WO2013010671A2 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2013010671A2
WO2013010671A2 PCT/EP2012/003040 EP2012003040W WO2013010671A2 WO 2013010671 A2 WO2013010671 A2 WO 2013010671A2 EP 2012003040 W EP2012003040 W EP 2012003040W WO 2013010671 A2 WO2013010671 A2 WO 2013010671A2
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
heat exchanger
receiving area
jacket
gas
Prior art date
Application number
PCT/EP2012/003040
Other languages
German (de)
English (en)
Other versions
WO2013010671A3 (fr
Inventor
Jürgen Misselhorn
Christian FREESE
Original Assignee
Maschinenwerk Misselhorn Gmbh
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 Maschinenwerk Misselhorn Gmbh filed Critical Maschinenwerk Misselhorn Gmbh
Publication of WO2013010671A2 publication Critical patent/WO2013010671A2/fr
Publication of WO2013010671A3 publication Critical patent/WO2013010671A3/fr

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Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid

Definitions

  • the present invention relates to a heat exchanger, in particular a heat exchanger, which can be acted upon transiently with pressure. Furthermore, the present invention relates to a method for condensing and vaporizing a fluid in a heat exchanger.
  • a heat exchanger for a variety of media or substances, wherein energy is transferred from one stream to another stream.
  • a heat exchanger has a heat exchanger jacket, which encloses an inner space which is divided into at least two partial areas. A portion of the interior is flowed through by a first fluid, while the other portion is traversed by the second fluid.
  • the media are separated by one or more partitions, which advantageously have good heat conduction and a large surface area.
  • One widely used type of construction is a shell-and-tube heat exchanger in which the first fluid is passed through a plurality of tubes, ie, a tube bundle, disposed within the heat exchanger shell.
  • the second fluid is located inside the heat exchanger shell and surrounds the tube bundle.
  • a plate heat exchanger Numerous parallel plates with slight curvature form contiguous spaces for receiving the first and second media. The rooms are flat and border each other alternately. The spaces between the parallel plates are alternately flowed through by the first and the second fluid.
  • the different media may both be gaseous, both liquid, or one fluid may be gaseous and the other fluid liquid.
  • Heat exchangers can be used in a stationary or in a transient operation. In steady state operation, the first and second fluids flow continuously through the heat exchanger. In a dynamic or transient process, the heat exchanger is continuously flowed through by a fluid, while the other fluid is introduced only in phases in the heat exchanger.
  • a first cold fluid is introduced in phases into the heat exchanger, which is continuously flowed through by a second warm fluid, which gives off heat.
  • the first fluid is introduced in phases into the heat exchanger, it is heated or vaporized in phases; depending on the temperature level and the pressure.
  • the heat exchanger can be continuously flowed through by a first cold fluid, while a second warm fluid is introduced only in phases into the heat exchanger. The second fluid is then cooled and / or condensed depending on the temperature and pressure of the two media.
  • Heat exchangers of the prior art are mostly used in stationary processes.
  • a heat exchanger In a stationary process, a heat exchanger is constantly flowed through by both media, i. from both a heat-releasing fluid and a heat-receiving fluid. Heat exchangers for transient processes are less widespread. In most cases, heat exchangers designed for a stationary process are not capable of withstanding highly fluctuating pressure loads within the heat exchanger.
  • vapor barriers can form between the introduced first fluid and the heated partitions, for example on the outer or inner surfaces of the tubes in a tube bundle heat exchanger.
  • the steam barriers can be used with strong steam development to prevent rapid heat transfer and also prevent the further introduction of the introduced first fluid.
  • the state changes of a fluid can take place in different ways, such as isentropic, adiabatic, isothermal or isochoric. In some applications, a specific state change is desired, such as an isothermal phase change. With conventional heat exchangers, the desired type of change of state can not always be achieved.
  • the object of the present invention is achieved by a heat exchanger according to claim 1 or 2.
