EP3748271B1 - Évaporateur de faisceau de tubes hybride doté d'un distributeur de fluide réfrigérant de service amélioré - Google Patents

Évaporateur de faisceau de tubes hybride doté d'un distributeur de fluide réfrigérant de service amélioré Download PDF

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Publication number
EP3748271B1
EP3748271B1 EP20175899.2A EP20175899A EP3748271B1 EP 3748271 B1 EP3748271 B1 EP 3748271B1 EP 20175899 A EP20175899 A EP 20175899A EP 3748271 B1 EP3748271 B1 EP 3748271B1
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EP
European Patent Office
Prior art keywords
tubes
evaporator
tube bundle
horizontal
refrigerant fluid
Prior art date
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Active
Application number
EP20175899.2A
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German (de)
English (en)
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EP3748271A1 (fr
Inventor
Mariano Covolo
Giacomo RUARO
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.)
Mitsubishi Electric Hydronics and IT Cooling Systems SpA
Original Assignee
Mitsubishi Electric Hydronics and IT Cooling Systems 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.)
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Publication of EP3748271A1 publication Critical patent/EP3748271A1/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
    • 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
    • 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
    • F28D3/00—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 flows in a continuous film, or trickles freely, over the conduits
    • F28D3/04—Distributing arrangements
    • 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
    • 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
    • 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
    • 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
    • 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
    • F28F2009/226—Transversal partitions

