EP3717843A1 - Évaporateur - Google Patents

Évaporateur

Info

Publication number
EP3717843A1
EP3717843A1 EP18750236.4A EP18750236A EP3717843A1 EP 3717843 A1 EP3717843 A1 EP 3717843A1 EP 18750236 A EP18750236 A EP 18750236A EP 3717843 A1 EP3717843 A1 EP 3717843A1
Authority
EP
European Patent Office
Prior art keywords
tray
exchanger tubes
coolant fluid
shell
evaporator according
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.)
Granted
Application number
EP18750236.4A
Other languages
German (de)
English (en)
Other versions
EP3717843B1 (fr
Inventor
Loris GIANCOTTI
Giuseppe CENSI
Enrico GOLIN
Paolo CALACIURA
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.)
ONDA SpA
Original Assignee
ONDA SpA
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 ONDA SpA filed Critical ONDA SpA
Publication of EP3717843A1 publication Critical patent/EP3717843A1/fr
Application granted granted Critical
Publication of EP3717843B1 publication Critical patent/EP3717843B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F28D5/00—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, using the cooling effect of natural or forced evaporation
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • 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
    • F28D21/0017—Flooded core heat exchangers
    • 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
    • F28D5/00—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, using the cooling effect of natural or forced evaporation
    • F28D5/02—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, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions

Definitions

  • the present invention relates to an evaporator.
  • the present invention relates to an evaporator that is adapted to be used in refrigeration cycles based on the expansion of coolant gas, for conditioning and refrigeration applications.
  • cooling apparatuses known as refrigerators or chillers
  • refrigerators or chillers comprise, very basically, a compressor, an expansion device, an evaporator and a condenser.
  • cooling apparatuses are in use which are constituted, in essence, by heat exchangers, which generally have a containment enclosure provided with a cylindrical shell which accommodates a tube bundle, which is composed of a plurality of exchanger tubes, and in which a first working fluid, which is constituted by a coolant fluid and is arranged outside exchanger tubes, evaporates, thus absorbing heat from a second working fluid, which is constituted typically by water or by an aqueous solution, which flows inside the exchanger tubes and which is thus cooled.
  • heat exchangers which generally have a containment enclosure provided with a cylindrical shell which accommodates a tube bundle, which is composed of a plurality of exchanger tubes, and in which a first working fluid, which is constituted by a coolant fluid and is arranged outside exchanger tubes, evaporates, thus absorbing heat from a second working fluid, which is constituted typically by water or by an aqueous solution, which flows inside the exchanger tubes and which is thus cooled.
  • the coolant fluid is fed from above by a dispenser so as to form, on the outer surface of the exchanger tubes, a film of coolant fluid which by gravity falls progressively downward, flowing along the outer surface of the exchanger tubes.
  • the exchanger tubes are arranged inside a container which is designed to be flooded with the coolant in the liquid phase, so as to keep the exchanger tubes submerged in the coolant fluid, while this evaporates.
  • a drawback of falling film evaporators is constituted by the fact that traditionally the dispenser of this type of evaporator works with a biphasic coolant fluid, i.e. made up of a liquid phase and a vapor phase, such that it is difficult to obtain a good distribution of the coolant fluid over the exchanger tubes.
  • a drawback that is found with pool boiling evaporators derives from the fact that when the refrigerator works with a partial load, such that less thermal power needs to be exchanged, the level of coolant liquid inside the container of the evaporator generally decreases and some rows of exchanger tubes, arranged in the upper part, remain dry, or in a condition known in the jargon as "dry-out" ft is evident that under such operating conditions, which are the most common kind in a pool boiling evaporator, it is not possible to take full advantage of the heat exchange surface made available by the exchanger tubes.
  • pool boiling evaporators Another disadvantage of pool boiling evaporators is that they require a considerable quantity of coolant liquid for their operation, which however contrasts with current environmental regulations which require the use of coolants that have a low environmental impact but which are high cost.
  • hybrid evaporators have been proposed in which, in the upper part of the containment enclosure, the coolant liquid is deposited on the outer surface of some exchanger tubes of the tube bundle so as to form a film, so as to have an operation similar to that of falling film evaporators, while other exchanger tubes, located in the lower part of the enclosure, remain immersed in the coolant liquid, with an operation similar to that of pool boiling evaporators.
  • Hybrid evaporators therefore have a clear separation between the part that is operating like a falling film evaporator and the part that is operating like a pool boiling evaporator, with the consequence that the advantages of one part do not make it possible to fully compensate the drawbacks of the other.
  • each tray is supplied with the coolant liquid by way of a corresponding draining tube that originates from a dispenser arranged above the tube bundle or, according to another embodiment, exclusively by overflowing of the coolant liquid from the outer lateral edge of the immediately overlying tray.
  • CN 104819604 describes an evaporator with pool boiling operation, which is conceptually similar to what is described in CN2708220, with the difference that it has a dispenser that is rather complex in implementation, which is situated in a lateral region of the shell.
  • CN104819604 there are again trays which are fed by overflowing the coolant liquid from the outer lateral edge of the overlying trays, and the possibility is not prevented of drawing the droplets of coolant liquid into the intake line of the compressor.
  • CN205807912U also describes a pool boiling evaporator, similar to those of the prior art documents cited previously.
  • the evaporator has a lateral shell containing a bundle of tubes which is divided into a plurality of layers, each one of which is arranged in a respective tray for collecting the coolant liquid, which falls by overflowing from one tray to the underlying tray, while the part of the coolant liquid that collects in the lower region of the shell is made to boil by exchanger tubes arranged on the bottom.
  • the trays To enable each tray to collect the coolant liquid that overflows from the overlying tray, the trays have a lateral space occupation that progressively increases, going from the tray located highest toward the tray located lowest, with the consequence that the tube bundle has, in a plane perpendicular to the axis of the lateral wall, a triangular arrangement which however limits the maximum number of exchanger tubes that can be positioned inside the shell proper.
  • US2008149311A1 then describes an evaporator that operates using the falling film method, in the upper part, and which has flat distribution units, provided with holes, which make it possible to evenly distribute the coolant liquid that drips onto the exchanger tubes.
