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
  • 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
• • 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
  • F28D1/053—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 straight
  • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
  • F28D1/05333—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
• • 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
  • F28F9/0243—Header boxes having a circular cross-section
• • 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
  • F28D1/053—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 straight
  • F28D1/0535—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 straight the conduits having a non-circular cross-section
  • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
• • 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
  • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
  • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
  • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
• • 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
  • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
  • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
  • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
  • F28F1/128—Fins with openings, e.g. louvered fins
• • 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
• • 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
  • F28D2001/0253—Particular components
  • F28D2001/026—Cores
  • F28D2001/0273—Cores having special shape, e.g. curved, annular
• • 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 heat exchanger, and more particularly to a bent parallel flow heat exchanger. Background technique
• Heat exchangers such as parallel flow heat exchangers (such as multi-channel heat exchangers), are widely used in refrigeration systems.
• the heat exchanger needs to be bent, that is, the manifold of the heat exchanger is bent.
• the heat exchanger is bent along the length of the header, if the bending is improper, it will adversely affect the heat exchange performance of the heat exchanger, or the application requirements cannot be met, so there is a bending heat exchanger. Improved demand. Summary of the invention
• the heat exchanger When the heat exchanger is bent along the length of the header, if the bending radius is too large, when the installation space of the heat exchanger is limited, the application requirements cannot be met. If the bending radius is too small, the flat tube of the heat exchanger will be deformed, the fins will be torn, and the heat exchange efficiency will be affected, thereby reducing the performance and even causing the flat tube to leak, and the heat exchanger is scrapped. In addition, excessive extrusion deformation of the header increases the pressure loss of the refrigerant in the header and reduces the performance of the heat exchanger. Therefore, the inventors realized that the control of the bending parameters is a factor that affects the performance, reliability, and ease of installation and application of the bending heat exchanger.
• an object of the present invention is to provide a bending heat exchanger, which can control the bending radius of the collecting pipe by designing the structural parameters of the collecting pipe, the flat pipe and the fin, and can realize the heat exchanger along the set.
• a bending heat exchanger includes: a first header and a second header, each of the first header and the second header having at least one bent section and a straight line segment adjacent to the bending section, the bending section of the first header corresponds to the bending section of the second header; the plurality of flat tubes, the two ends of the flat tube respectively a first header and a second header are connected, a plurality of the flat tubes are spaced apart from each other along an axial direction of the first header and the second header; and fins, the fins are disposed at Between adjacent flat tubes, the fins extend in a corrugated shape along a length of the flat tube, and the fins include a straight section and a circular arc section connected between the straight sections, the fins
• the thickness of the FT is FT
• the first and second headers have different outer diameters, wherein a larger outer diameter of the outer diameters of the first and second headers is 0D
• the first and the first The two headers have different wall thicknesses, wherein
• a bending heat exchanger includes: a first header and a second header, each of the first header and the second header having at least one bend a segment and a straight line segment adjacent to the bent portion, the bent portion of the first header corresponds to the bent portion of the second header; the plurality of flat tubes, the two ends of the flat tube are respectively The first header and the second header are connected, and the plurality of flat tubes are spaced apart from each other along an axial direction of the first header and the second header; and fins, the fins Provided between adjacent flat tubes, the fins extending in a corrugated shape along a length direction of the flat tubes, the fins including a straight section and a circular arc section connected between the straight sections, The thickness of the fin is FT, the first and second headers have the same outer diameter, and the outer diameters of the first and second headers are 0D, the first and second headers Having
• the thickness FT of the fin and the arc angle FR of the top of the fin and the height FH of the fin produce a significant tensile stress on the stretching of the fin during bending, and the tensile stress is set to Sfin, when Sfin exceeds the fin and When the yield strength of the welded portion of the flat tube is ⁇ s , the fin is easily separated from the flat tube, and even the fin is broken.
• the wall thickness ⁇ of the header and the outer diameter 0D produce significant bending stress during bending, and the bending stress is set to Shd. When Shd exceeds the tensile strength ⁇ b of the header, the current is collected. The tube will fail and will fail under certain pressure conditions.
