US20180128551A1 - Plate heat exchanger and reversible refrigerating machine including such an exchanger - Google Patents
Plate heat exchanger and reversible refrigerating machine including such an exchanger Download PDFInfo
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- US20180128551A1 US20180128551A1 US15/570,082 US201615570082A US2018128551A1 US 20180128551 A1 US20180128551 A1 US 20180128551A1 US 201615570082 A US201615570082 A US 201615570082A US 2018128551 A1 US2018128551 A1 US 2018128551A1
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- circuit
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- 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
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- 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
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- 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
Definitions
- the present invention relates to a plate heat exchanger as well as to a refrigerating machine including such an exchanger.
- FIG. 1 shows a brazed plate heat exchanger 100 , provided with a set of superposed plates 2 A, 2 B and 2 C.
- Each plate 2 A, 2 B and 2 C has its opposite surfaces corrugated according to a precise scheme, for example, a chevron profile.
- the edges of the plates are provided with gaskets to prevent fluid leaks.
- the plates 2 A, 2 B and 2 C are arranged against one another, between two end plates 11 and 12 , so that the corrugated surfaces of two adjacent plates together define channels 20 for the circulation of heat-exchanging fluids.
- Each plate 2 A, 2 B and 2 C and each end plate 11 and 12 comprises four openings each produced in one of their corners, namely a first opening 21 which is used as inlet E 1 for a first heat-exchanging fluid, a second opening 22 which is used as outlet S 1 for the first heat-exchanging fluid, a third opening 23 which is used as inlet E 2 for a second heat-exchanging fluid, and a fourth opening 24 which is used as outlet S 2 for the second heat-exchanging fluid.
- the channels 20 defined against each corrugated surface receive the first or the second heat-exchanging fluid.
- the first heat-exchanging fluid circulates in a first circuit between the second and third plates 2 B and 2 C.
- the second heat-exchanging fluid circulates in a second circuit which extends between the plates 2 A and 2 B.
- the first and second heat-exchanging fluids circulate alternately between two adjacent plates 2 A, 2 B and 2 C so as to ensure a transfer of thermal energy between the fluids.
- FIG. 2 shows a reversible refrigerating machine which includes a compressor 400 , a pressure reducing valve 200 and two exchangers 100 and 300 similar to the exchanger of FIG. 1 . These four elements are mounted on a common circuit C of refrigerant fluid.
- the exchangers 100 and 300 work alternately as condenser or evaporator depending on whether the refrigerating machine operates in heating mode or in air conditioning mode, the change in mode occurring by changing the direction of circulation of the refrigerant fluid in the common circuit C.
- the first exchanger 100 implements a heat transfer between the common circuit C and a first exchange circuit C 10 .
- the second exchanger 300 implements a heat transfer between the common circuit C and a second exchange circuit C 20 .
- one of the exchangers 100 and 300 runs counter-currently with respect to the exchange circuit C 10 or C 20 which interacts with this exchanger, while the other exchanger runs co-currently with respect to the other exchange circuit C 10 or C 20 .
- the performances of a plate heat exchanger are better counter-currently than co-currently, so that for each operating mode, one of the exchangers 100 and 300 does not have an optimized yield.
- DE 10 2006 002 018 discloses a reversible refrigerating machine which makes it possible to change the operating mode without reversing the direction of circulation of the refrigerant fluid, using a three-way valve installed on the refrigerating circuit.
- This solution is complex to implement, since it requires the installation of a device for distributing the refrigerant fluid.
- the invention aims to remedy more particularly by proposing a novel plate exchanger which is easy to use in a reversible refrigerating machine and which has a satisfactory yield.
- the invention relates to a plate heat exchanger including superposed plates which are inserted between two end plates and which define channels for circulation of heat-exchanging fluid, characterized in that the channels delimit
- such an exchanger can incorporate one or more of the following features, considered in any technically acceptable combination:
- Another aspect of the invention relates to a reversible refrigerating machine including a common circuit of refrigerating fluid, on which are arranged a compressor, a pressure reducing valve and two exchangers which are each as defined above.
- such a refrigerating machine can incorporate one or more of the following features, considered in any technically acceptable combination:
- FIG. 1 is an exploded perspective view of a plate exchanger of the prior art
- FIG. 2 is a diagrammatic view of a reversible refrigerating machine of the prior art
- FIG. 3 is an exploded diagrammatic view of an exchanger according to a first embodiment of the invention.
- FIGS. 4 and 5 are diagrams of the exchanger of FIG. 3 with a first and a second direction of circulation, respectively, of the heat-exchanging fluids;
- FIGS. 6 and 7 are diagrams of refrigerating machines including the exchanger of FIG. 3 ;
- FIG. 8 is a diagram of the exchanger of FIG. 3 according to another orientation
- FIG. 9 is an exploded perspective view of an exchanger according to a second embodiment of the invention.
- FIGS. 10 and 11 are diagrams of the exchanger of FIG. 9 with a first and a second direction of circulation, respectively, of the heat-exchanging fluids;
- FIGS. 12 and 13 are diagrams of a tube for distributing fluid
- FIGS. 14 to 17 are diagrams of an exchanger according to a third embodiment of the invention, with different directions of circulation of the heat-exchanging fluids;
- FIGS. 18 to 21 are diagrams of an exchanger according to a fourth embodiment of the invention, with different directions of circulation of the heat-exchanging fluids.
- FIGS. 22 and 23 are diagrams of the tube of FIGS. 12 and 13 , positioned for an exchanger in one of the configurations of FIGS. 14, 15, 18 and 19 and for one of the configurations of FIGS. 16, 17, 20 and 21 , respectively.
- FIG. 3 shows a plate exchanger 1100 according to the invention. It includes a first end plate 11 which defines a first external surface A of the exchanger 1100 , and a second end plate 12 which defines a second external surface B of the exchanger 1100 opposite the first surface A.
- Twelve plates 2 A to 2 L are superposed, that is to say arranged successively, one against the other, between the end plates 11 and 12 .
- the plate 2 K is arranged against the first end plate 11
- the plate 2 L is arranged against the second end plate 12 .
- the end plates 11 and 12 and the plates 2 A to 2 L have an overall rectangular shape.
- the exchanger 1100 has an overall parallelepiped shape with rectangular base. M is used to designate an upper edge of the exchanger 1100 located at the top of FIG. 3 , and N is used to designate a lower edge of the exchanger 1100 parallel to the upper edge M and located at the bottom of FIG. 3 .
- the edges M and N are of small length and connect together long edges O and P of the end plates 11 and 12 and of the plates 2 A to 2 L, which are perpendicular to the short edges M and N.
- the long edge O is located in the foreground of FIG. 3 and the long edge P in the background.
- Each plate 2 A to 2 L comprises two opposite rectangular surfaces which are corrugated according to a precise scheme which does not limit the invention, for example, a chevron profile. These corrugations are not represented in FIG. 3 ; they can be similar to those of the exchanger of FIG. 1 .
- the edges M, N, 0 and P of the plates 2 A to 2 L are provided with brazed gaskets, not shown, in order to prevent fluid leaks.
- the corrugated surfaces facing one another of two adjacent plates 2 A to 2 L together define channels for the turbulent circulation of heat-exchanging fluids, these channels not being shown in FIG. 3 but possibly similar to the channels 20 of FIG. 1 .
- the exchanger 1100 comprises a first zone Z 1 , between the first end plate 11 and the plate 2 E, and a second zone Z 2 , between the plate 2 F and the second end plate 12 .
- the zones Z 1 and Z 2 are adjoining.
- the first zone Z 1 is located on the side of the first surface A of the exchanger 1100
- the second zone Z 2 is located on the side of the second surface B.
