EP3362759B1 - Wärmetauscher für hlk-geräte im wohnbereich - Google Patents

Wärmetauscher für hlk-geräte im wohnbereich Download PDF

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Publication number
EP3362759B1
EP3362759B1 EP15804581.5A EP15804581A EP3362759B1 EP 3362759 B1 EP3362759 B1 EP 3362759B1 EP 15804581 A EP15804581 A EP 15804581A EP 3362759 B1 EP3362759 B1 EP 3362759B1
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EP
European Patent Office
Prior art keywords
heat exchanger
header
heat
fins
exchange tubes
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EP15804581.5A
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English (en)
French (fr)
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EP3362759A1 (de
Inventor
Charbel RAHHAL
Kazuo Saito
Michael F. Taras
Tobias H. Sienel
Arindom Joardar
Lee G. Tetu
Jackie S. ANDERSON
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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
    • 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

Definitions

  • This disclosure relates generally to heat exchangers and, more particularly, to a heat exchanger configured for use as an outdoor heat exchanger in residential air conditioning and heat pump applications.
  • heat exchangers of refrigerant systems particularly condensers and evaporators.
  • a relatively recent advancement in heat exchanger technology includes the development and application of parallel flow (such as microchannel, minichannel, brazed-plate, plate-fin, or plate- and frame) heat exchangers as condensers and evaporators.
  • JP 2013-139971 disclosing a heat exchanger according to the preamble of claim 1, US 5695004 and EP 0855567 disclose heat exchangers having headers with bends.
  • a heat exchanger including a first header, a second header, and a plurality of heat exchange tubes arranged in a spaced parallel relationship and fluidly coupling the first and second headers.
  • Both of the first header and second header include a bend.
  • the heat exchanger has an aspect ratio between about 2 and 6 after formation of the bend, where the aspect ratio is a ratio of a length of the heat exchanger to a height of the heat exchanger.
  • An inner diameter of the first header and the second header is equal to a width of one the plurality of heat exchanger tubes plus 1-4 mm
  • the plurality of heat exchange tubes may have a tube depth between about 8 mm and about 20 mm.
  • the depth of the plurality of heat exchange tubes may be about 10 mm.
  • the depth of the plurality of heat exchange tubes may be about 12 mm.
  • the depth of the plurality of heat exchange tubes may be about 16 mm.
  • the plurality of heat exchange tubes may have a height of about 1.3 mm ⁇ .3 mm.
  • the plurality of heat exchange tubes may have a tube pitch between about 8.9 mm and about 15.5. mm.
  • the plurality of heat exchange tubes may have a tube pitch of about 9.3 mm.
  • the heat exchanger may be configured for use in an air conditioning system.
  • the heat exchanger may be configured with a first pass and a second pass.
  • first portion of the plurality of heat exchange tubes is configured for the first pass
  • second portion of the plurality of heat exchange tubes is configured for the second pass
  • a ratio of a number of heat exchange tubes within the first portion and the second portion is about 2.5 to 6.
  • the heat exchanger may be configured for use in a heat pump system.
  • the first header and the second header may be oriented generally horizontally with the plurality of heat exchange tubes extending generally vertically there between.
  • the first header and the second header may be bent to form a C or U-shape.
  • the heat exchanger may be configured with a first pass and a second pass, wherein a first portion of the plurality of heat exchange tubes is configured for the first pass, and a second portion of the plurality of heat exchange tubes is configured for the second pass, and a ratio of a number of heat exchange tubes within the first portion and the second portion is about 0.3 to about 3.
  • a plurality of fins may be disposed in thermal communication with the plurality of heat exchange tubes.
  • the plurality of fins may have a louver length between about 80% and 90 % of a fin height.
  • the plurality of fins may have a louver pitch between about 1 mm and 1.7 mm.
  • the plurality of fins may have a louver angle between about 28 degrees and about 45 degrees.
  • the plurality of fins may have a louver angle of about 32 degrees.
  • the plurality of fins may have a louver angle of about 43 degrees.
  • the plurality of fins may have a fin density between about 10 fins per inch and about 25 fins per inch.
  • the plurality of fins may have a fin thickness between about .07 mm and about .1 mm.