• the relative stress Sfin/ ⁇ s on the fin and the relative tensile stress Shd/ ⁇ b on the collector tube and the fin under different application conditions of the bending radius R There is a certain relationship between the composite parameter (100 XFTXFRXT)/(FHXOD) and the collector. Among them, the relative stress Sf in / ⁇ s on the fin decreases as the composite parameter increases, and rises rapidly when it is lowered and close to 0, and generally decreases as the bending radius R increases.
• the relative tensile stress Shd/ ⁇ b on the header decreases first as the composite parameter increases (the strength is insufficient when the relative wall thickness of the header is thin), and then gradually rises (the relative wall thickness of the header) The deformation stress of the bend increases when thicker).
• the conventional copper tube fin-type heat exchanger has a common bending radius of more than R50mm.
• the lower limit of the composite parameter (100XFTXFRXT) / (FHX0D) is determined to be 0.01, respectively, according to the relative stress Sfin / ⁇ s and the relative tensile stress Shd / ⁇ b should be less than 1 to ensure that the bending strength does not cause failure.
• the upper limit is 9. Through the determination of the range, the microchannel heat exchanger does not have obvious fin cracking and collector tube deformation failure or blasting failure when the header is bent.
• the bending heat exchanger When the relationship of 0.01 (100XFTXFRXT) / (FHX0D) 9 is satisfied, after the bending heat exchanger is bent along the length direction of the first header and the second header, not only It is ensured that the fins are not torn and the flat tube is not deformed, and that the core has sufficient burst strength.
• the variation of the heat exchange performance of the bending heat exchanger can be limited to 4% (compared with before bending the bend heat exchanger), and no significant filling imbalance is generated.
• the condensate drainage performance of the bent heat exchanger is also optimal. Therefore, the bending heat exchanger according to the embodiment of the invention has the advantages of reasonable structure, stable structure, high heat exchange efficiency, good heat exchange performance, high reliability, convenient installation and application, and good drainage performance.
• the bending heat exchanger according to the above embodiment of the present invention may further have the following additional technical features: 0.0004 (FTXFR) / (FHX0D) 0.59 according to an embodiment of the present invention.
• 0.0061 FR/FH 0.6 0.0061 FR/FH 0.6.
• 0.04 T/0D 0.25.
• 0.0005 FT/0D 0.015 0.0005 FT/0D 0.015.
• 0.0016 FR/0D 0.4 0.0016 FR/0D 0.4.
• 0.05 FH/0D 2 0.05 FH/0D 2 .
• the bending heat exchanger is C-shaped or L-shaped.
• FIG. 1 is a perspective view of a bending heat exchanger according to an embodiment of the present invention.
• FIG. 2 is a schematic view of a bending heat exchanger before bending according to an embodiment of the present invention
• 3 is a schematic view of a bent header of a bending heat exchanger according to an embodiment of the present invention
• FIG. 4 shows a header and a flat tube of a bending heat exchanger according to an embodiment of the present invention.
• Figure 5 is a schematic illustration of a fin of a bend heat exchanger in accordance with an embodiment of the present invention.
• Figure 6 is a graph showing the relative stresses on the fins at different bend radii and the relative tensile stresses on the first and second headers versus the composite parameters.
• a bending heat exchanger 10 includes a first header 101, a second header 102, fins 104, and a plurality of flat tubes 103.
• Each of the first header 101 and the second header 102 has at least one bent section 1011 and a straight section 1012 adjacent to the bent section 1011.
• the bent section 1011 of the first header 101 corresponds to the bent section 1011 of the second header 102.
• Both ends of the flat tube 103 are connected to the first header 101 and the second header 102, respectively, and the plurality of flat tubes 103 are spaced apart from each other along the axial direction of the first header 101 and the second header 102.
• the fins 104 are disposed between adjacent flat tubes 103, and the fins 104 are corrugated along the length of the flat tubes 103.
