor vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
US20230288146A1 true US20230288146A1 (en) | 2023-09-14 |
Family
ID=73642981
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US18/013,390 Pending US20230288146A1 (en) | 2020-06-29 | 2021-06-17 | Heat exchanger for a motor vehicle |
Country Status (5)
Country | Link |
---|---|
US (1) | US20230288146A1 (en) |
EP (1) | EP4172549A1 (en) |
CN (1) | CN115769041A (en) |
FR (1) | FR3111971B1 (en) |
WO (1) | WO2022002617A1 (en) |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5462113A (en) * | 1994-06-20 | 1995-10-31 | Flatplate, Inc. | Three-circuit stacked plate heat exchanger |
US5964280A (en) * | 1996-07-16 | 1999-10-12 | Modine Manufacturing Company | Multiple fluid path plate heat exchanger |
SE514096C2 (en) * | 1999-05-17 | 2001-01-08 | Alfa Laval Ab | plate heat exchangers |
DE10328746A1 (en) * | 2003-06-25 | 2005-01-13 | Behr Gmbh & Co. Kg | Multi-stage heat exchange apparatus and method of making such apparatus |
EP2629040B1 (en) * | 2012-02-14 | 2020-07-29 | MAHLE International GmbH | A unitary heat pump air conditioner having a heat exchanger with an integral receiver and sub-cooler. |
-
2020
- 2020-06-29 FR FR2006807A patent/FR3111971B1/en active Active
-
2021
- 2021-06-17 CN CN202180046169.9A patent/CN115769041A/en active Pending
- 2021-06-17 EP EP21733972.0A patent/EP4172549A1/en active Pending
- 2021-06-17 US US18/013,390 patent/US20230288146A1/en active Pending
- 2021-06-17 WO PCT/EP2021/066457 patent/WO2022002617A1/en unknown
Also Published As
Publication number | Publication date |
---|---|
WO2022002617A1 (en) | 2022-01-06 |
CN115769041A (en) | 2023-03-07 |
FR3111971B1 (en) | 2022-08-05 |
EP4172549A1 (en) | 2023-05-03 |
FR3111971A1 (en) | 2021-12-31 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1058080B1 (en) | Heat exchanger | |
US11519673B2 (en) | Plate heat exchanger and heat pump device including the same | |
US10254022B2 (en) | Condenser with a refrigerant supply for an air-conditioning circuit | |
US20090151918A1 (en) | Heat Exchanger for Automobile and Fabricating Method Thereof | |
JP5985600B2 (en) | Reinforce connection between heat exchanger plates | |
WO2014041771A1 (en) | Heat exchanger | |
US20090242182A1 (en) | Heat Exchanger Plate | |
ES2626802T3 (en) | High cooling capacity heat exchanger | |
KR20040007807A (en) | Heat exchanger | |
US20090050304A1 (en) | Heat exchanger for motor vehicles | |
US20230288146A1 (en) | Heat exchanger for a motor vehicle | |
KR101745280B1 (en) | Heat transfer device and method for manufacturing thereof | |
KR102609386B1 (en) | Heat exchanger and air conditioner for vehicle | |
KR20170121756A (en) | Cooling water waste heat recovering heat exchanger manufacturing method thereof | |
JP4547205B2 (en) | Evaporator | |
CN114041035A (en) | CCF heater core subassembly | |
US20230003458A1 (en) | Three-fluid plate heat exchanger | |
WO2018229234A1 (en) | Evaporator having two layers, in particular for a motor vehicle air conditioning circuit, comprising u-shaped tubes and a corresponding air conditioning circuit | |
WO2009013180A1 (en) | Heat exchanger with mini- and/or micro-channels | |
US20210001690A1 (en) | Evaporator, notably for a motor vehicle air conditioning circuit, and corresponding air conditioning circuit | |
KR20230100174A (en) | Water cooled condenser | |
KR19980061905A (en) | Condenser of car air conditioners | |
WO2022248441A1 (en) | Heat exchanger for a motor vehicle | |
CN117716194A (en) | Heat exchanger for a motor vehicle | |
US20110005736A1 (en) | Heat exchanger, in particular for an internal combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |