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EP4105590A1 - Bloc d'échange de chaleur, son procédé de fabrication, échangeur de chaleur équipé d'un tel bloc et son procédé de mise en oeuvre - Google Patents

Bloc d'échange de chaleur, son procédé de fabrication, échangeur de chaleur équipé d'un tel bloc et son procédé de mise en oeuvre Download PDF

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Publication number
EP4105590A1
EP4105590A1 EP22171766.3A EP22171766A EP4105590A1 EP 4105590 A1 EP4105590 A1 EP 4105590A1 EP 22171766 A EP22171766 A EP 22171766A EP 4105590 A1 EP4105590 A1 EP 4105590A1
Authority
EP
European Patent Office
Prior art keywords
block
channels
fluid
called
heat exchange
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22171766.3A
Other languages
German (de)
English (en)
Inventor
Jérémie BENOIT
Matthieu BORIES
Guillaume BRUN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mersen France PY SAS
Original Assignee
Mersen France PY SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mersen France PY SAS filed Critical Mersen France PY SAS
Priority to US18/569,753 priority Critical patent/US20250012520A1/en
Priority to PCT/IB2022/055277 priority patent/WO2022263972A1/fr
Priority to JP2023577292A priority patent/JP2024523028A/ja
Publication of EP4105590A1 publication Critical patent/EP4105590A1/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/02—Constructions of heat-exchange apparatus characterised by the selection of particular materials of carbon, e.g. graphite
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining

Definitions

  • the invention relates to the technical field of block heat exchangers. It relates more particularly to a heat exchange block, which is provided with an improved geometry with regards to both thermal and mechanical issues.
  • the invention also relates to an exchanger which is equipped with such a heat exchange block.
  • the invention relates more particularly to a block type heat exchanger.
  • the latter typically comprises first an inlet and an outlet for a so-called process fluid, both provided along main axis of the exchanger.
  • the casing of this exchanger is equipped with transverse inlet and outlet, both for a so-called service fluid.
  • Process fluid is for example an acid while service fluid is a heat transfer fluid, such as water.
  • the casing accommodates at least one heat exchange block, typically a plurality of these blocks which are stacked on top on one another.
  • Each block is made of a thermally conductive material.
  • the present invention more specifically relates to process fluids which are corrosive to metals.
  • said material is typically graphite optionally associated with additives, for example of the polymer type.
  • This block may be parallelepipedic or cylindrical, bearing in mind that the invention more specifically aims cylindrical shaped blocks.
  • the first channels which are longitudinal, continuously extend between the front faces of the body and open onto said front faces.
  • the second channels which are transverse, continuously extend between the opposite transverse faces of the body and open onto said transverse faces.
  • Block heat exchangers of the above known type are described for example in EP-A-0 196 548 and WO-A-2006/081965 .
  • Block heat exchangers of the prior art are however not satisfactory, in particular with regard to mechanical issues. Indeed, some material failures have been observed, which reduce the lifetime of the exchanger. These failures occur in particular at the outer periphery of the front face of the block, which is upstream with reference to the flow of hot process fluid.
  • US-A-3,391,016 describes a process for manufacturing a heat exchange element, which is formed by an annular body of graphite.
  • US-A-2,821,369 discloses a heat exchanger comprising a plurality of hollow cylindrical blocks of graphite, which are arranged in axial alignment to form a column having a central hollow interior.
  • GB-A-1 078 868 discloses a heat exchanger equipped with several graphite blocks, but which is not provided with an external casing. Each of said blocks is formed by two distinct parts, which are mutually fixed by clamping.
  • This further document is not concerned with a heat exchange block of the type according to the invention, since this block does not include longitudinal and transverse channels. Indeed, in this British document, the process fluid and the service fluid flow into two series of channels which both open onto the front faces of the block. That being said, one aim of the present invention is providing a heat exchange block which makes it possible to remedy the drawbacks, inherent to above-mentioned prior art.
  • a further aim of the present invention is providing such a block which ensures both satisfactory mechanical and thermal performances to the heat exchanger equipped therewith.
  • a further aim of the present invention is providing such a heat exchanger, which has a relatively simple structure and which can be manufactured without any particular risk of mechanical rupture, particularly with respect to the channels hollowed in the blocks belonging to this exchanger.
