Heat exchanger having at least one particle filter in one or a plurality of passages

Abstract

To perform charging by using a method for holding a catalyst in a passage, and further easily and favorably controlling the passage.SOLUTION: In a heat exchanger having a stack of a plurality of plates which are parallel with a longitudinal direction z, the plates are piled up so as to be separable from one another in order to define a first serial passage 10 for a flow of at least a first fluid in an entire flow direction which is parallel with the longitudinal direction z between and among the plates, and the passage 10 is partitioned by closing bars 6 which are arranged between and among the plates. A filtering device 31 is arranged in at least first one passage 10, the filtering device 31 extends between the two adjacent plates for defining the passage 10 with respect to one portion, and extends between the two closing bars 6 which partition the passage 10 with respect to the other portion. Also, the filtering device 31 comprises a metal sheet material selected from a metal cloth, a metal-fiber nonwoven fabric, sintered metal powder or a sintered metal fiber, a metal foaming body, or a microperforated plate.SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001]

[0001] The present invention relates to a heat exchanger, more particularly a brazed fin and plate type heat exchanger, comprising at least one filter for limiting the introduction of undesirable particles into the body of the heat exchanger, or for retaining particles that perform a specific function inside the body of the heat exchanger.

[0002]

[0002] The present invention is particularly applicable to the field of hydrogen liquefaction. In particular, the present invention can be applied to a catalytic heat exchanger in which a flow of gaseous hydrogen is cooled or partially liquefied by heat exchange with a flow of refrigerant fluid, as well as to a cooling and / or liquefaction method that incorporates the heat exchanger.

[0003]

[0003] The present invention is also applicable to the cryogenic separation of gases, in particular to the separation of air by cryogenic distillation. In particular, the present invention can be applied to a heat exchanger that evaporates a flow of liquid, such as liquid oxygen, nitrogen and / or argon, by heat exchange with a gaseous flow, such as air or nitrogen.

[0004]

[0004] The present invention can also be applied to a heat exchanger that evaporates a flow of at least one liquid-gas mixture, such as a mixture of hydrocarbons, by heat exchange with at least one other fluid that is liquefied, such as natural gas. [Background technology]

[0005]

[0005] A commonly used technique for heat exchangers is that of brazed plate heat exchangers, which allows for extremely compact components that result in a large heat exchange surface area and low pressure loss. These heat exchangers comprise one or more exchange bodies formed by a set of parallel plates in which spacer elements, such as corrugated or wavy sections that form a fin-type heat exchange structure, can be inserted between them. The stacked plates form a stack of flat passages between them for the various fluids to be brought into the heat exchange relationship. The exchanger comprises a fluid manifold equipped with inlet and outlet pipes for introducing fluid into the heat exchange body and for discharging fluid from the heat exchange body.

[0006]

[0006] Certain heat exchangers may require the installation of a fluid filtration device to limit, or even avoid, the introduction of solid particles into the heat exchanger body that could adversely affect the thermal and hydraulic performance of the heat exchanger.

[0007]

[0007] In other heat exchangers, in contrast, it is necessary to hold particles inside the body of the heat exchanger. These particles may be placed inside the passages of the heat exchange body to perform various functions therein. In catalytic heat exchangers in particular, the particles are formed by catalytic material that produces chemical reactions with the fluid circulating in the passages.

[0008]

[0008] Catalytic heat exchangers intended for liquefying hydrogen are particularly known, in which ortho-hydrogen molecules are converted to para-hydrogen molecules during liquefaction by a suitable catalyst. In these heat exchangers, the inlet and outlet manifolds for introducing and discharging hydrogen are usually formed by domes, which cover the fluid inlet and outlet openings of the heat exchanger body over all sides of the body in which the domes are located. To restrict the movement of catalyst particles in the passages of the heat exchanger, the internal volumes of the inlet and outlet manifolds are also filled with catalyst, thereby significantly increasing the amount of catalyst used.

[0009]

[0009] The body and manifold of the heat exchanger are filled after these elements are brazed to each other. A heat exchanger equipped with such a filling device is partially schematic in [Figure 1]. The catalyst is located at the top of the heat exchanger and is distributed through one or more vertical pipes 100 connected to the internal volume of the manifold. Filling is carried out by gravity flow of catalytic fluid through the vertical pipes 100 by a specific distribution nozzle. The manifold is also equipped with a lateral pipe 200 into which cylindrical filtering cartridges are inserted before the catalyst is filled. These cartridges are made of a porous material configured to allow fluid to enter the manifold but to block catalyst particles. A fluid inlet duct 300 is connected to the lateral pipe so that the fluid is distributed within the heat exchanger via the filtering cartridges.

[0010]

[0010] This solution results in a complex architecture that requires the installation of numerous ducts in the heat exchanger manifold. In addition to the complexity of manufacturing and using the filtration cartridge, this solution unnecessarily increases the amount of catalyst used because the manifold is also filled with catalyst. In fact, catalyst is a specialized and expensive material.

[0011]

[0011] Furthermore, the use of a dome limits the width of the heat exchanger, which must not exceed this limit. This is because, with respect to the operating pressure of certain heat exchangers, particularly catalytic heat exchanger type heat exchangers, which can typically be between 25 and 60 bar in height, wider heat exchanger sections become more bulky and require a dome formed by a thicker metal sheet. Because it is difficult to fix such a dome onto the heat exchanger body, it is difficult to consider designing and manufacturing heat exchangers on an industrial scale.

[0012]

[0012] Furthermore, the introduction of the catalyst into the heat exchange body is complex and requires special tools and equipment. The uniformity of the distribution of catalyst particles between the various passages of the heat exchange body is difficult to control. [Overview of the project]

[0013]

[0013] The object of the present invention is to solve all or some of the problems mentioned above by providing a heat exchanger equipped with a filtering device, which is simpler than the prior art, which allows the catalyst to be retained in the passages and the passages to be filled in a way that is simpler and better controlled, especially when the heat exchanger is intended to carry out a catalytic reaction, which also allows for a reduction in the amount of catalyst used, and which also simplifies the design and fixing of all or some of the fluid inlet and outlet manifolds.

[0014]

[0014] The solution according to the present invention is a heat exchanger comprising a stack of a plurality of plates parallel to each other and in the longitudinal direction, wherein the plates are stacked spaced apart from each other to define a first series of passages between them for at least a first fluid flow in an overall flow direction parallel to the longitudinal direction, and each passage is separated by a closing bar disposed between the plates, wherein a filtration device is disposed in at least one of the first series of passages, wherein the filtration device extends between two adjacent plates defining the passage in one part and between two closing bars separating the passage in the other part, and the filtration device comprises a metal sheet material selected from metal cloth, metal fiber nonwoven fabric, sintered metal powder or sintered metal fibers, metal foam, or microperforated plate.

[0015]

[0015] Depending on the circumstances, the heat exchanger according to the present invention may have one or more of the following features.

