EP2865980A1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- EP2865980A1 EP2865980A1 EP20140177274 EP14177274A EP2865980A1 EP 2865980 A1 EP2865980 A1 EP 2865980A1 EP 20140177274 EP20140177274 EP 20140177274 EP 14177274 A EP14177274 A EP 14177274A EP 2865980 A1 EP2865980 A1 EP 2865980A1
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- EP
- European Patent Office
- Prior art keywords
- header
- heat exchanger
- flow
- refrigerant
- tubes
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
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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
- F28D1/053—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
- F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
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- 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
-
- 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
- F25B39/04—Condensers
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- 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
- F25B41/00—Fluid-circulation arrangements
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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
- F28D1/053—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
- F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
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- 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
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
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- 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
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
- F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
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- 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
- F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
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- 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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/02—Details of evaporators
- F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
- F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
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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
- 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
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- 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
- F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
Definitions
- the present invention relates to a heat exchanger, particularly to a heat exchanger provided with a header having an improved performance of distribution of a refrigerant.
- a heat exchanger which is an apparatus causing a refrigerant to exchange heat with external air, generally includes tubes having a refrigerant flowing therethrough and arranged to exchange heat with external air, a heat exchange fin contacting the tubes to increase the heat dissipation area, and a header allowing ends of the tubes to communicate with each other in order to guide the refrigerant to the tubes and adapted to support the tubes.
- Heat exchangers include a fin tube type heat exchanger, which is configured by inserting a heat transfer pipe formed of copper into a thin heat exchange fin formed of aluminum, and a parallel flow type heat exchanger, which is configured by disposing the heat exchange fin between the tubes having multiple micro-channels and formed of aluminum and arranging the tubes such that they are supported by a pair of headers.
- the parallel flow type heat exchanger is known to be relatively inexpensive and have high efficiency.
- a parallel flow type heat exchanger with vertical headers is used as an evaporator of an outdoor unit
- distribution of a refrigerant from the vertical headers to the tubes becomes unbalanced due to gravity and variation of physical properties of the refrigerant according to a physical phase of the refrigerant.
- the refrigerant may be distributed only to some of the tubes.
- the parallel flow type heat exchanger is often used only as a condenser.
- a heat exchanger includes a plurality of tubes disposed horizontally, a heat exchange fin to contact the tubes, a first header vertically disposed to communicate with one end of each of the tubes, a second header vertically disposed to communicate with the other end of each of the tubes, at least one flow passage defining baffle mounted to at least one header of the first header and the second header and adapted to define a flow passage of a refrigerant by interrupting flow of the refrigerant in the at least one header in a longitudinal direction and to divide the tubes into n (n ⁇ 2, where n is an even number) groups, each of the groups having tubes adjoining each other and allowing the refrigerant to flow in one direction therethrough and the number of the at least one flow passage defining baffle being n-1, and at least one flow distribution baffle mounted to a corresponding header of the first header and the second header arranged at an inlet of one group of the n groups such that the flow distribution baffle is positioned between the tubes belonging
- the flow distribution baffle may be positioned between the tubes belonging to the last group of the n groups arranged in a direction of flow of the refrigerant when the heat exchanger operates as an evaporator.
- the distribution hole may be spaced from an inner side surface of the corresponding header at an opposite side to the tubes of the corresponding header such that flow of the refrigerant along the inner side surface at the opposite side is interrupted.
- a cross section of each of the at least one distribution hole may have a shape of one of polygon, circle, and other different closed figures.
- the at least one distribution hole may include a hole formed in the flow distribution baffle and a hole formed between the flow distribution baffle and the inner side surface of the corresponding header by mounting the flow distribution baffle to the corresponding header.
- a total cross-sectional area of the at least one distribution hole may be 1 % to 40 % of a cross-sectional area of an inner surface of the corresponding header.
- Each of the groups may have 2 to 15 tubes.
- n 4
- the number of the at least one flow passage defining baffle may be 3
- the tubes may be divided into four groups.
- One header of the first header and the second header may be provided with an inlet pipe and an outlet pipe, and the flow distribution baffle may be mounted to the other header of the first header and the second header.
- the refrigerant may flow upward in the first header and the second header when the heat exchanger operates as an evaporator, and the refrigerant may flow downward in the first header and the second header when the heat exchanger operates as a condenser.
- the heat exchanger may further include at least one flow speed boosting baffle mounted to a corresponding header of the first header and the second header arranged at an inlet of one group of the n groups such that the flow speed boosting baffle is positioned between the one group and another group positioned immediately ahead of the one group in a direction of flow of the refrigerant when the heat exchanger operates as an evaporator, each of the at least one flow speed boosting baffle being provided with at least one boosting hole allowing the refrigerant to pass therethrough.