• the fins 104 include a straight section 1041 and a circular arc section connected between the straight sections 1041. 1042.
• the thickness of the fins 104 is FT
• the first header 101 and the second header 102 may have different outer diameters, wherein the outer diameters of the first header 101 and the second header 102 are larger
• the outer diameter is 0D.
• the first header 101 and the second header 102 may have the same outer diameter and both have an outer diameter of 0D.
• the first header 101 and the second header 102 may have different wall thicknesses, and the larger wall thickness of the first header 101 and the second header 102 is T, optionally, A header 101 and a second header 102 may have the same wall thickness and both have a wall thickness of ⁇ .
• the width of the flat tube 103 is W
• the radius of the arc of the fin 104 is FR
• the height of the fin 104 is FH, where 0. 01 ⁇ (100 X FT X FRX T) / (FHX 0D) ⁇ 9 o
• the first header 101 and the second header 102 may have the same outer diameter OD or may have different outer diameters.
• the larger of the outer diameters of the first header 101 and the second header 102 is 0D, and the first header 101 It has the same wall thickness T as the second header 102, and may have different wall thicknesses.
• the first header 101 and the second header 102 have different wall thicknesses
• the first header 101 and The larger wall thickness of the second header 102 is ⁇
• the inventors of the present application have found that the first header 101 and the second header 102 have different outer diameters and wall thicknesses, and the outer diameter Larger and/or larger wall thickness collectors are relatively difficult to bend and are significantly affected by the bend.
• the first episode The flow tube 101 and the second header 102 may have the same outer diameter and wall thickness, and in the case where the first header 101 and the second header 102 have the same outer diameter and/or wall thickness, the outer diameter is 0D It may be an outer diameter of any one of the first header 101 and the second header 102, and the wall thickness T may be a wall thickness of any one of the first header 101 and the second header 102.
• the thickness of the core (the width W of the flat tube 103)
• reducing the bending radius R causes the overall burst strength of the core to decrease, so it is necessary to increase the walls of the first header 101 and the second header 102.
• Thick the outer diameters of the first header 101 and the second header 102 are constant
• first header 101 and second The wall thickness of the header 102 is constant) to meet the strength requirements.
• increasing the wall thickness of the first header 101 and the second header 102 not only increases the cost, but also causes a decrease in the internal volume of the first header 101 and the second header 102.
• the arc of the top of the fin 104 is stretched after being bent, so the fin
• the greater the radius of the arc at the top of 104 the greater the stretch can be produced, thereby being able to withstand greater bending stresses and avoid tearing at the weld due to excessive stretching of the fins 104.
• an excessive radius of the arc causes the condensed water to accumulate at the arc due to the surface tension, and is not easily discharged to the outside of the fin 104.
• increasing the radius of the arc of the top of the fins 104 also increases the risk of collapse of the fins 104 after welding.
• the strength of the fins 104 is proportional to the thickness of the fins 104.
• the thicker fins 104 resist greater bending stress, so that the bent flat tubes 103 are less susceptible to wave deformation.
• increasing the thickness of the fins 104 not only causes an increase in the cost of the bent heat exchanger 10, but also causes an increase in ventilation resistance, which degrades the performance of the unit.
• the height of the fins 104 also affects the bending performance.
• the height of the fins 104 is too high.
• the larger the pitch of the flat tubes 103 the more the support force for the first header 101 and the second header 102 per unit length. Small, the first collector tube 101 and the second header 102 are more easily deformed after bending.
• the thickness FT of the fin 104 and the arc angle FR of the top of the fin 104 and the height FH of the fin 104 produce a significant tensile stress on the stretching of the fin 104 when bent, and the tensile stress is set to Sfin, when Sfin
• the yield strength ⁇ s of the welded portion of the fin 104 and the flat tube 103 is exceeded, the fin 104 is easily separated from the flat tube 103, and even the fin 104 is broken.
• the wall thickness ⁇ and the outer diameter OD of the first header 101 and the second header 102 cause significant bending stress during bending, and the bending stress is set to Shd, when Shd exceeds the first set.