[0016]

[0016] The heat exchanger comprises at least a first inlet or outlet manifold configured to introduce a first fluid into a first passage or to collect a first fluid from a first passage, the distribution structure and the heat exchange structure are arranged in a continuum from the first inlet or outlet manifold in at least one passage, and the filtration device is arranged between the distribution structure and the heat exchange structure.

[0017]

[0017] The heat exchanger comprises at least a first inlet or outlet manifold configured to introduce a first fluid into a first passage or to collect a first fluid from a first passage, the distribution structure and the heat exchange structure are arranged in a continuum from the first inlet or outlet manifold in at least one passage, and the filtration device is arranged between the distribution structure and the first inlet or outlet manifold.

[0018]

[0018] The at least one passage is provided with an inlet or outlet opening that leads into the first inlet or outlet manifold, the at least one passage is perpendicular to the longitudinal direction and has a width measured parallel to the transverse direction perpendicular to the plate, the width of the inlet or outlet opening measured parallel to the transverse direction being between 10% and 70%, preferably between 20% and 50%, of the width of the passage.

[0019]

[0019] The filtration device comprises two ends, each positioned within a recess in the closing bar.

[0020]

[0020] The recess has a maximum width measured parallel to the longitudinal direction and comprises a first portion formed over a maximum height corresponding to the height of the bar, the height measured parallel to the stacking direction perpendicular to the longitudinal and transverse directions, the first portion is formed over a minimum width less than the maximum width, and the recess further comprises at least one second portion formed over a minimum height less than the maximum height and extending over the maximum width.

[0021]

[0021] The filtration device comprises at least one front surface positioned perpendicular to the overall flow direction of the first fluid, the front surface being connected to at least one transverse surface positioned parallel to the plate.

[0022]

[0022] The filtration device has a total width measured parallel to the longitudinal direction, between 2 and 10 mm, preferably between 3 and 7 mm.

[0023]

[0023] The metal sheet material has a thickness between 0.20 and 0.75 mm, preferably between 0.3 and 0.5 mm.

[0024]

[0024] The metal sheet material has an open surface density in the range of 15% to 35%, or a pore volume density in the range of 75% to 98%.

[0025]

[0025] The metal sheet material is a fabric of metal threads, and the threads have a diameter between 0.10 and 0.30 mm, preferably between 0.10 and 0.25 mm.

[0026]

[0026] The metal sheet material comprises at least one series of first metal threads and a series of second threads intertwined to form a mesh, each mesh being delimited between two consecutive first threads and two consecutive second threads, and the mesh having an aperture size between 0.07 mm and 0.15 mm.

[0027]

[0027] The metal sheet material is a micro-perforated plate having a plurality of orifices sized between 0.07 mm and 0.15 mm, measured in a plane parallel to the plate.

[0028]

[0028] The heat exchanger is an exchanger-reactor configured to carry out a catalytic reaction between a first fluid and at least one catalytic material, and at least a part of a first series of passages contains particles of the at least one catalytic material.

[0029]

[0029] The catalytic material comprises particles having an equivalent diameter in the range from a minimum diameter to a maximum diameter, and the metal sheet material is a fabric of metal threads having a mesh aperture size in the range from 10% to 85% of the minimum diameter of the particles.

[0030]

[0030] The heat exchanger is configured to liquefy hydrogen as the first fluid, and the catalytic material is configured to convert ortho-hydrogen to para-hydrogen, and in particular the catalytic material is iron oxide.

[0031]

[0031] The present invention also relates to a method for cooling and / or liquefying at least a portion of a stream of gaseous hydrogen with respect to a stream of refrigerant fluid, wherein the stream is introduced into a first passage and a second passage of a heat exchanger according to the present invention, respectively.

[0032]

[0032] In particular, the method according to the present invention carries out the conversion of at least some of the ortho-hydrogen molecules in a stream of gaseous hydrogen to para-hydrogen molecules using particles of at least one catalyst material.

[0033]

[0033] In particular, the stream of gaseous hydrogen has a pressure in the range of 20 to 80 bar, preferably 25 to 40 bar.

[0034]

[0034] Next, the present invention will be better understood by referring to the accompanying figures, as given in the following description as an example that is not limiting to the description. [Brief explanation of the drawing]

[0035] [Figure 1]

[0035] A partial view of a heat exchanger equipped with a filtration device according to prior art. [Figure 2]

[0036] A three-dimensional view of a heat exchanger according to another embodiment of the present invention. [Figure 3]

[0037] A three-dimensional view of a heat exchanger according to another embodiment of the present invention. [Figure 4]

[0038] A partial longitudinal cross-section showing the passages of a heat exchanger according to one embodiment of the present invention. [Figure 5]

[0039] A partial longitudinal cross-section showing the passages of a heat exchanger according to another embodiment of the present invention. [Figure 6]

[0040] A diagram showing a filtration device according to several embodiments of the present invention. [Figure 7]

[0041] A diagram showing a filtration device according to several embodiments of the present invention. [Figure 8]

[0042] A partial three-dimensional view showing a recess according to one embodiment of the present invention. [Figure 9]

[0043] A partial longitudinal cross-sectional view showing a recess according to one embodiment of the present invention. [Figure 10]

[0044] A schematic diagram showing the structure of a filtration device according to another embodiment of the present invention. [Modes for carrying out the invention]

[0036]

[0045] Referring to Figure 2 or Figure 3, a heat exchanger according to one embodiment of the present invention is of the brazed fin and plate type. The elements constituting the heat exchanger are preferably made of aluminum or an aluminum alloy. The heat exchanger comprises a heat exchange body 1 formed by a stack of plates 2. The plates 2 extend in two dimensions, i.e., in length and width, in the longitudinal direction z and the transverse direction x, respectively. The plates 2 are arranged in a sequential stack parallel to each other and spaced apart from each other.

[0037]

[0046] These thus form at least a first series of passages 10 and a second series of passages 20 between them, the first series of passages 10 being provided for the flow of a first fluid, and the second series of passages being provided for the flow of at least a second fluid which is brought into an indirect heat exchange relationship with the first fluid through the plate 2. The lateral direction x is perpendicular to the longitudinal direction z and parallel to the plate 2. The fluid flow preferably flows along the length of the heat exchanger, and is generally parallel to the longitudinal direction z, and this length is large compared to the width of the heat exchanger.

[0038]

[0047] The spacing between two consecutive plates 2, corresponding to the height of the passage measured in the stacking direction y of plate 2, is small compared to the length and width of each consecutive plate. The stacking direction y is perpendicular to the plates. The passage 10 may be arranged alternately with or adjacent to all or part of the second series of passages 20, either entirely or partially. Preferably, at least part of the passages 10, 20 comprises a fin-type heat exchange structure, for example, a corrugated structure, that extends parallel to the plates 2 and along the width and length of the passages in the heat exchanger.

