EP3221656B1 - Gefalteter mikrokanalwärmetauscher mit mehreren durchgängen und platten - Google Patents

Gefalteter mikrokanalwärmetauscher mit mehreren durchgängen und platten Download PDF

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Publication number
EP3221656B1
EP3221656B1 EP15797809.9A EP15797809A EP3221656B1 EP 3221656 B1 EP3221656 B1 EP 3221656B1 EP 15797809 A EP15797809 A EP 15797809A EP 3221656 B1 EP3221656 B1 EP 3221656B1
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EP
European Patent Office
Prior art keywords
heat exchanger
manifold
tube segments
pass
section
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EP15797809.9A
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English (en)
French (fr)
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EP3221656A1 (de
Inventor
Arindom Joardar
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Carrier Corp
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Carrier Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—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, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—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, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0471—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/006—Preventing deposits of ice
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes

Definitions

  • EP 0 654 645 discloses a heat exchanger having the features of the preamble of claim 1.
  • HVAC&R Heating, ventilation, air conditioning and refrigeration
  • microchannel heat exchangers are also more environmentally friendly as they utilize less refrigerant charge which typically are synthetic fluids with high GWP (global warming potential).
  • a microchannel heat exchanger includes two or more containment forms, such as tubes, through which a cooling or heating fluid (i.e. refrigerant or a glycol solution) is circulated.
  • microchannel heat exchanger In the heat pump and refrigeration applications, when the microchannel heat exchanger is utilized as an evaporator, moisture present in the airflow provided to the heat exchanger for cooling may condense and then freeze on the external heat exchanger surfaces. The ice or frost formed may block the flow of air through the heat exchanger, thereby reducing the efficiency and functionality of the heat exchanger and HVAC&R system. Microchannel heat exchangers tend to freeze faster than the round tube and plate fin heat exchangers and therefore require more frequent defrosts, reducing useful heat exchanger utilization time and overall performance. Consequently, it is desirable to construct the microchannel heat exchanger with improved frost tolerance and enhanced performance.
  • the invention provides a heat exchanger comprising: a first manifold; a second manifold separated from the first manifold; a plurality of tube segments arranged in spaced parallel relationship and fluidly coupling the first manifold and the second manifold, the plurality of tube segments including a bend defining a first slab and a second slab, the second slab being arranged at an angle to the first slab; and a divider arranged within the first manifold to form a first manifold first section and a first manifold second section; and a divider arranged within the second manifold to form a second manifold first section and a second manifold second section; wherein the heat exchanger has a multi-pass configuration relative to an air flow including at least a first pass and a second pass, the first pass including a first portion of the plurality of tube segments and having a first flow orientation and the second pass including a second portion of the plurality of tube segments and having a second flow orientation, the second flow orientation being different
  • the first pass may have a cross parallel flow orientation.
  • the number of tube segments arranged within each of the first pass and the second pass may be selected to reduce the formation of frost on the heat exchanger.
  • the second portion may have a greater number of tube segments than the first portion.
  • a ratio of tube segments in the first portion to the second portion may be 20:80.
  • a ratio of tube segments in the first portion to the second portion may be 40:60.
  • a divider may be arranged within the first manifold to define a first manifold first section and a first manifold second section, wherein the first manifold first section is fluidly coupled to the first portion of the plurality of tube segments, and the first manifold second section is fluidly coupled to the second portion of the plurality of tube segments.
  • a distributor may be arranged within the first manifold first section.
  • a distributor may be provided between the first pass and the second pass.
  • the bend may be formed about an axis arranged perpendicular to a longitudinal axis of the plurality of tube segments.
  • each tube segment may include a ribbon fold.
  • the angle between the second slab and the first slab may be about 180 degrees.