  • One object of the present invention is a heat exchange block (1; 501; 1001, 2001, 3001) comprising:
  • One further object of the present invention is a manufacturing method of a heat exchanger block as defined above, said method comprising:
  • One further object of the present invention is a heat exchanger (I; II; III) comprising
  • One further object of the present invention is a method for the implementation of a heat exchanger as defined above, wherein the first and second fluids are circulated in the first and second channels, so as to enable the heat exchange thereof, first fluid flowing through the exchanger under a monophasic form, without significant condensation in case said first fluid is a gas, said first fluid being in particular admitted in the first inlet means at a temperature superior to 80°C, whereas second fluid is in particular admitted in the second inlet means at a temperature between -20°C and +35°C.
  • said first fluid may be admitted into first inlet means at a temperature superior to 200°C.
  • Still one further object of the present invention is a method for the implementation of a heat exchanger as defined above, wherein the first and second fluids are circulated in the first and second channels, so as to enable the heat exchange thereof, wherein first fluid is submitted to a condensation through the exchanger, the inlet temperature of first fluid being in particular between +80°C and +300°C whereas its outlet temperature is in particular between -15°C and +60°C, the inlet temperature of second fluid being in particular between -20°C and +35°C, whereas its outlet temperature is in particular between -15°C and +45°C.
  • FIG. 1 illustrates a heat exchanger according to a first embodiment of the invention, which is referenced I as a whole.
  • This exchanger firstly comprises a plurality of heat exchange blocks 1, 101 and 201.
  • block 1 is according to the invention whereas blocks 101 and 201 are conform to prior art.
  • three blocks stacked on top of one another have been represented, it being understood that a different number of blocks may be envisaged.
  • Each block has a body, which is referenced 10 for what concerns block 1.
  • Said body has a typical cylindrical shape, with a circular cross-section.
  • baffles 12 which are illustrated in particular on figure 2 as well as on figure 5 , are provided at the outer periphery of this body 10.
  • L1 refers to the main or longitudinal axis of each block, which is parallel with the main axis of the exchanger.
  • each block is hollowed with different channels, so as to permit the flow of two fluids intended to be placed in mutual heat exchange.
  • each front face 2 is called upstream and each opposite front face 6 is called downstream.
  • a second series of transverse channels 60 extending obliquely, particularly perpendicular to the axis L1, open onto the opposite transverse faces 7 and 8 of each block.
  • two fluids, circulating respectively in the first and second series of channels, are placed in heat exchange.
  • These channels 20 and 60 are distant from one another, that is to say they do not open into one another.
  • heat exchanger I also comprises a lower cover 310, an upper cover 320, as well as a peripheral casing 330.
  • Upper cover 320 is hollowed with an opening 322 intended for the inlet of a first so-called process fluid into the longitudinal channels of all three blocks. This inlet is connected with a source of this fluid, which is situated upstream and is not illustrated. Said opening leads to a space 324, provided in the lower face of the cover.
  • the lower cover 310 is hollowed with an opening 312 intended for the outlet of the first fluid outside the longitudinal channels.
  • This outlet is connected with an appropriate downstream equipment, such as a piping.
  • the latter which is known as such, is not illustrated on the figures.
  • Casing 330 defines, with the opposite walls of the blocks, a peripheral bowl 335 intended for the circulation of a second so-called service fluid, intended to be placed in heat exchange with the process fluid in the blocks 1 to 201.
  • the casing is equipped with respective inlet 336 and outlet 337 pipes of this second fluid, connected with another appropriate downstream equipment, such as a further piping.
  • the latter which is also known as such, is not illustrated on the figures.
  • space 324 delimits a peripheral collar 326 which rests upon the upstream block 1, in use. So as to avoid any contact between the two fluids, it is critical to ensure a tight seal between the conducting walls of the block 1 and the collar 326.
  • the interface between said block and said collar is equipped with sealing means, which are known as such and are not illustrated in detail.
  • upper cover 320 is provided with pressing means, adapted to exert a controlled compressive force on the block, as well as on said sealing means.
  • these pressing means are formed by springs 328, in a way known as such
  • downstream front face 6 of upstream block 1 as well as both front faces 102, 106, 202 and 206 of other blocks 101, 201 are manufactured according to prior art.
  • both front faces may be provided with a respective chamber as will be detailed hereafter.
  • each front face may be either completely flush or hollowed with at least one groove, the depth thereof is low, which is suitable for forming the seat of a sealing member, for example of the O-ring type.
  • Upstream front face 2 of upstream block 1 is on the contrary manufactured according to the invention. Indeed it is not flush but is however provided with a central recess 22, the depth thereof is substantial, thus delimiting:
  • said central bowl 3 is flush and defines a so-called central reference surface S3.
