EP1179724A1 - Echangeur thermique à blocs échangeurs multiples à ligne d'alimentation en fluide à distribution uniforme, et vaporiseur-condenseur comportant un tel échangeur - Google Patents
Echangeur thermique à blocs échangeurs multiples à ligne d'alimentation en fluide à distribution uniforme, et vaporiseur-condenseur comportant un tel échangeur Download PDFInfo
- Publication number
- EP1179724A1 EP1179724A1 EP01402093A EP01402093A EP1179724A1 EP 1179724 A1 EP1179724 A1 EP 1179724A1 EP 01402093 A EP01402093 A EP 01402093A EP 01402093 A EP01402093 A EP 01402093A EP 1179724 A1 EP1179724 A1 EP 1179724A1
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- European Patent Office
- Prior art keywords
- grid
- heat exchanger
- exchanger according
- fluid
- line
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
- F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
- F25J5/005—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger in a reboiler-condenser, e.g. within a column
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
- F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
- F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
- F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
- F25J3/04406—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system
- F25J3/04412—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air using a dual pressure main column system in a classical double column flowsheet, i.e. with thermal coupling by a main reboiler-condenser in the bottom of low pressure respectively top of high pressure column
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
- F28D9/0068—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2250/00—Details related to the use of reboiler-condensers
- F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2250/00—Details related to the use of reboiler-condensers
- F25J2250/20—Boiler-condenser with multiple exchanger cores in parallel or with multiple re-boiling or condensing streams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
- F25J2290/32—Details on header or distribution passages of heat exchangers, e.g. of reboiler-condenser or plate heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
- F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
- F25J2290/42—Modularity, pre-fabrication of modules, assembling and erection, horizontal layout, i.e. plot plan, and vertical arrangement of parts of the cryogenic unit, e.g. of the cold box
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2210/00—Heat exchange conduits
- F28F2210/08—Assemblies of conduits having different features
Definitions
- the invention relates to heat exchangers, in particular for vaporizers-condensers of cryogenic installations, for example for main evaporators of the double distillation columns air, and vaporizers-condensers comprising such an exchanger.
- This vaporizer-condenser intended to condense a first fluid arriving in the gaseous state by vaporizing a second fluid arriving in the state liquid, thus comprises, inside an enclosure 10 of general shape cylindrical, a heat exchanger 2 as shown in FIG. 2.
- the vaporizer-condenser illustrated in the figures includes a single enclosure, but commonly, vaporizers have several enclosures, for example two parallel enclosures, each equipped with an exchanger.
- the central region of one of the bases 101 thereof is provided with a supply duct 11; the central base region opposite is provided with a discharge duct not visible in the drawings, to evacuate from the enclosure the part of this second fluid which has not been vaporized as a result of heat exchange with the first fluid.
- the part upper side wall of the enclosure is provided with at least one evacuation pipe 12 to evacuate part of the second from the enclosure fluid which has been vaporized and is thus in the gaseous state.
- the heat exchanger 2 thus bathes in a bath 13 consisting of the part of the second fluid which is in the state liquid, surmounted by a gaseous sky 14 consisting of the part of this second fluid which has been vaporized as a result of heat exchange with the first fluid, channeled in the exchanger.
- the exchanger 2 shown in FIG. 2 and also visible on the Figure 3 includes an exchanger body made up of several blocks exchangers 20 with plates arranged aligned and joined, arranged for condense the first fluid by circulating it in passages substantially vertical exchanger blocks from top to bottom, in vaporizing the second fluid flowing in passages adjacent to those where the first fluid flows, from bottom to top.
- each exchanger block 20 includes plates 200 generally rectangular arranged parallel being braced by spacer waves which perform the function of thermal fins, so as to form a generally parallelepipedic stack assembled by brazing.
- the plates 200 thus define two by two of the passages intended for traffic in a vertical direction, alternately in from one end plate of the block to the opposite end plate, from first fluid and second fluid.
- the plates delimiting between them a rectangular passage 201 for the first fluid are further braced by bars running along their four sides; while the bars 202 of the horizontal sides extend over the entire length of these sides, the bars 203 on the vertical sides do not extend to the ends of these sides and have an approximately central interruption of so as to create windows 204 at the upper ends and halfway up passages, and windows 205 at the lower ends of the passages, constituting respectively entry and exit accesses for the first fluid.