Definitions

  • the present invention refers to an improved hybrid tube bundle evaporator having a low-load and high performance for vapour compression refrigeration circuits.
  • tube bundle and shell evaporators for known-type vapour compression refrigeration circuits, constituted substantially by a tube bundle inside a recipient usually having a cylindrical shape with a horizontal axis, usually known as a "shell", and closed at the ends.
  • the device is crossed by two fluid currents: a current corresponding to the process fluid, i.e. the fluid that is to be cooled, which flows on the "tube-side", that is, inside the tubes, while the other current corresponds to the service fluid, i.e. the refrigerant fluid used as the vector of the heat exchange and which flows on the "shell-side", i.e. in the space delimited between the inner surface of the shell and the outer surfaces of the tubes; the large outer surfaces of the tubes, generally having a modest diameter and in a large number, enable heat exchange of large quantities of heat.
  • the pathway of the tube bundle inside the shell can be straight, with a parallel axis to the longitudinal axis of the evaporator, from an inlet head to the opposite outlet head, or can be straight but with an outward and return pathway over the whole length of the shell, with an inlet and outlet at the same evaporator head; the type depends on the general characteristics of the system and the design choices and expected performances.
  • the process that takes place inside an evaporator in a refrigeration circuit is a continuous process, through which the flow of the service refrigerant fluid at a lower temperature subtracts heat from the process fluid flow at a higher temperature, and in turn heats up and changes from the liquid phase to the gaseous phase.
  • the flooded type i.e. with the tube bundle completely immersed in the service fluid in the moist phase
  • the low-load flooded type in which the service fluid load is reduced coherently with the setting and control of other parameters of the system
  • the falling film type in which the tubes are sprinkled by the service refrigerant fluid which falls in cascade
  • the spray type where the service refrigerant fluid is sprayed onto the tubes.
  • hybrid Another type, known as hybrid, pairs the characteristics of the low-load flooded type with those of the falling film type.
  • US 5638691 A discloses a horizontal tube bundle evaporator according to the preamble of claim 1.
  • the technical task of the present invention is, therefore, to provide a tube bundle evaporator which obviates the above-described technical drawbacks of the prior art.
  • an object of the invention is to realise a tube bundle evaporator of a hybrid type, which unites the characteristics of the low-load flooded type and of the falling film type, thus obviating the drawbacks of both.
  • a further aim of the invention is to realise a tube bundle evaporator of a hybrid type which optimises the fluid-dynamics of the service fluid and the heat exchange with the process flow.
  • a further aim of the invention is to realise a tube bundle evaporator of a hybrid type from which the service fluid in outlet can be returned to the refrigeration circuit prevalently in the gaseous phase.
  • a further aim of the invention is to realise a tube bundle evaporator of a hybrid type which improves the distribution system of the service fluid on the tubes.
  • a horizontal axis hybrid tube bundle evaporator is denoted in its entirety by reference number 1, essentially constituted by a cylindrical shell 2, by two closing heads 3A and 3B, a tube bundle 4 thus identified in its entirety and contained inside the shell 2 where the tubes individually perform an outward and return pathway parallel to the longitudinal horizontal axis and over the whole length of the shell 2, an inlet 5 in a closing head 3A of the process fluid to be cooled and an outlet 6 in a closing head 3A of the cooled process fluid;
  • the evaporator 1 further has two inlets 7A and 7B of the service refrigerant fluid in the liquid state in a lower lateral zone of the shell 2, symmetrically arranged in the direction of the longitudinal axis with respect to an outlet 8 of the service refrigerant fluid in the gaseous state positioned in an upper lateral zone of the shell 2, and an optical viewer 9 for controlling the level of the service refrigerant fluid on the lower lateral wall of the shell 2.
  • a first number of tubes 41 of the tube bundle 4 is positioned in a lower zone 21 of the evaporator 1 flooded by the service fluid, a second number of tubes 42 is positioned in an upper zone 22 of the evaporator 1 above the first number of tubes 41.
  • a distributor 70 of the service refrigerant fluid is positioned in an upper zone 22 of the evaporator 1 above the second number of tubes 42 of the tube bundle 4, and is constituted by two opposite collectors 71A and 71B respectively connected to the inlets 7A and 7B of the refrigerant fluid in the evaporator 1, and mounted with a perpendicular axis to the longitudinal axis of the evaporator 1 and of the tube bundle 4.
  • a plurality of straight distribution tubes 72i is perpendicularly connected to both collectors 71A and 71B, by means of respective fittings 73i at the ends thereof, with a longitudinal axis parallel to the axis of the evaporator 1 and the tube bundle 4.
  • the tube bundle 4 is supported inside the shell 2 by a plurality of transversal support plates 80i perpendicular to the longitudinal axis of the tubes and the evaporator 1, appropriately perforated for guided and continuous passage of the single tubes and appropriately configured for mounting inside the evaporator 1.
  • a further plurality of vertical longitudinal secondary partitions 81i advantageously joint-fixed to the transversal support plates 80i longitudinally divides, into a plurality of sectors, the tubes of the second number of tubes 42 of the tube bundle 4 in the zone 22 of the evaporator 1.
  • the transversal support plates 80i further divide the longitudinal sectors into sub-units.
  • a plurality of longitudinal deflecting fins 85i is further fixed on the longitudinal partitions 81i, again with the aim of equalising the flow distribution of the refrigerant fluid by force of gravity on the tubes of the second number of tubes 42.
  • a special primary vertical partition 88 longitudinally extended, conjoined at the top thereof to the internal lateral surface of the shell 2 and inferiorly extending downwards up to a suitable distance from the free surface of the flooded lower zone 21 for collecting the refrigerant fluid in the liquid state.
  • the head 3A has the inlet collector 51 connected to the inlet 5 of the process fluid in the evaporator 1, and an outlet collector 61 connected to the outlet 6 of the cooled process fluid; the inlet collector 51 supplies the first number of tubes 41, the third number of tubes 43 and the lower group of tubes of said second number of tubes 42; the outlet collector 61 is supplied by an upper group of tubes of said second number of tubes 42.
  • the process fluid to be cooled is introduced into the evaporator 1 through the inlet 5 in the head 3A, and thus in the inlet collector 51 from which it is distributed into the first number of tubes 41, the third number of tubes 43 and the lower group of tubes of the second number of tubes 42.