  • the heat exchanger optionally is configured for use in an air conditioning system, with the plurality of fins having a fin density of 23 fins per inch.
  • the plurality of fins may have a fin density of 16 fins per inch.
  • the bend may comprise a ratio of bend radius divided by a total thickness of the heat exchanger.
  • the ratio of the bend radius to the total thickness of the heat exchanger may be greater than 4.
  • the bend may comprise a ratio of bend radius divided by a total thickness of the heat exchanger, with the ratio of the bend radius to the total thickness of the heat exchanger is greater than 10.
  • the heat exchanger may be part of an air management system, wherein the air management system is in fluid communication with the heat exchanger and is configured to impart an airflow having an average face velocity of greater than or equal to 200 feet per minute over an outer surface of the heat exchanger when the system is operating.
  • the air management system may comprise a fan.
  • a noise level of the air management system at a measurement distance of 1 meter from the system may be less than or equal to 65 dBa.
  • Microchannel heat exchangers as outdoor coils entered residential cooling only air conditioning applications and are being considered for the residential heat pump applications as well. Due to regulatory efficiency requirements, sound constraints, and a non-optimized heat exchanger design, the size of the outdoor heat exchanger is typically large. As a result, the heat pump and air conditioning systems incur higher costs and have a higher refrigerant charge. Current legislation limits the amount of charge of refrigerant systems, and heat exchangers in particular, containing most low global warming potential refrigerants (currently classified as A2L substances).
  • Microchannel heat exchangers have a small internal volume and therefore store less refrigerant charge than conventional round tube plate fin heat exchangers. Although a lower refrigerant charge is generally beneficial, the smaller internal volume of microchannel heat exchangers makes them extremely sensitive to overcharge or undercharge situations, which could result in refrigerant charge imbalance, degrade refrigerant system performance, and cause nuisance shutdowns. In addition, the refrigerant charge contained in the manifolds of the microchannel heat exchanger, particularly when the heat exchanger operates as a condenser, is significant, such as about half of the total heat exchanger charge. As a result, the refrigerant charge reduction potential of the heat exchanger is limited.
  • the heat exchanger 20 includes a first manifold or header 30, a second manifold or header 40 spaced apart from the first manifold 30, and a plurality of heat exchange tubes 50 extending in a spaced parallel relationship between and fluidly connecting the first manifold 30 and the second manifold 40.
  • the first header 30 and the second header 40 are oriented generally horizontally and the heat exchange tubes 50 extend generally vertically between the two headers 30, 40.
  • the headers 30, 40 comprise hollow, closed end cylinders having a circular cross-section.
  • headers 30, 40 having other configurations, such as a semi-elliptical, square, rectangular, hexagonal, octagonal, or other cross-sections for example, are within the scope of the disclosure.
  • the heat exchanger 20 may be used as either a condenser or an evaporator in a vapor compression system, such as a heat pump for example.
  • each heat exchange tube 50 comprises a flattened heat exchange tube having a leading edge 52, a trailing edge 54, a first surface 56, and a second surface 58.
  • the leading edge 52 of each heat exchanger tube 50 is upstream of its respective trailing edge 52 with respect to an airflow A through the heat exchanger 20.
  • the interior flow passage of each heat exchange tube 50 may be divided by interior walls into a plurality of discrete flow channels 60 that extend over the length of the tubes 50 from an inlet end 62 to an outlet end 64 and establish fluid communication between the respective first and second manifolds 30, 40.
  • the flow channels 60 may have a circular cross-section, a rectangular cross-section, a trapezoidal cross-section, a triangular cross-section, or another non-circular cross-section (e.g. elliptical, star shaped, closed polygon having straight or curved sides).
  • the heat exchange tubes 50 including the discrete flow channels 60 may be formed using known techniques and materials, including, but not limited to, extrusion or folding.
  • a plurality of heat transfer fins 70 may be disposed between and rigidly attached, usually by a furnace braze process, to the heat exchange tubes 50, in order to enhance external heat transfer and provide structural rigidity to the heat exchanger 20.
  • Each folded fin 70 is formed from a plurality of connected strips or a single continuous strip of fin material tightly folded in a ribbon-like serpentine fashion thereby providing a plurality of closely spaced fins 72 that extend generally orthogonal to the flattened heat exchange tubes 50.