- the plates delimiting between them a passage for the second fluid are braced by bars running only along their vertical sides, over the whole length of these sides, so as to create all along their sides lower and upper horizontal windows, respectively entry and outlet for the second fluid.
- the spacer waves which extend in these passages are vertical generators.
- the passages 201 intended for the first fluid in the blocks 20 include a main heat exchange region 206, regions input distributors 207 extending at the level of the input windows 204, and outlet collecting regions 208 at the outlet windows 205.
- the input distributing regions 207 and the collecting regions of outlet 208 are here in the form of right triangles; the right triangles forming two of the four input distributor regions have respectively for right angles at the top the upper right angles of the passage rectangular for the first fluid, for short side of the right angle, the heights of the upper entrance windows 204, and for long sides of the right angle, the half-widths of the passage at the top of these Windows ;
- the right triangles of the other two distributing regions entry heights respectively have short sides of the right angle the heights entry windows 204 halfway up the passage and for long sides of the right angle about two-thirds of the half-widths of the level crossing from the top of these windows; the right triangles forming the two exit collecting regions have respectively right angles to the vertex the lower right angles of the rectangular passage
- the spacer waves which extend in the input distributor regions 207 and output collector regions 208 are horizontal generators, while the spacer waves which extend into the main heat exchange regions 206 are at vertical generators.
- each exchanger block 20 has four series of windows inlet 204 for the first fluid extending two by two respectively in two vertical parallel faces of the block and opening into four respective series of input distributor regions 207, two series of outlet windows 205 for the first fluid extending respectively in the same two faces and into which two series emerge respective output collector regions 208, a series of windows inlet for the second fluid extending in a horizontal face bottom of the block, and a series of outlet windows for the second fluid extending in an upper horizontal face of the block.
- the first fluid is circulated in a system of pipes connected to the exchanger blocks as described below.
- each of the series of entry windows has its windows 204 in communication with the internal space of a box respective fluid supply 21 carried by the block 20, of form elongated and which extends against the face of the block in which the series of windows; similarly, each of the series of exit windows 205 a its windows in communication with the internal space of a box respective fluid discharge 22 carried by the block 20, of form elongated and which extends against the face of the block in which the series is created windows 205.
- the supply boxes 21 and the outlet boxes 22 have a straight cross-section in the shape of a circular sector; here the section is in a semicircle, and the boxes thus have a semi-cylinder wall and are open along the diametrical plane of the half-cylinder by which the windows open into the internal space of the box.
- the two sets of entry windows located on the same side of a block open into the same supply box 21, respectively at the top and bottom of it.
- the supply boxes 21 counterparts of the neighboring blocks are in communication with each other to form a supply line in fluid
- the outlet boxes 22 counterparts of the neighboring blocks are in communication with each other to form an evacuation line from fluid, either by the fact that the homologous boxes of the different blocks constituting the same exchanger body are made in one piece ( Figure 2), either by the fact that the homologous boxes, which are provided on the and other of each block 20 of cylindrical taps 211, have their Respective connections located opposite connected by a link 23 ( Figure 4).
- the power boxes of the terminal block 20 of a exchanger have no downstream connection and have a semi-circular bottom, while one-piece power boxes exchanger are provided with an upstream 211 nozzle to facilitate their connection (figure 2).
- the upstream connections 211 of the two lines supply of the first gaseous fluid located on either side of the exchanger are connected to bent inlet pipes 24 themselves connected on either side of a through 25 input collector the base 101 of the enclosure 10, through which the first fluid is introduced in the state gaseous.
- the discharge lines of the first fluid in the gaseous state are closed at both ends; facing each block 20, the side wall of each box 22 has an opening through which the internal space of the box opens into a discharge pipe 26 respective extending in an approximately vertical plane and one of which part extends down below the box being bent so as to extend under the block 20 transversely to it in tilting down; the lower ends of all pipes evacuation 26 located on either side of the blocks 20 open into a same manifold 27 for discharging the first fluid in the liquid state, which crosses the base 101 of the enclosure 10.
- Each discharge pipe 26 also has an upwardly extending portion above the level of the box 22, and the upper ends of all the pipes outlet 26 open into one or the other of two conduits evacuation 28 of non-condensable or non-condensing residual gases extending horizontally respectively on either side of the exchanger, along it; these gas evacuation pipes 28 residual are located at an intermediate level between that of the boxes supply 21 and that of the outlet boxes 22; they emerge, at the upstream end of the exchanger, in a gas discharge manifold 29 residuals, also crossing base 101 of enclosure 10.