- the zones Z 1 and Z 2 divide the exchanger 1100 in two in its thickness, that is to say in a direction perpendicular to the end plates 11 and 12 and to the plates 2 A to 2 L.
- the exchanger 1100 delimits two heat-exchanging fluid circuits C 1 and C 2 .
- the first circuit C 1 is provided for water and the second circuit C 2 for a refrigerant fluid.
- the first circuit C 1 corresponds to one of the exchange circuits C 10 or C 20 of the refrigerating machine of FIG. 2
- the second circuit C 2 corresponds to the common circuit C.
- the circuits C 1 and C 2 are defined so that the water circuit C 1 comprises a single pass, that is to say the fluid circulates between the edges N and M in a single direction, namely from bottom to top in the example of FIG. 3 .
- the refrigerant fluid circuit C 2 comprises two passes, namely an inlet pass in the zone Z 2 , where the refrigerant fluid circulates in a first direction, namely from bottom to top between the edges N and M, and an outlet pass in the zone Z 1 , where the refrigerant fluid circulates in a second direction opposite from the first direction, that is to say from top to bottom between the edges M and N.
- This configuration results from the particular arrangement of the corrugations of the plates 2 A to 2 L and of the holes 21 to 24 produced in the corners of the end plates 11 and 12 and of the plates 2 A to 2 L as described below.
- the end plates 11 and 12 and the plates 2 A to 2 L are each provided with a number of holes between one and four, so as to guide the circulation of the fluids in the circuits C 1 and C 2 .
- the hole 21 is located in a first lower corner, at the junction between the edges N and P.
- the hole 22 is located in a second lower corner, at the junction between the edges N and O.
- the hole 23 is located in a first upper corner, at the junction between the edges M and P.
- the hole 24 is located in a second upper corner, at the junction between the edges M and O.
- an inlet E 1 of the first circuit C 1 is formed by a first hole 21 of the second end plate 12 , in the zone Z 2 .
- the first circuit C 1 comprises a first lower branch or forward branch C 11 in which the fluid circulates up to the plate 2 K, through holes 21 which are perforated in each plate 2 A to 2 J and 2 L.
- the first end plate 11 and the plate 2 K have no hole 21 .
- a second upper branch or return branch C 12 of the first circuit C 1 is defined between the plate 2 K and a hole 23 of the second end plate 12 , which defines an outlet S 1 of the first circuit C 1 in the second zone Z 2 .
- the first end plate 11 and the plate 2 K have no hole 23 . Between the plates 2 K and 2 L, the fluid circulates through holes 23 perforated in each plate 2 A to 2 J and 2 L.
- the first circuit C 1 comprises several intermediate branches C 13 to C 18 connected in parallel between the branches C 11 and C 12 .
- the intermediate branches C 13 to C 18 are represented in a rectilinear manner in the diagram of FIG. 3 , but in practice they meander in the pattern defined by the corrugations of the plates 2 A to 2 L.
- the branches C 13 to C 15 are part of the second zone Z 2
- the branches C 16 to C 18 are part of the first zone Z 1 .
- the first circuit C 1 has a single pass from the edge N and towards the edge M.
- the fluid circulates in the first circuit C 1 in a single direction, namely from bottom to top.
- An inlet E 2 of the second circuit C 2 is formed by a hole 22 of the second end plate 12 , in the second zone Z 2 .
- the second circuit C 2 comprises a first lower branch C 21 , which extends exclusively in the second zone Z 2 and which connects the second inlet E 2 to a first and a second intermediate branch C 22 and C 23 connected in parallel between the lower branch C 21 and an upper branch C 24 .
- the intermediate branches C 22 and C 23 the fluid circulates from bottom to top, from the edge N to the edge M.
- the plates 2 F and 2 G have no hole 22 .
- the upper branch C 24 extends through holes 24 perforated in the plates 2 B to 21 in zones Z 1 and Z 2 , and it is connected to two other intermediate branches C 25 and C 26 in which the fluid circulates from top to bottom, from the edge M to the edge N.
- the intermediate branches C 25 and C 26 connect in parallel the upper branch C 24 to a second lower branch C 27 , which extends exclusively in the first zone Z 1 , through holes 22 perforated in the plates 2 A to 2 C, 2 K and in the first end plate 11 , up to an outlet S 2 of the second circuit C 2 formed by the hole 22 of the end plate 11 , in the first zone Z 1 .
- the second circuit C 2 has an inlet pass where the fluid circulates in a first direction, namely from the lower edge N and towards the upper edge M.
- the second circuit C 2 has an outlet pass where the fluid circulates in a second direction opposite from the first direction, namely from the upper edge M and towards the lower edge N.
- FIGS. 4 and 5 more diagrammatically again show the arrangement of the circuits C 1 and C 2 of the exchanger 1100 .
- FIG. 4 corresponds to the first direction of circulation of FIG. 3 for the circuit C 2
- FIG. 5 to a second opposite direction of circulation.
- the first direction of circulation of FIGS. 3 and 4 corresponds to a first operating mode, in which the exchanger 1100 operates by evaporation.
- the refrigerant fluid of the circuit C 2 performs a first pass that is co-current with respect to the water of the circuit C 1 , it circulates from bottom to top between the edges N and M and, in the first zone Z 1 , the refrigerant fluid of the circuit C 2 performs a second pass that is counter-current with respect to the water of the circuit C 1 , it circulates from top to bottom between the edges M and N.
- the refrigerant fluid in the second circuit C 2 performs a first pass that is co-current with respect to the water of the first circuit C 1 , it circulates from bottom to top from the lower edge N towards the upper edge M, and, in the second zone Z 2 , the refrigerant fluid in the second circuit C 2 performs a second pass that is counter-current with respect to the water of the first circuit C 1 , it circulates from top to bottom from the upper edge M towards the lower edge N.
- the exchanger 1100 makes it possible for the refrigerant fluid of the circuit C 2 to perform a first pass that is co-current and a second pass that is counter-current with respect to the water of the circuit C 1 . In this manner, the thermal yield of the exchanger 1100 is improved, since, in each operating mode, the fluids of the circuits C 1 and C 2 circulate counter-currently for the zone corresponding to the outlet pass of the circuit C 2 .
- FIGS. 6 and 7 show a reversible refrigerating machine which includes a compressor 400 , a pressure reducing valve 200 , and two exchangers 1100 and 1200 each similar to the exchanger of FIGS. 3 to 5 . These four elements 400 , 200 , 1100 and 1200 are mounted on a common circuit C of refrigerant fluid.
- the first exchanger 1100 implements a heat transfer between the common circuit C and a first exchange circuit C 10 .
- the second exchanger 1200 implements a heat transfer between the common circuit C and a second exchange circuit C 20 .
- the exchangers 1100 and 1200 operate alternately as condenser or evaporator depending on whether the refrigerating machine operates in heating mode or in air conditioning mode.
- the change in mode occurs by changing the direction of circulation of the refrigerant fluid in the common circuit C using a four-way valve V 1 .
- the exchanger 1100 operates by condensation, and the second exchanger it operates by evaporation.
- the valve V 1 is in a first position.
- the refrigerant fluid of the common circuit C circulates in a first direction.
- the first exchange circuit C 10 is a hot water circuit
- the second exchange circuit C 20 is a cold water circuit.
- the exchanger 1100 operates by evaporation, and the second exchanger operates by condensation.
- the valve V 1 is in a second position.
- the refrigerant fluid of the common circuit C circulates in a second direction opposite from the first direction of FIG. 6 .
- the first exchange circuit C 10 is a cold water circuit
- the second exchange circuit C 20 is a hot water circuit.
- each of the exchangers 1100 and 1200 operates, for one of the zones Z 1 and Z 2 , counter-currently, while for the other zone Z 2 or Z 1 , the exchangers 1100 and 1200 operate co-currently.
