EP3748270B1 - Hybridrohrbündelverdampfer - Google Patents

Hybridrohrbündelverdampfer Download PDF

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Publication number
EP3748270B1
EP3748270B1 EP20175886.9A EP20175886A EP3748270B1 EP 3748270 B1 EP3748270 B1 EP 3748270B1 EP 20175886 A EP20175886 A EP 20175886A EP 3748270 B1 EP3748270 B1 EP 3748270B1
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EP
European Patent Office
Prior art keywords
tubes
evaporator
tube bundle
shell
refrigerant fluid
Prior art date
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Active
Application number
EP20175886.9A
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English (en)
French (fr)
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EP3748270A1 (de
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
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Mitsubishi Electric Hydronics and IT Cooling Systems SpA
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Publication of EP3748270A1 publication Critical patent/EP3748270A1/de
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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
    • F28D7/1607—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 particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • 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
    • 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

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 refrigerating 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 2010/276130 A1 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 tube bundle.
  • a further aim of the invention is to realise a tube bundle evaporator of a hybrid type which optimises the positions of the fittings towards the external devices.
  • 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 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.
  • transversal support plates 80i and the longitudinal partitions 81i have appropriate pluralities of savings and through openings, respectively 82i and 83i which have the function of equalising the pressure of the refrigerant fluid between these sectors and sub-units inside the evaporator 1.
  • a plurality of longitudinal deflecting fins 85ni 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 primary vertical partition 88 divides the upper zone 22 of the evaporator in which it defines a first upper chamber 23 in which the second number of tubes 42 and the distributor 70 of the service refrigerant fluid are housed, and a second upper lateral chamber 24 of the evaporator 1, towards the side of the shell 2 where the inlets 7A and 7B are located, to which the distributor 70 and the outlet 8 of the refrigerant fluid in the gaseous state are connected.
  • a third number of tubes 43 connected via a collector 51 in the head 3A is housed inside the second upper lateral chamber 24 of the evaporator 1.
  • the head 3 A 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; and an 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 process fluid to be cooled coming from the system circulation and appropriately moved by movement means outside the evaporator, travels through the tubes in a horizontal-axis outward and return pathway inside the evaporator 1 over the whole length of the shell 2.
  • 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 refrigerated 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 refrigerant fluid in its fall by force of gravity from the plurality of lower longitudinal dispensing openings 74i in the plurality of distribution tubes 72i on the second number of tubes 42, is compartmentalised into a plurality of sub-units of a plurality of sectors defined by the plurality of transversal support plates 80i and of vertical longitudinal partitions 81i.
  • 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 pluralities of savings and through openings, respectively 82i and 83i in the transversal support plates 80i and in the longitudinal partitions 81i which are compartmentalised into a plurality of sub-units of a plurality of sectors inside the evaporator 1, advantageously facilitate the uniformity of the distribution of the refrigerant fluid during the progressively gaseous and mixed-gaseous phase in the progressive fall thereof on the rows of the second number of tubes 42.
  • 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 level of the service refrigerant fluid in the flooded lower zone 21 is controlled, which level must be maintained, by an appropriate control and balancing of the functions of the system outside the evaporator 1, at a higher level than the upper horizontal row of the first number of tubes 41 of the tube bundle 4.
  • 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 primary partition 88 in cooperation with the free surface of the collecting flooded lower zone 21, inferiorly delimits a connecting passage between the first upper chamber 23 where a descending portion of circuit extends, and the second upper lateral chamber 24 where a rising portion of circuit extends in succession to a descending portion of circuit of the tortuous pathway of the refrigerant fluid in the gaseous and mixed-gaseous phase.
  • the tortuous pathway of the refrigerant fluid in gaseous and mixed-gaseous phase advantageously strikes, in the inversion from the descending portion of circuit to the 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 number of tubes 41 and thus actuates a heat exchange which tends to reduce the moisture of the mixed-gaseous phase which is still residual.
  • the third number of tubes 43 is also housed in the second upper lateral chamber 24 and is arranged at a greater height 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 refrigerated service 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.
  • a horizontal tube bundle evaporator according to the invention is particularly advantageous for optimisation of the fluid-dynamics of the service fluid and the heat exchange with the process flow.
  • the materials used, as well as the dimensions, can be any according to the needs and the state of the art.