- the first fluid brought to the state gas at the inlet manifold 25, is distributed between the two pipes input 24, then enters the line of supply boxes 21 succeeding along the line of blocks 20; from there he enters through the windows inlet 204 in the passages 201 which are intended for it between the plates.
- the second fluid brought to the liquid state by the supply conduit 11 in the enclosure 10 and which forms therein a bath 13 where the heat exchanger blocks 20 receives enough energy for part of it second fluid vaporizes while the first fluid, yielding part of its energy, liquefies.
- the first fluid comes out of the blocks exchangers 20 through the outlet windows 205 of the base of the blocks, penetrates in the evacuation boxes 22, and descends through the evacuation pipes 26 in the evacuation manifold 27 by which it is evacuated from the vaporizer-condenser ; generally, when the first fluid arrives in the gaseous state in the vaporizer-condenser, it is not perfectly pure and contains a fraction of noncondensable gases at operating temperature the vaporizer-condenser; non-condensable or non-condensing residual gases are entrained in the outlet boxes 22 with the first fluid in the liquid state, but escape from the boxes 22 through the pipes discharge 26, upwards, in the gas discharge conduits 28 residual, and are evacuated from the vaporizer-condenser by the collector evacuation 29 of non-condensed gases.
- the part of the second fluid which passes to the gaseous state in the passages which are their dedicated in block 20 escapes from these passages through the windows upper of these, and is discharged from the enclosure 10 where it constitutes the sky 14, via the exhaust pipes 12.
- the flow of the first fluid in the supply boxes 21 is very heterogeneous and may even be locally vortex by following in particular the passage of the circular straight cross section of the inlet ducts 24 to the semicircular cross section of the boxes 21, and if we consider a straight cross section of the boxes, the speeds in different very close locations belonging to this section can be extremely different; this results in an uneven distribution of the first fluid between the different inlet windows 204 and thus between the different passages 201 for the first fluid, often a lower flow rate in the windows closest to the nozzle.
- a consequence of this poor distribution is a disparity in the transformation of the first fluid in gas in the various passages 201, and thus a yield of the not optimal vaporizer-condenser.
- the invention aims to remedy this drawback, and relates to for this purpose a heat exchanger comprising an exchanger block or several aligned exchanger blocks where fluids are circulated in heat exchange relationship, at least one face of each block having entry windows for at least one of the fluids, the windows of entry of the same face of each block for this fluid being in communication with the internal space of the same power supply box fluid which extends against said face thereof, and which communicates with at minus a homologous box from a neighboring block if there is one, to form a fluid supply line, exchanger characterized in that the line fluid supply contains at least one grid arranged across the line and having through perforations and solid parts distributed to create, at locations on the grid surface, pressure losses such as fluid flow velocities in input windows downstream of the grid have similar values, and the distribution of the fluid in the entry windows as well as in the line supply downstream of the grid and upstream in the vicinity thereof is approximately homogeneous.
- the invention also relates to vaporizers-condensers, in particular air separation units, comprising such an exchanger.
- Such vaporizers-condensers are used in particular in cryogenic air distillation plants, in which they are associated and connected to a double distillation column comprising a low pressure column superimposed on a medium pressure column, for liquefy nitrogen gas taken from the top of the medium pressure column, by heat exchange with liquid oxygen which is in tank of the low pressure column and which is vaporized in the vaporizer-condenser.
- nitrogen constitutes the first fluid which is introduced in the gaseous state in the exchanger by the inlet manifold 25 and which is then evacuated therefrom in the liquid state by the exhaust manifold 27, and the oxygen is the second fluid which is introduced in the liquid state into the enclosure 10 by the supply line 11, part of which can be drawn off in the liquid state by an evacuation duct not shown and another part is evacuated in the gaseous state by one or more discharge pipes 12.
- this line contains one or more 30 flat or curved grids arranged crosswise the path of the fluid in the line, at an optimal location according to the flow lines in this line.
- this grid or these grids 30 have through holes 301 and solid parts 302 distributed for create pressure drops at locations on the grid surface such as fluid flow velocities in neighboring areas belonging to the same straight cross section of the line fluid supply downstream of the grid have similar values and the distribution of the fluid in the inlet windows 204 of all the blocks 20 supplied by this line is approximately homogeneous.