  • Each of the plurality of tube segments may be a microchannel tube having a plurality of discrete flow channels formed therein.
  • a vapor compression refrigerant cycle 20 of an air conditioning or refrigeration system is schematically illustrated.
  • Exemplary air conditioning or refrigeration systems include, but are not limited to, split, packaged, chiller, rooftop, supermarket, and transport refrigeration systems for example.
  • a refrigerant R is configured to circulate through the vapor compression cycle 20 such that the refrigerant R absorbs heat when evaporated at a low temperature and pressure and releases heat when condensed at a higher temperature and pressure.
  • the refrigerant R flows in a counterclockwise direction as indicated by the arrow.
  • the compressor 22 receives refrigerant vapor from the evaporator 24 and compresses it to a higher temperature and pressure, with the relatively hot vapor then passing to the condenser 26 where it is cooled and condensed to a liquid state by a heat exchange relationship with a cooling medium (not shown) such as air.
  • the liquid refrigerant R then passes from the condenser 26 to an expansion device 28, wherein the refrigerant R is expanded to a low temperature two-phase liquid/vapor state as it passes to the evaporator 24.
  • the low pressure vapor then returns to the compressor 22 where the cycle is repeated.
  • the vapor compression cycle 20 described herein is a heat pump cycle operating in a heating mode.
  • the outdoor coil of the cycle 20 is configured as the evaporator 24 and the indoor coil is configured as the condenser.
  • the vapor compression cycle additionally includes a four-way valve 29 disposed downstream of the compressor 22 with respect to the refrigerant flow that reverses the direction of refrigerant flow through the cycle 20 to switch between the cooling and heating mode of operation.
  • the refrigeration cycle 20 depicted in FIG. 1 is a simplistic representation of an HVAC&R system, and many enhancements and features known in the art may be included in the schematic.
  • the heat exchanger 30 may be used as either a condenser 24 or an evaporator 28 in the vapor compression system 20.
  • the heat exchanger 30 includes at least a first manifold or header 32, a second manifold or header 34 spaced apart from the first manifold 32, and a plurality of tube segments 36 extending in a spaced, parallel relationship between and connecting the first manifold 32 and the second manifold 34.
  • the first header 32 and the second header 34 are oriented generally horizontally and the heat exchange tube segments 36 extend generally vertically between the two headers 32, 34.
  • other configurations, such as where the first and second headers 32, 34 are arranged substantially vertically are also within the scope of the invention.
  • the tube segment 36 includes a flattened microchannel heat exchange tube having a leading edge 40, a trailing edge 42, a first surface 44, and a second surface 46.
  • the leading edge 40 of each heat exchanger tube 36 is upstream of its respective trailing edge 42 with respect to an airflow A passing through the heat exchanger 36.
  • the interior flow passage of each heat exchange tube segment 36 may be divided by interior walls into a plurality of discrete flow channels 48 that extend over the length of the tubes 36 from an inlet end to an outlet end and establish fluid communication between the respective first and second manifolds 32, 34.
  • the flow channels 48 may have a circular cross-section, a rectangular cross-section, a trapezoidal cross-section, a triangular cross-section, or another non-circular cross-section.
  • the heat exchange tubes 36 including the discrete flow channels 48 may be formed using known techniques and materials, including, but not limited to, extruded or folded.
  • the heat exchange tube segments 36 disclosed herein further include a plurality of fins 50.
  • the fins 50 are formed of a single continuous strip of fin material tightly folded in a ribbon-like serpentine fashion thereby providing a plurality of closely spaced fins that extend generally orthogonal to the heat exchange tube segments 36.
  • Heat exchange between the one or more fluids within the heat exchange tube segments 36 and an air flow, A occurs through the outside surfaces 44, 46 of the heat exchange tube segments 36 collectively forming a primary heat exchange surface, and also through the heat exchange surface of the fins 50, which forms a secondary heat exchange surface.
  • the heat exchanger 30 has a multi-pass configuration relative to airflow A.
  • the multi-pass configuration is achieved by forming at least one bend 60 in each tube segment 36 of the heat exchanger 30.
  • the bend 60 is formed about an axis extending substantially perpendicular to the longitudinal axis of the tube segments 36.
