EP3367036B1 - Trockenausdehnungs-rohrbündelwärmetauscher - Google Patents

Trockenausdehnungs-rohrbündelwärmetauscher Download PDF

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Publication number
EP3367036B1
EP3367036B1 EP18152542.9A EP18152542A EP3367036B1 EP 3367036 B1 EP3367036 B1 EP 3367036B1 EP 18152542 A EP18152542 A EP 18152542A EP 3367036 B1 EP3367036 B1 EP 3367036B1
Authority
EP
European Patent Office
Prior art keywords
shell
tube bundle
heat exchanger
end head
dry
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.)
Active
Application number
EP18152542.9A
Other languages
English (en)
French (fr)
Other versions
EP3367036A1 (de
Inventor
Mariano Covolo
Federico DAL FARRA
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
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Publication of EP3367036A1 publication Critical patent/EP3367036A1/de
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Publication of EP3367036B1 publication Critical patent/EP3367036B1/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
    • 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
    • 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
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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

Definitions

  • the present invention relates to a dry-expansion tube bundle heat exchanger.
  • dry-expansion tube bundle heat exchangers comprising a tube bundle arranged internally of a shell closed by a front end head and a rear end head.
  • the refrigerating fluid circulates on the tube side while the secondary fluid, typically water or a non-freezable solution, circulates on the shell side.
  • An inlet mouth of the secondary fluid is provided on the shell in proximity of an end head and an outlet mouth of the secondary fluid in proximity of the opposite head end.
  • the relative tubes extending internally of the shell have an inflow pathway and an outflow pathway positioned at the said end head.
  • These heat exchangers have some drawbacks, in particular linked to the size thereof, sometimes excessive with respect to the space available for the installation, to the efficiency thereof which can be negatively impacted by the presence of significant losses of load both on the tube side and on the shell side, and to the possible creation of stagnant zones of the secondary fluid in the corner zone between the shell and the end heads, with a consequent risk of freezing of the secondary fluid.
  • GB918180 and DE1190963 disclose heat exchangers according to the preamble of claim 1.
  • the technical task of the present invention is, therefore, to provide a dry-expansion tube bundle heat exchanger which obviates the above-described technical drawbacks of the prior art.
  • an objective of the invention is to provide a dry-expansion tube bundle heat exchanger that is compact and extremely efficient.
  • a dry-expansion tube bundle heat exchanger comprising a shell, a front end head, a rear end head, characterised in that it comprises a first and a second inlet mouth of a shell side secondary circulating fluid and a single secondary fluid outlet mouth.
  • said first inlet mouth is advantageously positioned on the shell between said front end head and said median plane and said second inlet mouth is positioned on the shell between said rear end head and said median plane.
  • said first inlet mouth is positioned at a distance from said front end head that is smaller than a distance thereof from said median plane, and said second inlet mouth is positioned at a distance from said rear end head that is smaller than a distance thereof from said median plane.
  • the outlet mouth can be positioned on the shell at a median plane of the shell that is perpendicular to the axis of the shell.
  • the outlet mouth can also be positioned on the shell at one of two semi-portions which make up one semi-part of the shell comprised between said median plane of the shell that is perpendicular to the axis of the shell and an end of the shell.
  • the tube bundle comprises at least a single circuit of refrigerating fluid.
  • the tube bundle can also advantageously comprise at least a first and at least a second circuit of refrigerating fluid in which the first refrigerating circuit has an inflow pathway at the front end head and the second refrigerating circuit has an inflow pathway at the rear end head.