- the first pass or inlet pass of the common circuit C in the zone Z 2 is performed co-currently with respect to the corresponding exchange circuit C 10 or C 20
- the second pass or outlet pass of the common circuit C in the zone Z 1 is carried out counter-currently with respect to the corresponding exchange circuit C 10 or C 20 .
- This configuration corresponds to that of FIG. 4 .
- the first pass or inlet pass of the common circuit C in the zone Z 1 is performed co-currently with respect to the corresponding exchange circuit C 10 or C 20
- the second pass or outlet pass of the common circuit C in the zone Z 2 is carried out counter-currently with respect to the corresponding exchange circuit C 10 or C 20 .
- This configuration corresponds to that of FIG. 5 .
- the exchanger 1100 is arranged according to a first orientation, in which the inlets E 1 and E 2 of the circuits C 1 and C 2 are arranged at the bottom of the exchanger 1100 , along the lower edge N.
- the fluid of the circuit C 1 , in the two zones Z 1 and Z 2 , and the fluid of the circuit C 2 , in the zone Z 2 for the configuration of FIG. 4 , and in the zone Z 1 for the configuration of FIG. 5 circulate upwards, against the force exerted by gravity.
- FIG. 8 shows the exchanger 1100 according to a second orientation, in which the edge M is oriented towards the bottom, while the edge N is oriented towards the top.
- the inlets E 1 and E 2 of the circuits C 1 and C 2 are arranged at the top of the exchanger 1100 , along the upper edge M.
- the fluid of the circuit C 1 , in the two zones Z 1 and Z 2 , and the fluid of the circuit C 2 , in the zone Z 1 circulate downward in the direction of the force exerted by gravity.
- the flow of the water in the circuit C 1 is counter-current with respect to the flow of the refrigerant fluid in the outlet pass of the circuit C 2 , that is to say the flow of the water is directed upward when the inlet E 2 and the outlet S 2 are at the bottom, as shown in FIGS. 4 to 7 , and is directed downward when the inlet E 2 and the outlet S 2 are at the top, as shown in FIG. 8 .
- FIG. 9 shows an exchanger 2100 according to a second embodiment of the invention, of the dual-circuit exchanger type.
- the elements of the exchanger 2100 similar to those of the exchanger 1100 bear the same reference numbers. Below, the elements of the exchanger 2100 that are similar to those of the exchanger 1100 are not described in detail.
- the exchanger 2100 comprises two independent refrigerant fluid circuits C 2 and C′ 2 , which can implement two passes when they are connected to one another appropriately by means of a duct C 3 represented with dotted lines in FIG. 9 .
- the duct C 3 is represented diagrammatically in FIGS. 10 and 11 which are described in greater detail below.
- the exchanger 2100 comprises two end plates 11 and 12 and eight corrugated plates 2 A to 2 H arranged between the end plates 11 and 12 .
- the exchanger 2100 also has an intermediate end plate 13 inserted between the plates 2 D and 2 E.
- the intermediate end plate 13 materially delimits the separation between the zones Z 1 and Z 2 .
- the exchanger 2100 has a generally rectangular shape and comprises an upper edge M, a lower edge N, and two lateral edges O and P.
- the end plates 11 , 12 and 13 and the plates 2 A to 2 H are provided with holes 21 , 22 , 23 and/or 24 .
- the first circuit C 1 provided, for example, for water in the case in which a refrigerating machine is used, comprises an inlet E 1 implemented by a hole 24 produced in the end plate 11 .
- the first circuit C 1 comprises a first branch or forward branch C 11 which starts from the inlet E 1 and passes through holes 24 produced in the plates 2 A to 2 G as well as in the intermediate end plate 13 .
- a second lower branch or return branch C 12 of the first circuit starts at the outlet S 1 and passes through holes 22 produced in the plates 2 A to 2 G as well as in the intermediate end plate 13 .
- the fluid circulates through holes 22 perforated in each plate 2 A to 2 G.
- the first circuit C 1 comprises several intermediate branches C 13 to C 16 connected in parallel between the branches C 11 and C 12 .
- the intermediate branches C 13 to C 16 are represented in a rectilinear manner in the diagram of FIG. 9 , but in practice they meander in the pattern defined by the corrugations of the plates 2 A to 2 H.
- the branches C 13 and C 14 are part of the first zone Z 1
- the branches C 15 and C 16 are part of the second zone Z 2 .
- the first circuit C 1 has a single pass, from the upper edge M and towards the lower edge N.
- the fluid circulates in the first circuit C 1 in a single direction, namely from top to bottom.
- the circuit C 2 comprises an inlet E 20 formed by a hole 23 produced in the end plate 12 .
- a first upper branch C 21 or forward branch of the circuit C 2 extends from the inlet E 20 and the plate 2 F, in the second zone Z 2 , through holes 23 produced in the plates 2 G and 2 H.
- the circuit C 2 has an outlet S 20 formed by a hole 21 produced in the end plate 12 .
- a second lower branch C 22 or return branch of the circuit C 2 extends between the outlet S 20 and the plate 2 F, in the second zone Z 2 , through holes 21 produced in the plates 2 G and 2 H.
- the branches C 21 and C 22 are connected to one another by an intermediate branch C 23 which is delimited between the plates 2 F and 2 G.
- the circuit C′ 2 comprises an inlet E′ 20 formed by a hole 21 produced in the end plate 11 .
- a first lower branch C′ 21 or forward branch of the circuit C′ 2 extends between the inlet E′ 20 and the plate 2 C, in the first zone Z 1 , through holes 21 produced in the plates 2 A and 2 B.
- the circuit C′ 2 comprises an outlet S′ 20 formed by a hole 23 produced in the end plate 11 .
- a second upper branch C′ 22 or return branch of the circuit C′ 2 extends between the outlet S′ 20 and the plate 2 C, in the first zone Z 1 , through holes 23 produced in the plates 2 A and 2 B.
- branches C′ 21 and C′ 22 are connected to one another by an intermediate branch C′ 23 which is delimited between the plates 2 B and 2 C.
- the refrigerant fluid in the circuits C 2 and C′ 2 circulates in a first direction, and the connection between the circuits C 2 and C′ 2 is implemented by means of a connection conduit C 3 which connects the outlet S 20 of the circuit C 2 to the inlet E′ 20 of the circuit C′ 2 .
- the outlet S′ 20 of the exchanger 2100 as represented in FIG. 9 becomes the outlet S 2 of the common circuit of heat-exchanging fluid formed by the combination of the circuits C 2 and C′ 2 .
- the inlet E 20 becomes the inlet E 2 of the common circuit C 2 and C′ 2 .
- the first circuit C 1 has a single pass, from the edge M and towards the edge N.
- the fluid circulates in the first circuit C 1 in a single direction, namely from top to bottom.
- the second circuit C 2 and C′ 2 comprises a first pass or forward pass in the zone Z 2 , where the fluid circulates co-currently in the circuit C 2 , and a second pass or return pass in the zone Z 1 , where the fluid circulates counter-currently in the circuit C′ 2 .
- FIG. 11 the direction of circulation of the fluid in the circuits C 2 and C′ 2 is reversed.
- the inlet E 2 is in the zone Z 1 at the beginning of the circuit C′ 2
- the outlet S 2 is in the zone Z 2 , at the outlet of the circuit C 2 .
- the second circuit C 2 and C′ 2 comprises a first pass or forward pass in the zone Z 1 , where the fluid circulates co-currently in the circuit C′ 2 , and a second pass or return pass in the zone Z 2 , where the fluid circulates counter-currently in the circuit C 2 .
- the exchanger 2100 comprises a pass that is co-current and a pass that is counter-current, which makes it possible to optimize the thermal exchanges.