[0039]

[0048] In certain embodiments of the present invention, a first series of passages 10 and a second series of passages 20 are provided, respectively, for the flow of hydrogen (H2) as the first fluid. The second fluid may be hydrogen (H2), helium (He), or nitrogen (N2). Preferably, the second fluid is liquid hydrogen or liquid helium, which makes it possible to improve thermal efficiency. In particular, the second fluid may be already cooled, especially whole or partially liquefied, hydrogen coming from another heat exchanger of the same type as the subject of the present invention. When the heat exchanger is used for cooling and / or liquefying hydrogen, the hydrogen as the first fluid is a heat-producing fluid, and the second fluid is a refrigerant fluid. It will be noted that other fluid compositions may be used as the refrigerant fluid.

[0040]

[0049] Preferably, each passage 10, 20 has a flat parallelepiped shape. The heat exchanger includes closing bars 6 disposed between plates 2 around the passage. These bars 6 provide a gap between plates 2 and ensure the passage is sealed.

[0041]

[0050] In a manner known by itself, the heat exchanger comprises distribution and discharge means 21, 22, 71, 72, referred to as manifolds or header tanks, which are joined to the side of the stack and configured to selectively distribute fluid into passages 10, 20 and discharge the fluid from the passages 10, 20. Each manifold has a surrounding wall that divides an internal volume, an open end located on the side of the heat exchange body, and pipes 23 designed to deliver fluid into or discharge fluid from the internal volume.

[0042]

[0051] The closing bar 6 does not completely close the passage, leaving the openings on the sides of the body 1 open for the corresponding fluids in the passage to enter or leave. Inlet openings 11 for introducing each of the fluids circulating within the heat exchanger are arranged coincidentally at the top and bottom. Outlet openings for discharging each of the fluids circulating within the heat exchanger are arranged coincidentally at the top and bottom. The inlet openings 11 in the first series of passages 10 are fluidically joined within the first inlet manifold 21. The outlet openings 12 in the first series of passages 10 are fluidically joined within the first outlet manifold 22.

[0043]

[0052] The first inlet opening in the second passage 20 is fluidically joined within the second inlet manifold 71. The outlet openings in the second passage 20, located above and below each other, are fluidly joined within the second outlet manifold 72.

[0044]

[0053] It is made clear that the features of the present invention given in this description in relation to a first series of passages can be applied to other passages, and that the filtration solutions according to the present invention can be considered for all or part of the fluid circulating within a heat exchanger.

[0045]

[0054] As shown in Figure 2, the inlet and outlet manifolds 21, 22, 71, and 72 are in the form of semi-tubular heads, i.e., semi-cylindrical, and only partially cover the sides of the main body in which they are arranged. A distribution corrugated section is positioned between the continuous plates 2, and this distribution corrugated section is in the form of a corrugated metal sheet extending from the inlet or outlet opening, providing uniform distribution and guidance of the fluid across the entire width of the passages 10 and 20 to the heat exchange zone of the passages.

[0046]

[0055] Preferably, at least one portion of the manifolds 21, 22, 71, and 72 faces the inlet and outlet openings in the passage 10 and extends in the stacking direction y over the entire height of the body 1 and in the lateral direction x over part of the width of the body 1.

[0047]

[0056] According to another possibility shown in [Figure 3], the inlet and / or outlet manifolds 21, 22, 71, 72 are dome-shaped and cover all sides of the main body in which they are installed.

[0048]

[0057] It should be noted that the heat exchanger according to the present invention may include both a dome-shaped manifold and a head-shaped manifold, and in particular, the first inlet manifold 21 may be dome-shaped and the first outlet manifold 22 may be head-shaped.

[0049]

[0058] In the illustrated embodiment, the first inlet manifold 21 and the second outlet manifold 72 for the first fluid are located at the same end of the heat exchanger, and the first and second fluids circulate in counterflow within the passages of the heat exchanger. Preferably, the longitudinal direction is vertical when the heat exchanger is operating. The first inlet manifold 21 for the first fluid is located at the upper end of the heat exchanger, and the first outlet manifold 22 for the first fluid is located at the lower end of the heat exchanger. The first fluid flows vertically downward overall, i.e., against direction z in [Figure 2]. Of course, other directions of fluid flow are conceivable without departing from the scope of the invention.

[0050]

[0059] As can be seen in Figure 4 or 5, which shows a longitudinal section of a first series of passages 10 according to the present invention, the filtration device 31 is positioned within at least one of the first series of passages 10. The filtration device 31 extends between two adjacent plates 2 in one portion and between two closing bars 6 that divide the passages 10 in the other portion. The filtration device 31 comprises a metal sheet material 30 selected from metal cloth, nonwoven metal fiber fabric, sintered metal powder or sintered metal fibers, metal foam, or microperforated plate.

[0051]

[0060] The term "metallic cloth" is understood to mean a product obtained by weaving metallic threads, that is, by intertwining threads to obtain a metallic fabric, i.e., metallic cloth. The term "metallic cloth" can also refer to a product obtained by welding metallic threads, i.e., a welded cloth formed by crossing threads that are spot-welded at intersections.

[0052]

[0061] The term “nonwoven fabric” or “unwoven fabric” is understood to mean a product formed of fibers arranged within a sheet, oriented randomly or directionally, and linked together by mechanical, chemical, or thermal means, or a combination thereof, without involving weaving. In particular, nonwoven fabrics may be formed of fibers linked together by friction, cohesive, or adhesive.

[0053]

[0062] The term "sintered" refers to a material obtained by sintering metal fibers or powder, that is, by heating the powder or fibers without melting them. Under the effect of heat, the particles or fibers are welded together, resulting in the aggregation of the material.

[0054]

[0063] The term "foam" refers to an alveolar structure made of metal that contains a large pore volume.

[0055]

[0064] A microperforated plate refers to a plate that has microperforations, i.e., through orifices that are micrometer-sized, i.e., less than a millimeter.

[0056]

[0065] As a result of using metal cloth, nonwoven metal fiber fabric, sintered metal, metal foam, or microperforated plates, materials having openings or perforations can be obtained that can be sized to allow fluid flow while preventing the passage of solid particles that should be retained within the heat exchange body or the introduction of solid particles into the body that should be avoided. These materials offer a good compromise between fluid permeability, the efficiency of the filtration action due to the small opening size that can be obtained, and the hardness of the filter.

[0057]

[0066] The filtration device, due to its sheet structure, can be easily formed, particularly by bending or molding in a press, so that it can be positioned transversely to the inside of the heat exchanger passage to realize a particle blocking function therein. The filtration device can therefore be positioned near the heat exchange or distribution structure located within the passage. In the case of a catalytic heat exchanger, this makes it possible to significantly reduce the amount of catalyst used, as it eliminates the need to fill the manifold with catalyst.