  • This evaporator too exhibits problems relating to the optimal distribution of the coolant liquid over the exchanger tubes, and offers no solution to the problem of drawing droplets of coolant liquid into the compressor.
  • an evaporator that operates using the falling film method in the upper and central part of the lateral shell and using the pool boiling method in the lower part.
  • the evaporator in this document has trays the purpose of which is to collect the coolant liquid in the lower part of the shell and to ensure, if there are compressors lubricated with oil, that the oil drains from the bottom.
  • a deflector structure the purpose of which is to capture the droplets of coolant liquid contained in the coolant vapor, but which however extends only to the upper region of the evaporator, such that it is not capable of offering valid assurances of certainty of interception of the droplets of coolant liquid drawn from the vapor originating from all the exchanger tubes of the evaporator.
  • the aim of the present invention is to provide an evaporator which is capable of improving the prior art in one or more of the above mentioned aspects.
  • an object of the invention is to provide an evaporator that is capable of positively combining the advantages of pool boiling evaporators with those of falling film evaporators, without exhibiting the respective drawbacks.
  • Another object of the invention is to provide an evaporator that is capable of operating efficiently even under partial load conditions, by preventing situations in which the exchanger tubes end up in dry-out.
  • Another object of the invention is to provide an evaporator that makes it possible to prevent the drawing of droplets of coolant liquid toward the compressor.
  • Another object of the invention is to provide an evaporator that makes it possible to have an even distribution of the exchanger tubes inside the shell.
  • Another object of the present invention is to overcome the drawbacks of the prior art in an alternative manner to any existing solutions.
  • Another object of the invention is to provide an evaporator that is highly reliable and which, furthermore, is easy to implement and at low cost.
  • Figure 1 is a perspective view of the evaporator according to the invention
  • Figure 2 is a perspective and longitudinal cross-sectional view of the evaporator according to the invention.
  • Figure 3 is a perspective and longitudinal cross-sectional view of the evaporator according to the invention from which the shell, the dispenser and a shielding wall have been omitted, in order to better show the interior of the evaporator;
  • Figure 4 is a perspective view of the evaporator according to the invention with the shell omitted;
  • Figure 5 is a perspective view of a tray for collecting and distributing the cooling liquid belonging to the evaporator according to the invention with a row of exchanger tubes that are associated therewith;
  • Figure 6 is a perspective view of a tray of the evaporator according to the invention without the exchanger tubes;
  • Figure 7 is a longitudinal cross-sectional view of the evaporator according to the invention.
  • Figure 8 is a transverse cross-sectional view of a detail of the evaporator according to the invention.
  • Figure 9 is a perspective and longitudinal cross-sectional view of the dispenser of coolant fluid arranged inside of the evaporator according to the invention.
  • Figure 10 is a cross-sectional view of some exchanger tubes of the evaporator according to the invention.
  • Figure 11 is a transverse cross-sectional view of the evaporator according to the invention.
  • Figure 12 is a perspective and transverse cross-sectional view of the evaporator according to the invention.
  • Figure 13 is a perspective and transverse cross-sectional view from a different angle with respect to Figure 12 of the evaporator according to the invention.
  • Figure 14 is a perspective view of different embodiment of the evaporator according to the invention, with several components omitted in order to show a first group of exchanger tubes and the corresponding trays;
  • Figure 15 is an enlarged-scale detail of Figure 14;
  • Figure 16 is a schematic perspective view of a possible embodiment of the trays for collecting and distributing the liquid coolant fluid, in a condition of operation;
  • Figure 17 is a transverse cross-sectional view of the tray in Figure 16;
  • Figure 18 is a schematic perspective view of the embodiment in Figure 16 in a different condition of operation
  • Figure 19 is a transverse cross-sectional view of the tray in Figure 18.
  • the evaporator according to the invention comprises an enclosure 2 which is provided with a lateral confinement shell 3 with a substantially horizontal axis, which internally defines a heat exchange chamber 3 a.
  • a dispenser 4 Accommodated inside the shell 3 is a dispenser 4, the function of which is to introduce a coolant fluid into the heat exchange chamber 3a of the shell 3, such fluid being fed to the dispenser 4 by way of a connector 5 passing through the shell 3.
  • the coolant fluid that is fed to the dispenser 4 is, generally, in a biphasic condition, i.e. it is made up of a liquid phase, hereinafter referred to as liquid coolant fluid, and by a vapor phase, hereinafter referred to as vapor of the coolant fluid.
  • the dispenser 4 comprises a distribution duct 4a, which extends substantially parallel to the axis of the shell 3 and is connected to the connector 5, by way of an own intake port 5 a, which is arranged substantially in a central position along its longitudinal extension.
  • the distribution duct 4a has a polygonal cross-section, with a flat lower wall 4b which has a plurality of delivery openings 4c from which the coolant fluid is drained downward in the direction of the tube bundle 6.
  • the exchanger tubes 7 are designed to be passed through by a fluid to be cooled, which is constituted, for example, by water or by an aqueous solution.