- each exchanger comprises two passes, namely the outlet pass which is counter-current and the inlet pass which is co-current, which promotes thermal exchanges regardless of the direction of circulation.
- the machine can be a water-water refrigerating machine in which the fluids that are cooled and heated by the exchangers 2100 are water.
- an air-water refrigerating machine including a first air-fluid exchanger also referred to as “battery,” and a second exchanger with two passes, such as the exchanger 2100 .
- FIGS. 12 and 13 represent a tube 500 incorporated in exchangers 3100 and 4100 represented in FIGS. 14 to 21 .
- the tube 500 is provided with a longitudinal slot 501 of width L.
- the slot 501 ensures the distribution of the fluid in the circuits C′ 2 of the zone Z 2 of the exchangers 3100 and 4100 when they operate by evaporation.
- the slot 501 extends over most of the tube 500 , the slot being interrupted at the ends so that the rigidity of the tube is ensured. In service, the slot 501 is oriented vertically towards the bottom of the tube.
- the exchanger 3100 is overall similar to the exchanger 2100 . It is provided with a connection conduit C 3 which connects two circuits C 2 and C′ 2 to one another.
- the circuit C 2 comprises a single channel in the zone Z 1
- the circuit C′ 2 comprises three channels in the zone Z 2 .
- the tube 501 distributes the fluid in the channels of the circuit C′ 2 of the second zone Z 2 when the exchanger operates by evaporation.
- the route of the refrigerant fluid in the circuits C 2 and C′ 2 is as follows for operation by evaporation: the fluid enters the channel of the circuit C 2 through an inlet E 2 located at the lower end N of the exchanger 3100 .
- the fluid rises in this channel and joins the conduit C 3 passing through an outlet S′ 2 of the circuit C 2 .
- the fluid circulates in the conduit C 3 and enters the tube 501 through an inlet E′ 2 located at the upper end M of the exchanger 3100 .
- the slot 51 distributes the fluid in the three channels of the circuit C′ 2 .
- the three channels are connected to an outlet S 2 of the exchanger 3100 .
- the detail of the route of the fluid in the three channels of the circuit C′ 2 is indicated in FIG. 22 .
- the route of the refrigerant fluid in the circuits C 2 and C′ 2 is the following for the operation by condensation in the opposite direction from the operation by evaporation: the fluid enters the channels of the circuit C′ 2 through an inlet S 2 located at the lower end N of the exchanger 3100 .
- the fluid rises in these channels, enters the tube 500 through the slot 501 and joins the conduit C 3 , passing through an outlet E′ 2 of the circuit C′ 2 .
- the fluid circulates in the conduit C 3 and enters the circuit C 2 through an inlet S′ 2 .
- the circuit C 2 is connected to an outlet E 2 of the exchanger 3100 .
- the dual-pass exchanger 3100 achieves an optimal yield when there are two to four times more channels in the outlet pass of the circuit C′ 2 than in the inlet pass of the circuit C 2 .
- FIG. 16 shows the exchanger 3100 with the inlet E 2 and the outlet S 2 of the circuit C 2 at the top for operation by evaporation.
- FIG. 17 shows the exchanger 3100 with the inlet S 2 and the outlet E 2 of the circuit C 2 at the top for operation by condensation. There are two to four times more channels in the outlet pass of the circuit C′ 2 than in the inlet pass of the circuit C 2 .
- FIGS. 18 and 19 show the exchanger 4100 respectively for the operations by evaporation and by condensation with the inlet and outlet of the circuits C 2 and C′ 2 at the bottom.
- FIGS. 20 and 21 show the exchanger 4100 respectively for the operations by evaporation and by condensation with the inlet and the outlet of the circuits C 2 and C′ 2 at the top.
- the exchanger differs from the exchanger 3100 in that it does not incorporate duct C 3 .
- the operation of the exchanger 4100 is similar to that of the exchanger 3100 .
- FIG. 22 shows the route of the fluid in a channel of the zone Z 2 of the exchanger of FIG. 14 or of the exchanger of FIG. 18 , operating by evaporation, with the slot 501 of tube 500 oriented vertically downward.
- FIG. 23 shows the route of the fluid in a channel of the zone Z 2 of the exchanger of FIG. 16 or of the exchanger of FIG. 20 , operating by evaporation, with the slot 501 of the tube 500 oriented vertically downward.
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Abstract
This exchanger (1100), including superposed plates (2A-2L) which are inserted between two end plates (11, 12) and which define channels for circulation of heat-exchanging fluid. These channels delimit a first circuit (C1) for circulation of a first heat-exchanging fluid, comprising a single pass, and a second circuit (C2) for circulation of a second heat-exchanging fluid, comprising two passes opposite one another, so that, for each direction of circulation of the second heat-exchanging fluid in the second circuit, one of the two passes of the second circuit is co-current with respect to the pass of the first circuit, while the other of the two passes of the second circuit is counter-current with respect to the pass of the first circuit.
Description
- The present invention relates to a plate heat exchanger as well as to a refrigerating machine including such an exchanger.
-
FIG. 1 shows a brazedplate heat exchanger 100, provided with a set ofsuperposed plates plate plates end plates channels 20 for the circulation of heat-exchanging fluids. - Each
plate end plate first opening 21 which is used as inlet E1 for a first heat-exchanging fluid, asecond opening 22 which is used as outlet S1 for the first heat-exchanging fluid, a third opening 23 which is used as inlet E2 for a second heat-exchanging fluid, and afourth opening 24 which is used as outlet S2 for the second heat-exchanging fluid. Thechannels 20 defined against each corrugated surface receive the first or the second heat-exchanging fluid. In the example ofFIG. 1 , the first heat-exchanging fluid circulates in a first circuit between the second andthird plates 2B and 2C. The second heat-exchanging fluid circulates in a second circuit which extends between theplates adjacent plates -
FIG. 2 shows a reversible refrigerating machine which includes acompressor 400, apressure reducing valve 200 and twoexchangers FIG. 1 . These four elements are mounted on a common circuit C of refrigerant fluid. Theexchangers - The
first exchanger 100 implements a heat transfer between the common circuit C and a first exchange circuit C10. Thesecond exchanger 300 implements a heat transfer between the common circuit C and a second exchange circuit C20. - For each operating mode, for example, one of the
exchangers - The performances of a plate heat exchanger are better counter-currently than co-currently, so that for each operating mode, one of the
exchangers - DE 10 2006 002 018 discloses a reversible refrigerating machine which makes it possible to change the operating mode without reversing the direction of circulation of the refrigerant fluid, using a three-way valve installed on the refrigerating circuit. This solution is complex to implement, since it requires the installation of a device for distributing the refrigerant fluid.
- These are the disadvantages that the invention aims to remedy more particularly by proposing a novel plate exchanger which is easy to use in a reversible refrigerating machine and which has a satisfactory yield.
- To this effect, the invention relates to a plate heat exchanger including superposed plates which are inserted between two end plates and which define channels for circulation of heat-exchanging fluid, characterized in that the channels delimit
-
- a first circuit for circulation of a first heat-exchanging fluid, comprising a single pass, and
- a second circuit for circulation of a second heat-exchanging fluid, comprising two passes opposite from one another,
- so that, for each direction of circulation of the second heat-exchanging fluid in the second circuit, one of the two passes of the second circuit is co-current with respect to the pass of the first circuit, while the other of the two passes of the second circuit is counter-current with respect to the pass of the first circuit.
- According to advantageous but non-obligatory aspects of the invention, such an exchanger can incorporate one or more of the following features, considered in any technically acceptable combination:
-
- the first circuit comprises several intermediate branches each delimited between two adjacent plates and connecting to one another in parallel a forward branch and a return branch of the first circuit;
- the second circuit comprises two adjacent zones, in which intermediate branches of the second circuit belong, for one of these zones, to one of the two passes of the second circuit, and for the other zone, to the other of the two passes of the second circuit;
- the second circuit comprises a first portion and a second portion, which are separated by an intermediate plate of the exchanger and which are connected to one another by a conduit outside of the exchanger;
- the exchanger includes a tube which is provided with a slot distributing the second heat-exchanging fluid in several channels of the second circuit.