  • the illustrated heat exchanger 20 has a single-pass flow configuration.
  • refrigerant is configured to flow from the first header 30 to the second header through the plurality of heat exchanger tubes 50 in the direction indicated by arrow B.
  • FIGS. 4 and 5 two forms of optimized microchannel heat exchanger 20 having a multi-pass configuration are illustrated.
  • the heat exchanger 20 is illustrated and described herein with reference to a plurality of microchannel tubes 50, embodiments including other types of tubes or conduits connecting the headers 30, 40 are also within the scope of the disclosure.
  • At least one of the first manifold 30 and the second manifold 40 includes two or more fluidly distinct sections or chambers.
  • the fluidly distinct sections are formed by coupling separate manifolds together to form the first or second manifold 30, 40.
  • a baffle or divider plate (not shown) known to a person of ordinary skill in the art may be arranged within at least one of the first header 30 and the second header 40 to define a plurality of fluidly distinct sections therein.
  • a heat exchanger 20 configured for use in an air conditioning system (typically as a condenser) is illustrated in more detail.
  • This heat exchange is outside the scope of the claims.
  • the first header 30 and the second header 40 are arranged substantially vertically such that the plurality of heat exchange tubes 50 extends horizontally there between.
  • the plurality of heat exchanger tubes 50 includes at least one bend.
  • the heat exchange tubes 50 form a substantial C or U-shape between the headers 30, 40.
  • heat exchanger tubes 50 having any number of bends, such as to form an L, V, W, or S-shape for example, are also within the scope of the disclosure.
  • the heat exchanger 20 has a two-pass configuration, with each of the first header 30 and second header 40 being divided into a first section and a second section.
  • a gaseous refrigerant is provided to a first section 30a of the first header 30 via an inlet 80.
  • the refrigerant flows through a first group 50a of heat exchange tubes 50 to the first section 40a of the second header 40.
  • the refrigerant then passes into the second section 40b of the second header 40, through the second group 50b of heat exchange tubes 50, and into the second section 30b of the first header 30.
  • Refrigerant within the second section 30b of the first header 30 may be provided to a downstream component of the system via an outlet 82.
  • the refrigerant flows sequentially through the first and second groups 50a, 50b of heat exchanger tubes 50, heat from the refrigerant is transferred to an adjacent flow of air A.
  • a substantially liquid refrigerant is provided at the outlet 82.
  • a heat exchanger having two passes illustrated and described herein is intended as an example only, and that a heat exchanger having any number of passes is also within the scope of the disclosure.
  • the number of passes of the heat exchanger 20 may be selected between 1 and 4 depending on the system capacity, refrigerant charge, and thermodynamic efficiency.
  • the heat exchanger 20 is generally optimized to minimize size and cost while similarly reducing refrigerant charge for a variety of air management systems and airflow configurations. Regardless of the pass configuration, the heat exchanger 20 may have a face area between about 30% and about 60% of a baseline round tube plate fin heat exchanger.
  • an air management system including a fan is configured to move air over an outer surface of the heat exchanger 20 with a face velocity of up to three times that of a baseline conventional propeller fan. For example, when the air management system is configured as an air conditioning system, the minimum face velocity is about 270 ft/min and when the air management system is configured as a heat pump syste, the minimum face velocity is about 220 ft/min.
  • the heat exchanger 20 may also be configured such that a ratio of the heat exchange tubes 50a in the first pass to the heat exchange tubes 50b in the second pass is about 2.5 to 6.
  • a ratio of the length of the heat exchanger 20 to the height of the heat exchanger 20 measured in a plane coinciding with the face area of the heat exchanger 20 e.g. a plane perpendicular to the dimension along which the tube depth is measured
  • the aspect ratio is between about 2 and 6.
  • a heat exchanger 20 configured for use in a heat pump system also has a shape including at least one bend.
  • the illustrated heat exchanger 20 has a C or U-shape similar to the heat exchanger 20 of FIG. 4 .
  • the at least one bend is formed in the first header 30 and the second header 40, not the tubes 50.
  • Each of the first header 30 and the second header 40 is generally divided into a first, second, and third section, respectively.
