Patent Application
20240418456
The present invention concerns the field of plate heat exchangers, used notably for heat exchange between two gases, but also between two liquids, or between a liquid and a gas.
Heat exchangers of particular interest for the invention are gas-gas exchangers that operate with large or small flow volumes at relatively low pressures, from 0.01 to 1.5 MPa for example. They can be used for example as air preheaters for furnaces, or they can be part of NOx reduction systems (“DeNOx” devices).
The purpose of heat exchangers is to provide thermal exchange between a high-temperature fluid and a low-temperature fluid without mixing thereof. Plate heat exchangers have good thermal performances due to their large exchange surface, while being compact.
Plate heat exchangers recover heat by means of a plurality of plates stacked parallel to one another, at predetermined intervals. Said plates are spaced apart such that the space between two adjacent plates forms a channel through which a fluid can flow. A high-temperature fluid and a low-temperature fluid are alternately supplied to the successive channels so as to achieve heat transfer between the high-temperature fluid and the low-temperature fluid through the agency of each plate.
The efficiency of plate heat exchangers is mainly determined by the heat exchanges between fluids flowing therethrough. The exchanger plate geometry affects the heat exchangers. The plates may notably be substantially plane, or have parts in relief.
Patent applications FR-3,086,742 (WO-2020/069,880) and FR-3,108,714 (WO-2021/190,879) describe a plate heat exchanger within which plate pairs are formed. For this plate exchanger, each plate comprises a central panel, the central panels of the two plates being parallel and spaced apart so as to form a channel for a fluid. Furthermore, the plate pair comprises at least one junction panel between the central panels of the plates, so as to assemble and space them apart. The junction panels are inclined relative to the central panels. Within this heat exchanger, heat exchanges occur notably through plane plates, possibly without relief. Although satisfactory, the thermal efficiency of this plate heat exchanger can be improved.
In order to enable stirring of these fluids so as to increase heat exchanges, the plates of the heat exchangers can be equipped with fluid flow disruption devices.
For economic and practical reasons, the arrangement of these disruption devices is generally the same for all the plates.
Patent application FR-3,003,637 describes a plate heat exchanger comprising at least one pair of similar plates, spaced apart and substantially parallel. Said plates can have spaced grooves extending in a direction oriented at 45° to the sides of each plate. The second plate is of invariant shape by 90° rotation relative to an axis normal to the main panel. Thus, the grooves of the first plate are perpendicular to the grooves of the second plate. The grooves thus form a relief allowing stirring of the fluids and thereby increasing heat exchange. However, the heat exchange performances can be improved, and this heat exchanger only enables co-current heat exchange, and no counter-current or cross-current heat exchange.
The invention aims to provide a plate heat exchanger with optimized thermal performances and limited pressure drop. The invention therefore concerns a pair of heat exchanger plates. Each plate comprises a central panel provided with at least one groove protruding into a channel defined by an inner volume between the plates. Within the pair of plates, each groove of the first plate is parallel to each groove of the second plate. The grooves in the two plates form a relief allowing stirring of the fluids, thus providing increased heat exchanges with limited pressure drop. Furthermore, this design can be used for co-current, counter-current or cross-current heat exchanges.
The invention further concerns a stack of plate pairs, a heat exchanger comprising such a plate pair. The invention also concerns a method of manufacturing such a stack of plate pairs or such a heat exchanger.
The invention concerns a pair of heat exchanger plates comprising a first and a second heat exchanger plate, arranged face to face and spaced apart so as to define an inner volume capable of forming a channel for flow of a first fluid, each plate comprising a central panel, said central panels of said first and second plates being preferably substantially quadrilateral, optionally with truncated, cut or rounded edges, and said central panels of said first and second plates being plane and parallel to one another. Said central panel of each plate comprises at least one groove, preferably a substantially rectilinear groove, protruding into said inner volume, and each groove of said first plate is parallel to each groove of said second plate.
According to one embodiment, each groove is inclined at a non-zero and non-right angle α to one side of said central panel, angle α being greater than or equal to 10°, preferably ranging between 10° and 80°, inclusive, more preferably ranging between 30° and 70°, inclusive, and most preferably ranging between 40° and 50°, inclusive.
According to one implementation, each groove of said second plate is offset with respect to each groove of said first plate in a direction perpendicular to said grooves of said first and second plates.
According to one embodiment option, each central panel of each plate comprises a plurality of grooves parallel to one another, and preferably evenly spaced apart.