- Another aspect of the invention relates to a reversible refrigerating machine including a common circuit of refrigerating fluid, on which are arranged a compressor, a pressure reducing valve and two exchangers which are each as defined above.
- According to advantageous but non-obligatory aspects of the invention, such a refrigerating machine can incorporate one or more of the following features, considered in any technically acceptable combination:
-
- the refrigerating machine comprises a four-way valve capable of changing the direction of circulation of the refrigerant fluid in the common circuit;
- the common circuit is formed by the second circuit of the exchangers;
- the second circuit comprises an inlet and an outlet arranged at the top of the exchangers;
- the second circuit comprises an inlet and an outlet arranged at the bottom of the exchangers.
- The invention will be understood better, and other advantages of said invention will become clearer in light of the following description of a plate exchanger according to the invention, which is given only as an example and in reference to the drawings in which:
-
FIG. 1 is an exploded perspective view of a plate exchanger of the prior art; -
FIG. 2 is a diagrammatic view of a reversible refrigerating machine of the prior art; -
FIG. 3 is an exploded diagrammatic view of an exchanger according to a first embodiment of the invention; -
FIGS. 4 and 5 are diagrams of the exchanger ofFIG. 3 with a first and a second direction of circulation, respectively, of the heat-exchanging fluids; -
FIGS. 6 and 7 are diagrams of refrigerating machines including the exchanger ofFIG. 3 ; -
FIG. 8 is a diagram of the exchanger ofFIG. 3 according to another orientation; -
FIG. 9 is an exploded perspective view of an exchanger according to a second embodiment of the invention; -
FIGS. 10 and 11 are diagrams of the exchanger ofFIG. 9 with a first and a second direction of circulation, respectively, of the heat-exchanging fluids; -
FIGS. 12 and 13 are diagrams of a tube for distributing fluid; -
FIGS. 14 to 17 are diagrams of an exchanger according to a third embodiment of the invention, with different directions of circulation of the heat-exchanging fluids; -
FIGS. 18 to 21 are diagrams of an exchanger according to a fourth embodiment of the invention, with different directions of circulation of the heat-exchanging fluids; and -
FIGS. 22 and 23 are diagrams of the tube ofFIGS. 12 and 13 , positioned for an exchanger in one of the configurations ofFIGS. 14, 15, 18 and 19 and for one of the configurations ofFIGS. 16, 17, 20 and 21 , respectively. -
FIG. 3 shows aplate exchanger 1100 according to the invention. It includes afirst end plate 11 which defines a first external surface A of theexchanger 1100, and asecond end plate 12 which defines a second external surface B of theexchanger 1100 opposite the first surface A. - Twelve
plates 2A to 2L are superposed, that is to say arranged successively, one against the other, between theend plates plate 2K is arranged against thefirst end plate 11, and the plate 2L is arranged against thesecond end plate 12. - The
end plates plates 2A to 2L have an overall rectangular shape. Theexchanger 1100 has an overall parallelepiped shape with rectangular base. M is used to designate an upper edge of theexchanger 1100 located at the top ofFIG. 3 , and N is used to designate a lower edge of theexchanger 1100 parallel to the upper edge M and located at the bottom ofFIG. 3 . The edges M and N are of small length and connect together long edges O and P of theend plates plates 2A to 2L, which are perpendicular to the short edges M and N. The long edge O is located in the foreground ofFIG. 3 and the long edge P in the background. - Each
plate 2A to 2L comprises two opposite rectangular surfaces which are corrugated according to a precise scheme which does not limit the invention, for example, a chevron profile. These corrugations are not represented inFIG. 3 ; they can be similar to those of the exchanger ofFIG. 1 . The edges M, N, 0 and P of theplates 2A to 2L are provided with brazed gaskets, not shown, in order to prevent fluid leaks. The corrugated surfaces facing one another of twoadjacent plates 2A to 2L together define channels for the turbulent circulation of heat-exchanging fluids, these channels not being shown inFIG. 3 but possibly similar to thechannels 20 ofFIG. 1 . - In the direction of its thickness, the
exchanger 1100 comprises a first zone Z1, between thefirst end plate 11 and the plate 2E, and a second zone Z2, between theplate 2F and thesecond end plate 12. The zones Z1 and Z2 are adjoining. The first zone Z1 is located on the side of the first surface A of theexchanger 1100, and the second zone Z2 is located on the side of the second surface B. The zones Z1 and Z2 divide theexchanger 1100 in two in its thickness, that is to say in a direction perpendicular to theend plates plates 2A to 2L. - The
exchanger 1100 delimits two heat-exchanging fluid circuits C1 and C2. For use in a refrigerating machine, the first circuit C1 is provided for water and the second circuit C2 for a refrigerant fluid. The first circuit C1 corresponds to one of the exchange circuits C10 or C20 of the refrigerating machine ofFIG. 2 , and the second circuit C2 corresponds to the common circuit C. - The circuits C1 and C2 are defined so that the water circuit C1 comprises a single pass, that is to say the fluid circulates between the edges N and M in a single direction, namely from bottom to top in the example of
FIG. 3 . The refrigerant fluid circuit C2 comprises two passes, namely an inlet pass in the zone Z2, where the refrigerant fluid circulates in a first direction, namely from bottom to top between the edges N and M, and an outlet pass in the zone Z1, where the refrigerant fluid circulates in a second direction opposite from the first direction, that is to say from top to bottom between the edges M and N. - This configuration results from the particular arrangement of the corrugations of the
plates 2A to 2L and of theholes 21 to 24 produced in the corners of theend plates plates 2A to 2L as described below. Theend plates plates 2A to 2L are each provided with a number of holes between one and four, so as to guide the circulation of the fluids in the circuits C1 and C2. - The
hole 21 is located in a first lower corner, at the junction between the edges N and P. Thehole 22 is located in a second lower corner, at the junction between the edges N and O. Thehole 23 is located in a first upper corner, at the junction between the edges M and P. Thehole 24 is located in a second upper corner, at the junction between the edges M and O. - For a first direction of circulation of the fluids in the circuits C1 and C2, as defined in
FIG. 3 , an inlet E1 of the first circuit C1 is formed by afirst hole 21 of thesecond end plate 12, in the zone Z2. The first circuit C1 comprises a first lower branch or forward branch C11 in which the fluid circulates up to theplate 2K, throughholes 21 which are perforated in eachplate 2A to 2J and 2L. Thefirst end plate 11 and theplate 2K have nohole 21. A second upper branch or return branch C12 of the first circuit C1 is defined between theplate 2K and ahole 23 of thesecond end plate 12, which defines an outlet S1 of the first circuit C1 in the second zone Z2. Thefirst end plate 11 and theplate 2K have nohole 23. Between theplates 2K and 2L, the fluid circulates throughholes 23 perforated in eachplate 2A to 2J and 2L. - Between the branches C11 and C12, the first circuit C1 comprises several intermediate branches C13 to C18 connected in parallel between the branches C11 and C12. The intermediate branches C13 to C18 are represented in a rectilinear manner in the diagram of
FIG. 3 , but in practice they meander in the pattern defined by the corrugations of theplates 2A to 2L. - The branches C13 to C15 are part of the second zone Z2, and the branches C16 to C18 are part of the first zone Z1.
- Thus, in the zones Z1 and Z2, the first circuit C1 has a single pass from the edge N and towards the edge M. In other words, between the edges N and M and for the two zones Z1 and Z2, the fluid circulates in the first circuit C1 in a single direction, namely from bottom to top.