  • the object is achieved by a heat exchanger having a heat exchanger jacket, which encloses an inner space for receiving a first flow medium, and having a plurality of fluid-tight passages for a second fluid, which run through the interior of the heat exchanger jacket, wherein the heat exchanger jacket a liquid receiving area for Receiving liquid first fluid and a gas receiving area for receiving gaseous first fluid.
  • the cross section of the heat exchanger jacket tapers from the liquid receiving area to the gas receiving area so that the liquid receiving area has a larger volume than the gas receiving area.
  • the object is achieved by a heat exchanger having a heat exchanger jacket, which encloses an inner space for receiving a first fluid, and having a plurality of fluid-tight passages for a second fluid, which extend through the inner space of the heat exchanger jacket, wherein the heat exchanger jacket Liquid receiving portion for receiving liquid first fluid and a gas receiving portion for receiving gaseous first fluid.
  • the cross section of the heat exchanger jacket tapers from the gas receiving area to the liquid receiving area so that the gas receiving area has a larger volume than the liquid receiving area.
  • the liquid receiving area is preferably located below the gas receiving area during operation of the heat exchanger in the direction of gravity, so that the liquid portion of the first fluid either depending on the design of the heat exchanger as evaporator or condenser can either be evaporated faster or can be collected better.
  • the cross section of the heat exchanger jacket can be linear, curved or stepped taper.
  • a compact design of the heat exchanger is possible, which can adapt to the surrounding components.
  • the heat exchanger jacket has fluid-tight passages for the second fluid.
  • the passages may optionally serve for insulation, for heating or for cooling the heat exchanger jacket.
  • An embodiment of the heat exchanger has a first inlet for introducing the first fluid, which opens into the interior in the region of the gas receiving area.
  • a first inlet for introducing the first fluid which opens into the interior in the region of the gas receiving area.
  • liquid fluid can be vaporized faster, or gaseous fluid can be condensed better.
  • a first outlet for discharging the first fluid can advantageously be provided, which opens into the interior in the region of the fluid receiving area.
  • liquid first fluid can be easily diverted.
  • a heat exchanger in the embodiment for evaporation can advantageously have a first outlet for discharging the first fluid, which opens in the region of the gas receiving area in the interior.
  • gaseous first fluid can be easily discharged.
  • the heat exchanger jacket has at least a first jacket part (head part) having a second inlet or a second outlet for the second fluid, and a second jacket telf (middle part) in which the passages are arranged so as to face the first jacket part to open. This makes it easy to repair and install the heat exchanger.
  • the first and the second jacket part are preferably connected at an interface by means of a flange 1 .
  • the flange forms a strut for stabilizing the heat exchanger jacket against deformation by pressure differences between the interior and the surroundings of the heat exchanger.
  • the heat exchanger jacket has a multiplicity of second components. telteil, which are serially connected by flanges. This makes a modular design possible. For example, heat exchangers with different capacity can be assembled from only two different shell parts, namely two first shell parts as head parts and a selectable number of second shell parts as middle parts. Furthermore, the first shell parts can be used as head parts for both the type of evaporator as well as the design as a capacitor.
  • a support jacket surrounds the heat exchanger jacket. As a result, the compressive strength of the heat exchanger is increased.
  • a distributor pipe is connected to the inlet for introducing the first fluid.
  • the manifold is adapted to distribute introduced first fluid over the interior.
  • the first fluid is distributed over a large heat exchange surface of the interior, and a fast phase change, ie a rapid evaporation, is achieved.
  • the method is provided for vaporizing a first fluid in a heat exchanger having a fluid receiving area and a gas receiving area.
  • the liquid receiving area has a larger volume than the gas receiving area
  • the method comprises the steps of: heating the heat exchanger by a second fluid; Introducing liquid first fluid into the fluid receiving area; Vaporizing the first fluid in the fluid receiving area; and collecting the vaporized first fluid in the gas receiving area. So in one transient process allows a rapid change of the state of aggregation of the introduced first fluid from liquid to gaseous.