- such a grid 30 may include perforations through and solid parts distributed approximately uniformly on its surface so that the presence of the grid introduces a significant uniform pressure drop across the entire section fluid flow.
- the line pressure drop is as low as possible, and it is generally advantageous that the perforation rate of the surface of the grid 30, defined as being, for a given region of the grid, the ratio from the area occupied by perforations 301 to the total area of the region, varies on it or from one region to another of it in reverse of the value of flow velocities at the same locations on the line when there is no grid.
- the perforation rate varies from region to region by the surface of the grid in a substantially inversely proportional manner flow velocities at the same locations in the absence of a grid.
- a swirl region in the box immediately downstream of the the grid can often, advantageously, be arranged in this vortex region.
- the grid it is sometimes necessary for the grid to be arranged more downstream in the line, or to have several identical grids or no, for example a grid in each box 21 near the entrance to it.
- the perforations 301 are circular and the rate of perforation rises at the same time as the diameter of the perforations, but these can take any suitable form, in particular in regular polygon, and it is possible to obtain a region with low perforation rate with large perforations if they are few in
- the grid it is also possible to place the grid either on a straight cross section, but obliquely in the supply line, and make it play the role of deflector for example oriented downstream in direction of the cylindrical surface of the box; if the boxes are, like this is generally the case, semi-cylindrical, and if the grid occupies all the area of an inclined section of a box, the grid has a shape semi-elliptical exterior.
- the exchanger comprises two supply lines to bring the fluid to the windows 204 of the faces opposite blocks 20
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- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Separation By Low-Temperature Treatments (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
Abstract
Description
- la figure 1 est une vue extérieure schématique en perspective d'un vaporiseur-condenseur pouvant être équipé intérieurement d'un échangeur agencé selon l'invention,
- la figure 2 est une vue extérieure schématique en perspective d'un échangeur équipant intérieurement le vaporiseur-condenseur de la figure 1,
- la figure 3 est une section transversale schématique du vaporiseur-condenseur de la figure 1.
- la grille présente des perforations réparties sur sa surface de manière non uniforme ;
- la grille présente des perforations traversantes avec un taux de perforation de sa surface qui varie sur celle-ci approximativement en sens inverse de la valeur des vitesses d'écoulement aux mêmes emplacements en l'absence de grille ;
- le taux de perforation varie sur la surface de la grille de manière sensiblement inversement proportionnelle aux vitesses d'écoulement aux mêmes emplacements en l'absence de grille ;
- la grille comporte plusieurs régions juxtaposées présentant chacune un même taux de perforation sur leur surface, et des taux de perforation respectifs différents d'une région à une région adjacente ;
- la grille comporte au moins une région constituée par une échancrure ou une découpe ;
- la grille comporte au moins une région continue sans perforations représentant une fraction substantielle de son aire ;
- la grille s'étend sur une section transversale de la ligne ;
- la grille s'étend sur une section transversale droite de la ligne ;
- la grille est disposée obliquement dans la ligne d'alimentation ;
- la grille s'étend sur toute l'aire d'une section transversale de la ligne ;
- la grille s'étend sur une aire inférieure à une section transversale de la ligne ;
- l'échangeur thermique comprend une ligne d'alimentation comportant un piquage présentant une section transversale droite circulaire et relié à des boítes d'alimentation présentant une section transversale droite semi-circulaire, et la grille est disposée dans une boíte d'alimentation à proximité du piquage.
- la ligne d'alimentation contient plusieurs grilles ;
- l'échangeur thermique comprend deux lignes d'alimentation, et chaque ligne contient au moins une grille ; et
- ledit fluide circulant dans la ligne d'alimentation en fluide est à l'état gazeux.
- la figure 4 est une vue extérieure schématique en perspective d'une partie d'une autre forme de réalisation possible d'un échangeur pour équiper intérieurement le vaporiseur-condenseur de la figure 1, et
- la figure 5 est une vue de face d'un exemple de réalisation d'une grille d'uniformisation adaptée pour équiper, suivant l'invention, une ligne d'alimentation en fluide d'un échangeur tel que celui des figures 2 et 4.