- The remainder of the description concerns the second circuit C2. An inlet E2 of the second circuit C2 is formed by a
hole 22 of thesecond end plate 12, in the second zone Z2. The second circuit C2 comprises a first lower branch C21, which extends exclusively in the second zone Z2 and which connects the second inlet E2 to a first and a second intermediate branch C22 and C23 connected in parallel between the lower branch C21 and an upper branch C24. In the intermediate branches C22 and C23, the fluid circulates from bottom to top, from the edge N to the edgeM. The plates 2F and 2G have nohole 22. - The upper branch C24 extends through
holes 24 perforated in theplates 2B to 21 in zones Z1 and Z2, and it is connected to two other intermediate branches C25 and C26 in which the fluid circulates from top to bottom, from the edge M to the edge N. The intermediate branches C25 and C26 connect in parallel the upper branch C24 to a second lower branch C27, which extends exclusively in the first zone Z1, throughholes 22 perforated in theplates 2A to 2C, 2K and in thefirst end plate 11, up to an outlet S2 of the second circuit C2 formed by thehole 22 of theend plate 11, in the first zone Z1. - Thus, in the zone Z2, the second circuit C2 has an inlet pass where the fluid circulates in a first direction, namely from the lower edge N and towards the upper edge M. In the zone Z1, the second circuit C2 has an outlet pass where the fluid circulates in a second direction opposite from the first direction, namely from the upper edge M and towards the lower edge N.
-
FIGS. 4 and 5 more diagrammatically again show the arrangement of the circuits C1 and C2 of theexchanger 1100.FIG. 4 corresponds to the first direction of circulation ofFIG. 3 for the circuit C2, andFIG. 5 to a second opposite direction of circulation. - The first direction of circulation of
FIGS. 3 and 4 corresponds to a first operating mode, in which theexchanger 1100 operates by evaporation. In the second zone Z2, the refrigerant fluid of the circuit C2 performs a first pass that is co-current with respect to the water of the circuit C1, it circulates from bottom to top between the edges N and M and, in the first zone Z1, the refrigerant fluid of the circuit C2 performs a second pass that is counter-current with respect to the water of the circuit C1, it circulates from top to bottom between the edges M and N. - In
FIG. 5 , the direction of circulation of the refrigerant fluid in the second circuit C2 is reversed. The direction of circulation of the water in the circuit C1 remains unchanged. The inlet E2 of the circuit C2 becomes the outlet S2 and vice versa. Theexchanger 1100 then operates in a second mode, by condensation. - In this second mode, for the first zone Z1, the refrigerant fluid in the second circuit C2 performs a first pass that is co-current with respect to the water of the first circuit C1, it circulates from bottom to top from the lower edge N towards the upper edge M, and, in the second zone Z2, the refrigerant fluid in the second circuit C2 performs a second pass that is counter-current with respect to the water of the first circuit C1, it circulates from top to bottom from the upper edge M towards the lower edge N.
- Thus, for each operating mode, the
exchanger 1100 makes it possible for the refrigerant fluid of the circuit C2 to perform a first pass that is co-current and a second pass that is counter-current with respect to the water of the circuit C1. In this manner, the thermal yield of theexchanger 1100 is improved, since, in each operating mode, the fluids of the circuits C1 and C2 circulate counter-currently for the zone corresponding to the outlet pass of the circuit C2. -
FIGS. 6 and 7 show a reversible refrigerating machine which includes acompressor 400, apressure reducing valve 200, and twoexchangers FIGS. 3 to 5 . These fourelements - The
first exchanger 1100 implements a heat transfer between the common circuit C and a first exchange circuit C10. Thesecond exchanger 1200 implements a heat transfer between the common circuit C and a second exchange circuit C20. - The
exchangers - In
FIG. 6 , for the first operating mode, theexchanger 1100 operates by condensation, and the second exchanger it operates by evaporation. The valve V1 is in a first position. The refrigerant fluid of the common circuit C circulates in a first direction. The first exchange circuit C10 is a hot water circuit, and the second exchange circuit C20 is a cold water circuit. - In
FIG. 7 , for the second operating mode, theexchanger 1100 operates by evaporation, and the second exchanger operates by condensation. The valve V1 is in a second position. The refrigerant fluid of the common circuit C circulates in a second direction opposite from the first direction ofFIG. 6 . The first exchange circuit C10 is a cold water circuit, and the second exchange circuit C20 is a hot water circuit. - For each operating mode, each of the
exchangers exchangers - More precisely, in the first operating mode represented in
FIG. 6 , and for eachexchanger FIG. 4 . - In the second operating mode represented in
FIG. 7 and for eachexchanger FIG. 5 . - In
FIGS. 3 to 7 , theexchanger 1100 is arranged according to a first orientation, in which the inlets E1 and E2 of the circuits C1 and C2 are arranged at the bottom of theexchanger 1100, along the lower edge N. The fluid of the circuit C1, in the two zones Z1 and Z2, and the fluid of the circuit C2, in the zone Z2 for the configuration ofFIG. 4 , and in the zone Z1 for the configuration ofFIG. 5 , circulate upwards, against the force exerted by gravity. -
FIG. 8 shows theexchanger 1100 according to a second orientation, in which the edge M is oriented towards the bottom, while the edge N is oriented towards the top. The inlets E1 and E2 of the circuits C1 and C2 are arranged at the top of theexchanger 1100, along the upper edge M. The fluid of the circuit C1, in the two zones Z1 and Z2, and the fluid of the circuit C2, in the zone Z1, circulate downward in the direction of the force exerted by gravity. - For the two orientations of the
exchanger 1100, the flow of the water in the circuit C1 is counter-current with respect to the flow of the refrigerant fluid in the outlet pass of the circuit C2, that is to say the flow of the water is directed upward when the inlet E2 and the outlet S2 are at the bottom, as shown inFIGS. 4 to 7 , and is directed downward when the inlet E2 and the outlet S2 are at the top, as shown inFIG. 8 . -
FIG. 9 shows anexchanger 2100 according to a second embodiment of the invention, of the dual-circuit exchanger type. The elements of theexchanger 2100 similar to those of theexchanger 1100 bear the same reference numbers. Below, the elements of theexchanger 2100 that are similar to those of theexchanger 1100 are not described in detail. - As described below and in contrast to the
exchanger 1100, theexchanger 2100 comprises two independent refrigerant fluid circuits C2 and C′2, which can implement two passes when they are connected to one another appropriately by means of a duct C3 represented with dotted lines inFIG. 9 . The duct C3 is represented diagrammatically inFIGS. 10 and 11 which are described in greater detail below. - The
exchanger 2100 comprises twoend plates corrugated plates 2A to 2H arranged between theend plates exchanger 2100 also has anintermediate end plate 13 inserted between the plates 2D and 2E. Theintermediate end plate 13 materially delimits the separation between the zones Z1 and Z2. - The
exchanger 2100 has a generally rectangular shape and comprises an upper edge M, a lower edge N, and two lateral edges O and P. Theend plates plates 2A to 2H are provided withholes - The first circuit C1 provided, for example, for water in the case in which a refrigerating machine is used, comprises an inlet E1 implemented by a
hole 24 produced in theend plate 11. The first circuit C1 comprises a first branch or forward branch C11 which starts from the inlet E1 and passes throughholes 24 produced in theplates 2A to 2G as well as in theintermediate end plate 13. A second lower branch or return branch C12 of the first circuit starts at the outlet S1 and passes throughholes 22 produced in theplates 2A to 2G as well as in theintermediate end plate 13. Between theend plate 11 and the plate 2H, the fluid circulates throughholes 22 perforated in eachplate 2A to 2G. - Between the branches C11 and C12, the first circuit C1 comprises several intermediate branches C13 to C16 connected in parallel between the branches C11 and C12. The intermediate branches C13 to C16 are represented in a rectilinear manner in the diagram of
FIG. 9 , but in practice they meander in the pattern defined by the corrugations of theplates 2A to 2H. - The branches C13 and C14 are part of the first zone Z1, and the branches C15 and C16 are part of the second zone Z2.