  • the bend 60 is a ribbon fold (see FIG. 6 ) formed by bending and twisting the heat exchange tube segments 36 about a mandrel (not shown); however other types of bends are within the scope of the invention.
  • a plurality of bends 60 may be formed at various locations along a length of the plurality of the heat exchange tube segments 36.
  • the heat exchanger 30 can be formed such that the first slab 66 is positioned at an obtuse angle with respect to the second slab 68. Alternatively, or in addition, the heat exchanger 30 can also be formed such that the first slab 66 is arranged at either an acute angle or substantially parallel ( FIG. 5 ) to the second slab 68. As a result of the bend 60 between the first and second slabs 66, 68, the heat exchanger 30 may be formed having a conventional A-coil or V-coil shape. Forming the heat exchanger 30 by bending the tube segments 36 results in a heat exchanger 30 having a reduced bending radius, such as when configured with a 180° bend for example. As a result, the heat exchanger 30 may be adapted to fit within the sizing envelopes defined by existing air conditioning and refrigeration systems.
  • first fins 50a extend from the first slab 66 and a plurality of second fins 50b extend from the second slab 68 of the heat exchanger 30.
  • first fins 50a and the second fins 50b may be substantially identical, or alternatively, may vary in one of size, shape, and density.
  • the heat exchanger 30 may have any of a variety of multi-pass configurations such that the refrigerant passes through the heat exchanger 30 in one or more of a parallel flow orientation, a cross flow orientation, and a counter flow orientation for example.
  • a divider 38 may be arranged within one or both of the first and second headers 32, 34 to increase the number of passes, and therefore the length of the flow path, within the heat exchanger 30.
  • a divider 38 is arranged within the first header 32 to form a first section 32a and a second section 32b.
  • refrigerant supplied to an inlet (not shown) of the first header 32 is only configured to flow through the portion 36a of the tube segments 36 fluidly connected to the first section 32a.
  • the refrigerant After passing through a first portion 36a of the tube segments 36, the refrigerant is received in the second header 34.
  • the refrigerant flows away from the first portion 36a of tube segments 36, towards a second, adjacent portion 36b of tube segments 36.
  • the second portion 36b includes a different number of tube segments 36 to the first portion 36a. In one embodiment, the ratio of tube segments in the first portion 36a to the second portion 36b is 20:80, or alternatively, 40:60.
  • the second header 34 may similarly include a divider 38 to define a fluidly coupled first and second section 34a, 34b thereof.
  • the refrigerant is configured to flow from the second header 34 through the second portion 36b of tube segments 36 fluidly connected to the second section 32b of the first header 32 and to an outlet (not shown) formed therein.
  • the illustrated heat exchanger 30 includes two distinct portions of heat exchanger tube segments 36, heat exchangers 30 having any number of portions of tube segments 36 that form discrete passes through the heat exchanger 30 are within the scope of the invention.
  • header 32 or 34 or an intermediate header for example is a common problem of microchannel heat exchangers. It is generally easy to distribute the refrigerant evenly for small manifold lengths, but mal-distribution becomes a more significant problem as the length of the manifold increases.
  • the heat exchanger 30 disclosed herein has improved refrigerant distribution by partitioning at least one of the first and second headers 32, 34, with a divider 38. As a result, the lengths of the manifold in which refrigerant must be evenly distributed is decreased. In addition, by bending the heat exchanger 30, the need for an intermediate header, and therefore the distribution problems associated with such a header, is eliminated.
  • a longitudinally elongated distributor insert 70 as is known in the art, is positioned within the second section 34b of the second header 34. Another distributor 70 may be arranged within one or more of the sections of either the first header 32 or the second header 34 of the heat exchanger 30.
  • a heat exchanger 30 having a multi-pass, multi-slab, folded construction allows for optimization of the refrigerant pressure drop, thereby improving performance.
  • the refrigerant flows through the heat exchange tube segments 36, the vapor quality continuously increases, leading to increased volumetric flow and therefore increased pressure drop.
  • Improvement in the operational efficiency of the heat exchanger 30 may allow the size of the heat exchanger 30 required for a desired application to be reduced.
  • size of other system components, such as a compressor for example may be reduced which in turn would cause even higher evaporation temperature and further reduction of defrost cycles as well as the system performance boost.