- the at least one flow speed boosting baffle may be positioned between the last group of the n groups arranged in the direction of flow of the refrigerant and another group immediately ahead of the last group when the heat exchanger operates as the evaporator.
- a cross section of each of the at least one boosting hole may have a shape of one of polygon, circle, and other different closed figures.
- a total cross-sectional area of the at least one boosting hole may be 5 % to 70 % of a cross-sectional area of an inner space of the corresponding header.
- a total cross-sectional area of the at least one boosting hole may be greater than the total cross-sectional area of the at least one distribution hole.
- a heat exchanger includes a plurality of tubes disposed horizontally, a heat exchange fin to contact the tubes, a first header vertically disposed to communicate with one end of each of the tubes, a second header vertically disposed to communicate with the other end of each of the tubes, at least one flow passage defining baffle mounted to at least one header of the first header and the second header and adapted to define a flow passage of a refrigerant by interrupting flow of the refrigerant in the at least one header in a longitudinal direction and to divide the tubes into n (n ⁇ 2, where n is an even number) groups, each of the groups having tubes adjoining each other and allowing the refrigerant to flow in one direction therethrough and the number of the at least one flow passage defining baffle being n-1, and at least one flow speed boosting baffle mounted to a corresponding header of the first header and the second header arranged at an inlet of one group of the n groups such that the flow speed boosting baffle is positioned
- the at least one flow speed boosting baffle may be positioned between the last group of the n groups arranged in the direction of flow of the refrigerant and another group immediately ahead of the last group when the heat exchanger operates as the evaporator.
- a cross section of each of the at least one boosting hole may have a shape of one of polygon, circle, and other different closed figures.
- a total cross-sectional area of the at least one boosting hole may be 5 % to 70 % of a cross-sectional area of an inner space of the corresponding header.
- a heat exchanger in accordance with another aspect of the present invention, includes a plurality of tubes disposed horizontally, a heat exchange fin to contact the tubes, a first header vertically disposed to communicate with one end of each of the tubes and provided with an inlet pipe and an outlet pipe, a second header vertically disposed to communicate with the other end of each of the tubes, at least one flow passage defining baffle mounted to at least one header of the first header and the second header and adapted to define a flow passage of a refrigerant by interrupting flow of the refrigerant in the at least one header in a longitudinal direction and to divide the tubes into a plurality of groups, each of the groups having tubes adjoining each other and allowing the refrigerant to flow in one direction therethrough, and at least one flow distribution baffle mounted to the second header such that a supply section of the second header to supply the refrigerant to the tubes belonging to one of the groups positioned at an uppermost side is partitioned into an upper section communicating one portion of the tubes and a lower section communicating with
- the heat exchanger may further include a flow speed boosting baffle mounted to the second header to be positioned between the supply section and an introduction section of the second header and provided with at least one boosting hole allowing the refrigerant to flow therethrough, the introduction section being positioned immediately under the supply section to receive the refrigerant from the tubes of another one of the groups positioned immediately under the group positioned at the uppermost side, wherein a flow speed of the refrigerant flowing from the introduction section to the supply section through the at least one boosting hole is boosted by boosting pressure in the introduction section.
- the heat exchanger 10 is a parallel flow type heat exchanger having a vertical header.
- the heat exchanger 10 includes a plurality of tubes 60 having a refrigerant flowing therethrough and may be horizontally disposed to exchange heat with external air, a pair of headers 20 and 30 vertically disposed to guide the refrigerant to the tubes 60 and communicate with the tubes 60, and a heat exchange fin 50 to contact the tubes 60.
- the tubes 60 may be formed of aluminum in a flat shape and provided therein with microchannels 61 allowing the refrigerant to flow therethrough.
- the tubes 60 are horizontally disposed and spaced a certain distance from each other.
- the heat exchange fin 50 may take various forms that increase the heat transfer area and facilitate drainage of condensated water, and may be formed of aluminum.
- the heat exchange fin 50 may be arranged between the tubes 60 and joined to the tubes 60 by brazing.
- Headers 20 and 30 may be vertically disposed and spaced a predetermined distance from each other, with the tubes 60 placed therebetween.
- the header 20 disposed on the right side of the tubes 60 in FIG. 1 will be defined as a first header 20 and the header 30 disposed on the left side of the tubes 60 will be defined as a second header 30.