[0058]

[0067] Similarly, one could consider providing a distribution zone without a catalyst in the passage, which would allow the use of a semi-cylindrical manifold. Semi-cylindrical heads can be manufactured more easily than domes and can be joined to the heat exchanger body in a shorter time and in a less complex manner. The use of heads makes it possible to increase the sections of the heat exchanger body and thus reduce the number of heat exchanger bodies that are installed in one identical cryogenic box.

[0059]

[0068] The use of filtration devices is particularly advantageous in heat exchange methods where at least the first fluid is at a relatively high pressure, i.e., 20 to 80 bar, and especially 25 to 40 bar. This is because these pressures require an increase in the thickness of the material used to form the fluid manifold. In detail, fixing domes to the body of the heat exchanger by welding requires an increase in the thickness of the metal sheets of these domes, which in turn requires an increase in the thickness of the closing bars of the heat exchanger. Thus, this industrial and economic constraint limits the increase in the above section of the heat exchanger. In the case of manifolds in the form of domes, this limits their size, and therefore the dimensions of the body of the heat exchanger. The distribution zone formed by the filtration device allows for an increase in the thickness of that section of the heat exchanger, with a reasonable thickness, and thus limits the number of heat exchange bodies required.

[0060]

[0069] The manufacturing and implementation of these filters are also simplified in relation to those of conventional filtration cartridges. The filtration device can be inserted into the passage while the plates are stacked, before the stack is brazed. Once the filter is assembled within the stack, it can be positioned vertically so that the catalyst is filled by gravity. The filtration device, placed at the bottom of the stack, holds the catalyst within the passage. This allows for a more uniform filling of the passage throughout the height of the stack.

[0061]

[0070] The present invention also makes it possible to avoid welding filters onto the manifold or body, as any welding operation on the body poses a risk of overheating and aggregation of brazed elements within the stack.

[0062]

[0071] Preferably, the filtration device as described herein is positioned within a plurality of passages 10, or in all of the passages 10. Preferably, in all or some of the passages 10, the filtration device is also provided on each side of the passage 10, at least on the side with the outlet manifold 22, or on the side with the inlet manifold 21 and the side with the outlet manifold 22.

[0063]

[0072] According to one embodiment, the main portion of the length of the passage 10 constitutes the actual heat exchange zone, i.e., the zone in which the fluid exchanges heat and / or reacts with a catalyst, where appropriate. The heat exchange zone is preferably bordered on both sides by distribution zones through which the fluid is transported to or from the inlet or outlet manifold. These distribution and heat exchange zones are advantageously fitted with structures 24, 25 that extend parallel to the plate 2 and along the width and length of the passage 10. The distribution structures 24 are configured to ensure uniform collection and distribution of the fluid from the inlet manifold or to the outlet manifold, across the entire width of the heat exchange zone.

[0064]

[0073] The distribution and heat exchange structures may, advantageously, include corrugated or wavy sections. These structures can be selected from various types of corrugated sections commonly implemented in brazed fin and plate type heat exchangers, such as straight corrugated sections, partially offset corrugated sections (of the "sawtooth" type), or herringbone corrugated sections. These corrugated sections may or may not be perforated. The structure may be formed as a single piece or as a plurality of juxtaposed sheets of corrugated sections.

[0065]

[0074] According to the embodiment shown in [Figure 4], the at least one passage 10 comprises at least one distribution structure 24 and a heat exchange structure 25 positioned in a continuous manner from the first outlet manifold 22. It should be noted that the same arrangement may be provided on the side where the first inlet manifold 21 is located. The filtration device 31 is located in a free space 26 between the distribution structure 24 and the heat exchange structure 25, preferably formed between the structures. The free space 26 extends from a space in the passage 10 that does not have a distribution or heat exchange structure.

[0066]

[0075] This embodiment is particularly advantageous for use in catalytic heat exchanger-reactors because it allows for the provision of a catalyst-free distribution zone between the heat exchange zone and the manifold, and the filtration device holds the catalyst in the heat exchange zone where it is used to react with the first fluid. This further reduces the amount of catalyst used in the heat exchanger passages. This also makes it possible to use inlet and / or outlet manifolds in the form of heads that only partially cover the stack surface, as shown in [Figure 2]. The use of heads can be advantageous compared to the use of domes that cover the entire stack surface because it reduces the bulk of the manifold, making it easier to join the manifold to the heat exchanger body and reducing the welding time required to weld the manifold to the body.

[0067]

[0076] Preferably, the filtration device 31 is positioned at a distance of 10 to 50 cm from the outlet opening 12 in the passage 10, or from the inlet opening 11 if the filtration device is located on the side where the inlet manifold 21 is located.

[0068]

[0077] Preferably, the filtration device 31 extends over a total width which may be equal to, substantially equal to, and preferably smaller than, the width of free space measured parallel to the longitudinal direction z, preferably in the same manner. Preferably, there is a relatively small gap between the filtration device, the distribution structure 24, and the heat exchange structure 25, or there is no gap, or there is substantially no gap. In particular, there is a first gap corresponding to the distance between the filtration device 31 and the distribution structure 24, and / or the distance separating the filtration device 31 from the heat exchange structure 25, measured parallel to the longitudinal zone z. Preferably, the first gap is between 0 and 3 mm, particularly between 0.5 and 3 mm. This avoids the possibility of particles passing around the filtration device. Furthermore, the presence of a small gap can compensate for any defects in the linearity of the filtration device 31.

[0069]

[0078] In the embodiment shown in Figure 4, the filtration device extends parallel to the longitudinal direction z and between two closing bars 6 that each demarcate the longitudinal edge of the passage 10, i.e., the edge parallel to the longitudinal direction z. Preferably, the filtration device 31 has a length measured parallel to the transverse direction x that is greater than or equal to the width of the passage 10.

[0070]

[0079] Advantageously, the length of the filtration device 31 is greater than the width of the passage 10 so that the two ends 32 engage within each of the closure bars 6. Preferably, each of these closure bars 6 has a recess 36 molded to accommodate the ends 32 of the filtration device 31.

[0071]

[0080] According to another embodiment of one example shown in [Figure 5], the heat exchanger according to the present invention comprises a distribution structure 24 and a filtration device 31 disposed between a first inlet or outlet manifold 21, 22 preferably located in an inlet or outlet opening 11, 12 in a passage 10.

[0072]

[0081] The filtration device 31 is positioned to separate the internal volume of the manifold from the internal volume of the passage 10. This embodiment is particularly suitable for heat exchangers that have a filtering function to prevent the introduction of particles as soon as they enter the heat exchanger. It becomes possible to use a filtration device having a length smaller than the width of the passage 10, thereby reducing the size of the device and facilitating its manufacture. It is sufficient for the filtration device 31 to have a length at least equal to the width of the opening formed between the closing bars 6 that separate the lateral edge of the passage in which the manifold is located. The lateral edge extends from the edge parallel to the lateral direction x.