  • the shell 3 is closed, at one end, by a first head 8a, which is provided with an entry connection 9a and with an exit connection 9b for the fluid to be cooled, and, at its opposite end, by a second head 8b.
  • a first head 8a which is provided with an entry connection 9a and with an exit connection 9b for the fluid to be cooled, and, at its opposite end, by a second head 8b.
  • channels 10 for the fluid to be cooled to circulate which are connected to the inside of the exchanger tubes 7, in order to allow the fluid to be cooled, once it is introduced into the shell 3 through the entry connection 9a, to follow a path, inside the exchanger tubes 7, with various passes along the longitudinal extension of the shell 3, prior to exiting from the wall through the exit connection 9b, as shown schematically in Figure 7.
  • the tube bundle 6 comprises at least one first group of exchanger tubes 7 which is arranged along rows which extend on substantially horizontal and mutually superimposed planes.
  • each tray 11 has, along at least one first longitudinal edge, at least one first containment sidewall 12 which is adapted to allow the liquid coolant fluid contained therein to fall by overflowing into an underlying tray 11.
  • each tray is furthermore provided in its bottom 11a with a plurality of openings for draining l ib the liquid coolant fluid, such holes being arranged at the exchanger tubes 7 contained in the underlying tray 11 in order to allow the fall of the liquid coolant fluid from each tray 11 onto the outer surface of the exchanger tubes 7 placed below it.
  • each tray 11 is furthermore provided with a second containment sidewall 13, which extends upward so as to contain, at least partially, the overlying tray 11.
  • second containment sidewall 13 is arranged along a second longitudinal edge of the tray 11, opposite to the first longitudinal edge along which the first containment sidewall 12 is present.
  • the second containment sidewall 13 has a portion, the extension of which is inclined toward the outside of the corresponding tray 11 , which conveniently is connected to a vertical portion that protrudes upward from the bottom 11a of the tray 11 so as to create, between the second containment sidewall 13 of each tray 11 and the overlying tray 11 , a space for the outflow of the vapor produced by the boiling of the liquid coolant fluid contained in each tray 11.
  • the trays 11 In their succession along a vertical direction, the trays 11 present their first longitudinal edge, with the corresponding first containment sidewall 12, alternately directed toward one side of the shell 3 or toward the opposite side.
  • Such alternating arrangement, toward one side or the other of the shell 3, of the first containment sidewall 12 of the various trays 11 allows an arrangement of the exchanger tubes 7 that is square or rectangular, when seen in transverse cross-section, with the consequence of enabling the positioning in the shell 3 of a greater number of exchanger tubes 7 with respect to triangular arrangements, as in the prior art.
  • the trays 11 have the corresponding first containment sidewall 12 arranged laterally spaced apart toward the inside of the shell 3 with respect to the second confinement sidewall 13 of the underlying tray 11, so that the liquid coolant fluid overflowing from each tray 11 over the corresponding first containment sidewall 12 can fall, without losses, into the underlying tray 11.
  • the openings for draining l ib defined in the bottom 11a of the trays 11 have a size that is calibrated to balance the quantity of liquid coolant fluid that enters each tray 11 with the quantity of coolant fluid that exits in vapor form from each tray 11.
  • equal importance lies with the total passage section made available for the liquid coolant fluid by the set of the openings for draining l ib, in combination with the size of each one of these openings.
  • the size of the openings for draining l ib can be the same for all the trays 11 or different from tray to tray.
  • the sizes of the openings for draining l ib can conveniently vary substantially from 1 mm to 20 mm.
  • the size of the openings for draining l ib to progressively decrease starting from the tray 11 located highest and proceeding progressively toward the tray located lowest.
  • each tray 11 provides means of flow control which are adapted to at least partially block the openings for draining l ib and can move on command in order to vary the degree of opening of the openings for draining l ib.
  • means of flow control can comprise, for each tray 11, a plate 110 which is provided with passage openings 111, which have, conveniently, a size and an arrangement that are substantially the same as the openings for draining l ib.
  • the plate 110 is slideably mounted with respect to the bottom 11a of the respective tray 11 in order to pass from a first condition, shown in Figures 18 and 19, in which its passage openings 111 are arranged in alignment with the openings for draining l ib of the corresponding tray 11, to at least one second condition, shown in Figures 16 and 17, in which the plate 110 at least partially occludes the openings for draining l ib of the corresponding tray l ib, and vice versa.
  • each tray 11 is stacked by interlocking on the underlying tray 11, advantageously without requiring welding or other types of fixing, so as to provide a supporting structure capable of supporting at least the exchanger tubes 7 of the first group.
  • the trays 11 are arranged alternately staggered toward one side or toward the other side of the shell 3, so as to create between each tray 11 and the overlying tray the space for the passage of the liquid coolant fluid overflowing over the first confinement sidewall 12 of the overlying tray and for the egress from each tray 11 of the vapor of the coolant fluid.
  • each tray 11 at its longitudinal ends, arranged along its axis of extension parallel to the axis of the shell 3, is provided, advantageously, with containment end walls 14 which define receptacles 15 for the respective exchanger tubes 7, which are constituted by holes that are passed through hermetically by the exchanger tubes 7, so that each tray 11 can also act as a support per the corresponding exchanger tubes 7.