- the first header 20 and the second header 30 may be formed approximately in the shape of a cylinder having an inner space. Accordingly, the cross sections of the first header 20 and the second header 30 are approximately formed in the shape of a circle. However, embodiments of the present invention are not limited thereto. The cross sections may be formed approximately in a "D" shape or other shapes.
- the first header 20 and the second header 30 may be respectively formed by coupling cylindrical bodies 21 and 31 with inner spaces 22 and 32 and open opposites ends to upper caps 25 and 35 and lower caps 26 and 36 covering open opposite ends of the bodies 21 and 31.
- the bodies 21 and 31, the upper caps 25 and 35, and the lower caps 26 and 36 may all be formed of aluminum and coupled by brazing.
- Tube insertion holes 23 and 33 allowing the tubes 60 to be inserted thereinto are formed on one side surface of each of the bodies 21 and 31. Opposite ends of each of the tubes 60 may be inserted into and joined to the tube insertion holes 23 and 33 by brazing. Thereby, the microchannels 61 of the tubes 60 may communicate with the inner space 22 and 32 of the first header 20 and the second header 30, and the refrigerant may flow between the headers 20 and 30 and the tubes 60.
- baffle insertion holes 24 and 34 allow baffles 70, 80, 90 and 100 to be inserted thereinto.
- Flow passage defining baffles 70 may be inserted into the baffle insertion holes 24 of the first header 20.
- a flow passage defining baffle 70, a flow speed boosting baffle 100, and flow distribution baffles 80 and 90 may be inserted into the baffle insertion holes 34 of the second header 30.
- baffles 70, 80, 90 and 100 may be inserted into the baffle insertion holes 24 of the first header 20 or the second header 30 in the direction inwardly extending from the exterior of the heat exchanger 10.
- the baffles 70, 80, 90 and 100 may all be formed of aluminum and joined to the baffle insertion holes 24 by brazing after being inserted into the baffle insertion holes 24.
- the first header 20 may be provided with an inlet pipe 27 and an outlet pipe 28 through which the refrigerant flows into and out of the first header 20.
- the inlet pipe 27 may be provided to a lower portion of the first header 20, and the outlet pipe 28 may be provided to an upper portion of the first header 20.
- the refrigerant in a liquid state or gaseous state may be introduced through the inlet pipe 27.
- the introduced refrigerant may be evaporated after absorbing heat from external air while passing through the tubes 60. There, it may be discharged through the outlet pipe 28 in the gaseous state.
- the refrigerant in the gaseous state may be introduced through the outlet pipe 28.
- the introduced refrigerant may lose heat to the external air while passing through the tubes 60. Then, the refrigerant may be condensed into the liquid state and discharged through the inlet pipe 27.
- the heat exchanger 10 which may operate as an evaporator and condenser of the outdoor unit vertical headers 20 and 30 as described above, is a parallel flow type heat exchanger. Particularly, when the heat exchanger 10 operates as the evaporator of the outdoor unit, the flow distribution baffles 80 and 90 and flow speed boosting baffle 100 provided to the second header 30 may ensure that the refrigerant is evenly distributed, thereby enhancing heat exchange efficiency.
- FIG. 4 is a front view illustrating the heat exchanger of FIG. 1
- FIG. 5 is a view illustrating main parts of the heat exchanger of FIG. 1
- FIG. 6 is a cross-sectional view taken along line I-I of FIG. 1
- FIGS. 7 to 11 are cross-sectional views illustrating flow distribution baffles according to other embodiments of the present invention.
- FIG. 12 is a cross-sectional view illustrating a flow speed boosting baffle of the heat exchanger of FIG. 1 .
- FIG. 13 is a cross-sectional view illustrating a header and a flow distribution baffle according to another embodiment of the present invention.
- FIGS. 4 and 5 indicate flow of the refrigerant when the heat exchanger 10 operates as the evaporator of the outdoor unit.
- two flow passage defining baffles 70 are mounted to the first header 20, and one flow passage defining baffles 70 is mounted to the second header 30.
- the heat exchanger 10 is provided with three flow passage defining baffles 70, which are disposed at different vertical levels.
- the three flow passage defining baffles 70 interrupt flow of the refrigerant in the headers 20 and 30 in the longitudinal direction of the headers 20 and 30. Accordingly, the refrigerant introduced into the first header 20 through the inlet pipe 27 provided to a lower portion of the first header 20 rises in a zigzag form, repeatedly passing through the first header 20, the tubes 60 and the second header 30 as indicated by arrows in FIG. 4 .
- the flow passage defining baffles 70 define a flow passage of the refrigerant.