  • a first group 50a of heat exchanger tubes 50 extends vertically between the first sections 30a, 40a of the first and second header 30, 40
  • a second group 50b of heat exchanger tubes 50 extends vertically between the second sections 30b, 40b of the first and second header 30, 40
  • a third group 50c of heat exchanger tubes 50 extends vertically between the third sections 30c, 40c of the first and second header 30, 40.
  • a length of the first and third sections of the headers 30, 40 and the number of tubes 50 within the first and third groups 50a, 50c are substantially identical.
  • the heat exchanger 20 of FIG. 5 has a two-pass flow configuration, a configuration including any number of passes, for example between 2 and 5 passes is within the scope of the disclosure.
  • the direction of fluid through the heat exchanger 20 may depend on the mode in which the heat pump is being operated. For example, when the heat exchanger 20 is configured to operate as an evaporator and heat the fluid therein, a two-phase refrigerant mixture is provided via an inlet (not shown) to the second section 30b of the first header 30. Within the second section 30b, the refrigerant is configured to flow through the second group 50b of tubes 50 to the second section 40b of the second header 40.
  • the fluid flow is configured to divide such that a portion of the fluid flows into the first section 40a of the second header 40 and a portion of the fluid flows into the third section 40c of the second header 40, and through the first and third groups of tubes 50a, 50c, simultaneously.
  • the fluid is provided via outlets 80 to a conduit (not shown) where the fluid is rejoined and provided to a downstream component of a vapor compression system.
  • refrigerant flows sequentially through the second and first groups 50b, 50a of heat exchanger tubes 50, or alternatively, through the second and third groups 50b, 50c of heat exchanger tubes 50, heat from an adjacent flow of air A, is transferred to the refrigerant.
  • a substantially vaporized refrigerant is provided at the outlets 80.
  • refrigerant is configured to flow in a reverse direction through the heat exchanger 20 when operated as a condenser.
  • the face area of the heat exchanger 20 configured for use in a heat pump is between about 30% and about 70% of the baseline round tube plate fin heat exchanger with a higher face velocity of up to three times a baseline conventional propeller fan. This increased face velocity occurs as a result of the combination of increased air flow and the smaller face area of the heat exchanger 20.
  • the noise generated by the heat exchanger 20 may be reduced compared to conventional heat exchangers.
  • the noise of a system containing by the heat exchanger 20 is at or below an allowable noise level for residential applications.
  • the noise level of a refrigerant system measured at a distance of 1 meter from the system is less than or equal to 65dBa.
  • the heat exchanger 20 may also be configured such that when operated as a condenser, a ratio of the heat exchange tubes 50 in the first pass (50a and 50c) to the second pass (50b) is about .3 to 3. In another embodiment, the aspect ratio of the heat exchanger 20 is between about 2 and 6.
  • the size of the headers 30, 40 is such that the headers 30, 40 have an inner diameter equal to a width of one of the heat exchange tubes 50 plus 1-4 mm (millimeters).
  • the tubes 50 of the heat exchangers 20 may have a depth between about 8 mm and 16 mm, and in an embodiment between about 10 to 12 mm, or 10 mm.
  • the tubes 50 may have a depth between about 12 mm and 22 mm, more specifically 14 to 16 mm.
  • the tubes 50 may have a height of about 1.3 mm ⁇ .3 mm.
  • the tubes of the heat exchanger 20 may additionally have a tube pitch between about 8.9 mm and 15.5 mm, e.g., 9.3 mm.
  • the fins 70 mounted to each of the plurality of tubes 50 may have a louver length between about 80%-90% of the fin height, a louver pitch between about 0.8 mm and 1.7 mm, e.g., 1.3 mm, and a louver angle between 28 degrees and 47 degrees.
  • the louver angle of the fins 70 in a heat exchanger 20 configured for use in an air conditioning system is about 30 degrees and the louver angle in a heat exchanger configured for use in a heat pump is about 45 degrees.
  • the fin density in a heat exchanger 20 for use in an air conditioning system may be between about 18-25 fins/inch, e.g., 23 fins per inch.
  • the fin density of a heat exchanger 20 configured for use in a heat pump may be between about 12-18 fins/inch, e.g., about 16 fins per inch.