[0073]

[0082] The configuration in [Figure 4] is particularly suitable for catalytic heat exchangers having a filtration device located on the side with the outlet manifold 22 to hold the catalyst. The configuration in [Figure 5] can be adapted to any heat exchanger where the introduction of solid particles should be blocked. It should be noted that these considerations do not necessarily rule out other configurations that may still be conceivable.

[0074]

[0083] Preferably, the filtration device 31 is positioned between two closure bars 6 that divide the passage 10 at its lateral edge. According to one possibility, the filtration device 31 has two ends 32, each of which is positioned within a recess 36 in each closure bar 6.

[0075]

[0084] As can be seen in Figure 4 or Figure 5, the at least one passage 10 includes inlet or outlet openings 11, 12 leading into the first inlet or outlet manifolds 21, 22. Each of the passage 10 and the openings 11, 12 has a width measured parallel to the lateral direction x. Preferably, the width of the inlet or outlet openings 11, 12 is less than the width of the passage 10, and in particular the width of the inlet or outlet openings 11, 12 is between 10% and 70% of the width of the passage 10, preferably between 20% and 50%. This makes it possible to significantly reduce the width of the inlet or outlet manifold covering the opening.

[0076]

[0085] In the context of the present invention, the recess 36 may take the form of a blind hole, a notch, and / or a groove formed within the bar 6.

[0077]

[0086] It should be noted that for a bar 6 positioned parallel to the longitudinal direction z, the width of the bar is measured parallel to the transverse direction x. The closing bar can have a width between 15 and 40 mm.

[0078]

[0087] The filtration device 31 can be fixed within the passage 10 in various ways. In particular, the filtration device 31 can be joined by brazing to one and / or the other of the plates 2 that separate the passage 10 in which the filtration device is located. The filtration device 31 can also be joined to one and / or the other of the plates 2 by thermal bonding.

[0079]

[0088] Preferably, the brazing material is placed between the metal sheet material 30 and at least one plate 2 that separates the passage 10. The metal sheet material 30 has a melting temperature higher than the melting temperature of the brazing material. The brazing material may also be in the form of a coating deposited on at least a portion of the surface of the plate 2.

[0080]

[0089] In particular, the metal sheet material 30 is formed entirely or partially from aluminum or aluminum alloy, steel, especially stainless steel, nickel or nickel alloy, especially Inconel-type alloys containing between 50% and 75% by weight of nickel. These materials have the advantages of good mechanical strength and good durability, and can easily withstand cryogenic temperatures. These properties are important in the context of resistance to the dynamic pressure of the fluid and retention of the catalyst load, especially when the filter is located in the lower part of the heat exchanger.

[0081]

[0090] In particular, filtration devices made entirely or partially from aluminum or aluminum alloy can be joined by brazing, and this material can be brazed to other elements of heat exchangers, which are most commonly made from aluminum or aluminum alloy. If the filtration device is made entirely or partially from stainless steel, it is preferably thermally bonded to plate 2.

[0082]

[0091] The filtration device 31 can have an overall width of 2 to 10 mm, preferably 3 to 7 mm, measured parallel to the longitudinal direction z. This provides a good compromise between the need to withstand the tensile force associated with the pressurizing force acting in the passage and the pressure loss generated by the filtration device. A width between 3 and 7 mm is particularly suitable for fluid pressures between 20 and 40 bar.

[0083]

[0092] The filtration device 31 may have a height measured parallel to the stacking direction y, which is equal to or substantially equal to the height of the closing bar 6 and / or the height of the distribution and heat exchange structures 24, 25. The height of the filtration device is specified to be equal to or slightly greater than the height of the passage 10, so that the filtration device contacts the adjacent plate 2. In particular, the height of the filtration device may be 0.05 mm to 0.2 mm greater than the height of the passage 10.

[0084]

[0093] The filtration device 31 can be formed in various ways, particularly by stamping it in a press, or by bending the sheet material 30 that forms the filtration device.

[0085]

[0094] Figure 6 schematically shows possible shapes of the filtration device 31. In different embodiments, the filtration device 31 preferably comprises at least one front surface 31a positioned perpendicular to the overall flow direction of the first fluid. The front surface 31a extends parallel to the lateral direction x. This is the front surface 31a that provides a barrier function for the particle filtration action. This is connected to at least one lateral surface 31b positioned parallel to the plate 2. The lateral surface 31b serves as a surface for joining the filtration device 31. The lateral surface 31b may be joined to the plate 2 by brazing or by heat bonding. The front surface 31a and the lateral surface 31b may be joined within a joining zone that can have a larger or smaller radius of curvature depending on the technique used to shape the filtration device, particularly by stamping or bending.

[0086]

[0095] In the embodiment schematically shown in Figure 6A, the filtration device 31 comprises two front surfaces 31a arranged continuously in the longitudinal direction z, and three lateral surfaces 31b, one of which is intended to be positioned in contact with one of the plates 2 forming the passage 10, and the other two intended to be positioned in contact with the other of the plates 2 forming the passage 10.

[0087]

[0096] In the embodiment schematically shown in Figure 6B, the filtration device 31 comprises a front surface 31a and two lateral surfaces 31b, each intended to be positioned parallel to the adjacent plate 2. The lateral surfaces 31b may extend to the left or right of the front surface 31a. The filtration device has a U-shaped transverse profile. It should be noted that the branching of the U-shaped profile may extend in the direction of fluid flow or in the opposite direction. It should be noted that the front surface 31a may have a flat surface as schematically shown in Figure A or B, or a curved surface, particularly a concave surface, as in the example schematically shown in Figure 6C.

[0088]

[0097] It should be noted that at least one lateral surface 31b is not perpendicular to the front surface 31a, but can form an angle between 90° and 94° with the front surface 31a, for example, as shown in D in [Figure 6]. If it is difficult to obtain a constant height along the entire length of the filtration device within the currently desired (sought-after) tolerance, an upper lateral surface 31b positioned at an angle slightly greater than 90° to the front surface can provide a height that, after the upper separating metal sheet is placed on top, provides a contact surface with the device along its entire length.

[0089]

[0098] As can be seen in [Figure 7], the filtration device 31 comprises at least two corrugated sides 123, which are connected by corrugated peaks 121 extending perpendicularly to the corrugated sides 123. The corrugated sides 123 are sequential to each other in a direction D1 referred to as the corrugation direction and are arranged periodically at a pitch p. The corrugated sides 123 and corrugated peaks 121 have a thickness e, preferably 0.2 to 0.75 mm.