Claims (18)
- Echangeur thermique (2) comportant un bloc échangeur ou plusieurs blocs échangeurs (20) alignés où des fluides sont mis en circulation en relation d'échange thermique, au moins une face de chaque bloc comportant des fenêtres d'entrée (204) pour au moins l'un des fluides, les fenêtres d'entrée d'une même face de chaque bloc pour ce fluide étant en communication avec l'espace interne d'une même boíte (21) d'alimentation en fluide qui s'étend contre ladite face de celui-ci, et qui communique avec au moins une boíte homologue d'un bloc voisin si il en existe un, pour former une ligne d'alimentation en fluide, échangeur caractérisé en ce que la ligne d'alimentation en fluide contient au moins une grille (30) disposée en travers de la ligne et présentant des perforations traversantes (301) et des parties pleines (302) réparties pour créer, en des emplacements de la surface de la grille, des pertes de charge telles que les vitesses d'écoulement du fluide dans des fenêtres d'entrée en aval de la grille (30) ont des valeurs voisines, et la répartition du fluide dans les fenêtres d'entrée (204) ainsi que dans la ligne d'alimentation en aval de la grille (30) et en amont au voisinage de celle-ci est approximativement homogène.
- Echangeur thermique selon la revendication 1, caractérisé en ce que la grille (30) présente des perforations réparties sur sa surface de manière non uniforme.
- Echangeur thermique selon la revendication 2, caractérisé en ce que la grille (30) présente des perforations traversantes (301) avec un taux de perforation de sa surface qui varie sur celle-ci approximativement en sens inverse de la valeur des vitesses d'écoulement aux mêmes emplacements en l'absence de grille.
- Echangeur thermique selon la revendication 3, caractérisé en ce que le taux de perforation varie sur la surface de la grille (30) de manière sensiblement inversement proportionnelle aux vitesses d'écoulement aux mêmes emplacements en l'absence de grille.
- Echangeur thermique selon l'une quelconque des revendications 2 à 4, caractérisé en ce que la grille (30) comporte plusieurs régions juxtaposées présentant chacune un même taux de perforation sur leur surface, et des taux de perforation respectifs différents d'une région à une région adjacente.
- Echangeur thermique selon l'une quelconque des revendications 2 à 5, caractérisé en ce que la grille (30) comporte au moins une région constituée par une échancrure ou une découpe.
- Echangeur thermique selon l'une quelconque des revendications 2 à 6, caractérisé en ce que la grille (30) comporte au moins une région continue sans perforations représentant une fraction substantielle de son aire.
- Echangeur thermique selon l'une quelconque des revendications 1 à 7, caractérisé en ce que la grille (30) s'étend sur une section transversale de la ligne.
- Echangeur thermique selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la grille (30) s'étend sur une section transversale droite de la ligne.
- Echangeur thermique selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la grille (30) est disposée obliquement dans la ligne d'alimentation.
- Echangeur thermique selon l'une quelconque des revendications 1 à 10, caractérisé en ce que la grille (30) s'étend sur toute l'aire d'une section transversale de la ligne.
- Echangeur thermique selon l'une quelconque des revendications 1 à 10, caractérisé en ce que la grille (30) s'étend sur une aire inférieure à une section transversale de la ligne.
- Echangeur thermique selon l'une quelconque des revendications 1 à 12 comprenant une ligne d'alimentation comportant un piquage (211) présentant une section transversale droite circulaire et relié à des boítes d'alimentation (21) présentant une section transversale droite semi-circulaire, caractérisé en ce que la grille (30) est disposée dans une boíte d'alimentation à proximité du piquage.
- Echangeur thermique selon l'une quelconque des revendications 1 à 13, caractérisé en ce que la ligne d'alimentation contient plusieurs grilles (30).
- Echangeur thermique selon l'une quelconque des revendications 1 à 14 comprenant deux lignes d'alimentation, caractérisé en ce que chaque ligne contient au moins une grille (30).
- Echangeur thermique selon l'une quelconque des revendications 1 à 15, caractérisé en ce que ledit fluide circulant dans la ligne d'alimentation en fluide est à l'état gazeux.
- Vaporiseur-condenseur caractérisé en ce qu'il comporte au moins un échangeur thermique selon l'une quelconque des revendications 1 à 16.