- the tubes 60 are classified into a plurality of groups A, B, C and D. Tubes classified into the same group adjoin each other and allow the refrigerant to flow therethrough in the same direction.
- the tubes 60 are divided into tubes of one group (hereinafter, group A) disposed adjacent to each other at the lowest position and causing the refrigerant to flow from the first header 20 to the second header 30 therethrough, tubes of another group (hereinafter, group B) disposed adjacent to each other on the tubes of group A and causing the refrigerant to flow from the second header 30 to the first header 20 therethrough, tubes of another group (hereinafter, group C) disposed adjacent to each other on the tubes of group B and causing the refrigerant to flow from the first header 20 to the second header 30 therethrough, and tubes of the other group (hereinafter, group D) disposed adjacent to each other on the tubes of group C and causing the refrigerant to flow from the second header 30 to the first header 20 therethrough.
- each of the groups may include 2 to 15 tubes.
- the heat exchanger 10 of this embodiment is provided with three flow passage defining baffles 70, and the tubes 60 are divided into four groups by the three flow passage defining baffles 70.
- the first header 20 of the pair of headers 20 and 30 is provided with both the inlet pipe 27 and the outlet pipe 28.
- the number of the flow passage defining baffles 70 is n - 1
- the number of groups of tubes is n, where n is an even number greater than 2.
- the number of the flow passage defining baffles 70 may be greater or less than 3, and the number of groups of the tubes may also be greater or less than the number illustrated in FIG. 4 .
- the heat exchanger may have n - 1 flow passage defining baffles that divide the tubes 60 into n (n ⁇ 2, where n is an even number) groups, each of which has tubes adjoining each other and causing the refrigerant to flow in one direction.
- the flow distribution baffles 80 and 90 are provided to ensure that the refrigerant in the header 30 is evenly distributed to the tubes 60.
- two flow distribution baffles 80 and 90 are mounted to an upper portion of the second header 30.
- the number of the flow distribution baffles is not limited. Depending upon various factors such as the number and length of the tubes 60 and pressure of the refrigerant, one flow distribution baffle may be provided, or two, three or more flow distribution baffles may be provided.
- the two flow distribution baffles 80 and 90 of this embodiment substantially have the same shape and function, and therefore only the flow distribution baffle 80 disposed at a lower position of the two flow distribution baffles 80 and 90 will be described.
- the flow distribution baffle 80 may include an interruption wall 89 arranged perpendicular to the longitudinal direction of the header to interrupt flow of the refrigerant in the header in the longitudinal direction of the header, a distribution hole 81 (91 for the flow distribution baffle 90) formed in the interruption wall 89 to allow the refrigerant to flow in the header in the longitudinal direction of the header, and a stopper 88 protruding from opposite sides of the interruption wall 89 to restrict the insertion depth of the flow distribution baffle 80.
- the interruption wall 89 may closely contact the inner side surface of the header to interrupt flow of the refrigerant, and thus the refrigerant directed to the flow distribution baffle 80 may be allowed to flow via the flow distribution baffle 80 only by passing through the distribution hole 81.
- the distribution hole 81 needs to be spaced a predetermined distance G from the inner side surface 37 on the opposite side facing the tubes in the header such that flow of the liquid refrigerant along the inner side surface 37 on the opposite side facing the tubes is interrupted.
- the distribution hole 81 may be formed in any shape.
- the number of the distribution holes is not limited. That is, the distribution hole shown in FIG. 6 has a rectangular cross section.
- the flow distribution baffle 82 may be provided with a distribution hole 82a having a circular cross section as shown in FIG. 7 .
- a flow distribution baffle 83 may be provided with a distribution hole 83a whose cross section is formed in the shape of multiple slits, as shown in FIG. 8 .
- a flow distribution baffle 84 may be provided with a distribution hole 84a whose cross section has the shape of a closed figure different from a circle and a rectangle, as shown in FIG. 9 .
- a flow distribution baffle 85 may have a porous distribution hole 85a as shown in FIG. 10 .
- the distribution hole of the flow distribution baffle 82 may include not only the hole formed in the flow distribution baffle 82 but also a hole defined between the flow distribution baffle 82 and the header. That is, a hole 86a defined between one surface 86b of the flow distribution baffle 82 and the inner side surface 38 of the header 31 by mounting the flow distribution baffle 86 to the header 31 is also provided as a distribution hole 86a of the flow distribution baffle 86, as shown in FIG. 11 .
- the flow distribution baffle 80 is applicable not only to a header having a circular cross section but also to a header having a cross section formed in a shape different from a circle.