Advantageously, the even spacing or pitch of said grooves of said first plate is identical to the pitch of said grooves of said second plate.
Preferably, the offset in the direction perpendicular to said grooves has a distance between one third and two thirds of said pitch, and it is preferably half of said pitch.
Advantageously, the pitch between two successive grooves ranges between 10 mm and 80 mm, inclusive, preferably between 20 mm and 60 mm, inclusive.
According to one aspect, each groove has a cross section whose shape is selected from among an arc of a circle, a semicircle, a U, a V, an ellipse, an airplane wing, a spearhead, and the shape is preferably selected from among an arc of a circle and an airplane wing.
According to a feature, the width of each groove ranges between 4 mm and 30 mm, inclusive, preferably between 6 mm and 25 mm, inclusive.
According to an embodiment, the protrusion height of each groove ranges between 1.5 mm and 6 mm, inclusive, preferably between 2 mm and 5 mm, inclusive.
According to an implementation, all the grooves of the first and second plates have the same cross section, the same width and the same protrusion height.
According to an embodiment option, said first plate and said second plate are connected by means of one or two junction panel(s) arranged on one or two side(s) of a central panel.
Furthermore, the invention concerns a stack of pairs of heat exchanger plates comprising at least two pairs of plates according to one of the above features, said plate pairs being stacked in such a way that said successive plate pairs are spaced apart. For two successive plate pairs respectively referred to as first plate pair and second plate pair:
According to an embodiment, said channel for flow of the second fluid is perpendicular to said channel for flow of the first fluid.
The invention further concerns a plate heat exchanger comprising plate pairs according to one of the above features, or a stack of plate pairs according to one of the above features, said plate pairs or said stack of plate pairs being arranged in a frame.
Besides, the invention concerns a method of manufacturing a stack of plate pairs according to one of the above features, or a heat exchanger according to one of the above features. For this method, the following steps are carried out:
Other features and advantages of the device according to the invention will be clear from reading the description hereafter of embodiments given by way of non-limitative example, with reference to the accompanying figures wherein:
For clarity reasons, the figures do not necessarily show the plates in the spatial position in which they can be assembled, or in their position of use. Indeed, the plates are represented in all the figures in different planes. The figures remain schematic representations, therefore all of the components shown are not necessarily to scale, and they have been simplified to facilitate reading.
Throughout the present text, the terms “supply” or “inlet” and “outlet” or “discharge”, and “in” or “out of” are used in reference to the direction of flow of the fluids.
Throughout the present text, the term “side” or “edge” of the central panel is used in reference to the periphery of the central panel, over a certain width, for example up to 5% or 10% of the width of the plate.
Throughout the present text, the term “mirror image” relates to a symmetry with respect to a plane located in the middle of the space that separates the object from its image.
Throughout the present text, the “inner face” of a plate designates the face turned towards the other plate with which it is assembled into a plate pair, and the “outer face” of this plate is the face turned in the opposite direction to the other plate of the plate pair in question.
The invention concerns a pair of plates of a plate heat exchanger. A heat exchanger allows heat exchange between two fluids, or between a fluid and a heat source or a cold source. Generally, such a heat exchanger comprises at least one wall, notably a metal wall (here a plate for a plate heat exchanger) allowing heat transfer between the two fluids or between the fluid and the heat source or the cold source. The metal of the wall (the metal of the plate for a plate heat exchanger) can be of any type, notably steel, aluminum, copper, etc., and alloys thereof. As a variant, the wall can be provided with a coating. Alternatively, the wall can be made of plastic or any similar material.
The invention can be used for example for plate heat exchangers operating on the cross-flow principle, wherein the fluids flowing on both faces of each plate are directed substantially perpendicular to one another. The invention can also be used for plate heat exchangers operating on the counter-current principle, wherein the fluids flowing on both faces of each plate are directed substantially in opposite directions. The invention can also be used for plate heat exchangers operating on the co-current principle, wherein the fluids flowing on both faces of each plate are directed substantially in the same direction. The invention can also be used for plate type heat exchangers operating on other flow principles.
The invention is particularly suitable for heat exchange between two fluids, notably two gases, but it can also be used for heat exchange between two liquids, or between a liquid and a gas.
The invention is more particularly suited to heat exchange between two gases, notably gas flows at the inlet and the outlet of a single equipment, such as for example the air to be conveyed to a furnace and the fumes from this furnace or, likewise, the hot stream from an NOx reduction system and the cold stream flowing into this NOx reduction system.