  • the heat exchangers 20 provided herein result in a substantial size and therefore cost reduction, between 30 and 70% compared to other heat exchangers. Further, this reduced size can allow for refrigerant charge of the system to be reduced from 50-70% compared to the baseline heat exchanger.
  • the heat exchangers 20 additionally have a higher performance due to improvements in both refrigerant and air distribution, along with the optimal heat transfer and hydraulic resistance balance by optimizing the number of refrigerant passes and airflow.
  • the heat exchanger 20 has a multi-slab configuration such that the heat exchanger 20 includes at least a first slab 80 and a second, substantially identical slab 82 arranged downstream from the first slab 80 relative to an airflow A.
  • the plurality of heat exchange tubes 50, or alternatively, the headers 30, 40 include at least one bend to form the first heat exchanger slab 80 and the second heat exchanger slab 82.
  • the first slab 80 and the second slab 82 may be distinct.
  • FIG. 6 Various configurations of a heat exchanger 20 having a first and second heat exchanger slab 80, 82 are illustrated in FIG. 6 . It should be understood that embodiments including more than two heat exchanger slabs are also within the scope of the disclosure.
  • a total thickness of the heat exchanger 20 is measured between an exterior surface of a first heat exchanger slab and an exterior surface of the furthest heat exchanger slab of the heat exchanger 20.
  • the ratio of the bend radius (measured to a centerline of the heat exchanger 20) to the total thickness of the heat exchanger 20 at the bend is greater than 10, and in an embodiment is equal to about 15 ⁇ 4.
  • the ratio of the bend radius to the total thickness of the heat exchanger at the bend is greater than 4, and in an embodiment is equal to about 7 ⁇ 2.5.
  • a spacer may be positioned on opposing sides of the bend to prevent the adjacent portions from contacting one another.

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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 (15)

  1. Wärmetauscher, umfassend:
    ein erstes Sammelrohr (30);
    ein zweites Sammelrohr (40);
    eine Vielzahl von Wärmetauscherrohren (50), die in beabstandeter paralleler Beziehung angeordnet sind und das erste Sammelrohr und das zweite Sammelrohr fluidisch koppeln;
    wobei das erste Sammelrohr und das zweite Sammelrohr jeweils eine Biegung einschließen, wobei der Wärmetauscher nach Bildung der Biegung ein Seitenverhältnis zwischen 2 und 6 aufweist, wobei das Seitenverhältnis ein Verhältnis einer Länge des Wärmetauschers zu einer Höhe des Wärmetauschers ist; und
    dadurch gekennzeichnet, dass ein Innendurchmesser des ersten Sammelrohrs und des zweiten Sammelrohrs gleich einer Breite von einem der Vielzahl von Wärmetauscherrohren plus 1-4 mm ist.
  2. Wärmetauscher nach Anspruch 1, wobei die Vielzahl von Wärmetauscherrohren (50) eine Rohrtiefe zwischen 8 mm und 20 mm aufweist.
  3. Wärmetauscher nach Anspruch 2, wobei, wenn der Wärmetauscher zur Verwendung in einem Kühlsystem mit einer Kapazität von weniger als drei Tonnen konfiguriert ist, die Tiefe der Vielzahl von Wärmetauscherrohren (50) etwa 10 mm, etwa 12 mm oder etwa 16 mm beträgt.
  4. Wärmetauscher nach einem der vorstehenden Ansprüche, wobei die Vielzahl von Wärmetauscherrohren (50) eine Höhe von 1,3 mm ± ,3 mm aufweist.
  5. Wärmetauscher nach einem der vorstehenden Ansprüche, wobei die Vielzahl von Wärmetauscherrohren (50) einen Rohrabstand zwischen 8,9 mm und 15,5 mm wie etwa 9,3 mm aufweist.
  6. Wärmetauscher nach einem der vorstehenden Ansprüche, wobei der Wärmetauscher zur Verwendung in einem Klimaanlagensystem konfiguriert ist.
  7. Wärmetauscher nach einem der vorstehenden Ansprüche, wobei der Wärmetauscher zur Verwendung in einem Wärmepumpensystem konfiguriert ist.