- a flow distribution baffle 87 with a distribution hole 87a may be mounted to the header 39.
- the sum of the cross-sectional area of the distribution hole 81 in the flow distribution baffle 80 may be 1 to 40 % of the cross-sectional area of the inner space of the header.
- a portion of the inner space of the second header 30 that supplies the refrigerant to the tubes of group D will be defined as a supply section 40.
- the lower end of the supply section 40 in the second header is limited by the flow speed boosting baffle 100, and the upper end thereof is limited by the upper cap 35.
- the refrigerant generally rapidly flows upward.
- the liquid refrigerant rapidly rises along the inner side surface of the second header 30 facing the tube 60.
- the refrigerant is not evenly distributed to the tubes of the group D in the supply section 40. That is, most of the refrigerant is distributed to some of the tubes of group D which are positioned at the upper side, and little refrigerant is distributed to the other tubes of group D positioned at the lower side.
- the flow distribution baffle 80 according to one embodiment is mounted in the supply section 40 to ensure that the refrigerant of the supply section 40 is evenly distributed to all the tubes of group D.
- the flow distribution baffle 80 is mounted to the second header 30 such that it is positioned between the tubes of group D.
- positioning the flow distribution baffle 80 between the tubes of group D means that at least one of the tubes of group D is positioned over the flow distribution baffle 80, and at least one of the tubes of group D is positioned under the flow distribution baffle 80.
- the supply section 40 is partitioned into two spaces by the flow distribution baffle 80.
- one of the two spaces positioned over the flow distribution baffle 80 is defined as an upper section 41, and the other space positioned under the flow distribution baffle 80 is defined as a lower section 42.
- the liquid refrigerant rising fast along the inner side surface of the header facing the tubes is resisted by the flow distribution baffle 80, and mixing of the refrigerant may occur in the lower section 42.
- the flow distribution baffle 80 may improve distribution of the refrigerant to the tubes 60 in the header 30.
- flow distribution baffle 80 of this embodiment is illustrated as being mounted to an upper portion of the second header communicating with the tubes of group D, embodiments of the present invention are not limited thereto.
- the flow distribution baffle may be mounted to any portion of the second header where fast flow causes uneven distribution of the refrigerant, according to the specifications of the heat exchanger refrigerant.
- the flow speed boosting baffle 100 is provided to increase the flow speed of the refrigerant in the header 30 to improve distribution of the refrigerant.
- one flow speed boosting baffle 100 is mounted to the middle portion of the second header 30.
- the number of the flow speed boosting baffles 100 is not limited thereto. Depending upon the specifications of the heat exchanger, two or more flow speed boosting baffles may be provided. If unnecessary, they may not be provided.
- the flow speed boosting baffle 100 has at least one boosting hole 101 allowing the refrigerant to pass therethrough, as shown in FIG. 12 .
- the flow speed boosting baffle 100 has almost the same shape as the flow distribution baffle 80.
- the sum of the cross-sectional area of the at least one boosting hole 101 in the flow speed boosting baffle 100 may occupy 5 % to 70 % of the cross-sectional area of the inner space of the header. Accordingly, the sum of the cross-sectional area of the at least one boosting hole 101 in the flow speed boosting baffle 100 is generally greater than the sum of the cross-sectional area of the at least one distribution hole 81 in the flow distribution baffle 80.
- the shape of the boosting hole 101 in the flow speed boosting baffle 100 is not limited. Unlike the distribution hole 81 in the flow distribution baffle 80, the boosting hole 101 in the flow speed boosting baffle 100 is not necessarily spaced from the inner side surface of the header facing the tubes.
- an introduction section 43 a portion of the inner space of the second header 30 positioned under the supply section 40 to receive the refrigerant from the tubes of group C will be defined as an introduction section 43.
- the flow speed boosting baffle 100 is mounted to the second header 30 such that it is positioned between the supply section 40 and the introduction section 43. That is, the flow speed boosting baffle 100 is mounted to the second header 30 such that it is positioned between the tubes of group D and the tubes of group C.
- the refrigerant is caused to flow upward to the supply section 40 by the refrigerant introduced from the tubes of group C.
- the refrigerant flowing from the introduction section 43 to the supply section 40 is interrupted since the flow speed boosting baffle 100 is installed between the supply section 40 and the introduction section 43. Thereby, the pressure of the refrigerant in the introduction section 43 increases.
- the flow speed of the refrigerant flowing from the introduction section 43 to the supply section 40 is boosted when the refrigerant passes through the boosting hole 101 in the flow speed boosting baffle 100.