  • this bowl may not be flush, for example may have a corrugated shape.
  • said reference surface is defined by the average altitude of said bowl.
  • Said seat 4 protrudes upstream with respect to said central bowl 3 along the longitudinal direction L1. It defines a so-called peripheral reference surface S4 which is flush in the present embodiment. In some variants this seat is not flush, but is provided for example with grooves adapted to receive some seals. Surface S4 is then defined by the average altitude of the seat, the same way as above mentioned surface S3. In use, collar 326 of upper cover 320 rests upon seat 4, while exerting compressing action on this seat due to the springs 328.
  • a shoulder 41 is provided at the radial inner end of seat 4. This shoulder, the function of which is typically to maintain an annular seal, exerts no mechanical action.
  • Transition portion 5 is rectilinear in the present example, when viewed in cross-section on figure 5 . By way of an alternatives, this portion may have other shapes with the provision for example of steps. Portion 5 is associated with a transition surface S which is defined the same way as surfaces S3 and S4.
  • said distance h4 is far superior to said distance h3.
  • the applicant has identified explanations with respect to the drawbacks of prior art, as well as the importance of said essential feature.
  • figure 4 illustrating an exchanger IV according to prior art.
  • mechanical elements which are analogous to those of exchanger I are given the same references, added by number 400.
  • R the so-called rest zone where the upper cover 420 rests upon the upstream graphite block 401.
  • a minimum clamping force has to be applied, which induces a noticeable compressive stress on the area of the graphite column, where the cover 420 is bearing.
  • the compressive load on the rest zone R leads to tensile stresses close to the maximum allowable tensile stress. This problem is compounded by the presence of the upstream transverse channels 460a passing under the surface supporting the cover.
  • the graphite surface In the center C' of front face 402 the graphite surface is firstly in contact with the hot incoming process fluid. Moreover it is far away from the first cooling channel, due to the high value of h402. In periphery P' of this front face, the graphite surface is also in contact with the hot incoming process fluid. However, contrary to center C', this periphery P' is also quite close from the service fluid, the temperature of which is far inferior to that of process fluid.
  • one essential feature of the invention is to significantly increase ratio h4/h3.
  • figure 6 illustrates the variations of both mechanical and thermal stresses, with respect to ratio h4/h3.
  • x-axis corresponds to said ratio.
  • chain-dotted lines illustrate the variation of a parameter M which is representative of mechanical stress of the block
  • dotted lines illustrate the variation of parameter T which is representative of thermal stress of the block
  • solid lines illustrate the global stress G, i.e. the sum of M and T stress values. Both for M and T, the lower the value, the better is the behaviour.
  • thermal stress decreases as ratio h4/h3 increases.
  • mechanical stress increases as said ratio h4/h3 increases.
  • the decrease of thermal stress is far more significant than the increase of mechanical stress.
  • the value of the global stress G tends to decrease due to the increase of ratio h4/h3.
  • h4 is advantageously set so that the stress applied by the clamping force, through the upper cover, is compatible with the material mechanical properties. Due to the specific geometry of the front face 2 of the block, the clamping force is mostly carried by the annular seat 4, as well as subsidiary by the transition portion 5.
  • h3 is significantly reduced so as to reach values that are far inferior to prior art.
  • the central portion of the front face is rendered much thinner than the periphery of the block.
  • this reduction of h3 is not prejudicial to the global mechanical behavior. This makes it possible to lower by far thermal stress, with respect to prior blocks with flush front face such as illustrated on figure 4 . Therefore h 3 can be advantageously set at a very low value, without any regards for mechanical stresses imposed by the clamping force. This low value favors an efficient thermal exchange between the top surface of bowl 3 and the underlying layer of horizontal channels 60a, as they are close from each other.
  • the invention takes the side to remove graphite material in a targeted zone. This makes it possible to improve thermal performances, due to this local thinning, while preserving high mechanical performances. Therefore, in a surprising way, removing material is not prejudicial to global mechanical behaviour.
  • this improvement is due to a technical effect of temperature homogenization throughout the block, the magnitude of which increases with the value of above ratio h4/h3.
  • threshold ratio the ratio above which this technical effect becomes significant.
  • this threshold ratio h4/h3 is advantageously superior to 1.2, preferably superior to 2.
  • said ratio h4/h3 is advantageously inferior to 50, preferably inferior to 15.
  • a5 the angle between reference surface S5 of portion 5 and surface S3.
  • said angle a5 is between 30 and 90°.
  • said portion is rectilinear.
  • said portion 5 may be differently shaped, in particular stepped.
  • reference surface is a line passing through bottom point and top point of said portion 5.
  • Block 1 may be manufactured starting from a standard block according to prior art, opposite front faces of which are substantially flush.
  • recess 22 is provided in one single of these front faces. This stage may be carried out typically by a machining process. Once said recess has been provided, this leads to the formation of both central bowl 3 and transition portion 5. Typically no material is removed in the periphery of said standard block, at the level of seat 4. Such a manufacturing method is advantageous, since it makes it possible to revamp a classic heat exchange block.
  • process fluid and service fluid are admitted in a way known as such, via inlets 322 and 336.
  • Exchanger I is more specifically adapted for a so-called cooling operation, which corresponds to a substantially monophasic flow of process fluid.
  • said process fluid may be a liquid or, in case it is a gas, it does not undergo any significant condensation.
  • admission temperature of process fluid is superior to 80°C.
  • the invention also encompasses the possibility of bowls, which are deeper than the one 3 of the present embodiment.
  • block 1 and exchanger I are more particularly dedicated to treat a process fluid with an admission temperature inferior to 200°C.
  • the specific geometry of this first embodiment is advantageous with regard to prior art designs, for what concerns thermal issues.
  • the manufacturing of the block is convenient.
  • admission temperature of service fluid is typically between -20°C and +35°C. Once these two fluids have been admitted in the exchanger, they are placed in heat exchange in a usual way. Cooled process fluid is discharged via the outlet opening 312, at a typical temperature between -15°C and +60°C, whereas warmed up service fluid is discharged via the outlet tube 337 at a typical temperature between -15°C and +45°C.
  • Figures 7, 8 and 10 illustrate a heat exchanger II and a block 501 according to a second embodiment of the invention.
  • the mechanical elements which are analogous to those of the first embodiment, are given the same references added by number 500.
  • Figure 7 represents only the upstream block 501, according to the invention, as well as part of the adjacent block 601 which is conform to prior art.
  • Heat exchange block 501 of this second embodiment mainly differs from above described block 1, in that it is provided with a deeper bowl 503.
  • the upstream transverse channel 560a is positioned far below transverse channel 60a.
  • block 501 is provided with less transverse channels with respect to block 1, in the upstream part of these blocks.
  • Schematic figure 10 which illustrates block 501 with comparison to figure 9 , shows that block 501 does not include any more the upper channels 60a and 60b of block 1.
  • FIG 8 let us note 838 the wall of pipe 837, in contact with exhaust service fluid.
  • This wall 838 is called superior, by convention, since it is turned towards the inlet of process fluid.
  • the distance d561 between upper wall 561 of channel 560a and above described superior wall 838 is advantageously inferior to 20 mm, in particular to 10 mm.
  • the invention encompasses a possibility, according to which upper wall 561 is located under superior wall 838 of the pipe.
  • this latest possibility is less preferred since it renders the manufacturing more complicated and it reduces heat transfer area, while bringing no further thermal effect.
  • This second embodiment provided with a so-called deep bowl 503, is more specifically adapted for cooling operation of the exchanger with high inlet temperature of process fluid, typically superior to 200 °C.
  • a bowl such as the one 3 of first embodiment, does not ensure a completely satisfactory temperature homogenization.
  • service fluid flow has specific properties, in the very upstream part of block 1.
  • FIG. 9 apart from line of upstream channels 60a, other adjacent lines of channels are noted 60b to 60d.
  • the applicant has acknowledged that far less service fluid flows along these four lines of upper channels 60a to 60d of block 1 according to the first embodiment, bearing in mind that this number of lines may be different.
  • block 501 since the manufacturing process of block 501 is less convenient than that of block 1, block 501 remains satisfactory for what concerns mechanical strength.
  • FIG 11 shows another variant of the invention, which can be applied either to block 1 or block 501.
  • upstream front face 2/502 of block 1/501 is provided with a bowl 3/503 as above described.
  • downstream front face 6/506 of the block is provided with a chamber 903, typically according to prior art described in US-A-3,391,016 , US-A-2,821,369 and GB-A-1 078 868 .
  • This chamber which ensures only a function of fluid distribution between block 1/501 and adjacent not shown block, has a depth D903 which is far inferior to that D3/D503 of bowl. Typically the ratio between D3/D503 and D903 is superior to 1.3.
  • the two above embodiments of the invention which are dedicated to cooling operations, refer to an exchanger I/II equipped with one single block 1/501 according to the invention.
  • Said block which is provided upstream with respect to the process fluid flow, is equipped with one single bowl 3/503 which is turned towards fluid process inlet.
  • graphite temperature tends to decrease from the top surface S3 or S503 of the block towards the outlet of process fluid, in a substantial linear way.
  • the need for temperature homogenization is more particularly required at the upstream part of upstream block, which explains the provision of this single bowl
  • the exchanger may be equipped with an upstream so-called neutral block.
  • this neutral block does not ensure any exchange function, but an auxiliary function such as the fluid distribution.
  • the single block according to the invention is positioned upstream, adjacent said neutral block.
  • Figure 12 illustrates a heat exchanger III according to a third embodiment of the invention.
  • the mechanical elements which are analogous to those of the first embodiment, are given the same references added by number 1000.
  • Heat exchanger III of this third embodiment mainly differs from above described exchangers I and II, essentially in that it is equipped with blocks 1001, 2001 and 3001 which are according to the invention.
  • each of these blocks is provided with two temperature homogenization bowls, each located on a respective front face.
  • upstream block 1001 is provided with an upstream bowl 1003 on its upstream front face 1002, as well as with a downstream bowl 1103 on its downstream front face 1006.
  • intermediate block 2001 is provided with an upstream bowl 2003 on its upstream front face 2002, as well as with a downstream bowl 2103 on its downstream front face 2006.
  • downstream block 3001 is provided with an upstream bowl 3003 on its upstream front face 3002, as well as with a downstream bowl 3103 on its downstream front face 3006.
  • bowls 1003, 1103, 2003, 2103, 3003 and 3103 have the same depths, which advantageously corresponds to the depth of bowl 3 of first embodiment.
  • Figure 12 illustrates three exchange blocks the one on top of the other, bearing in mind that this number may be different.
  • the exchanger III of this embodiment is more particularly adapted for a condensation operation, which corresponds to a biphasic flow of process fluid.
  • said process fluid is a gas submitted to a condensation, which may be complete or partial.
  • the inlet temperature of process fluid is between +80°C and +300°C, whereas its outlet temperature is between -15°C and +60°C.
  • the inlet temperature of service fluid is between -20°C and +35°C, whereas its outlet temperature is between -15°C and +45°C.
  • Z'2 may vary along the exchanger, depending upon several parameters which may be the type of fluids, but also the operative conditions.
  • the solid line curve of figure 13 illustrates a zone Z2, which is close to the process fluid inlet.
  • the dotted line curve shows a zone Z'2 which is in the vicinity of process fluid outlet.
  • Figure 14 illustrates a modelling of the technical effect brought about by the invention in case of a condensation.
  • the solid line curve shows the variation of graphite temperature GT along the main dimension Zexch of the exchanger, in case of a prior art exchanger which is not provided with a bowl.
  • the dotted line curve shows the same temperature variation for the same spots of the exchanger, in case of the exchanger III provided with a plurality of bowls.
  • the gas condensation provokes a significant temperature increase DT, which is likely to break or at least weaken the graphite in prior art.
  • the temperature barely increases in the zone dt, which is favorable to the mechanical integrity of the exchanger.
  • the two above commented curves are mixed in the very upstream part of the exchanger, as well as in its downstream part.
  • all blocks are provided with opposite bowls.
  • the invention may encompass variants wherein at least one block is provided with one single bowl, or even with no bowl at all.
  • This variant may be suitable, in certain cases where the location of condensation can be precisely identified.
  • such a variant is far less preferred, since it does not ensure the temperature homogenization in each region of the exchanger.
  • the exchanger extends vertically with a top inlet of process fluid, as well as a bottom outlet of said process fluid.
  • said process fluid may flow from the bottom to the top.
  • the exchanger may extend horizontally or in an oblique manner.
  • the invention is based on the identification of the function of the bowl, which makes it possible to homogenize the graphite temperature over at least part of the exchanger.
  • several embodiments may be considered, as it has been above detailed.
  • a cooling one single bowl is preferred, in particular with a deep bowl if admission temperature of process fluid is high.
  • a plurality of bowls are preferred on every front face of every block.
  • the bowl(s), provided in the front face(s) of the block(s) according to the invention is (are) different from the chambers provided in the blocks disclosed in the above discussed US-A-3,391,016 , US-A-2,821,369 and GB-A-1 078 868 .
  • said chambers only ensure a function of fluid distribution between two adjacent blocks.