  • the upper group of tubes of the second number of tubes 42 thus returns to the outlet collector 61 in the head 3A, from which the appropriately-cooled process fluid is collected and connected to the outlet 6 from the evaporator 1 and reinjected into the cooling system circulation of which the evaporator is a part.
  • the service refrigerant fluid in the liquid state coming from other lines of the cooling system and appropriately moved by movement means outside the evaporator, is injected into the evaporator 1 symmetrically, given equal conditions of temperature and pressure, through the two inlets 7A and 7B positioned in the lower lateral zone of the shell 2 the inside of which corresponds to the second upper lateral chamber 24 of the evaporator 1.
  • the two opposite collectors 71A and 71B are respectively connected to the inlets 7A and 7B of the fluid distributor 70 of the service refrigerant fluid, via which collectors and via the successive plurality of fittings 73i derived therefrom, the refrigerant fluid reaches the plurality of distribution tubes 72i from opposite ends.
  • the supply of the refrigerant fluid from the collectors 71A and 71B to the opposite ends of the plurality of distribution tubes 72i advantageously guarantees the homogeneity of the temperature and pressure conditions of the refrigerant fluid in each tube and inside each of the tubes of the plurality of distribution tubes 72i.
  • the refrigerant fluid locates, in the plurality of distribution tubes 72i, the plurality of lower longitudinal dispensing openings 74i, through which the refrigerating fluid in the liquid state sprinkles the second number of tubes 42 by force of gravity.
  • the heat exchange by convection, between the refrigerant flow and the outer walls of the second number of tubes 42 inside which the process fluid flows at a higher temperature causes, among other things, the raising of the temperature of the refrigerant fluid, and a partial passage thereof from the liquid phase to the mixed-gaseous phase ("mist") and to the gaseous phase.
  • the plurality of longitudinal deflecting fins 85i fixed on the longitudinal partitions 81i advantageously facilitates the detachment of the refrigerant fluid that might have accumulated on the longitudinal partitions 81i during the liquid phase and a better and progressive redistribution on the rows of the second number of tubes 42 positioned inferiorly of the longitudinal deflecting fins 85i.
  • the portion of refrigerant fluid still in the liquid phase after having sprayed the second number of tubes 42 by force of gravity, precipitates and is collected (floods) in the lower zone 21 of the evaporator 1, where the first number of tubes 41 of the tube bundle 4 is positioned and where the heat exchange is actuated in a static form by conduction between the refrigerant fluid in the liquid phase and the outer walls of the first number of tubes 41 of the tube bundle 4 which remains completely immersed (flooded) in the fluid.
  • the portion of refrigerant fluid in the gaseous and mixed-gaseous phase, created for the heat exchange realised with interaction of the refrigerant fluid and the second number of tubes 42 in the first upper chamber 23 of the evaporator 1, physically and naturally tending to vertically rise towards the top of the first upper chamber 23, is advantageously aspirated by means of an appropriate depression created by aspirating means outside the evaporator 1 at the outlet 8 from the shell 2, positioned at the upper lateral chamber 24 of the evaporator 1.
  • the tortuous pathway of the refrigerant fluid in the gaseous and mixed-gaseous phase advantageously strikes, in the inversion from descending portion of circuit to rising portion of circuit, the upper horizontal row 44 of tubes of the first number of tubes 41 and thus actuates a heat exchange which tends to reduce the moisture still remaining in the mixed-gaseous phase.
  • the third number of tubes 43 is also housed in the second upper lateral chamber 24 and is arranged at a higher level than the horizontal row of tubes 44, which is further struck by the refrigerant fluid in the gaseous and mixed-gaseous phase in a rising portion of circuit of the tortuous pathway, actuating a further heat exchange which tends to eliminate the moisture still residual in the mixed-gaseous phase (mist).
  • the service refrigerant fluid is advantageously thus distanced by the evaporator 1 from the outlet 8 and injected into the circuit of the refrigeration system in prevalently gaseous phase.
  • the horizontal tube bundle evaporator of the invention is characterised by the specific construction of the distributor 70.
  • the tubes 72i are supplied at both ends by opposite tubular collectors 71a, 71B.
  • the tubes 72i can have various shapes, dimensions and arrangements.
  • the tubes 72i are preferably straight, cylindrical, and are orientated horizontally in the longitudinal direction of the evaporator 1.
  • the tubes 72i do not necessarily need to be all positioned at the same height, in particular, to optimise the occupation of the space inside the shell 2, the arrangement of the tubes 72i can be adapted to the internal profile of the shell 2.
  • the distribution tubes 72i can be arranged following the internal profile of the shell 2, with the central tubes 72i higher and the lateral tubes 72i gradually lower.
  • the distribution tubes 72i can be all of identical transversal dimensions, inside diameter and external diameter in the case of the cylindrical shape.
  • the central tubes 72i can have an internal passage section that is greater than the passage section of the lateral tubes 72i and longitudinal openings 74i having a greater area than that of the lateral tubes 72i.
  • the distribution tubes 72i can be supported directly by the transversal support plates 80i.
  • the transversal support plates 80i can therefore have first support holes of the tube bundle 4 and, above the first holes, second support holes of the distribution tubes 72i.
  • the lower longitudinal dispensing openings 74i are preferably formed by laser cutting so as to have high dimensional precision.
  • the number, shape and dimension of the lower longitudinal dispensing openings 74i can vary.
  • the lower longitudinal dispensing openings 74i are straight slots. In an embodiment the lower longitudinal dispensing openings 74i are slots having a constant width.
  • the lower longitudinal dispensing openings 74i are slots having a constant length.
  • the lower longitudinal dispensing openings 74i are slots having, from the end of the distribution tubes 72i towards the centre of the distribution tubes 72i, a constant width and a progressively increasing length, or a constant length and a progressively increasing width, or a width and a length that are progressively increasing, or an increasing width in the case of a single longitudinal dispensing opening 74i.
  • the lower longitudinal dispensing openings 74i are slots having, from the end of the distribution tubes 72i connected to the collector towards the free end of the distribution tubes 72i, a constant width and a progressively increasing length, or a constant length and a progressively increasing width, or a progressively increasing width and length, or an increasing width in the case of a single longitudinal dispensing opening 74i.
  • the distribution tubes 71i can project below the lower axial generatrix of the tubular collectors 71A, 71B.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (12)