- the flow speed may be increased by installing the flow speed boosting baffle.
- the flow speed boosting baffle may not be necessary.
- FIG. 14 is a view illustrating overall flow of a refrigerant in a cooling and heating system according to an embodiment of the present invention
- FIG. 15 is a view illustrating flow of the refrigerant when the heat exchanger of FIG. 1 operates as a condenser
- FIG. 16 is a view illustrating flow of the refrigerant when the heat exchanger of FIG. 1 operates as an evaporator.
- a two-way heat pump cooling and heating system may include an outdoor unit 1 and an indoor unit 2.
- the outdoor unit 1 may include a first heat exchanger 10 according to one embodiment, a compressor 3 to compress the refrigerant, and an expansion unit 4 to expand the refrigerant and a switching valve 5 to switch the flow passage of the refrigerant, and the indoor unit 2 may include a second heat exchanger 11.
- the refrigerant flows sequentially through the compressor 3, the first heat exchanger 10, expansion unit 4, and the second heat exchanger 11 along the solid arrows. Accordingly, the first heat exchanger 10 operates as a condenser, and the second heat exchanger 11 operates as an evaporator.
- the gaseous refrigerant turned to a high-temperature and high-pressure refrigerant by being compressed in the compressor 3 is introduced into the outlet pipe 28 of the first heat exchanger 10.
- the introduced refrigerant is condensed by losing heat to the external air as it flows down in a zigzag pattern.
- the condensed refrigerant is discharged through the inlet pipe 27.
- the refrigerant flows sequentially through the compressor 3, the second heat exchanger 11, expansion unit 4, and the first heat exchanger 10 along the dotted arrows. Accordingly, the first heat exchanger 10 operates as an evaporator, and the second heat exchanger 11 operates as a condenser.
- the liquid or gaseous refrigerant turned into a low-temperature and low-pressure refrigerant by being expanded in the expansion unit 4 is introduced into the inlet pipe 27 of the first heat exchanger 10.
- the introduced refrigerant is evaporated by absorbing heat as it flows upward in a zigzag pattern.
- the evaporated refrigerant is discharged through the outlet pipe 28.
- the flow speed of the refrigerant rising up in the second header 30 may be high and thus the refrigerant may show a tendency of being concentrated at the upper end of the second header 30.
- at least one flow distribution baffle 80, 90 may be mounted to the second header 30 of the first heat exchanger 10.
- the flow speed of the refrigerant rising up in the second header 30 may be low and thus the refrigerant may not be sufficiently supplied to the upper end of the second header 30.
- at least one flow speed boosting baffle 100 may be mounted to the second header 30 of the first heat exchanger 10.
- the refrigerant is smoothly distributed.
- the unbalanced performance of the heat pump cooling and heating system in the cooing mode and the heating mode may be addressed.
- a parallel flow type heat exchanger with vertical headers may ensure balanced distribution of a refrigerant from the headers to the tubes even when the heat exchanger operates as an evaporator of an outdoor unit. Thereby, degradation of heat exchange performance may not occur.
- the parallel flow type heat exchanger with vertical headers when used in an outdoor unit of a heat pump type heating and cooling system, it may exhibit constant performance in both cooling and heating.
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Abstract
Description
- The present invention relates to a heat exchanger, particularly to a heat exchanger provided with a header having an improved performance of distribution of a refrigerant.
- A heat exchanger, which is an apparatus causing a refrigerant to exchange heat with external air, generally includes tubes having a refrigerant flowing therethrough and arranged to exchange heat with external air, a heat exchange fin contacting the tubes to increase the heat dissipation area, and a header allowing ends of the tubes to communicate with each other in order to guide the refrigerant to the tubes and adapted to support the tubes.
- Heat exchangers include a fin tube type heat exchanger, which is configured by inserting a heat transfer pipe formed of copper into a thin heat exchange fin formed of aluminum, and a parallel flow type heat exchanger, which is configured by disposing the heat exchange fin between the tubes having multiple micro-channels and formed of aluminum and arranging the tubes such that they are supported by a pair of headers. The parallel flow type heat exchanger is known to be relatively inexpensive and have high efficiency.
- In the case that a parallel flow type heat exchanger with vertical headers is used as an evaporator of an outdoor unit, distribution of a refrigerant from the vertical headers to the tubes becomes unbalanced due to gravity and variation of physical properties of the refrigerant according to a physical phase of the refrigerant. Thereby, the refrigerant may be distributed only to some of the tubes. For this reason, the parallel flow type heat exchanger is often used only as a condenser.