- Thus, in the zones Z1 and Z2, the first circuit C1 has a single pass, from the upper edge M and towards the lower edge N. In other words, between the edges M and N and for the two zones Z1 and Z2, the fluid circulates in the first circuit C1 in a single direction, namely from top to bottom.
- The remainder of the description concerns the circuits C2 and C′2 of refrigerant fluid.
- The circuit C2 comprises an inlet E20 formed by a
hole 23 produced in theend plate 12. A first upper branch C21 or forward branch of the circuit C2 extends from the inlet E20 and theplate 2F, in the second zone Z2, throughholes 23 produced in the plates 2G and 2H. - The circuit C2 has an outlet S20 formed by a
hole 21 produced in theend plate 12. A second lower branch C22 or return branch of the circuit C2 extends between the outlet S20 and theplate 2F, in the second zone Z2, throughholes 21 produced in the plates 2G and 2H. - The branches C21 and C22 are connected to one another by an intermediate branch C23 which is delimited between the
plates 2F and 2G. - The circuit C′2 comprises an inlet E′20 formed by a
hole 21 produced in theend plate 11. A first lower branch C′21 or forward branch of the circuit C′2 extends between the inlet E′20 and the plate 2C, in the first zone Z1, throughholes 21 produced in theplates - The circuit C′2 comprises an outlet S′20 formed by a
hole 23 produced in theend plate 11. A second upper branch C′22 or return branch of the circuit C′2 extends between the outlet S′20 and the plate 2C, in the first zone Z1, throughholes 23 produced in theplates - The branches C′21 and C′22 are connected to one another by an intermediate branch C′23 which is delimited between the
plates 2B and 2C. - In
FIG. 10 , the refrigerant fluid in the circuits C2 and C′2 circulates in a first direction, and the connection between the circuits C2 and C′2 is implemented by means of a connection conduit C3 which connects the outlet S20 of the circuit C2 to the inlet E′20 of the circuit C′2. Thus, the outlet S′20 of theexchanger 2100 as represented inFIG. 9 becomes the outlet S2 of the common circuit of heat-exchanging fluid formed by the combination of the circuits C2 and C′2. The inlet E20 becomes the inlet E2 of the common circuit C2 and C′2. - In the zones Z1 and Z2, the first circuit C1 has a single pass, from the edge M and towards the edge N. In other words, between the edges M and N and for the two zones Z1 and Z2, the fluid circulates in the first circuit C1 in a single direction, namely from top to bottom.
- In the direction of circulation of the fluid of
FIG. 10 , the second circuit C2 and C′2 comprises a first pass or forward pass in the zone Z2, where the fluid circulates co-currently in the circuit C2, and a second pass or return pass in the zone Z1, where the fluid circulates counter-currently in the circuit C′2. - In
FIG. 11 , the direction of circulation of the fluid in the circuits C2 and C′2 is reversed. The inlet E2 is in the zone Z1 at the beginning of the circuit C′2, and the outlet S2 is in the zone Z2, at the outlet of the circuit C2. - In the direction of circulation of the fluid of
FIG. 11 , the second circuit C2 and C′2 comprises a first pass or forward pass in the zone Z1, where the fluid circulates co-currently in the circuit C′2, and a second pass or return pass in the zone Z2, where the fluid circulates counter-currently in the circuit C2. - Thus, regardless of the direction of circulation of the fluid in the circuit C2 and C′2, the
exchanger 2100 comprises a pass that is co-current and a pass that is counter-current, which makes it possible to optimize the thermal exchanges. - Two exchangers similar to the
exchanger 2100 and provided with the duct C3 can be used in a reversible refrigerating machine, in a manner similar to theexchanger 1100 as implemented inFIGS. 6 and 7 . For the two directions of circulation of the fluid in the common circuit C, each exchanger comprises two passes, namely the outlet pass which is counter-current and the inlet pass which is co-current, which promotes thermal exchanges regardless of the direction of circulation. - The machine can be a water-water refrigerating machine in which the fluids that are cooled and heated by the
exchangers 2100 are water. - It is also possible to use an air-water refrigerating machine including a first air-fluid exchanger also referred to as “battery,” and a second exchanger with two passes, such as the
exchanger 2100. -
FIGS. 12 and 13 represent atube 500 incorporated inexchangers FIGS. 14 to 21 . - The
tube 500 is provided with alongitudinal slot 501 of width L. Theslot 501 ensures the distribution of the fluid in the circuits C′2 of the zone Z2 of theexchangers slot 501 extends over most of thetube 500, the slot being interrupted at the ends so that the rigidity of the tube is ensured. In service, theslot 501 is oriented vertically towards the bottom of the tube. - The
exchanger 3100 is overall similar to theexchanger 2100. It is provided with a connection conduit C3 which connects two circuits C2 and C′2 to one another. The circuit C2 comprises a single channel in the zone Z1, while the circuit C′2 comprises three channels in the zone Z2. Thetube 501 distributes the fluid in the channels of the circuit C′2 of the second zone Z2 when the exchanger operates by evaporation. - The route of the refrigerant fluid in the circuits C2 and C′2, in reference to
FIG. 14 , is as follows for operation by evaporation: the fluid enters the channel of the circuit C2 through an inlet E2 located at the lower end N of theexchanger 3100. The fluid rises in this channel and joins the conduit C3 passing through an outlet S′2 of the circuit C2. The fluid circulates in the conduit C3 and enters thetube 501 through an inlet E′2 located at the upper end M of theexchanger 3100. Theslot 51 distributes the fluid in the three channels of the circuit C′2. At the lower end N, on the opposite side from thetube 501, the three channels are connected to an outlet S2 of theexchanger 3100. The detail of the route of the fluid in the three channels of the circuit C′2 is indicated inFIG. 22 . - The route of the refrigerant fluid in the circuits C2 and C′2, in reference to
FIG. 15 , is the following for the operation by condensation in the opposite direction from the operation by evaporation: the fluid enters the channels of the circuit C′2 through an inlet S2 located at the lower end N of theexchanger 3100. The fluid rises in these channels, enters thetube 500 through theslot 501 and joins the conduit C3, passing through an outlet E′2 of the circuit C′2. The fluid circulates in the conduit C3 and enters the circuit C2 through an inlet S′2. At the lower end N, the circuit C2 is connected to an outlet E2 of theexchanger 3100. - As for the thermal exchanges, the dual-
pass exchanger 3100 achieves an optimal yield when there are two to four times more channels in the outlet pass of the circuit C′2 than in the inlet pass of the circuit C2. -
FIG. 16 shows theexchanger 3100 with the inlet E2 and the outlet S2 of the circuit C2 at the top for operation by evaporation.FIG. 17 shows theexchanger 3100 with the inlet S2 and the outlet E2 of the circuit C2 at the top for operation by condensation. There are two to four times more channels in the outlet pass of the circuit C′2 than in the inlet pass of the circuit C2.FIGS. 18 and 19 show theexchanger 4100 respectively for the operations by evaporation and by condensation with the inlet and outlet of the circuits C2 and C′2 at the bottom.FIGS. 20 and 21 show theexchanger 4100 respectively for the operations by evaporation and by condensation with the inlet and the outlet of the circuits C2 and C′2 at the top. The exchanger differs from theexchanger 3100 in that it does not incorporate duct C3. The operation of theexchanger 4100 is similar to that of theexchanger 3100. -
FIG. 22 shows the route of the fluid in a channel of the zone Z2 of the exchanger ofFIG. 14 or of the exchanger ofFIG. 18 , operating by evaporation, with theslot 501 oftube 500 oriented vertically downward. -
FIG. 23 shows the route of the fluid in a channel of the zone Z2 of the exchanger ofFIG. 16 or of the exchanger ofFIG. 20 , operating by evaporation, with theslot 501 of thetube 500 oriented vertically downward. - In the context of the invention, the embodiments can be combined with one another, at least partially.