[0090]

[0099] By forming the filtration device 31 from the corrugated product 100, it becomes possible to combine items of equipment for manufacturing a heat exchanger, in particular using the same pressurizing tools to form the filtration device, such as those used to form a distribution or heat exchange structure inserted into a passage. Multiple filtration devices may be cut out within one same corrugated product 100. The corrugated product 100 may be of the same type as, for example, those used to form a distribution structure 24 and / or a heat exchange structure 25, and in particular may have the same transverse profile, the same pitch between corrugated sides, and the same height. Preferably, the corrugated product 100 is of a straight corrugated type, but other corrugated shapes can also be considered.

[0091]

[0100] According to one possibility, the filtration device 31 comprises at least two front surfaces 31a, each formed by the corrugated sides 123 of the corrugated product 100, and at least one lateral surface 31b, each formed by the corrugated peaks 121 of the corrugated product 100. In particular, the filtration device 31 may comprise two front surfaces 31a and three lateral surfaces 31b, one of which is formed by an upper corrugated peak 121 connecting the upper ends of the corrugated sides 123, and the other two lateral surfaces 31b are formed by two lower corrugated peaks 121, each connected to the lower ends of the corrugated sides 123. This filtration device 31 is schematically shown by the dotted line in [Figure 7] and may be formed by cutting out the corrugated product 100, which would allow for the type A filtration device in [Figure 6]. The cutting may be done, for example, at a lower corrugated peak 121, or at a connecting surface that connects a lower corrugated peak 121 to an adjacent corrugated side 123.

[0092]

[0101] According to another possibility, the filtration device 31 comprises a front surface 31a formed by the corrugated peaks 121 of the corrugated product 100 and two lateral surfaces 31b, each formed by the corrugated side surfaces 123 of the corrugated product 100. This filtration device 31 may be formed by cutting out the corrugated product 100, schematically shown by the dotted line in [Figure 7], which would allow for the production of the type B filtration device in [Figure 6]. The cutting may be done, for example, at each corrugated side surface 123, or at a connecting surface that connects each corrugated side surface 123 to an adjacent lower corrugated peak 121. The filtration device 31 may be positioned within the passage 10 in a corrugated direction D1 perpendicular (shown in B) or parallel (not shown) to the longitudinal direction z.

[0093]

[0102] According to one possibility not shown in detail, at least one recess 36 is formed by a recess fabricated within the bar 6 over the entire height of the bar, the height of which is measured in the stacking direction y of the plate 2. The recess 36 has a maximum width l measured parallel to the longitudinal direction z, which is equal to, or substantially equal to, preferably slightly larger than, the entire width of the filtration device 31. max The recess 36 has a maximum width l over a predetermined depth measured in the lateral direction x. max Over the course of the bar, and at a height h corresponding to the height of bar 6. max It is created by removing material over a certain area. The recess, therefore, has a transverse profile in a cross-sectional plane parallel to the plate 2 that is identical or essentially identical in shape, particularly square or rectangular, from the face 6c of the bar 6 facing the passage 10 to the base of the recess.

[0094]

[0103] According to another possibility shown in Figures 8 and 9, at least one recess 36 extends along the entire height of the bar 6 and across the maximum width l of the orifice. max Minimum width less than l min It comprises a first portion 36a formed over a certain length, with a minimum width l measured parallel to the longitudinal direction z. minis preferably equal to or substantially equal to, and preferably slightly greater than, the thickness of the sheet material forming the filtration device 31. In particular, the first portion 36a forms a groove shaped to receive the front face 31a of the filtration device 31 at its end 32.

[0095]

[0104] The recess 36 is further formed only over a portion h min of the height of the bar 6 and comprises at least one second portion 36b extending over the maximum width l max of the recess. Preferably, the height h min measured parallel to the stacking direction y is equal to or substantially equal to, and preferably slightly greater than, the thickness of the sheet material forming the filtration device 31. In particular, the second portion 36b is suitable for receiving the lateral face 31b of the filtration device 31 at its end 32. This embodiment enables good retention of the filtration device within the recess 36. Preferably, the recess 36 is formed on each surface 6a, 6b and comprises two second portions 36b parallel to the plate 2 of the bar 6. The recess 36 is thus shaped to receive the end 32 of the filtration device having a front face 31a and two lateral faces 31b.

[0096]

[0105] It will be noted that the first portion 36a and the second portion 36b of the recess are produced over a predetermined width in the lateral direction x. The recess has a transverse profile with different dimensions depending on whether it is seen in the first portion or the second portion in a cross-sectional plane parallel to the plate 2. The transverse profile of the first portion and / or the second portion can have a square or rectangular shape.

[0097]

[0106] It should be noted that the first portion 36a can extend perpendicular to the longitudinal direction z and within a cross-sectional plane parallel to the plate 2, or it can form an angle A between 88° and 82° with respect to the longitudinal direction z. The presence of this angle causes the end portion 32 of the filtration device to deform slightly when inserted into the recess 36, thereby allowing it to lock into place.

[0098]

[0107] The recess 36 has a width l measured parallel to the longitudinal direction z, which is equal to, or substantially equal to, and preferably slightly smaller than, the width of the filtration device 31. max The recess 36 may have a predetermined depth measured parallel to the transverse direction x, which is 10% to 20% of the width of the bar 6. In particular, the recess 36 has a depth between 2 and 7 mm, preferably between 4 and 6 mm, and ideally about 5 mm. These dimensions provide a good compromise between ease of machining the bar, embedding the filtration device, and reduction of the bar width. Preferably, the length of the filtration device measured in the transverse direction x is between the width of the passage and twice the depth of the recess.

[0099]

[0108] The width and depth of the recess 36 are specifically defined to ensure tightness to the catalyst particles, taking into account their size and shape so that the catalyst particles cannot advance into the residual space formed between the filtration device and the bar 6. Preferably, a second gap exists corresponding to the difference between the width of the filtration device 31 and the width of the recess, which is less than 0.5 mm, particularly less than 0.1 mm. In the case of a recess having multiple parts 36a, 36b, it will be noted that the width of the filtration device and the recess are understood to mean the width measured in the part in question. Preferably, the second gap is zero. The depth of the recess corresponding to the length of the end 32 engaged within the recess is defined to ensure sufficient retention of the filtration device within the recess.

[0100]

[0109] The present invention is particularly advantageous when implemented in a heat exchanger with brazed fins and plates, as it allows for easy implementation and joining. However, it should be noted that other types of heat exchangers may be used, such as plate heat exchangers, shell and tube heat exchangers, or "core-in-kettle" type assemblies, i.e., plate heat exchangers or plate and fin heat exchangers embedded in a shell in which the refrigerant fluid evaporates. When the heat exchanger is a tubular heat exchanger, the first and second passages may be formed by spaces within, around, and between the tubes.

[0101]

[0110] Preferably, when the metal sheet material is a metal cloth or a microperforated plate, it has an open surface density in the range of 15% to 35%, preferably 17% to 22%. The open surface density, i.e., the permeability of the cloth or plate, is defined as the ratio of the area of ​​openings or perforations to the total area of ​​the cloth or microperforated plate, respectively. These ranges of values ​​provide a good compromise between the hardness of the material, which gives the material good mechanical strength, and the fluid permeability, which minimizes pressure loss.