- Therefore, it is an aspect of the present invention to provide a parallel flow type heat exchanger having vertical headers which allow a refrigerant introduced into the headers to be uniformly distributed to the tubes even when the heat exchanger operates as an evaporator of an outdoor unit, thereby preventing degradation of heat exchange performance.
- Additional aspects of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
- In accordance with one aspect of the present invention, a heat exchanger includes a plurality of tubes disposed horizontally, a heat exchange fin to contact the tubes, a first header vertically disposed to communicate with one end of each of the tubes, a second header vertically disposed to communicate with the other end of each of the tubes, at least one flow passage defining baffle mounted to at least one header of the first header and the second header and adapted to define a flow passage of a refrigerant by interrupting flow of the refrigerant in the at least one header in a longitudinal direction and to divide the tubes into n (n ≥ 2, where n is an even number) groups, each of the groups having tubes adjoining each other and allowing the refrigerant to flow in one direction therethrough and the number of the at least one flow passage defining baffle being n-1, and at least one flow distribution baffle mounted to a corresponding header of the first header and the second header arranged at an inlet of one group of the n groups such that the flow distribution baffle is positioned between the tubes belonging to the one group, each of the at least one flow distribution baffle being provided with at least one distribution hole allowing the refrigerant to pass therethrough.
- The flow distribution baffle may be positioned between the tubes belonging to the last group of the n groups arranged in a direction of flow of the refrigerant when the heat exchanger operates as an evaporator.
- The distribution hole may be spaced from an inner side surface of the corresponding header at an opposite side to the tubes of the corresponding header such that flow of the refrigerant along the inner side surface at the opposite side is interrupted.
- A cross section of each of the at least one distribution hole may have a shape of one of polygon, circle, and other different closed figures.
- The at least one distribution hole may include a hole formed in the flow distribution baffle and a hole formed between the flow distribution baffle and the inner side surface of the corresponding header by mounting the flow distribution baffle to the corresponding header.
- A total cross-sectional area of the at least one distribution hole may be 1 % to 40 % of a cross-sectional area of an inner surface of the corresponding header.
- Each of the groups may have 2 to 15 tubes.
- Here, n = 4, the number of the at least one flow passage defining baffle may be 3, and the tubes may be divided into four groups.
- One header of the first header and the second header may be provided with an inlet pipe and an outlet pipe, and the flow distribution baffle may be mounted to the other header of the first header and the second header.
- The refrigerant may flow upward in the first header and the second header when the heat exchanger operates as an evaporator, and the refrigerant may flow downward in the first header and the second header when the heat exchanger operates as a condenser.
- The heat exchanger may further include at least one flow speed boosting baffle mounted to a corresponding header of the first header and the second header arranged at an inlet of one group of the n groups such that the flow speed boosting baffle is positioned between the one group and another group positioned immediately ahead of the one group in a direction of flow of the refrigerant when the heat exchanger operates as an evaporator, each of the at least one flow speed boosting baffle being provided with at least one boosting hole allowing the refrigerant to pass therethrough.
- The at least one flow speed boosting baffle may be positioned between the last group of the n groups arranged in the direction of flow of the refrigerant and another group immediately ahead of the last group when the heat exchanger operates as the evaporator.
- A cross section of each of the at least one boosting hole may have a shape of one of polygon, circle, and other different closed figures.
- A total cross-sectional area of the at least one boosting hole may be 5 % to 70 % of a cross-sectional area of an inner space of the corresponding header.
- A total cross-sectional area of the at least one boosting hole may be greater than the total cross-sectional area of the at least one distribution hole.
- In accordance with another aspect of the present invention, a heat exchanger includes a plurality of tubes disposed horizontally, a heat exchange fin to contact the tubes, a first header vertically disposed to communicate with one end of each of the tubes, a second header vertically disposed to communicate with the other end of each of the tubes, at least one flow passage defining baffle mounted to at least one header of the first header and the second header and adapted to define a flow passage of a refrigerant by interrupting flow of the refrigerant in the at least one header in a longitudinal direction and to divide the tubes into n (n ≥ 2, where n is an even number) groups, each of the groups having tubes adjoining each other and allowing the refrigerant to flow in one direction therethrough and the number of the at least one flow passage defining baffle being n-1, and at least one flow speed boosting baffle mounted to a corresponding header of the first header and the second header arranged at an inlet of one group of the n groups such that the flow speed boosting baffle is positioned between the one group and another group positioned immediately ahead of the one group in a direction of flow of the refrigerant when the heat exchanger operates as an evaporator, each of the at least one flow speed boosting baffle being provided with at least one boosting hole allowing the refrigerant to pass therethrough.