Claims (10)
1. Plate heat exchanger (1100; 2100; 3100; 4100) including superposed plates (2A-2L), which are inserted between two end plates (11, 12) and which channels for circulation of heat-exchanging fluid, characterized in that the channels delimit
a first circuit (C1) for circulation of a first heat-exchanging fluid, comprising a single pass, and
a second circuit (C2, C′2, C3) for circulation of a second heat-exchanging fluid, comprising two passes opposite from one another,
so that, for each direction of circulation of the second heat-exchanging fluid in the second circuit, one of the two passes of the second circuit is co-current with respect to the pass of the first circuit (C1), while the other of the two passes of the second circuit is counter-current with respect to the pass of the first circuit (C1).
2. Plate heat exchanger (1100) according to claim 1 , characterized in that the first circuit (C1) comprises several intermediate branches (C13-C18) each delimited between two adjacent plates (2A-2L) and connecting to one another in parallel a forward branch (C11) and a return branch (C12) of the first circuit (C1).
3. Plate heat exchanger (1100) according to claim 1 , characterized in that the second circuit (C2) comprises two adjacent zones (Z1, Z2), in which intermediate branches (C23-C26) of the second circuit (C2) belong, for one of these zones, to one of the two passes of the second circuit, and for the other zone, to the other of the two passes of the second circuit.
4. Plate heat exchanger (2100; 3100) according to claim 1 , characterized in that the second circuit comprises a first portion (C2) and a second portion (C′2), which are separated by an intermediate plate (13) of the exchanger and which are connected to one another by a conduit (C3) outside of the exchanger.
5. Plate heat exchanger (3100; 4100) according to claim 1 , characterized in that the exchanger includes a tube (500) which is provided with a slot (501) distributing the second heat-exchanging fluid in several channels of the second circuit (C′2).
6. Reversible refrigerating machine including a common circuit (C) of refrigerant fluid on which are arranged a compressor (400), a pressure reducing valve (200), and two exchangers (1100; 2100; 3100; 4100) which are each in accordance with claim 1 .
7. Refrigerating machine according to claim 6 , characterized in that it comprises a four-way valve (V1) capable of changing the direction of circulation of the refrigerant fluid in the common circuit (C).
8. Refrigerating machine according to claim 6 , characterized in that the common circuit (C) is formed by the second circuit (C2, C′2, C3) of the exchangers (1100; 2100; 3100; 4100).
9. Refrigerating machine according to claim 6 , characterized in that the second circuit (C2, C′2, C3) comprises an inlet (E2) and an outlet (S2) arranged at the top the exchangers.
10. Refrigerating machine according to claim 6 , characterized in that the second circuit (C2, C′2, C3) comprises an inlet (E2) and an outlet (S2) arranged at the bottom of the exchangers.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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FR1553870A FR3035710B1 (en) | 2015-04-29 | 2015-04-29 | PLATE HEAT EXCHANGER AND REVERSIBLE REFRIGERATING MACHINE COMPRISING SUCH AN EXCHANGER |
FR1553870 | 2015-04-29 | ||
PCT/US2016/029473 WO2016176276A1 (en) | 2015-04-29 | 2016-04-27 | Plate heat exchanger and reversible refrigerating machine including such an exchanger |
Publications (1)
Publication Number | Publication Date |
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US20180128551A1 true US20180128551A1 (en) | 2018-05-10 |
Family
ID=53794348
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US15/570,082 Abandoned US20180128551A1 (en) | 2015-04-29 | 2016-04-27 | Plate heat exchanger and reversible refrigerating machine including such an exchanger |
Country Status (6)
Country | Link |
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US (1) | US20180128551A1 (en) |
EP (1) | EP3289305B1 (en) |
CN (1) | CN107532857A (en) |
ES (1) | ES2818177T3 (en) |
FR (1) | FR3035710B1 (en) |
WO (1) | WO2016176276A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3124588A1 (en) * | 2021-06-29 | 2022-12-30 | Valeo Systemes Thermiques | Motor vehicle heat exchanger |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220155031A1 (en) * | 2019-03-28 | 2022-05-19 | Zhejiang Sanhua Automotive Components Co., Ltd. | Heat exchanger and heat exchange device |
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WO1998036212A1 (en) * | 1997-02-14 | 1998-08-20 | Aga Aktiebolag | Method and apparatus for cooling a product using a condensed gas |
JPH10288480A (en) * | 1997-04-15 | 1998-10-27 | Daikin Ind Ltd | Plate type heat-exchanger |
US20050211421A1 (en) * | 2002-05-29 | 2005-09-29 | Rolf Ekelund | Plate heat exchanger device and a heat exchanger plate |
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FR2614684B1 (en) * | 1987-04-30 | 1989-06-30 | Chausson Usines Sa | HEAT EXCHANGER FOR LIQUID FLUIDS |
US6935417B1 (en) * | 1998-10-19 | 2005-08-30 | Ebara Corporation | Solution heat exchanger for absorption refrigerating machine |
DE102006002018A1 (en) | 2006-01-13 | 2007-07-26 | Technische Universität Dresden | Internal radiator used in central heating systems with reversible heat pumps, comprises stacked panels with lower outlets and upper inlets for gas and atomized fluid |
JP5132091B2 (en) * | 2006-06-20 | 2013-01-30 | 株式会社ササクラ | Plate type fresh water generator |
KR101326841B1 (en) * | 2011-12-07 | 2013-11-11 | 현대자동차주식회사 | Condenser for vehicle |
-
2015
- 2015-04-29 FR FR1553870A patent/FR3035710B1/en active Active
-
2016
- 2016-04-27 US US15/570,082 patent/US20180128551A1/en not_active Abandoned
- 2016-04-27 ES ES16720675T patent/ES2818177T3/en active Active
- 2016-04-27 CN CN201680024693.5A patent/CN107532857A/en active Pending
- 2016-04-27 EP EP16720675.4A patent/EP3289305B1/en active Active
- 2016-04-27 WO PCT/US2016/029473 patent/WO2016176276A1/en active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1998036212A1 (en) * | 1997-02-14 | 1998-08-20 | Aga Aktiebolag | Method and apparatus for cooling a product using a condensed gas |
JPH10288480A (en) * | 1997-04-15 | 1998-10-27 | Daikin Ind Ltd | Plate type heat-exchanger |
US20050211421A1 (en) * | 2002-05-29 | 2005-09-29 | Rolf Ekelund | Plate heat exchanger device and a heat exchanger plate |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3124588A1 (en) * | 2021-06-29 | 2022-12-30 | Valeo Systemes Thermiques | Motor vehicle heat exchanger |
WO2023274722A1 (en) * | 2021-06-29 | 2023-01-05 | Valeo Systemes Thermiques | Heat exchanger for a motor vehicle |
Also Published As
Publication number | Publication date |
---|---|
WO2016176276A1 (en) | 2016-11-03 |
FR3035710B1 (en) | 2018-09-07 |
FR3035710A1 (en) | 2016-11-04 |
EP3289305A1 (en) | 2018-03-07 |
CN107532857A (en) | 2018-01-02 |
EP3289305B1 (en) | 2020-06-24 |
ES2818177T3 (en) | 2021-04-09 |
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