- Vaporiseur-condenseur d'unité de séparateur d'air, caractérisé en ce qu'il comporte au moins un échangeur thermique selon l'une quelconque des revendications 1 à 16.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0010433 | 2000-08-08 | ||
FR0010433A FR2812935B1 (fr) | 2000-08-08 | 2000-08-08 | Echangeur thermique a blocs echangeurs multiples a ligne d'alimentation en fluide a distribution uniforme, et vaporiseur-condenseur comportant un tel echangeur |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1179724A1 true EP1179724A1 (fr) | 2002-02-13 |
EP1179724B1 EP1179724B1 (fr) | 2005-04-27 |
Family
ID=8853399
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01402093A Expired - Lifetime EP1179724B1 (fr) | 2000-08-08 | 2001-08-02 | Echangeur thermique à blocs échangeurs multiples à ligne d'alimentation en fluide à distribution uniforme, et vaporiseur-condenseur comportant un tel échangeur |
Country Status (7)
Country | Link |
---|---|
US (1) | US6817407B2 (fr) |
EP (1) | EP1179724B1 (fr) |
JP (1) | JP2002098495A (fr) |
CN (1) | CN1227505C (fr) |
CA (1) | CA2353691A1 (fr) |
DE (1) | DE60110328T2 (fr) |
FR (1) | FR2812935B1 (fr) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2843059B1 (fr) * | 2002-07-30 | 2005-02-25 | Air Liquide | Echangeurs thermiques en cuivre brases et leur procede de fabrication par soudage |
EP1452817A1 (fr) | 2003-02-25 | 2004-09-01 | Linde Aktiengesellschaft | Echangeur de chaleur |
CN100541107C (zh) * | 2003-02-25 | 2009-09-16 | 林德股份公司 | 热交换器 |
US7100280B2 (en) * | 2003-02-25 | 2006-09-05 | Linde Aktiengesellschaft | Method for producing a heat exchanger |
US20070204981A1 (en) * | 2006-03-02 | 2007-09-06 | Barnes Terry W | Modular manifolds for heat exchangers |
US9528772B2 (en) * | 2008-01-28 | 2016-12-27 | Freimut Joachim Marold | Multi-passage thermal sheet and heat exchanger equipped therewith |
JP5795994B2 (ja) | 2012-07-09 | 2015-10-14 | 住友精密工業株式会社 | 熱交換器 |
CN103063073B (zh) * | 2012-12-28 | 2014-08-13 | 广东工业大学 | 分液芯及带有分液芯的多级冷却换热器 |
US9593598B2 (en) | 2014-05-13 | 2017-03-14 | Holtec International | Steam conditioning system |
CN106500538B (zh) * | 2016-12-16 | 2019-04-19 | 山东擎雷环境科技股份有限公司 | 一种双流程板管式换热器 |
JP6746234B2 (ja) * | 2017-01-25 | 2020-08-26 | 日立ジョンソンコントロールズ空調株式会社 | 熱交換器、及び、空気調和機 |
CN107934987B (zh) * | 2017-12-21 | 2024-05-14 | 中冶焦耐(大连)工程技术有限公司 | 一种除结晶自冲洗型氨冷凝冷却装置 |
CN109798411A (zh) * | 2019-01-16 | 2019-05-24 | 中国寰球工程有限公司 | 单一轴向入口多侧向出口流体平均分配器 |
CN113309603B (zh) * | 2021-05-14 | 2022-06-03 | 中国汽车工程研究院股份有限公司 | 一种快速、准确增大缩比尺寸散热器压降性能的方法 |
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DE1901475A1 (de) * | 1969-01-14 | 1970-08-27 | Messer Griesheim Gmbh | Vorrichtung zum Verteilen einer Zweiphasenstroemung auf Plattenwaermeaustauscher |
FR2037366A5 (en) * | 1969-03-03 | 1970-12-31 | Chicago Bridge & Iron Co | Liquid distributor for heat exchanger |
US3623505A (en) * | 1969-08-20 | 1971-11-30 | Westinghouse Electric Corp | Flow distribution device |
US3830292A (en) * | 1972-05-01 | 1974-08-20 | Atomic Energy Commission | Flow distribution for heat exchangers |
US5107923A (en) * | 1991-06-10 | 1992-04-28 | United Technologies Corporation | Flow distribution device |
EP0546947A1 (fr) * | 1991-12-11 | 1993-06-16 | L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude | Echangeur de chaleur indirect du type à plaques |