• the tensile strength ob of the flow tube 101 and the second header 102 is reached, the first header 101 and the second header 102 may fail and cause failure under a certain pressure condition.
• the fins The relative stress Sf in / ⁇ s on 104 and the relative tensile stress Shd / 0 b on the first header 101 and the second header 102 and the fins 104, the first header 101 and the second current collector
• the composite parameter of the tube 102 (100 ?1 ?) ⁇ 1 /(?1 ⁇ 00) has a certain relationship.
• the relative stress Sfin / ⁇ s on the fin 104 increases with the composite parameter. Large and decreasing, and rising rapidly with decreasing and close to 0, and generally decreasing as the bending radius R increases.
• Relative tensile stress Shd on the first header 101 and the second header 102 / ⁇ b decreases first as the composite parameter increases (the strength of the first collector tube 101 and the second header 102 is relatively thin when the relative wall thickness is thin), and then gradually rises (the first header 101 and When the opposing wall thickness of the second header 102 is thick, the deformation stress of the bending increases.
• the conventional copper tube fin-type heat exchanger has a common bending radius of more than R50mm.
• the lower limit of the composite parameter (100XFTXFRXT) / (FHX0D) is determined to be 0.01, respectively, according to the relative stress Sfin / ⁇ s and the relative tensile stress Shd / ⁇ b should be less than 1 to ensure that the bending strength does not cause failure.
• the upper limit is 9. By the determination of the range, the bent heat exchanger 10 does not exhibit significant fin breakage and collector deformation failure or blast failure when the first header 101 and the second header 102 are bent.
• the bending heat exchanger 10 according to the embodiment of the invention has the advantages of reasonable structure, stable structure, high heat exchange efficiency, good heat exchange performance, high reliability, convenient installation and application, and good drainage performance.
• the axial directions of the first header 101 and the second header 102 may be the longitudinal directions of the first header 101 and the second header 102.
• the large wall thickness T, the width W of the flat tube 103, the arc radius FR of the fin 104, and the length of each of the fins 104 height FH are in millimeters, 0.01 mm (100X FTX FRXT) / (FHX0D) 9 Mm, the same as below.
• the bend heat exchanger 10 can be C-shaped.
• the bend heat exchanger 10 is bent three times along the length direction of the first header 101 and the second header 102. That is, each of the first header 101 and the second header 102 may include three bent segments 1011 and four straight segments 1012, and each bent segment 1011 is located adjacent to two straight lines Between segments 1012.
• bent heat exchanger 10 may also be L-shaped.
• the thickness FT of the fin 104, the arc radius FR of the fin 104, the height FH of the fin 104, and the larger outer diameter OD of the outer diameters of the first header 101 and the second header 102 may satisfy The following relationship: 0.0004 (FT XFR) / (FHX0D) ⁇ 0.59.
• 0.004 ⁇ (FTXFR)/(FHX0D) ⁇ 0.3.
• the thickness of the fin 104, the radius FR of the fin 104, and the height FH of the fin 104 can satisfy the following relationship:
• 0.05 (FTXFR) / FH ⁇ 3c is further preferably 0. K (FTXFR) / FH 2 .
• the thickness FT of the fin 104 and the height of the fin 104 FH can satisfy the following relationship: 0.002 ⁇ FT/FH ⁇ 0.04.
• the arc radius FR of the fin 104 and the height FH of the fin 104 can satisfy the following relationship: 0.0061 ⁇ FR/FH ⁇ 0.6. Thereby, it is possible to further ensure that the fins 104 are not torn, the flat tube 103 is not deformed, and the core body has sufficient burst strength, and the heat exchange efficiency and drainage performance of the bending heat exchanger 10 can be further improved.
• 0.05 FR/FH 0.1 thereby, it is possible to further ensure that the fins 104 are not torn, the flat tube 103 is not deformed, and the core body has sufficient burst strength, and the heat exchange efficiency and drainage performance of the bending heat exchanger 10 can be further improved.