  • these chambers are not adapted to fulfil a significant function of temperature homogenization. In any case, these documents are not concerned with this homogenization function
  • This block 1 differs from the one 401 according to prior art, essentially in that
  • This block 1 was accommodated in an enclosure with other blocks according to prior art, which are similar to the one 401.
  • a block 501 was provided, according to the second embodiment of the invention.
  • This block 501 differs from the one 1 according to the first embodiment of the invention, essentially in that
  • This block 501 was accommodated in an enclosure with other blocks according to prior art, which are similar to the one 401.
  • gaseous chloric acid HCl was fed in the process channels at a flow rate of 3142.8kg/h, at a temperature of 1335°C and at a pressure of 3.20barg.
  • a service fluid typically water, was fed in the service channels 460 at a flow rate of 87000kg/h, at a temperature of 63.6°C and at a pressure of 4.25 barg.
  • T1max which is the maximal temperature of water flowing into the fluid channels.
  • the location of T1max, referenced on figure 8 corresponds to the upper edge of channel 560a, close to wall 561.
  • - T2max which is the maximal temperature of graphite skin of the exchangers.
  • the location of T2max, referenced on figure 8 corresponds to the graphite wall 561.
  • - T3max which is the maximal temperature of graphite skin of the exchangers.
  • the location of T3max referenced on figure 8 , corresponds to the graphite surface S503.
  • the invention makes it possible to substantially lower different characteristic temperatures of the implementation, with respect to prior art.
  • exchanger II and block 501 bring about a further lowering of these temperatures with respect to exchanger I and block 1, according to first embodiment.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP22171766.3A 2021-06-14 2022-05-05 Bloc d'échange de chaleur, son procédé de fabrication, échangeur de chaleur équipé d'un tel bloc et son procédé de mise en oeuvre Pending EP4105590A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US18/569,753 US20250012520A1 (en) 2021-06-14 2022-06-07 Heat exchange block, method for manufacturing same, heat exchanger equipped with such a block and method for implementing same
PCT/IB2022/055277 WO2022263972A1 (fr) 2021-06-14 2022-06-07 Bloc d'échange thermique, son procédé de fabrication, échangeur thermique équipé d'un tel bloc et son procédé de mise en œuvre
JP2023577292A JP2024523028A (ja) 2021-06-14 2022-06-07 熱交換ブロックおよびその製造方法、並びにそのブロックを備えた熱交換器およびその実装方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21179189.2A EP4105589A1 (fr) 2021-06-14 2021-06-14 Bloc d'échange de chaleur, son procédé de fabrication, échangeur de chaleur équipé d'un tel bloc et son procédé de mise en uvre

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EP4105590A1 true EP4105590A1 (fr) 2022-12-21

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EP21179189.2A Withdrawn EP4105589A1 (fr) 2021-06-14 2021-06-14 Bloc d'échange de chaleur, son procédé de fabrication, échangeur de chaleur équipé d'un tel bloc et son procédé de mise en uvre
EP22171766.3A Pending EP4105590A1 (fr) 2021-06-14 2022-05-05 Bloc d'échange de chaleur, son procédé de fabrication, échangeur de chaleur équipé d'un tel bloc et son procédé de mise en oeuvre

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2821369A (en) 1952-10-14 1958-01-28 Lorraine Carbone Heat exchangers
GB1078868A (en) 1964-11-12 1967-08-09 Dietrich Schwemann Heat exchange column
US3391016A (en) 1964-02-07 1968-07-02 Texas Instruments Inc Silicon carbide coating on graphite bores of heat exchanger
EP0196548A1 (fr) 1985-03-19 1986-10-08 GEA Wiegand GmbH Echangeur à blocs compact en graphite imprégné
WO2006081965A1 (fr) 2005-02-04 2006-08-10 Sgl Carbon Ag Echangeur thermique modulaire en graphite

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2821369A (en) 1952-10-14 1958-01-28 Lorraine Carbone Heat exchangers
US3391016A (en) 1964-02-07 1968-07-02 Texas Instruments Inc Silicon carbide coating on graphite bores of heat exchanger
GB1078868A (en) 1964-11-12 1967-08-09 Dietrich Schwemann Heat exchange column
EP0196548A1 (fr) 1985-03-19 1986-10-08 GEA Wiegand GmbH Echangeur à blocs compact en graphite imprégné
WO2006081965A1 (fr) 2005-02-04 2006-08-10 Sgl Carbon Ag Echangeur thermique modulaire en graphite

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