  • the trays 11 are provided with the same shape and each one is arranged rotated by 180° about a vertical axis with respect to the two contiguous ones, in succession along the direction of stacking, so as to alternately present the first containment sidewall 12 toward one side or toward the other side of the shell 3.
  • each tray 11 is provided with at least one supporting partition 16 for the overlying tray 11.
  • each tray 11 has a pair of supporting partitions 16, which are arranged at its opposing longitudinal ends and are preferably defined continuously with the containment end walls 14. Each one of such supporting partitions 16 protrudes laterally outward with respect to the first confinement sidewall 12 of each tray 11.
  • such supporting partitions 16 define a positioning abutment for the tray 11 stacked on top of the corresponding tray 11.
  • the supporting partitions 16 define, in a position laterally spaced apart and outward with respect to the first containment sidewall 12 of the corresponding tray 11, at least one lateral abutment shoulder 16a, on which the second confinement sidewall 13 of the tray 11 stacked above is placed, so as to ensure the arrangement in a mutually spaced apart position between the first confinement sidewall 12 of each tray 11 and the second confinement sidewall 13 of the underlying tray.
  • the vapor produced by the boiling of the liquid coolant fluid is conveyed outside the shell 3 by way of an exit connector 17 defined in the upper part of the shell 3.
  • an exit connector 17 defined in the upper part of the shell 3.
  • shielding wall 18 which makes it possible to prevent the egress, by way of an exit connector 17, of droplets of liquid together with the vapor of the coolant fluid.
  • the shielding wall 18 extends downward, with two portions that are mutually opposite with respect to the tube bundle 6, and defines, for the vapor of the coolant fluid exiting from the trays 11, at least one respective first flow channel 18a and at least one respective second flow channel 18b.
  • the first flow channel 18a extends downward and is delimited between the tube bundle 6 and the shielding wall 18, while the second flow channel 18b extends upward and is delimited between the shell 3 and the shielding wall 18.
  • the shielding wall is arc-shaped with the concavity directed toward the tube bundle 6 so as to cover the upper part thereof and at least partially the lateral part thereof and is passed through by the intake port 5a of the distribution duct 4a.
  • the shielding wall 18 is supported at its longitudinal ends by a pair of tuyere plates 19a and 19b, between which the shell 3 is interposed and to which the heads 8a and 8b are fixed, on the side thereof opposite the shell 3.
  • the first group of exchanger tubes 7 i.e. the exchanger tubes 7 arranged in the trays 11
  • a pump or an ejection system to make the liquid coolant fluid recirculate from the bottom of the shell to the connector 5.
  • At least one discharge outlet 20 which is provided, conveniently, with an adapted connector 21, in order to allow, in the eventuality that the evaporator is used in refrigeration systems in which oil- lubricated compressors are used, the extraction from the shell 3 of the oil originating from the compressor, so as to permit the return of same to the compressor.
  • the coolant fluid generally in the form of a biphasic mixture composed of a liquid phase and a vapor phase, enters, from the upper part of the shell 3, through the connector 5, into the dispenser 4, feeding the distribution duct 4a, from which it exits, through the delivery openings 4c, so as to be evenly distributed in the first tray 11 which is arranged higher than the others.
  • the fluid to be cooled is made to enter the shell 3, through the entry connection 9a, so that it can run through the exchanger tubes 7 until it arrives at the exit connection as shown in Figure 7, where arrows show the possible path of the fluid to be cooled.
  • the coolant fluid coming into contact with the exchanger tubes 7 passed through by the fluid to be cooled, starts to evaporate and the two phases, vapor and liquid, of the coolant fluid separate, following different paths.
  • the liquid coolant fluid which does not evaporate, falls onto the row of exchanger tubes 7 arranged in the second tray 11 , arranged below the first tray 11, in two possible ways: either by overflowing over the first confinement sidewall 12 or by passing through the openings for draining l ib.
  • a part of the liquid coolant fluid falls into the second tray 11 by overflowing, while another part of the liquid coolant fluid can fall at each exchanger tube 7 of the underlying row arranged in the second tray 11, through the openings for draining l ib arranged on the bottom 11a of the first tray 11, as shown in Figure 8, with a falling film operating method.
  • the liquid coolant fluid gathered in the bottom of the shell 3 is made to evaporate by the exchanger tubes 7 of the second group, with a pool boiling operating method.
  • the invention fully achieves the intended aim and objects, in that, by virtue of the presence of the trays provided with openings for draining and the possibility for the coolant liquid to overflow from them, it makes it possible to take better advantage of the exchange surface of the exchanger tubes with respect to a traditional falling film evaporator, and, by virtue of the openings for draining arranged on the bottom of the trays, it makes it possible to prevent, under partial load conditions, some rows of exchanger tubes from remaining dry, with a consequent improvement of the wettability of the exchanger tubes with respect to a traditional pool boiling evaporator as well.
  • Another advantage of the evaporator according to the invention is that it enables a reduction of the quantity of coolant required with respect to a pool boiling evaporator.