  • the liquid first fluid temporarily flows through the gas-receiving region as it is introduced, and a first portion of the first fluid is vaporized as it passes through the gas-receiving region.
  • the evaporation is accelerated and the formation of
  • the method for condensing a first fluid in a heat exchanger having a fluid receiving area and a gas receiving area.
  • the gas receiving area has a larger volume than the liquid receiving area
  • the method comprises the following steps: cooling the heat exchanger by a second fluid; Introducing gaseous first fluid into the gas receiving area; Condensing the gaseous first fluid in the gas receiving area; and collecting the condensed first fluid in the fluid receiving area.
  • FIG. 1 shows a front view of an embodiment of a heat exchanger according to the present invention
  • Fig. 2 shows a side view of the heat exchanger shown in Figure 1 as seen from the direction of the arrow II in Figure 1.
  • Fig. 3 is a sectional view of the heat exchanger shown in Fig. 1 taken along section line 3-3 in Fig. 2;
  • Fig. 4 is a sectional view of the heat exchanger shown in Fig. 1 taken along section line 4-4 in Fig. 2;
  • Fig. 5 is a sectional view of the heat exchanger shown in Fig. 1 taken along section line 5-5 in Fig. 1;
  • Fig. 6 shows a sectional view similar to Fig. 3, another embodiment of a heat exchanger according to the present invention.
  • Fig. 7a shows a sectional view similar to Figure 3, wherein the heat exchanger is surrounded by a support shell.
  • FIG. 7b shows a sectional view similar to FIG. 5, wherein the support jacket shown in FIG. 7a can be seen in a section rotated by 90 ° with respect to FIG. 7a.
  • the heat exchangers described here utilize, inter alia, the effect that a liquid medium or fluid runs downwards following gravity.
  • the heat exchangers are shown in the figures so that the gravity is directed from top to bottom.
  • the terms top, bottom, right and left as well as similar statements refer to the orientations or arrangements shown in the figures. In the following, therefore, when speaking of the directions “above” and “below”, these directions in the drawings and with respect to the earth's surface are meant. However, the terms “left,” “right,” “front,” “back,” and the like are not to be understood in a limiting sense.
  • FIGS. 1-5 show a heat exchanger 1 according to an embodiment of the present invention.
  • the heat exchanger 1 has a heat exchange jacket 5, which encloses an inner space 6 of the heat exchanger 1.
  • the heat exchanger jacket 5 has a right and a left head piece 7 and a middle part 8, which is arranged between the first and second head pieces 7.
  • the interior 6 of the heat exchanger 1 is divided into two subspaces, namely a first subspace 9 for a first fluid and a second subspace 11 for a second fluid.
  • the two subranges 9, 11 are separated by partitions 13, which run parallel to the plane of the drawing of FIG. 1 and are best seen in FIG. 5. Between the partitions 13 extends a plurality of tubes 15.
  • the tubes 15 may have any cross-section, but are preferably round.
  • the first subspace 9 is bounded by the first and second header pieces 7, the partition walls 13 and the inner surfaces of the tubes 15.
  • the second subspace 11 of the inner space 6 is bounded by the middle part 8, the partitions 13 and the outer surfaces of the tubes 15. The second subspace 11 is thus delimited from the first subspace 9 by the tubes 15 and the partitions 13.
  • the two head parts 7 each have a flange 17, which is oriented towards the middle part 8.
  • the middle part 8 has two flanges 18, which are respectively oriented towards the flanges 17 of the two head parts 7.
  • the flanges 17 and the flanges 18 are sealed together by a plurality of screws 20. Between the flanges 17 and 18 seals not shown are arranged.