• the larger wall thickness T of the wall thicknesses of the first header 101 and the second header 102 and the larger outer diameter OD of the outer diameters of the first header 101 and the second header 102 may satisfy the following Relational expression: 0. 04 ⁇ T/0D ⁇ 0. 25.
• the fin 104 can be further prevented from being torn, the flat tube 103 is not deformed, and the core has sufficient burst strength, and the heat exchange efficiency and drainage performance of the bending heat exchanger 10 can be further improved.
• the thickness FT of the fins 104 and the larger outer diameter 0D of the outer diameters of the first header 101 and the second header 102 can satisfy the following relationship: 0. 0005 FT/0D 0. 015. Thereby, it is possible to further ensure that the fins 104 are not torn, the flat tube 103 is not deformed, and the core body has sufficient burst strength, and the heat exchange efficiency and drainage performance of the bending heat exchanger 10 can be further improved.
• the fins 104 are not torn, the flat tube 103 is not deformed, and the core body has sufficient burst strength, and the heat exchange efficiency and drainage performance of the bending heat exchanger 10 can be further improved.
• the arc radius FR of the fin 104 and the larger outer diameter 0D of the outer diameters of the first header 101 and the second header 102 can satisfy the following relationship: 0. 0016 FR/0D 0.4. Thereby, it is possible to further ensure that the fins 104 are not torn, the flat tube 103 is not deformed, and the core body has sufficient burst strength, and the heat exchange efficiency and drainage performance of the bending heat exchanger 10 can be further improved.
• the fins 104 are not torn, the flat tube 103 is not deformed, and the core body has sufficient burst strength, and the heat exchange efficiency and drainage performance of the bending heat exchanger 10 can be further improved.
• the fin 104 height FH and the larger outer diameter 0D of the outer diameters of the first header 101 and the second header 102 may be sufficient for the following relationship: 0. 05 FH/0D 2.
• first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated.
• features defining “first”, “second” may include at least one of the features, either explicitly or implicitly.
• the meaning of “plurality” is at least two, such as two, three, etc., unless specifically defined otherwise.
• the terms “installation”, “connected”, “connected”, “fixed” and the like are to be understood broadly, and may be either a fixed connection or a detachable connection, unless otherwise explicitly stated and defined. , or integrated; can be mechanical or electrical; can be directly connected, or indirectly connected through an intermediate medium, can be the internal communication of two elements or the interaction of two elements, unless otherwise specified Limited.
• the specific meaning of the above terms in the present invention can be understood by those skilled in the art on a case-by-case basis.
• the first feature "on” or “below” the second feature may be the direct contact of the first and second features, or the first and second features may be indirectly through the intermediate medium, unless otherwise explicitly stated and defined. contact.
• the first feature "above”, “above” and “above” the second feature may be that the first feature is directly above or above the second feature, or merely that the first feature level is higher than the second feature.
• the first feature “below”, “below” and “below” the second feature may be that the first feature is directly below or obliquely below the second feature, or merely that the first feature level is less than the second feature.
• the description of the terms “one embodiment”, “some embodiments”, “example”, “specific example”, or “some examples” and the like means a specific feature described in connection with the embodiment or example.
• a structure, material or feature is included in at least one embodiment or example of the invention.
• the schematic representation of the above terms is not necessarily directed to the same embodiment or example.
• the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples.
• various embodiments or examples described in the specification, as well as features of various embodiments or examples may be combined and combined.

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

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• 2014
  • 2014-05-06 CN CN201410188198.0A patent/CN103925745B/zh active Active
• 2015
  • 2015-05-06 WO PCT/CN2015/078406 patent/WO2015169231A1/zh not_active Ceased
  • 2015-05-06 MX MX2016014494A patent/MX386160B/es unknown
  • 2015-05-06 KR KR1020167033719A patent/KR101897385B1/ko active Active
  • 2015-05-06 EP EP15788925.4A patent/EP3141858B1/de active Active
  • 2015-05-06 US US15/308,421 patent/US20170059252A1/en not_active Abandoned

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