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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. Horizontaler Rohrbündelverdampfer (1), der sich längs entlang einer horizontalen Achse erstreckt, umfassend einen Mantel (2), ein Rohrbündel (4), das im Mantel (2) untergebracht ist, ein mantelseitiges Kältemittel, ein rohrseitiges Kältemittel, eine untere Zone (21) des Verdampfers (1), die vom Kältemittel im flüssigen Zustand geflutet ist und eine erste Anzahl von Rohren (41) des Rohrbündels (4) enthält, einen Prozessmediumverteiler (70), der in einer oberen Zone (22) des Verdampfers (1) positioniert ist, eine zweite Anzahl von Rohren (42) des Rohrbündels (4), die außerhalb der gefluteten unteren Zone (21) positioniert sind, und mindestens einen Auslass (8) des Kältemittels im gasförmigen Zustand aus dem Mantel (2), zudem umfassend im Mantel (2) einen gewundenen Kreislauf für das Kältemittel, das bei Kontakt mit der zweiten Anzahl (42) von Rohren verdampft, umfassend mindestens einen absteigenden Abschnitt des Kreislaufs, wobei der absteigende Kreislaufabschnitt durch mindestens eine vertikale Haupttrennunterteilung (88) begrenzt ist, die sich längs entlang der horizontalen Achse erstreckt, wobei die vertikale Hauptunterteilung (88) eine erste obere Kammer (23) des Verdampfers, in der die zweite Anzahl von Rohren (42) positioniert ist, von einer zweiten oberen Seitenkammer (24) des Verdampfers (1) trennt, in der der Auslass (8) aus dem Mantel untergebracht ist, dadurch gekennzeichnet, dass er eine Vielzahl von vertikalen Nebenlängsunterteilungen (81i) umfasst, die die erste obere Kammer (23) in eine Vielzahl von Sektoren teilt, in denen die Rohre der zweiten Anzahl (42) von Rohren verteilt sind, und wobei die vertikalen Nebenunterteilungen (81i) mit einer Vielzahl von Längsablenkrippen (85i) des Kältemittels versehen sind.
  2. Horizontaler Rohrbündelverdampfer (1) nach dem vorhergehenden Anspruch, wobei die zweite Anzahl von Rohren (42) größer ist als die erste Anzahl von Rohren (41) .
  3. Horizontaler Rohrbündelverdampfer (1) nach einem der vorhergehenden Ansprüche, wobei die vertikale Haupttrennunterteilung (88) oberseitig die erste obere Kammer (23) und die zweite obere Seitenkammer (24) trennt und sich nach unten bis zu einem Abstand von der freien Oberfläche der gefluteten unteren Zone (21) erstreckt, um das Kältemittel im flüssigen Zustand zu sammeln.
  4. Horizontaler Rohrbündelverdampfer (1) nach dem vorhergehenden Anspruch, wobei die vertikale Haupttrennunterteilung (88) in Kooperation mit der freien Oberfläche der unteren Zone (21) unterseitig einen Verbindungsdurchgang zwischen der ersten oberen Kammer (23), in der sich der absteigende Kreislaufabschnitt erstreckt, und der zweiten oberen Seitenkammer (24), in der sich in Folge des absteigenden Kreislaufabschnitts ein aufsteigender Kreislaufabschnitt erstreckt, begrenzt.
  5. Horizontaler Rohrbündelverdampfer (1) nach dem vorhergehenden Anspruch, wobei die zweite obere Seitenkammer (24) eine dritte Anzahl von Rohren (43) des Rohrbündels (4) enthält, die außerhalb der unteren Zone (21) angeordnet ist.