  • the flanges 17, 18 extend around the entire heat exchanger jacket 5 around. In the screwed together state of the flanges 17, 18 results in a strut surrounding the heat exchanger jacket 5, which gives the heat exchanger jacket 5 stability against pressure differences between the interior 6 and the environment.
  • the head pieces 7 each have a head piece connection 24, on which a head piece flange 25 is defined, in order to fix a feed or discharge, not shown in detail in the figures.
  • the headpiece connection 24 opens into the first subspace 9.
  • the middle part 8 has two middle part connections 28, on each of which a middle part flange 29 are defined.
  • the middle part connections 28 open into the second subspace 11.
  • a first fluid is introduced into the subspace 11 during operation 1 of the heat exchanger 1 initiated.
  • a second fluid is introduced into the subspace 9 of the heat exchanger.
  • the central partial connection 28 for introducing the liquid first fluid is as far above as possible, so that the introduced first fluid flows through as many tubes 15 as possible.
  • the middle part connection 28 for diverting the vaporous first Strömüngsffens may open at any point above the highest level of liquid in operation in the subspace 1 1.
  • the heat exchanger jacket 5 has a substantially triangular cross-section.
  • the heat exchanger jacket 5 has a base part 34 which tapers in the figures upwards to a tip part 35.
  • the base part 34 is substantially aligned, ie with a deviation of ⁇ 15 degrees, parallel to the ground.
  • a curved or stepped tapered cross-sectional shape could also be employed. It is important that the heat exchanger 1 in the lower region of the base part 34 has a large cross-sectional area and has a decreasing cross-sectional area in the region of the tip part 35.
  • the lower region forms a liquid receiving region 36
  • the upper region with decreasing cross-sectional area at the tip part 35 forms a gas receiving region 37 during operation.
  • the middle part ports 28 open into the second subspace 11 in the region of the tip part 35, ie in the gas receiving region 37.
  • a dashed dividing line AA is shown to distinguish between the liquid receiving area 36 and the gas receiving area 37.
  • the dividing line AA could represent, for example, a maximum level of the liquid in operation.
  • the heat exchanger jacket 5 further has fluid channels 38, which can serve for insulating, for heating or for cooling the heat exchanger jacket 5.
  • the fluid channels 38 extend parallel at least in parts of the heat exchanger jacket 5. It is not necessary for the entire heat exchanger jacket 5 to have the fluid channels 38.
  • the fluid channels 38 are not flowed through by the first or second fluid and are sealed off from the surroundings of the heat exchanger 1 and with respect to the interior 6.
  • the fluid channels 38 may be filled with a gas, or be evacuated to effect isolation from the environment of the heat exchanger 1.
  • the fluid channels 38 are connected to the first subspace 9. In operation, the subspace 9 and the fluid channels 38 are thereby filled with the second fluid. Depending on whether the second fluid is a cold or a hot fluid, the heat exchanger jacket 5 is cooled or heated in the region of the fluid channels 38.
  • the heat exchanger 1 has a plurality of central parts 8.
  • the middle parts 8 are connected by the flanges 18 in series with each other and thus build a longer heat exchanger 1.
  • two middle parts 8 are each connected to one another via their one flange 18.
  • a flange 17 of a head part 7 is fastened in each case to the conclusion.
  • a second fluid introduced into the first head part 7 first flows through the first head part 7, then through the tubes 15 of the middle parts 8 and finally into the second head part 7.
  • the operation of the heat exchanger 1 will be described in detail with reference to FIGS. 4 and 5.
  • the first fluid is a cold fluid and the second fluid is a warm fluid.
  • the first fluid is to be vaporized in the heat exchanger 1.
  • the energy for evaporation is supplied by the second fluid.
  • the second fluid is introduced continuously through the head part port 24 of the head part 7 shown on the left in FIG.
  • the second fluid is distributed over the interior of the head portion 7 and flows through the tubes 15 of the middle part 8.
  • the second fluid flows successively through the tubes 15 of all consecutively arranged middle parts 8.