  • the position of the inlet mouths of the secondary fluid in proximity of the end heads enables obtaining the desired extra heating on the aspiration, with a consequent improvement in the efficiency and a reduction of load losses on the tube side and the shell side.
  • the flow rate of the secondary fluid is halved with respect to the traditional configuration of a single inlet mouth, so that the tube bundle and consequently the shell can have a smaller diameter, which also allows a reduction of size and an installation in smaller spaces.
  • the inlet point of the secondary fluid which is the hottest point
  • the inlet point of the refrigerating fluid which is the coldest point
  • the inlet mouths have an inclined axis towards the end heads.
  • inlet mouths inclined in this way can be connected to an inlet manifold by bends of less than 90°, with a further reduction in loss loads on the inlet manifold.
  • the present invention also relates to a refrigerating plant of a liquid which comprises, as an evaporator of the refrigerating fluid, at least a heat exchanger of this type.
  • the heat exchanger 1 comprises a shell 2 closed at the ends by a front end head 3 and a rear end head 4.
  • the tube bundle (not illustrated) is present internally of the shell 2 in which the refrigerating fluid circulates.
  • the heat exchanger 1 comprises a first inlet mouth 5 of the secondary fluid which circulates on the shell side 2, a second inlet mouth 6 of the secondary fluid and a single outlet mouth 7 of the secondary fluid.
  • the first inlet mouth 5 is positioned on the shell 2 between the front end head 3 and the median plane M of the shell 2 and the second inlet mouth 6 is positioned on the shell 2 between the rear end head 4 and the median plane M of the shell 2.
  • first inlet mouth 5 is positioned at a distance from the front end head 3 that is smaller than a distance thereof from the median plane M of the shell 2
  • second inlet mouth 6 is positioned at a distance from the rear end head 4 that is smaller than a distance thereof from the median plane M of the shell 2.
  • the first inlet mouth 5 and the second inlet mouth 6 are more precisely arranged in a symmetrical position with respect to the median plane M of the shell 2.
  • the outlet mouth 7 is in turn positioned on the shell 2 at a median plane M of the shell 2.
  • the first inlet mouth 5 and the second inlet mouth 6 have a passage section of a same size, and the outlet mouth 7 has a passage section of a size equal to the passage section of the first outlet mouth 5, and of the second outlet mouth 6.
  • the velocity of the secondary fluid at the outlet is doubled with respect to the velocity of the secondary fluid at the inlet.
  • the outlet mouth 7 in order to maintain the same velocity of the secondary fluid at the inlet and at the outlet the outlet mouth 7 has a passage section equal to the sum of the passage sections of the first inlet mouth 5 and the second inlet mouth 6.
  • the tube bundle comprise a first refrigerating circuit and a second refrigerating circuit.
  • the first refrigerating circuit has an inflow pathway 8 at the front end head 3 and the second refrigerating circuit has an inflow pathway 9 at the rear end head 4.
  • the first refrigerating circuit further has an outflow pathway 10 at the rear end head 4, while the second refrigerating circuit has an outflow pathway 11 at the front end head 3.
  • the first inlet mouth 5 has an axis B1 orientated towards the front end head 3 and likewise the second inlet mouth 6 has an axis B2 orientated towards the rear end head 4.
  • the first inlet mouth 5 has an axis B1 orientated at an angle ⁇ comprised between 60° and 90° with respect to the axis L of the shell 2 and likewise the second inlet mouth 6 has an axis B2 that is orientated at an angle ⁇ comprised between 60° and 90° with respect to the axis L of the shell 2.
  • the first inlet mouth 5 and the second inlet mouth 6 are arranged with the axes B1, B2 thereof lying in a same plane.
  • the axis B3 of the outlet mouth 7 is offset from the plane in which the axes B1, B2 of the first inlet mouth 5 and second inlet mouth 6 are positioned.
  • the axis B3 of the outlet mouth 7 is orientated at an angle comprised between 0° and 90° with respect to the plane in which the axes B1, B2 of the first inlet mouth 5 and second inlet mouth 6 are positioned.
  • the heat exchanger 1 functions as an evaporator in a liquid refrigeration plant. More in general, the heat exchanger can be integrated in a conditioning plant, in a cooling plant, or in a heat pump plant.