  8. Wärmetauscher nach Anspruch 7, wobei das erste Sammelrohr (30) und das zweite Sammelrohr (40) im Allgemeinen horizontal ausgerichtet sind und sich die Vielzahl von Wärmetauscherrohren (50) im Allgemeinen vertikal dazwischen erstrecken, wobei vorzugsweise das erste Sammelrohr (30) und das zweite Sammelrohr (40) gebogen sind, um eine C- oder U-Form zu bilden.
  9. Wärmetauscher nach Anspruch 7 oder 8, wobei der Wärmetauscher mit einem ersten Durchgang und einem zweiten Durchgang konfiguriert ist, wobei ein erster Abschnitt der Vielzahl von Wärmetauscherrohren für den ersten Durchgang konfiguriert ist und ein zweiter Abschnitt der Vielzahl von Wärmetauscherrohren für den zweiten Durchgang konfiguriert ist, wobei ein Verhältnis einer Anzahl von Wärmetauscherrohren innerhalb des ersten Abschnitts und des zweiten Abschnitts 0,3 bis 3 beträgt.
  10. Wärmetauscher nach einem der vorstehenden Ansprüche, wobei eine Vielzahl von Rippen in thermischer Verbindung mit der Vielzahl von Wärmetauscherrohren angeordnet ist; wahlweise; wobei die Vielzahl von Rippen eine Lamellenlänge zwischen 80 % und 90 % einer Rippenhöhe aufweist; und/oder wobei wahlweise die Vielzahl von Rippen einen Lamellenabstand zwischen 1 mm und 1,7 mm aufweist; und/oder wobei wahlweise die Vielzahl von Rippen einen Lamellenwinkel zwischen 28 Grad und 45 Grad, wie 32 Grad oder 43 Grad, aufweist, wenn der Wärmetauscher zur Verwendung in einem Klimaanlagensystem bzw. einem Wärmepumpensystem konfiguriert ist.
  11. Wärmetauscher nach Anspruch 10, wobei die Vielzahl von Rippen eine Rippendichte zwischen 10 Rippen pro Zoll und 25 Rippen pro Zoll aufweist.
  12. Wärmetauscher nach Anspruch 10 oder 11, wobei die Vielzahl von Rippen eine Rippendicke zwischen .7mm und .1mm aufweiset, wobei wahlweise, wenn der Wärmetauscher zur Verwendung in einem Klimaanlagensystem konfiguriert ist, die Vielzahl von Rippen eine Rippendichte von 23 Rippen pro Zoll aufweist, oder wobei, wenn der Wärmetauscher zur Verwendung in einem Wärmepumpensystem konfiguriert ist, die Vielzahl von Rippen eine Rippendichte von 16 Rippen pro Zoll aufweist.
  13. Wärmetauscher nach einem der vorstehenden Ansprüche, wobei die Biegung weiter ein Verhältnis von Biegeradius dividiert durch eine Gesamtdicke des Wärmetauschers umfasst, wobei das Verhältnis größer als 4 ist.
  14. Wärmetauscher nach einem der vorstehenden Ansprüche, wobei die Biegung weiter ein Verhältnis von Biegeradius dividiert durch eine Gesamtdicke des Wärmetauschers umfasst, wobei das Verhältnis größer als 10 ist.
  15. System, umfassend:
    den Wärmetauscher nach einem der vorstehenden Ansprüche; und
    ein Luftmanagementsystem, das in Fluidverbindung mit dem Wärmetauscher steht und konfiguriert ist, um einen Luftstrom mit einer durchschnittlichen Anströmgeschwindigkeit von größer oder gleich 200 Fuß pro Minute über eine Außenoberfläche des Wärmetauschers zu übertragen, wenn das System in Betrieb ist.
EP15804581.5A 2015-10-12 2015-10-12 Wärmetauscher für hlk-geräte im wohnbereich Active EP3362759B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IB2015/002175 WO2017064531A1 (en) 2015-10-12 2015-10-12 Heat exchanger for residential hvac applications

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EP3362759A1 EP3362759A1 (de) 2018-08-22
EP3362759B1 true EP3362759B1 (de) 2022-07-27

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US (1) US20180299205A1 (de)
EP (1) EP3362759B1 (de)
WO (1) WO2017064531A1 (de)

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