According to the invention, the pair of heat exchange plates comprises a first substantially plane heat exchanger plate and a second substantially plane heat exchanger plate. Within the plate pair, the first and second plates are assembled and arranged face to face, and spaced apart so as to define an inner volume capable of forming a single channel for flow of a first fluid.
Each plate comprises a central panel serving as a heat exchange surface between the two fluids within the heat exchanger. The central panels are substantially plane. The central panel has a first face (or lower face) and a second face (or upper face) opposite the first face. The terms “lower” and “upper” therefore relate by convention to a panel arranged in a horizontal plane. Within the pair of plates, the central panel of the first plate is parallel to the central panel of the second plate. The central panel of the heat exchanger plate according to the invention can have any suitable shape, trapezoidal, hexagonal or quadrilateral for example. The central panel is most preferably quadrilateral, notably rectangular or square, possibly with truncated, cut or rounded edges.
Moreover, the central panel of each plate comprises at least one groove protruding into the inner volume. In other words, at least one groove protrudes on the inner face of the central panel of each plate. The grooves on the two plates form a relief providing stirring of the fluids in the inner volume, thus allowing thermal exchanges to be increased. Indeed, the grooves increase the turbulence level of at least one fluid flowing through the heat exchanger and break the boundary layer of the flow at the plate, which promotes heat exchanges. Furthermore, the central panel being plane, the central panel consists of at least one plane portion and at least one groove. Preferably, the central panel of each plate comprises only grooves protruding into the inner volume; no groove is provided in the outer volume.
According to an implementation of the invention, the at least one groove can be inclined at an angle α to an edge of the central panel.
Preferably, this angle α can be non-zero and non-right. In other words, for this preferred embodiment, the groove is parallel to no edge of the central panel. Thus, the groove is neither parallel nor perpendicular to the direction of flow of the fluid.
According to an aspect, angle α of inclination of the grooves relative to one side of the central panel can be greater than or equal to 10°, preferably ranging between 10° and 80°, inclusive, more preferably ranging between 30° and 70°, inclusive, and most preferably ranging between 40° and 50°, inclusive. These value ranges allow to increase the flow turbulence level of at least one fluid in the heat exchanger, and to break the boundary layer of the fluid flow, which is the main reason for the heat exchange increase.
Advantageously, the at least one groove can be rectilinear (in the plane of the central panel). This shape promotes the manufacture thereof and limits pressure drops.
Within the pair of plates according to the invention, each groove of the first plate is parallel to each groove of the second plate. Thus, the parallelism of the grooves of the first and second plates enables to simplify the assembly: the two plates are nearly similar, and they require no modification of the orientation of one plate in relation to the other.
According to a preferred embodiment, each groove of the second plate can be offset with respect to each groove of the first plate in a direction perpendicular to the grooves of the first and second plates. In other words, each groove of the second plate does not face a groove of the first plate in the inner volume defined by the pair of plates. In other words still, where applicable (plurality of grooves on each plate), each groove of the second plate is interposed between two grooves of the first plate in a direction perpendicular to the grooves. The groove offset promotes optimization of the fluid flow disruption in the channel, which allows the thermal performances of the plate pair to be increased.
According to an aspect, the grooves can be manufactured by deformation, for example by rolling, drawing, rubber forming for example, or any similar process.
The channel height (space between two consecutive plates) can be determined according to the operating conditions of the heat exchanger. Typically, it can be 5 mm to 30 mm, inclusive, notably 5 mm, 10 mm, 15 mm, 20 mm, 30 mm, or any suitable height. According to an aspect, the channel height can be different between the cold side of the heat exchanger and the hot side of the heat exchanger.
The width of the heat exchanger plate according to the invention can typically range between 750 mm and 2000 mm, inclusive, preferably between 1000 mm and 1700 mm, inclusive. The length of the heat exchanger plate according to the invention can typically range between 1000 mm and 7500 mm, inclusive, preferably between 1500 mm and 7000 mm, inclusive.
The thickness of the plate can range between 0.6 mm and 6 mm, inclusive, preferably between 1.5 mm and 2.0 mm, inclusive.
According to an embodiment of the invention, each central panel of each plate can comprise a plurality of parallel grooves (i.e. at least two grooves parallel to one another). In addition, the grooves of each central panel can be evenly spaced apart. In other words, a plane portion of the central panel is interposed between two consecutive grooves. The number of grooves allows to increase stirring of the fluids, thereby increasing thermal exchanges.