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

Claims (14)

  1. Wärmetauscher, umfassend:
    eine erste Sammelleitung (32);
    eine zweite Sammelleitung (34), die von der ersten Sammelleitung getrennt ist;
    eine Vielzahl von Rohrsegmenten (36), die in einem beabstandeten parallelen Verhältnis angeordnet sind, und die erste Sammelleitung und die zweite Sammelleitung fluidisch koppeln, wobei die Vielzahl von Rohrsegmenten eine Biegung (60) beinhalten, die eine erste Platte (66) und eine zweite Platte (68) definieren, wobei die zweite Platte in einem Winkel zur ersten Platte angeordnet ist; und
    einen Teiler (38), der innerhalb der ersten Sammelleitung angeordnet ist, um eine erste Sektion einer ersten Sammelleitung (32a) und eine zweite Sektion einer ersten Sammelleitung (32b) zu bilden; und
    einen Teiler, der innerhalb der zweiten Sammelleitung angeordnet ist, um eine erste Sektion einer zweiten Sammelleitung (34a) und eine zweite Sektion einer zweiten Sammelleitung (34b) zu bilden;
    wobei der Wärmetauscher eine Konfiguration mit mehreren Durchgängen in Bezug auf eine Luftströmung aufweist, die mindestens einen ersten Durchgang und einen zweiten Durchgang beinhaltet, wobei der erste Durchgang einen ersten Abschnitt (36a) der Vielzahl von Rohrsegmenten beinhaltet und eine erste Strömungsausrichtung aufweist und der zweite Durchgang einen zweiten Abschnitt (36b) der Vielzahl von Rohrsegmenten beinhaltet und eine zweite Strömungsausrichtung aufweist, wobei sich die zweite Strömungsausrichtung von der ersten Strömungsausrichtung unterscheidet, wobei eine Anzahl von Rohrsegmenten in dem ersten Abschnitt und eine Anzahl von Rohrsegmenten in dem zweiten Abschnitt unterschiedlich sind;
    gekennzeichnet durch einen länglich ausgedehnten Verteilereinsatz (70), der innerhalb der zweiten Sektion der zweiten Sammelleitung angeordnet ist.
  2. Wärmetauscher nach Anspruch 1, wobei der erste Durchgang eine parallele Querströmungsausrichtung aufweist.
  3. Wärmetauscher nach Anspruch 2, wobei der zweite Durchgang eine gegenläufige Querströmungsausrichtung aufweist.
  4. Wärmetauscher nach einem vorstehenden Anspruch, wobei eine Anzahl von Rohrsegmenten (36), die innerhalb jedes des ersten Durchgangs und des zweiten Durchgangs angeordnet ist, ausgewählt ist, um die Bildung von Frost in dem Wärmetauscher zu verringern.
  5. Wärmetauscher nach einem vorstehenden Anspruch, wobei der zweite Abschnitt (36b) eine größere Anzahl von Rohrsegmenten (36) aufweist als der erste Abschnitt (36a).
  6. Wärmetauscher nach Anspruch 5, wobei ein Verhältnis von Rohrsegmenten (36) in dem ersten Abschnitt (36a) zum zweiten Abschnitt (36b) 20:80 ist.
  7. Wärmetauscher nach Anspruch 5, wobei ein Verhältnis von Rohrsegmenten (36) in dem ersten Abschnitt (36a) zum zweiten Abschnitt (36b) 40:60 ist.
  8. Wärmetauscher nach einem vorstehenden Anspruch, wobei ein Teiler (38) innerhalb der ersten Sammelleitung (32) angeordnet ist, um eine erste Sektion einer ersten Sammelleitung (32a) und eine zweite Sektion einer ersten Sammelleitung (32b) zu definieren, wobei die erste Sektion einer ersten Sammelleitung fluidisch mit dem ersten Abschnitt (36a) der Vielzahl von Rohrsegmenten (36) gekoppelt ist, und die zweite Sektion einer ersten Sammelleitung fluidisch mit dem zweiten Abschnitt (36b) der Vielzahl von Rohrsegmenten gekoppelt ist.
  9. Wärmetauscher nach Anspruch 8, wobei ein Verteiler (70) innerhalb der ersten Sektion der ersten Sammelleitung (32a) angeordnet ist.
  10. Wärmetauscher nach Anspruch 8, wobei ein Verteiler (70) zwischen dem ersten Durchgang und dem zweiten Durchgang bereitgestellt ist.
  11. Wärmetauscher nach Anspruch 1, wobei die Biegung (60) um eine Achse gebildet wird, die senkrecht zu einer Längsachse der Vielzahl von Rohrsegmenten (36) angeordnet ist.
  12. Wärmetauscher nach Anspruch 1, wobei die Biegung (60) jedes Rohrsegments (36) eine Bandfalte beinhaltet.
  13. Wärmetauscher nach Anspruch 1, wobei der Winkel zwischen der zweiten Platte (68) und der ersten Platte (66) etwa 180 Grad beträgt.
  14. Wärmetauscher nach Anspruch 1, wobei jedes der Vielzahl von Rohrsegmenten (36) ein Mikrokanalrohr ist, das eine Vielzahl von diskreten Strömungskanälen (48) aufweist, die darin gebildet sind.
EP15797809.9A 2014-11-17 2015-11-13 Gefalteter mikrokanalwärmetauscher mit mehreren durchgängen und platten Active EP3221656B1 (de)

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Application Number Priority Date Filing Date Title
US201462080741P 2014-11-17 2014-11-17
PCT/US2015/060607 WO2016081306A1 (en) 2014-11-17 2015-11-13 Multi-pass and multi-slab folded microchannel heat exchanger

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EP3221656A1 EP3221656A1 (de) 2017-09-27
EP3221656B1 true EP3221656B1 (de) 2020-10-28

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US (1) US20170343288A1 (de)
EP (1) EP3221656B1 (de)
CN (1) CN107110568A (de)
ES (1) ES2831020T3 (de)
RU (1) RU2722930C2 (de)
WO (1) WO2016081306A1 (de)

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RU2722930C2 (ru) 2020-06-04
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EP3221656A1 (de) 2017-09-27
CN107110568A (zh) 2017-08-29
ES2831020T3 (es) 2021-06-07
RU2017118516A (ru) 2018-12-19
US20170343288A1 (en) 2017-11-30

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