  • the first fluid After emerging from the tubes 15 on the right side of FIG. 5, the first fluid enters the interior of the right-side head part 7 and finally exits from the head part connection 24 of the right head part 7.
  • the first fluid also flows through the fluid passages 38 and heats the heat exchanger wall 5.
  • the second fluid is introduced and discharged continuously or stationarily.
  • the first fluid which is a fluid that is cold relative to the second fluid, is introduced in a phased manner through one of the midportions 28.
  • the introduced portion of the first fluid is relatively small compared to the volume of the second subspace 1 and is, for example, 20% of the volume of the second subspace 11 or less.
  • the first fluid flows down the tubes 15 of the central part 8 down to the base part 34.
  • the first fluid is introduced through one of the middle part ports 28 into the gas receiving area 37 at the top of the heat exchanger 1.
  • the first fluid initially receives a high power (heat energy) from the tubes 15 arranged in the vicinity of the tip part 36.
  • a portion of the introduced portion of first fluid evaporates already on the surface of the heated tubes 15 in Gasaufnah- me Colour 37.
  • the first fluid flows through a plurality of the continuously heated tubes 15 and thereby absorbs heat.
  • the tubes 15 and the second fluid passed therethrough form a large, warm mass that has a substantially constant temperature during evaporation of the first fluid.
  • the resulting vapor will be distributed in the subspace 11 of the central portion 8, and the vapor pressure will increase until the vapor is saturated at the temperature of the first fluid.
  • vapor barriers can adversely affect the operation of shell and tube heat exchangers.
  • local steam barriers can also arise here, which hinder the passage of liquid first fluid.
  • Such steam barriers in the embodiment described herein can never prevent the further inflow and evaporation of liquid second fluid.
  • the portion of the second fluid that is not immediately vaporized at the top or central tubes 15 will collect in the fluid receiving area 36 of the heat exchanger 1.
  • a plurality of tubes 15 are arranged, which are traversed by a large proportion of the second fluid and thus provide a large heat capacity.
  • the not yet vaporized first fluid can be evaporated quickly.
  • the liquid first fluid in the subspace 11 is heavier than the gaseous first fluid and will therefore collect by the action of gravity in the underlying fluid receiving area 36.
  • the vapor collects in the overlying gas receiving area 37.
  • the resulting vapor of the first fluid may be diverted via the other central part port 28, for example the right center port 28 (FIG. 4).
  • the vapor pressure within the region 11 decreases and any liquid portion of the first fluid in the lower liquid receiving region 36 of the heat exchanger 1 is continuously further evaporated. If the liquid portion of the first Strömüngsstoffs be completely evaporated, both the liquid receiving portion 36 and the gas receiving portion 37 are filled with steam, and there is a further heating of the vapor contained in the subspace 11.
  • the first fluid introduced through the one middle port 28 passes by gravity through a plurality of tubes 5 and eventually collects in the base 34 and fluid receiving area 36, respectively, which has more cross-sectional area and thus more hot tubes 15 than the upper portion of the tube Heat exchanger jacket 5.
  • the volume occupied by the vaporized first fluid (gas intake area 37) is small, which allows rapid pressure build-up.
  • the number of tubes that could be accommodated on a lower base part of the heat exchanger low.
  • FIG. 6 An embodiment of a heat exchanger V which offers advantages in the condensation of a gaseous first fluid is described below with reference to FIG.
  • the structure of the heat exchanger 1 "of Fig. 6 is substantially the same as the structure of the heat exchanger 1 of Figs. 1-5. Therefore, similar or corresponding features have the same reference numerals as are provided in Fig. 6. In the following mainly the differences of the heat exchanger 1 'with respect to the heat exchanger 1. It should be noted that variations ⁇ _
  • the heat exchanger 1 ' e.g. the fluid channels 38 and the modular design with several or different sized middle parts 8.