[0102]

[0111] For metal sheet materials other than metal cloth or microperforated plates, they preferably have a pore volume density, or porosity, of at least 75%, more preferably greater than 90%, and advantageously 98% or less. These ranges allow for the retention of fine solid particles while providing good mechanical strength and low fluid pressure loss. It should be noted that pore volume density is defined as the ratio of the volume of voids within the material to the total volume of the material. It should also be noted that voids are understood as openings, i.e., fluid communication with the external environment in which the material is located.

[0103]

[0112] According to a preferred embodiment of the present invention, the metal sheet material 30 is a metal cloth formed by metal threads 301, 302. More specifically, the material comprises intertwining at least one series of first metal threads 301 and a series of second metal threads 302 to form an open mesh 33. Depending on the method used to weave the threads, the mesh may have a square, rectangular, or triangular shape. The first metal threads 301 and the second metal threads 302 may, but do not necessarily, have the same characteristics, namely material, diameter, etc.

[0104]

[0113] Figure 10 schematically shows an exemplary weaving method in which the first and second threads intersect alternately above and below each other. Other weaving methods are possible, such as two threads intersecting alternately above and below each other, or one thread below and two threads above.

[0105]

[0114] It should be noted that the features of fabric described in this application also apply when threads are joined by welding.

[0106]

[0115] The use of metallic cloth allows for precise and reproducible control of the filter's characteristics, thanks to the perfectly controlled mesh shape during the weaving process. The regularity of the mesh results in uniform permeability across the entire surface of the filter. This avoids harmful effects on the heat exchanger's performance due to the uniform distribution of fluid flow through the filter. In addition, the metallic cloth allows for a mesh-defined opening surface density to optimally block target particles and limit the pressure loss of the fluid passing through it. This also results in good planarity, which allows the cloth to be fitted between closure bars without significant deformation, especially when the cloth is placed in recesses within the closure bars.

[0107]

[0116] Preferably, the threads 301 and 302 have a diameter d in the range of 0.10 to 0.30 mm, particularly 0.10 to 0.25 mm, thereby enabling good mechanical strength to be imparted to the fabric by the tensile strength of the threads. More preferably, the threads may have a diameter in the range of 0.12 to 0.18 mm.

[0108]

[0117] Each mesh 33 is separated by two consecutive first threads 301 and two consecutive second threads 302, and the mesh preferably has an opening size of 0.07 mm to 0.15 mm. The dimensioning of the mesh opening size is determined to hold the larger solid particles that need to be stopped.

[0109]

[0118] For square or rectangular meshes as shown in [Figure 10], the mesh opening size is defined by the distance D1 between two consecutive first threads 301 and / or the distance D2 between two consecutive second threads 302. For triangular meshes (not shown), the mesh opening size is defined by the diameter of the tangent sphere inserted into the mesh.

[0110]

[0119] Preferably, the metal sheet material 30 has a thickness in the range of 0.2 to 0.75 mm. This thickness provides the material with sufficient mechanical strength. In the case of metal cloth, this thickness is obtained as a result of the diameter of the threads and the method by which the resulting mesh is joined.

[0111]

[0120] According to one possibility, the metal sheet material is sintered metal powder or sintered metal fibers. In particular, stainless steel, or copper powder bonded by atomic diffusion at a temperature lower than the melting point of the material, may be used.

[0112]

[0121] According to another possibility, the metal sheet material is a microperforated plate with a plurality of preferably circular orifices having a diameter of advantageously 0.07 mm to 0.15 mm. Preferably, the plate has a thickness between 0.2 mm and 0.5 mm. Preferably, the orifices are uniformly distributed across the microperforated plate.

[0113]

[0122] According to another possibility, the metal sheet material is a foam formed from a metallic material. Preferably, the metal foam has a pore volume density of at least 75%, more preferably over 90%, to allow fluid to pass through with a manageable pressure loss. Preferably, the pores in the metal foam have a size between 0.04 mm and 0.15 mm. Preferably, the pore size is understood to mean its equivalent diameter. The term “equivalent diameter” for non-spherical pores is understood to mean the diameter of a sphere with the same volume as the pore.

[0114]

[0123] The present invention is a catalytic heat exchanger configured to carry out a catalytic reaction between an exchanger-reactor, i.e., a first fluid F1 and at least one catalytic material, and is particularly advantageous when a first series of passages contains the at least one catalytic material in the form of particles. In particular, the heat exchanger is configured to cool or liquefy at least a portion of the hydrogen that makes up the first fluid F1, and the catalytic material is configured to convert ortho-hydrogen to para-hydrogen, and in particular the catalytic material is a catalyst containing a metal oxide, preferably iron oxide (Fe2O3). During operation, hydrogen is introduced in a gaseous state through a first inlet manifold 21 and flows through the first passage 10 so as to be cooled in the first passage 10 against a stream of liquid nitrogen flowing through a second passage 20. At least a portion of the molecules in the gaseous hydrogen stream are converted from ortho-hydrogen to para-hydrogen by the catalytic material. The hydrogen is discharged through a first outlet manifold 22 at a low temperature, or in a whole or partially liquefied state.

[0115]

[0124] Preferably, the catalyst material comprises particles having an equivalent diameter in the range from a minimum particle diameter to a maximum particle diameter. Preferably, the minimum diameter is between 0.2 and 0.4 mm. Preferably, the maximum diameter is between 0.5 and 0.7 mm. More preferably, the particles of the catalyst material have an equivalent diameter in the range of 0.2 to 0.7 mm.

[0116]

[0125] Preferably, the metal sheet material 30 is a woven metal yarn fabric having a mesh opening size that comprises between 30% and 70% of the minimum particle diameter. These ratios are specified to contain very fine particles or dust resulting from the abrasion of catalyst particles during filling or operation, while providing a good compromise with respect to pressure loss.

[0117]

[0126] In this application, the term "equivalent diameter" of a non-spherical particle is understood to mean the diameter of a spherical particle with the same volume as the said particle.

[0118]

[0127] The present invention also relates to a method for assembling a catalytic heat exchanger, which can be carried out more easily and with better control by the present invention. A filtration device 31 is positioned within all or part of the passage 10 on the side of the outlet surface 12. The body 1 is brazed to join elements that make up the heat exchanger together, such as plates, bars, heat exchange structures, and, where appropriate, distribution structures. The brazed stack is positioned vertically, and the outlet manifold 22 is joined below the body in the upward vertical direction z. The passage 10 is then filled with catalyst. The filtration device 31 positioned within the lower part of the body holds the catalyst. Filling may optionally be carried out by a tray, which may be rectangular, positioned on the heat exchange body 1 so as to face the opening of the passage to be filled. The tray is removed after filling is complete. The first inlet manifold 21 is joined.