Advantageously, for this embodiment, the pitch between the grooves of the first plate can be identical to the pitch between the grooves of the second plate. Thus, the plates can be manufactured with the same machine and with similar tools, which promotes the design thereof.
Advantageously, for the embodiment wherein the grooves of the second plate are offset with respect to the grooves of the first plate, the offset in the perpendicular direction of the grooves can have a distance ranging between one third and two thirds of the pitch. Thus, the grooves of the second plate can be interposed between the grooves of the first plate. Preferably, the offset in the perpendicular direction can have a distance substantially equal to half the pitch. Thus, the grooves of the second plate can be interposed in the middle, between the grooves of the first plate.
Advantageously, the pitch can range between 10 mm and 80 mm, inclusive, preferably between 20 mm and 60 mm, inclusive. The pitch is the dimension between two successive groove vertices measured in a direction perpendicular to the first edge of said groove.
According to an embodiment option, each groove can have a cross section in a transverse direction to the groove (the cross section is also referred to as groove profile) whose shape is selected from among: an arc of a circle, a semicircle, a U, a V, an ellipse, an airplane wing, a spearhead (shape of the pointed iron head attached to the end of a spear, an arrow or a spike), or any similar shape. Preferably, the grooves have the shape of an arc of a circle or an airplane wing. These shapes promote stirring of the fluid, thereby increasing heat exchanges, and they have no protruding angle.
According to an embodiment of the invention, the width of each groove can range between 4 mm and 30 mm, inclusive, preferably between 6 mm and 25 mm, inclusive. The width of a groove is measured from one edge to the opposite second edge in a direction perpendicular to the first edge of said groove.
According to an implementation, the protrusion height of each groove can range between 1.5 mm and 6 mm, inclusive, preferably between 2 mm and 5 mm, inclusive. The protrusion height of a groove is the dimension in an orthogonal direction to the plane of the central panel. It is measured exclusive of the exchanger plate thickness, i.e. from the lower face of the plate to the top of the groove.
Preferably, the width-to-height ratio of the grooves can range between 3 and 5, more preferably between 3 and 4. These value ranges enable realization of the grooves and they provide a turbulent flow promoting heat exchanges.
Advantageously, all the grooves of the first plate and/or of the second plate can have a constant profile, width and height over the entire length of the groove. Thus, the protrusions are identical over the entire central panel.
Advantageously, all the grooves of the first and second plates have the same cross section (profile), the same width and the same protrusion height. Thus, the protrusions are identical, which simplifies the manufacture of the plate pair.
According to an aspect, spacers, manufactured for example from strips, profiles or pin fins can be inserted in at least one/each channel so as to ensure spacing between the plates. They may be loose or spot welded, or held in position by means of U-shaped clamps at the supply and discharge.
According to an embodiment of the invention, the first plate and the second plate can be mechanically fastened by means of a junction panel arranged on at least one side of a central panel. The at least one junction panel is connected, notably welded, to the central panel of at least one plate of the plate pair.
The junction panels are preferably obtained by plate folding operations, but they can also be obtained differently, and even attached to the central panels using various conventional fastening means. Each junction panel can preferably be formed in a single step, by deformation/folding. Deformation can be obtained by press forming and/or folding. A series of steps of deformation of the flat metal sheet can be required to form a series of lateral junction panels on a single plate (one or two pairs of panels).
Thus, for this embodiment, a heat exchanger plate can comprise a central panel and a junction panel. The heat exchanger plate according to the invention can preferably be made in one piece, usually by deformation, in one step, of a flat metal sheet consisting of a weldable material, for example a metal plate, notably steel, stainless steel for example.
Alternatively, each junction panel can be mechanically attached to the central panel of the adjacent plate by any conventional technique, typically by welding.
Furthermore, each junction panel can be made of two parts, inclined relative to one another so as to promote fastening to a plate.
Advantageously, the second part of each junction panel can be sufficiently large to enable mechanical fastening of the second part to the central panel of the adjacent plate using a conventional means known to those skilled in the art.
In the rest of the description, a distinction is made between a “first junction panel”, a junction panel allowing two plates of a single pair of plates to be connected, and a “second junction panel”, a junction panel allowing two plates of two pairs of plates to be connected (when forming a stack of plate pairs or a heat exchanger).