  6. Horizontaler Rohrbündelverdampfer (1) nach dem vorhergehenden Anspruch, wobei der Auslass (8) in der zweiten oberen Seitenkammer (24) über der dritten Anzahl von Rohren (43) positioniert ist.
  7. Horizontaler Rohrbündelverdampfer (1) nach einem der vorhergehenden Ansprüche, wobei die vertikalen Nebenunterteilungen (81i) mit einer Vielzahl von Durchführungsöffnungen (83i) für den Ausgleich des Drucks des Kältemittels zwischen den Sektoren versehen sind.
  8. Horizontaler Rohrbündelverdampfer (1) nach einem der vorhergehenden Ansprüche, wobei eine Vielzahl von Querhalterungsplatten (80i) des Rohrbündels (4) innerhalb des Mantels (2) positioniert ist, wobei die vertikalen Nebenunterteilungen (81i) an dieser Vielzahl von Querhalterungsplatten (80i) fixiert sind.
  9. Horizontaler Rohrbündelverdampfer (1) nach dem vorhergehenden Anspruch, wobei die Querhalterungsplatten (80i) die Sektoren in Untereinheiten teilen und mit Durchführungsöffnungen (82i) für den Ausgleich des Drucks des Kältemittels zwischen den Untereinheiten versehen sind.
  10. Horizontaler Rohrbündelverdampfer (1) nach einem der vorhergehenden Ansprüche, wobei über der gefluteten unteren Zone (21) zum Sammeln eines Betriebsmediums und vertikal an der Position der zweiten oberen Seitenkammer (24) eine obere horizontale Reihe von Rohren (44) der ersten Anzahl von Rohren (41) bereitgestellt ist, die auf einem höheren Niveau als die obere horizontale Reihe der Rohre positioniert ist, die der ersten oberen Kammer (23) zugewandt und vertikal an dieser positioniert sind.
  11. Horizontaler Rohrbündelverdampfer (1) nach einem der Ansprüche 5 bis 10, wobei der Mantel (2) einen Kopf 3A aufweist, der mit einem Einlasssammler (51) versehen ist, der die erste Anzahl von Rohren (41), die dritte Anzahl von Rohren (43) und eine untere Gruppe von Rohren der zweiten Anzahl von Rohren (42) versorgt, und einem Auslasssammler (61), der von einer unteren Gruppe von Rohren der zweiten Anzahl von Rohren (42) versorgt wird.
  12. Dampfkompressionskältekreislauf, umfassend einen horizontalen Rohrbündelverdampfer nach einem der vorhergehenden Ansprüche.
EP20175886.9A 2019-06-05 2020-05-21 Hybridrohrbündelverdampfer Active EP3748270B1 (de)

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EP3748270B1 true EP3748270B1 (de) 2022-08-17

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202100030026A1 (it) 2021-11-26 2023-05-26 Mitsubishi Electric Hydronics & It Cooling Systems S P A Assieme di evaporatore ibrido migliorato
IT202100029945A1 (it) 2021-11-26 2023-05-26 Mitsubishi Electric Hydronics & It Cooling Systems S P A Assieme di evaporatore ibrido migliorato
CN115756031B (zh) * 2022-10-12 2023-10-10 东方电气集团东方汽轮机有限公司 一种绕管式蒸发器控制方法及系统

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1809966B1 (de) * 2004-10-13 2011-07-27 York International Corporation Fallfilmverdampfer
WO2008080085A2 (en) * 2006-12-21 2008-07-03 Johnson Controls Technology Company Falling film evaporator with a hood and a flow distributor
ATE554355T1 (de) * 2008-01-11 2012-05-15 Johnson Controls Tech Co Dampfkompressionssystem
EP2457051A2 (de) * 2009-07-22 2012-05-30 Johnson Controls Technology Company Kompakter vedampfer für kühlaggregate

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