FR2697906A1 (fr) * | 1992-11-10 | 1994-05-13 | Packinox Sa | Faisceau de plaques pour échangeur thermique. |
EP0826528A2 (fr) * | 1996-08-30 | 1998-03-04 | Keihin Corporation | Appareil de chauffage de véhicules |
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DE1152432B (de) * | 1962-04-21 | 1963-08-08 | Linde Eismasch Ag | Platten-Kondensator-Verdampfer, insbesondere fuer Gas- und Luftzerleger |
US3590914A (en) * | 1969-10-01 | 1971-07-06 | Trane Co | Countercurrent flow plate-type heat exchanger with leak detector |
FR2456924A2 (fr) * | 1979-05-18 | 1980-12-12 | Air Liquide | Ensemble d'echange thermique du genre echangeur de chaleur a plaques |
US4276927A (en) * | 1979-06-04 | 1981-07-07 | The Trane Company | Plate type heat exchanger |
FR2691242B1 (fr) * | 1992-05-13 | 1994-07-08 | Valeo Thermique Moteur Sa | Boite a eau a vase d'expansion integre pour echangeur de chaleur, en particulier pour vehicule automobile. |
US5186249A (en) * | 1992-06-08 | 1993-02-16 | General Motors Corporation | Heater core |
US5671808A (en) * | 1995-07-26 | 1997-09-30 | Kleyn; Hendrik | Polymeric radiators |
US5979544A (en) * | 1996-10-03 | 1999-11-09 | Zexel Corporation | Laminated heat exchanger |
JPH10300384A (ja) * | 1997-04-24 | 1998-11-13 | Daikin Ind Ltd | プレート式熱交換器 |
-
2000
- 2000-08-08 FR FR0010433A patent/FR2812935B1/fr not_active Expired - Fee Related
-
2001
- 2001-07-24 CA CA002353691A patent/CA2353691A1/fr not_active Abandoned
- 2001-08-02 DE DE60110328T patent/DE60110328T2/de not_active Expired - Lifetime
- 2001-08-02 EP EP01402093A patent/EP1179724B1/fr not_active Expired - Lifetime
- 2001-08-02 JP JP2001235179A patent/JP2002098495A/ja active Pending
- 2001-08-07 CN CNB011255080A patent/CN1227505C/zh not_active Expired - Fee Related
- 2001-08-08 US US09/923,396 patent/US6817407B2/en not_active Expired - Lifetime
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
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DE1901475A1 (de) * | 1969-01-14 | 1970-08-27 | Messer Griesheim Gmbh | Vorrichtung zum Verteilen einer Zweiphasenstroemung auf Plattenwaermeaustauscher |
FR2037366A5 (en) * | 1969-03-03 | 1970-12-31 | Chicago Bridge & Iron Co | Liquid distributor for heat exchanger |
US3623505A (en) * | 1969-08-20 | 1971-11-30 | Westinghouse Electric Corp | Flow distribution device |
US3830292A (en) * | 1972-05-01 | 1974-08-20 | Atomic Energy Commission | Flow distribution for heat exchangers |
US5107923A (en) * | 1991-06-10 | 1992-04-28 | United Technologies Corporation | Flow distribution device |
EP0546947A1 (fr) * | 1991-12-11 | 1993-06-16 | L'air Liquide, Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude | Echangeur de chaleur indirect du type à plaques |
FR2697906A1 (fr) * | 1992-11-10 | 1994-05-13 | Packinox Sa | Faisceau de plaques pour échangeur thermique. |
EP0826528A2 (fr) * | 1996-08-30 | 1998-03-04 | Keihin Corporation | Appareil de chauffage de véhicules |
Also Published As
Publication number | Publication date |
---|---|
CN1227505C (zh) | 2005-11-16 |
FR2812935B1 (fr) | 2002-10-18 |
US20020023739A1 (en) | 2002-02-28 |
DE60110328D1 (de) | 2005-06-02 |
FR2812935A1 (fr) | 2002-02-15 |
JP2002098495A (ja) | 2002-04-05 |
EP1179724B1 (fr) | 2005-04-27 |
US6817407B2 (en) | 2004-11-16 |
CN1337561A (zh) | 2002-02-27 |
CA2353691A1 (fr) | 2002-02-08 |
DE60110328T2 (de) | 2006-01-26 |
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