For example, each plate can comprise:
The at least one junction panel can be in accordance with one of the embodiments described in patent application FR-3,086,742 (WO-2020/069,880) or in patent application FR-3,108,714 (WO-2021/190,879).
Advantageously, at least one and notably all of the junction panels comprise a first part extending from the central panel and a second part extending from said first part, said first part forming an angle δ with the central panel, and said second part being parallel to said central panel. It is a very advantageous configuration because it thus allows to fasten the second part of the panel, a plane surface, to an edge of the other plate that is also plane and parallel thereto: weld type fastening is in particular facilitated.
Advantageously, the junction panels, in particular the two parts of these junction panels, can be obtained by folding the plate. The inclination of the junction panel, notably of the first part when it comprises two parts, does not necessarily involve a perfect angle at the folding: the intersection between the plane of the central panel and that of the junction panel can form a rounded angle/curved transition zone. It is the same between the first part and the second part of the junction panel when it comprises two parts: the second part can extend the first with a curved transition zone between them.
Advantageously, angle δ between the first part of the junction panel and the central panel is at least 45°, preferably at least 60°, notably ranging between 80° and 110°, inclusive, preferably close to 90°.
In fact, the width of the first part of the junction panel and its inclination angle δ relative to the central panel define the spacing between the two plates: for example, for the same angle, the wider the first part of the junction panel, the larger the space between the two plates. The junction panel thus determines alone, due to its dimensioning and positioning relative to the central panel, the height of the volume in which one of the fluids will flow once the exchanger consists of one or more of these pairs, with a given plate size.
According to a first variant described in these patent applications, each pair of plates can comprise a pair of junction panels. For this variant, each plate can comprise a junction panel. This embodiment allows to achieve, for two plates of a pair of plates, identical junction panels, which facilitates manufacture of the junction panels. The design of the junction panels of the plate pair can be obtained by turning one plate relative to the other. Alternatively, one of the two plates can comprise the two junction panels, preferably arranged on opposite sides of the central panel.
According to a second variant described in these patent applications, each pair of plates can comprise two pairs of junction panels. Each pair of junction panels can be provided on a different side of the central panels. For this variant, each plate can comprise two junction panels on two adjacent sides of the central panel, one of the two junction panels being a “first junction panel”, and the other junction panel being a “second junction panel”. This embodiment allows to achieve, for two plates of a pair of plates, similar junction panels, which facilitates manufacture of the junction panels of the plate pair. The design of the junction panels of the plate pair can be obtained by turning one plate relative to the other.
The invention also concerns a stack of heat exchanger plate pairs. Such a stack comprises at least two pairs of plates according to any one of the variants or variant combinations described above. Two successive pairs of plates in the stack are respectively denoted by first pair of plates and second pair of plates so as to distinguish them. However, the two plate pairs can be identical, or they can be a mirror image (i.e. symmetrical) relative to one another.
In the stack, the first plate pair and the second plate pair are arranged parallel to one another and opposite one another. Within each plate pair, the inner volume between the two plates forms a single channel receiving the flow of a first fluid. It is the inner volume comprising the protruding grooves. Thus, the clogging risk is lower in this volume. Furthermore, the volume between the two consecutive plate pairs in the stack forms a single channel receiving the flow of a second fluid. This volume does not comprise the protruding grooves, but the recessed grooves.
For the embodiment where the plates comprise the second junction panels, the second junction panels can be used to connect two consecutive plate pairs, and to maintain a distance between the two consecutive plate pairs. Moreover, the second junction panels delimit the channel for the flow of the second fluid.
The direction of flow of the fluids is determined by the design of the plates and by the way they are connected via the junction panels.
According to an implementation of the invention, wherein heat exchange occurs in cross-flow mode, the channel intended for the second fluid can be substantially perpendicular to the channel intended for the first fluid. This implementation can notably be achieved by means of second junction panels perpendicular to the first junction panels.
According to a variant, wherein heat exchange occurs in counter-current or co-current mode, the channel intended for the second fluid can be substantially parallel to the channel intended for the first fluid.
According to an aspect of the invention, the height between two pairs of plates can be identical to the height between two plates.
Alternatively, the height between two pairs of plates can be different from the height between two plates.
The invention further concerns a plate heat exchanger. The plate heat exchanger comprises plate pairs according to any one of the variants or variant combinations described above, or a stack of plate pairs according to any one of the variants or variant combinations described above.