[0119]

[0128] Furthermore, the heat exchanger may include a filtration device 31 located on the side of the inlet surface 11. The filtration device 31 is located in all or part of the passage 10 on the side of the inlet surface 11. The main body 1 is brazed, and then the first inlet manifold 21 is joined to the main body 1.

[0120]

[0129] In the context of the present invention, it will be understood that the filtration device is preferably joined to the body 1 before the body is brazed. Preferably, the manifold is joined to the brazed body 1 by welding.

[0121]

[0130] This assembly method is particularly suitable for heat exchangers having passages that need to be filled with catalyst particles. The passages are filled with catalyst particles after the heat exchange body, equipped with a filtration device and an outlet manifold, is positioned vertically, thereby allowing the catalyst to be filled under the effect of gravity and enabling better control over the distribution of the catalyst between the various passages.

[0122]

[0131] It should be noted that, in the case of a heat exchanger where the intrusion of dust from the upstream fluid circuit should be avoided, placing the filtration device on the side of the heat exchanger outlet manifold is optional. Furthermore, it should be understood that other filtration devices according to the present invention may be placed with respect to the second passage 20 to provide one or more of the functions described in this application.

Claims

1. A heat exchanger comprising a stack of plates (2) parallel to each other and to a longitudinal direction (z), said plates (2) being stacked and spaced apart from each other to define between each other a first series of passages (10) for the flow of at least a first fluid in a general flow direction parallel to said longitudinal direction (z), each passage (10) being delimited by a closure bar (6) disposed between said plates (2), 1. A heat exchanger comprising: a filtering device (31) arranged in at least one of said first series of passages (10), said filtering device (31) extending for a part between two adjacent plates (2) defining said passages (10) and for another part between two of said closure bars (6) delimiting said passages (10), said filtering device (31) comprising a metal sheet material (30) selected from among a metal cloth, a non-woven fabric of metal fibers, a sintered metal powder or sintered metal fibers, a metal foam, or a micro-perforated plate.

2. 2. The heat exchanger according to claim 1, characterized in that the heat exchanger comprises at least a first inlet manifold (21) configured to introduce the first fluid into the first series of passages (10) or a first outlet manifold (22) configured to collect the first fluid from the first series of passages (10), a distribution structure (24) and a heat exchange structure (25) are arranged successively from the first inlet or outlet manifold (21, 22) in at least one passage (10) of the first series of passages (10), and the filtration device (31) is arranged between the distribution structure (24) and the heat exchange structure (25).

3. 2. The heat exchanger according to claim 1, characterized in that the heat exchanger comprises at least a first inlet manifold (21) configured to introduce the first fluid into the first series of passages (10) or a first outlet manifold (22) configured to collect the first fluid from the first series of passages (10), a distribution structure (24) and a heat exchange structure (25) are arranged successively from the first inlet or outlet manifold (21, 22) in at least one passage (10) of the first series of passages (10), and the filtration device (31) is arranged between the distribution structure (24) and the first inlet or outlet manifold (21, 22).

4. 4. A heat exchanger according to claim 2 or 3, characterized in that the at least one passage (10) comprises an inlet opening (11) leading into the first inlet manifold (21) or an outlet opening (12) leading into the first outlet manifold (22), and at least one passage (10) of the first series of passages (10) has a width measured parallel to a transverse direction (x) perpendicular to the longitudinal direction (z) and perpendicular to the plate (2), and the width of the inlet or outlet opening (11, 12), measured parallel to the transverse direction (x), constitutes between 10% and 70%, preferably between 20% and 50%, of the width of the at least one passage (10).

5. 4. A heat exchanger according to claim 1, characterized in that the filtering device (31) comprises two ends (32) each arranged in a respective recess (36) in the closure bar (6).

6. The recess (36) has a maximum width (l) measured parallel to the longitudinal direction (z). max ), which has a maximum height (h max ), the height being measured parallel to a stacking direction (y) perpendicular to the longitudinal direction (z) and the lateral direction (x), and the first portion (36a) is formed over a length of (l max The minimum width (l min ), and the recess (36) is further formed over the maximum height (h max Minimum height (h) less than min ) over the maximum width (l max 6. The heat exchanger according to claim 5, further comprising at least one second portion (36b) extending over the first portion (36b).

7. 4. A heat exchanger according to claim 1, characterized in that the filtering device (31) comprises at least one front face (31a) arranged perpendicular to the overall flow direction of the first fluid, said front face (31a) being connected to at least one lateral face (31b) arranged parallel to the plate (2).

8. 4. A heat exchanger according to any one of claims 1 to 3, characterized in that the filtering device (31) has an overall width, measured parallel to the longitudinal direction (z), of between 2 and 10 mm, preferably between 3 and 7 mm.

9. A heat exchanger according to any one of claims 1 to 3, characterised in that the metal sheet material (30) has a thickness of 0.20 to 0.75 mm, preferably 0.3 to 0.5 mm.

10. 4. A heat exchanger according to any one of claims 1 to 3, characterized in that the metal sheet material (30) has an open surface density in the range of 15% to 35% or a volume density of holes in the range of 75% to 98%.

11. 4. A heat exchanger according to any one of claims 1 to 3, characterized in that the metal sheet material (30) is a woven fabric of metal threads (301, 302), the metal threads (301, 302) having a diameter of 0.10 to 0.30 mm, preferably 0.10 to 0.25 mm.

12. 4. A heat exchanger according to any one of claims 1 to 3, characterized in that the metal sheet material (30) comprises at least one series of first metal threads (301) and a series of second threads (302) intertwined to form a mesh (33), each mesh (33) being bounded between two continuous first threads (301) and two continuous second threads (302), the mesh (33) having an opening size of 0.07 mm to 0.15 mm.

13. 4. A heat exchanger according to any one of claims 1 to 3, characterised in that the metal sheet material is a micro-perforated plate having a plurality of orifices with a size, measured in a plane parallel to the plate (2), of at most between 0.07 mm and 0.15 mm.

14. 4. A heat exchanger according to claim 1, characterized in that the heat exchanger is an exchanger-reactor configured to carry out a catalytic reaction between the first fluid (F1) and at least one catalytic material, and at least a part of the first series of passages (10) contains particles of the at least one catalytic material.

15. 15. The heat exchanger of claim 14, characterized in that the catalytic material comprises particles having an equivalent diameter ranging from a minimum diameter to a maximum diameter, and the metal sheet material (30) is a woven fabric of metal threads (301, 302) having a mesh opening size ranging from 10% to 85% of the minimum diameter of the particles.

16. The heat exchanger is adapted to liquefy hydrogen as a first fluid (F1), and the catalytic material is adapted to convert ortho-hydrogen to para-hydrogen, in particular the catalytic material is made of iron oxide (Fe ２ O ３ 15. The heat exchanger according to claim 14, characterized in that

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