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)
  • Drying Of Solid Materials (AREA)

Claims (12)

  1. Trockenausdehnungs-Rohrbündelwärmetauscher (1), umfassend eine Hülle (2), einen frontseitigen Endkopf (3), einen rückseitigen Endkopf (4), eine erste und eine zweite Öffnung (5, 6) für den Einlass eines hüllenseitigen Sekundärzirkulationsfluids (2) und eine einzelne Sekundärfluidauslassöffnung (7), wobei das Rohrbündel mindestens einen Kühlkreislauf in der Hülle (2) umfasst, dadurch gekennzeichnet, dass jeweils die erste und die zweite Einlassöffnung (5, 6) jeweilige Achsen (B1, B2) aufweisen, die hinführend zum frontseitigen Endkopf (3) bzw. hinführend zum rückseitigen Endkopf (4) ausgerichtet sind.
  2. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach Anspruch 1, dadurch gekennzeichnet, dass die erste Einlassöffnung (5) gegenüber einer Medianebene (M) der Hülle (2), die senkrecht zur Achse (L) der Hülle (2) angeordnet ist, auf der Hülle (2) zwischen dem frontseitigen Endkopf (3) und der Medianebene (M) positioniert ist und dass die zweite Einlassöffnung (6) auf der Hülle (2) zwischen dem rückseitigen Endkopf (4) und der Medianebene (M) positioniert ist.
  3. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach dem vorhergehenden Anspruch, dadurch gekennzeichnet, dass die erste Einlassöffnung (5) in einem Abstand vom frontseitigen Endkopf (3) positioniert ist, der geringer als deren Abstand von der Medianebene (M) ist und dass die zweite Einlassöffnung (6) in einem Abstand vom rückseitigen Endkopf (4) positioniert ist, der geringer ist als deren Abstand von der Medianebene (M).
  4. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach Anspruch 1, dadurch gekennzeichnet, dass die Auslassöffnung (7) auf der Hülle (2) an einer Medianebene (M) der Hülle (2) positioniert ist, die senkrecht zur Achse (L) der Hülle (2) angeordnet ist.
  5. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach Anspruch 1, dadurch gekennzeichnet, dass die Auslassöffnung (7) auf der Hülle (2) an einem von zwei Halbabschnitten positioniert ist, die einen Halbteil der Hülle (2) bilden, umfasst zwischen einer Medianebene (M) der Hülle (2), die senkrecht zur Achse der Hülle (2) angeordnet ist, und einem Ende der Hülle (2).
  6. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die erste und die zweite Einlassöffnung (5, 6) einen Durchgangsquerschnitt derselben Größe aufweisen und dass die Auslassöffnung (7) einen Durchgangsquerschnitt aufweist, der die gleiche Größe wie der Durchgangsquerschnitt der ersten und der zweiten Einlassöffnung (5, 6) besitzt oder doppelt so groß ist wie der Durchgangsquerschnitt der ersten oder der zweiten Einlassöffnung (5, 6).
  7. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass ein erster und mindestens ein zweiter Kühlkreislauf im Rohrbündel umfasst sind, wobei der erste Kühlkreislauf einen Einströmungsweg (8) am frontseitigen Endkopf (3) aufweist und der zweite Kühlkreislauf einen Einströmungsweg (9) am rückseitigen Endkopf (4) aufweist.
  8. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach dem vorhergehenden Anspruch, dadurch gekennzeichnet, dass der erste Kühlkreislauf einen Ausströmungsweg (10) am rückseitigen Endkopf (4) umfasst und der zweite Kühlkreislauf einen Ausströmungsweg (11) am frontseitigen Endkopf (3) umfasst.
  9. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach Anspruch 1, dadurch gekennzeichnet, dass die erste und jeweils die zweite Einlassöffnung (5, 6) jeweilige Achsen (B1, B2) umfassen, die an einem Winkel (α, β) zwischen 60° und 90° zur Achse (L) der Hülle (2) ausgerichtet sind.
  10. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Achsen (B1, B2) der ersten und der zweiten Einlassöffnung (5, 6) auf einer selben Ebene liegen.
  11. Trockenausdehnungs-Rohrbündelwärmetauscher (1) nach dem vorhergehenden Anspruch, dadurch gekennzeichnet, dass die Achse (B3) der Auslassöffnung (7) winkelig von der Ebene versetzt ist, in der die Achsen (B1, B2) der ersten und der zweiten Einlassöffnung (5, 6) positioniert sind.
  12. Kälte- oder Kühl- oder Klima- oder Wärmepumpenanlage, dadurch gekennzeichnet, dass sie mindestens einen Wärmetauscher (1) nach einem der vorhergehenden Ansprüche umfasst.
EP18152542.9A 2017-02-24 2018-01-19 Trockenausdehnungs-rohrbündelwärmetauscher Active EP3367036B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT102017000021474A IT201700021474A1 (it) 2017-02-24 2017-02-24 Scambiatore di calore a fascio tubiero ad espansione secca

Publications (2)

Publication Number Publication Date
EP3367036A1 EP3367036A1 (de) 2018-08-29
EP3367036B1 true EP3367036B1 (de) 2020-10-28

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Country Status (2)

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EP (1) EP3367036B1 (de)
IT (1) IT201700021474A1 (de)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB918180A (en) * 1959-11-18 1963-02-13 Ckd Praha Improvements in devices for distributing a liquid in cooling chemical and similar apparatus
DE1190963B (de) * 1961-12-05 1965-04-15 Gutehoffnungshuette Sterkrade Verfahren zur Herstellung grosser Waermetauscher u. dgl.
US3269135A (en) * 1963-10-07 1966-08-30 Worthington Corp Multi-stage heat exchange apparatus and method
JP5988296B2 (ja) * 2011-08-10 2016-09-07 臼井国際産業株式会社 多管式熱交換器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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IT201700021474A1 (it) 2018-08-24
EP3367036A1 (de) 2018-08-29

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