  • the heat exchanger V is operated in reverse order relative to gravity or to the earth's surface. That is, the tip portion 35 'is down in the direction of gravity, while the base portion 34' is up in the direction of gravity.
  • the base part 34' is substantially, i. with a deviation of ⁇ 15 degrees, aligned parallel to the ground.
  • the illustrated triangular cross-sectional shape is preferred, however, a curved or stepped tapered cross-sectional shape could also be used.
  • the small volume in the lower area forms a fluid receiving area 36 '
  • the large volume in the Spi zenteils 35' forms a gas receiving area 37 "in operation.” It is important that the heat exchanger 1 'in the upper part of the base part 34 a
  • the volume of the liquid receiving region 36 ' is smaller than the volume of the gas receiving region 37', since the cross section of the heat exchanger jacket 5 'tapers downwards, even in the case of the embodiment shown in FIG In the embodiment shown, the liquid receiving region 36 'is located in the direction of gravity below the gas receiving region 37'.
  • the head parts 7 ' are designed exactly as described above for the embodiment of FIGS. 1-5, but they are installed in the opposite direction with regard to the direction of gravity.
  • the middle part 8 ' in the embodiment of FIG. 6 also has two middle part connections 28', which open into the second subspace 1 1.
  • the first middle part connection 28 -1 opens in the area of the base part 34, ie in the gas receiving area 37 ', into the second subspace 11.
  • the first middle part connection 28 -1 can also be guided at a lower point into the second subspace 1 1, provided that it is ensured that liquid is not used during operation. 1 b ges first fluid flows into the mouth opening.
  • the second middle part connection 28 -2 for discharging liquid first fluid opens into the second subspace 11 in the region of the tip part 35 ', ie in the liquid receiving region 36'.
  • the second fluid introduced through the head portions 7 ' is a relatively cold fluid relative to the first fluid.
  • the cold second fluid in this case, in the same way as described above for the warm fluid, is introduced into the head part port of the one head part 7 ', through the tubes 15' of one (or more in-line) middle parts 8 'passed and led out of the head part connection 24' of the opposite head part 7 '.
  • the heat exchanger 1 ' is cooled continuously or stationarily by the second fluid.
  • gaseous first fluid is further introduced into the mid-section port 28'-1 in phases or continuously.
  • the vapor of the first fluid is hot and accumulates in the upper base 34 'of the heat exchanger 1, i. in the gas receiving area 37 '.
  • the steam is distributed and flows around a multiplicity of tubes 15 ', since the base part 34' has a comparatively larger cross-section and thus volume fraction with more tubes 15 'than the tip part 35'.
  • the vapor is cooled by the cool tubes 15 'and condensed liquid first fluid is formed.
  • This liquid first fluid passes by gravity down to the tip portion 35 'of the heat exchanger 1'.
  • the liquid first fluid (condensate) collects in the vicinity of the lower middle part port 28'-2.
  • the liquid first fluid may then be diverted via the lower center port 28'-2.
  • a support jacket 42 surrounds the heat exchanger jacket 5.
  • the support jacket 42 has a support structure 43 and a support belt 44.
  • the support structure 43 is disposed between the support belt 44 and the outer wall of the heat exchanger shell 5 and shaped to match.
  • the support belt 44 has the shape of a tube, in the inner diameter of the heat exchanger jacket 5 can be arranged.
  • the inner diameter of the support belt 44 is thus at least as large as the circumference of the heat exchanger shell 5.
  • the support structure 43 has a tubular outside and a substantially triangular cross-section according to the triangular outer shape of the heat exchanger shell 5.
  • the support structure 43 is made stiff and is suitable to transmit a force acting on the heat exchanger jacket 5 from the inside to the support belt 44.
  • the support structure 43 may be made of a glass fiber reinforced plastic (GRP) or metal struts.
  • GRP glass fiber reinforced plastic
  • the support structure 43 has a plurality of hollow interspaces 46 in three subregions 47 between the tips of the triangular heat exchanger jacket 5.