  1. Évaporateur de faisceau de tubes horizontal (1) s'étendant longitudinalement le long d'un axe horizontal, comprenant une coque (2), un faisceau de tubes (4) logé à l'intérieur de la coque, un fluide réfrigérant côté coque, un fluide réfrigéré côté tube, une zone inférieure (21) dudit évaporateur (1) inondée par le fluide réfrigérant à l'état liquide et contenant un premier nombre de tubes (41) dudit faisceau de tubes (4), comprenant un distributeur de fluide réfrigérant de service (70) positionné dans une zone supérieure (22) dudit évaporateur (1), comprenant une pluralité de tubes de distribution (72i) pourvus d'une ou plusieurs ouvertures de distribution longitudinales inférieures (74i) pour distribuer le fluide réfrigérant à l'état liquide par chute libre sur un second nombre de tubes (42) du faisceau de tubes (4), lequel deuxième nombre de tubes (42) est positionné à l'extérieur de ladite zone inférieure (21) au-dessus dudit premier nombre de tubes (41), ladite pluralité de tubes de distribution (72i) étant superposée longitudinalement sur ledit deuxième nombre de tubes (42) dudit faisceau de tubes (4), caractérisé en ce que ledit distributeur de fluide réfrigérant de service (70) comprend un premier collecteur tubulaire d'alimentation (71A) d'une première extrémité desdits tubes de distribution (72i) et un deuxième collecteur tubulaire d'alimentation (71B) d'une deuxième extrémité desdits tubes de distribution (72i).
  2. Évaporateur horizontal selon la revendication précédente, dans lequel ledit distributeur de fluide réfrigérant de service (70) comprend une pluralité de raccords angulaires (73i) entre ledit au moins un premier collecteur tubulaire (71A) et ladite pluralité de tubes de distribution (71i).
  3. Évaporateur horizontal selon la revendication précédente, dans lequel lesdits raccords angulaires (73i) se connectent audit premier collecteur tubulaire (71A) en dessous du plan longitudinal médian de celuici.
  4. Évaporateur horizontal selon la revendication précédente, dans lequel lesdits tubes de distribution (71i) font saillie en dessous de la génératrice axiale inférieure dudit au moins un premier collecteur tubulaire (71A).
  5. Évaporateur horizontal selon la revendication 1, dans lequel lesdits tubes de distribution (72i) sont droits.
  6. Évaporateur horizontal selon la revendication 1, dans lequel lesdits tubes de distribution (72i) sont horizontaux.
  7. Évaporateur horizontal selon la revendication 1, dans lequel lesdits tubes de distribution (72i) sont disposés avec leur axe longitudinal parallèle audit axe horizontal dudit évaporateur (1).
  8. Évaporateur horizontal selon la revendication 1, dans lequel lesdits tubes de distribution (72i) sont disposés à différentes hauteurs.
  9. Évaporateur horizontal selon la revendication 1, dans lequel lesdits tubes de distribution (72i) sont cylindriques.
  10. Évaporateur horizontal selon la revendication 1, qui a, à l'intérieur de ladite coque (2), une pluralité de plaques de support transversales (80i) ayant des premiers trous de support pour supporter ledit faisceau de tubes (4), et, au-dessus desdits premiers trous, des seconds trous de support desdits tubes de distribution (72i).
  11. Évaporateur horizontal selon la revendication 1, dans lequel lesdits tubes de distribution (72i) ont un diamètre intérieur égal.
  12. Circuit de réfrigération par compression de vapeur qui comprend un évaporateur (1) selon l'une quelconque des revendications précédentes.
EP20175899.2A 2019-06-05 2020-05-21 Évaporateur de faisceau de tubes hybride doté d'un distributeur de fluide réfrigérant de service amélioré Active EP3748271B1 (fr)

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IT201900008139 2019-06-05

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EP3748271B1 true EP3748271B1 (fr) 2022-08-24

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202100029945A1 (it) * 2021-11-26 2023-05-26 Mitsubishi Electric Hydronics & It Cooling Systems S P A Assieme di evaporatore ibrido migliorato

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2807439B1 (fr) * 2012-01-27 2017-08-23 Carrier Corporation Évaporateur et distributeur de liquide

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5588596A (en) * 1995-05-25 1996-12-31 American Standard Inc. Falling film evaporator with refrigerant distribution system
ATE554355T1 (de) * 2008-01-11 2012-05-15 Johnson Controls Tech Co Dampfkompressionssystem

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2807439B1 (fr) * 2012-01-27 2017-08-23 Carrier Corporation Évaporateur et distributeur de liquide

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