According to the invention, the plate heat exchanger comprises a frame for mounting the plate pairs or for stacking the plate pairs.
The heat exchanger further comprises:
The inlet and the outlet for the first fluid are connected to the channels through which the first fluid flows. The inlet and the outlet for the second fluid are connected to the channels through which the second fluid flows.
A plate heat exchanger according to the invention can be used for fluids operating at a pressure ranging from total vacuum pressure to 1.5 MPa, preferably from 0.01 MPa to 1.0 MPa, and more preferably from 0.01 MPa to 0.6 MPa.
A plate heat exchanger according to the invention can consist either of channels of uniform height, or of channels of different heights in each circuit. Likewise, the height of the first junction panel and the heights of the second and third junction panels, if applicable, can be similar or different.
Advantageously, the plate heat exchanger can operate on the cross-flow principle, wherein the fluids flowing on both faces of each plate are directed substantially perpendicular to one another. Alternatively, the invention can also be used for plate heat exchangers operating on the counter-current principle, wherein the fluids flowing on both faces of each plate are directed substantially in opposite directions. As a variant, the invention can also be used for plate heat exchangers operating on the co-current principle, wherein the fluids flowing on both faces of each plate are directed substantially in the same direction. The invention can further be used for plate type heat exchangers operating on other flow principles.
The heat exchanger according to the invention is particularly suitable for heat exchange between two fluids, notably two gases, but it can also be used for heat exchange between two liquids, or between a liquid and a gas.
The invention is more particularly suited to heat exchange between two gases, notably gas flows at the inlet and the outlet of a single equipment, such as for example the air to be conveyed to a furnace and the fumes from this furnace or, likewise, the hot stream from a NOx reduction system and the cold stream flowing into this NOx reduction system. For this application, the first fluid (flow with grooves) can be air, and the second fluid (flow without grooves) can be fumes.
Alternatively, the heat exchanger can have an application in all fields of industry or energy production, or in any similar system.
The invention further concerns a method of manufacturing a stack of plate pairs according to any one of the variants or variant combinations described above, or a heat exchanger according to any one of the variants or variant combinations described above.
For the manufacturing method, the following steps are carried out:
According to an implementation of the invention, the manufacturing method can comprise an additional step wherein, after the plate preparation step, the heat exchanger plates can be arranged in two stacks (first half of the plates and second half of the plates) so as to prepare two different plate types (first plate and second plate respectively).
Due to the parallelism, the possible inclination and optionally the groove offset, the plates of the first half of the plates are, except in specific cases, different from the plates of the second half of the plates. Indeed, the grooves made are, except in special cases, different between these plates.
For this implementation, the grooves can be formed in the plates such that the grooves of the plates of the second stack are offset by a regular pitch with respect to the grooves of the plates of the first stack.
Depending on the embodiments of the stack or the exchanger to be manufactured, the method can further comprise at least one of the following steps:
It goes without saying that the invention is not limited solely to the embodiments of the plate pairs described above by way of example, and that it encompasses all variant embodiments.
Other features and advantages of the system according to the invention will be clear from reading the comparative example hereafter.
For this comparative example, the thermal performance of a plate exchanger according to the invention and that of two plate exchangers according to the prior art are determined.
For these three configurations, the other design elements (dimensions for example) and the operating conditions are identical.
For each configuration, the heat transfer (Nusselt number, denoted by Nu, a dimensionless number used to characterize the type of heat transfer between a fluid and a wall) and the friction factor (a dimensionless number characterizing the pressure drop, denoted by ξ) are evaluated as a function of the Reynolds number (a dimensionless number characterizing the flow type, in particular the nature of the flow regime). Ratio
representing the thermal performances of the heat exchange in relation to the pressure drops is then determined. A high value of such a ratio allows to qualify the heat transfer with respect to the pressure drops; if two heat exchangers have the same pressure drop, but a different ratio, the one with the higher ratio will have better heat transfer and may require a smaller heat exchange surface.
as a function of the Reynolds number. It is noted that the invention INV has a higher ratio
whatever the Reynolds number. It follows that the invention provides greater heat transfer reinforcement for an identical pressure drop in relation to the plate heat exchangers of the prior art. The invention is therefore more efficient in terms of heat transfer than the solutions of the prior art.
| Number | Date | Country | Kind |
|---|---|---|---|
| FR2111317 | Oct 2021 | FR | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2022/078118 | 10/10/2022 | WO |