  • the provision of the gaps 46 results in material savings and weight savings.
  • a thermal insulation of the heat exchanger shell 5 can be achieved.
  • a manifold 50 is connected to the middle port 28 for introducing the first fluid.
  • the manifold 50 has a plurality of passages 51 through which the introduced first fluid can flow.
  • the distributor tube 50 runs parallel to the tubes 15 and is suitable for distributing introduced first flow medium via the inner space 6.
  • header ports 24, 24 "and the mid-port ports 28, 28'-1 and 28-2 may be located elsewhere if convenient for a compact or low cost design of the heat exchangers 1, 1 ' , 24 'there is no restriction, but they should be arranged so that the flow of the second fluid flowing through counteracts the lowest possible flow resistance.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

L'invention concerne un échangeur de chaleur. L'invention vise à permettre un changement rapide de l'état physique d'un premier fluide introduit lors d'un processus instationnaire dans un échangeur de chaleur. A cet effet, l'échangeur de chaleur selon l'invention comporte une enveloppe extérieure, qui définit un espace intérieur destiné à recevoir un premier fluide, et une pluralité d'ouvertures de passage étanches au fluide pour un deuxième fluide, lesquelles traversent l'espace intérieur de l'enveloppe extérieure de l'échangeur de chaleur. L'enveloppe extérieure de l'échangeur de chaleur comporte une zone de réception d'un liquide pour la réception d'un premier fluide liquide et une zone de réception d'un gaz pour la réception d'un premier fluide gazeux. Dans un mode de réalisation sous la forme d'un évaporateur, la section transversale de l'enveloppe extérieure de l'échangeur de chaleur se rétrécit à partir de la zone de réception du liquide vers la zone de réception du gaz, de sorte que la zone de réception du liquide présente un volume plus grand que celui de la zone de réception du gaz. Dans un mode de réalisation sous la forme d'un condenseur, la section transversale de l'enveloppe extérieure de l'échangeur de chaleur se rétrécit à partir de la zone de réception du gaz vers la zone de réception du liquide, de sorte que la zone de réception du gaz présente un volume plus grand que celui de la zone de réception du liquide. L'invention concerne par ailleurs un procédé d'évaporation et de condensation rapides d'un fluide.
PCT/EP2012/003040 2011-07-19 2012-07-19 Échangeur de chaleur WO2013010671A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110108094 DE102011108094A1 (de) 2011-07-19 2011-07-19 Wärmetauscher
EP102011108094.9 2011-07-19

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WO2013010671A2 true WO2013010671A2 (fr) 2013-01-24
WO2013010671A3 WO2013010671A3 (fr) 2013-04-25

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WO (1) WO2013010671A2 (fr)

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Publication number Priority date Publication date Assignee Title
DE565150C (de) * 1928-11-07 1932-11-26 Hugo Kosmack Waermeaustauscher
US3191396A (en) * 1963-01-14 1965-06-29 Carrier Corp Refrigeration system and apparatus for operation at low loads
DD262776A3 (de) * 1987-03-24 1988-12-14 Schwermasch Liebknecht Veb K Abdichtung fuer rohrbuendelwaermeuebertrager
US5839294A (en) * 1996-11-19 1998-11-24 Carrier Corporation Chiller with hybrid falling film evaporator
DE19722360A1 (de) * 1997-05-28 1998-12-03 Bayer Ag Verfahren und Vorrichtung zur Verbesserung des Wärmeüberganges
JP3572250B2 (ja) * 2000-10-24 2004-09-29 三菱重工業株式会社 冷凍機用凝縮器
US20070095512A1 (en) * 2005-10-31 2007-05-03 Wei Chen Shell and tube evaporator

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* Cited by examiner, † Cited by third party
Title
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WO2013010671A3 (fr) 2013-04-25
DE102011108094A1 (de) 2013-01-24

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