Landscapes

  • 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)

Abstract

L'invention concerne un évaporateur comprenant une enceinte (2) munie d'une coque de confinement latéral (3) à axe sensiblement horizontal, pouvant recevoir intérieurement un distributeur (4) d'un fluide de refroidissement et au moins un faisceau de tubes (6), agencé en dessous du distributeur (4) et comprenant une pluralité de tubes d'échangeur (7) traversés par un fluide à refroidir. Au moins un premier groupe de tubes d'échangeur (7) est agencé le long de plusieurs rangées s'étendant sur des plans sensiblement horizontaux et superposés les uns aux autres. Les tubes d'échangeur (7) de chaque rangée sont agencés dans au moins un plateau respectif (11) afin de collecter et de distribuer le fluide de refroidissement liquide. Chaque plateau (11) comporte, le long d'au moins un premier bord longitudinal, au moins une première paroi latérale de confinement (12) conçue pour permettre au fluide de refroidissement liquide contenu dans le plateau de tomber par débordement dans un plateau sous-jacent (11), le plateau étant muni dans sa partie inférieure (11a) d'une pluralité d'ouvertures permettant d'évacuer (11b) le fluide de refroidissement liquide.
EP18750236.4A 2017-11-28 2018-08-13 Évaporateur Active EP3717843B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT201700136156 2017-11-28
PCT/EP2018/071947 WO2019105607A1 (fr) 2017-11-28 2018-08-13 Évaporateur

Publications (2)

Publication Number Publication Date
EP3717843A1 true EP3717843A1 (fr) 2020-10-07
EP3717843B1 EP3717843B1 (fr) 2021-09-08

Family

ID=61581526

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18750236.4A Active EP3717843B1 (fr) 2017-11-28 2018-08-13 Évaporateur

Country Status (3)

Country Link
US (1) US20200370802A1 (fr)
EP (1) EP3717843B1 (fr)
WO (1) WO2019105607A1 (fr)

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Publication number Priority date Publication date Assignee Title
SG11202009879SA (en) * 2018-04-06 2020-11-27 Carrier Corp Integrated separator and distributor
FR3097307B1 (fr) * 2019-06-17 2021-05-14 Naval Energies Évaporateur d’un fluide de travail pour une centrale ETM comportant une coiffe

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JP2004176969A (ja) * 2002-11-26 2004-06-24 Kubota Corp 吸収式ヒートポンプ
CN2708220Y (zh) 2004-06-24 2005-07-06 上海交通大学 制冷装置用高效托盘低压蒸发器
TWI320094B (en) 2006-12-21 2010-02-01 Spray type heat exchang device
US9677818B2 (en) 2013-07-11 2017-06-13 Daikin Applied Americas Inc. Heat exchanger
CN104819604A (zh) 2015-04-27 2015-08-05 上海理工大学 一种分层式的满液式蒸发器
CN205807912U (zh) 2016-06-14 2016-12-14 青岛海尔智能技术研发有限公司 多层满液式蒸发器及制冷、空调系统

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