- The at least one flow speed boosting baffle may be positioned between the last group of the n groups arranged in the direction of flow of the refrigerant and another group immediately ahead of the last group when the heat exchanger operates as the evaporator.
- A cross section of each of the at least one boosting hole may have a shape of one of polygon, circle, and other different closed figures.
- A total cross-sectional area of the at least one boosting hole may be 5 % to 70 % of a cross-sectional area of an inner space of the corresponding header.
- In accordance with another aspect of the present invention, a heat exchanger includes a plurality of tubes disposed horizontally, a heat exchange fin to contact the tubes, a first header vertically disposed to communicate with one end of each of the tubes and provided with an inlet pipe and an outlet pipe, a second header vertically disposed to communicate with the other end of each of the tubes, at least one flow passage defining baffle mounted to at least one header of the first header and the second header and adapted to define a flow passage of a refrigerant by interrupting flow of the refrigerant in the at least one header in a longitudinal direction and to divide the tubes into a plurality of groups, each of the groups having tubes adjoining each other and allowing the refrigerant to flow in one direction therethrough, and at least one flow distribution baffle mounted to the second header such that a supply section of the second header to supply the refrigerant to the tubes belonging to one of the groups positioned at an uppermost side is partitioned into an upper section communicating one portion of the tubes and a lower section communicating with the other portion of the tubes, each of the at least one flow distribution baffle being provided with at least one distribution hole allowing the refrigerant to pass therethrough, wherein one portion of the refrigerant directed from the lower section to the upper section is distributed to the one portion of the tubes communicating with the upper section through the at least distribution hole, and the other portion of the refrigerant fails to pass through the at least one distribution hole and is distributed to the other portion of the tubes communicating with the lower section.
- The heat exchanger may further include a flow speed boosting baffle mounted to the second header to be positioned between the supply section and an introduction section of the second header and provided with at least one boosting hole allowing the refrigerant to flow therethrough, the introduction section being positioned immediately under the supply section to receive the refrigerant from the tubes of another one of the groups positioned immediately under the group positioned at the uppermost side, wherein a flow speed of the refrigerant flowing from the introduction section to the supply section through the at least one boosting hole is boosted by boosting pressure in the introduction section.
- These and/or other aspects of the invention will become apparent and more readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings in which:
-
FIG. 1 is a view illustrating an external appearance of a heat exchanger according to an exemplary embodiment of the present invention; -
FIG. 2 is an exploded view illustrating constituents of a second header of the heat exchanger shown inFIG. 1 ; -
FIG. 3 is an exploded view illustrating constituents of a first header of the heat exchanger shown inFIG. 1 ; -
FIG. 4 is a front view illustrating the heat exchanger ofFIG. 1 ; -
FIG. 5 is a view illustrating main parts of the heat exchanger ofFIG. 1 ; -
FIG. 6 is a cross-sectional view taken along line I-I ofFIG. 1 ; -
FIGS. 7 to 11 are cross-sectional views illustrating flow distribution baffles according to other embodiments of the present invention; -
FIG. 12 is a cross-sectional view illustrating a flow speed boosting baffle of the heat exchanger ofFIG. 1 ; -
FIG. 13 is a cross-sectional view illustrating a header and a flow distribution baffle according to another embodiment of the present invention; -
FIG. 14 is a view illustrating overall flow of a refrigerant in a cooling and heating system according to an embodiment of the present invention; -
FIG. 15 is a view illustrating flow of the refrigerant when the heat exchanger ofFIG. 1 operates as a condenser; and -
FIG. 16 is a view illustrating flow of the refrigerant when the heat exchanger ofFIG. 1 operates as an evaporator. - Reference will now be made in detail to the embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to like elements throughout.
- Referring to
FIGS. 1 to 3 , theheat exchanger 10 is a parallel flow type heat exchanger having a vertical header. Theheat exchanger 10 includes a plurality oftubes 60 having a refrigerant flowing therethrough and may be horizontally disposed to exchange heat with external air, a pair ofheaders tubes 60 and communicate with thetubes 60, and aheat exchange fin 50 to contact thetubes 60. - The
tubes 60 may be formed of aluminum in a flat shape and provided therein withmicrochannels 61 allowing the refrigerant to flow therethrough. Thetubes 60 are horizontally disposed and spaced a certain distance from each other. - The
heat exchange fin 50 may take various forms that increase the heat transfer area and facilitate drainage of condensated water, and may be formed of aluminum. Theheat exchange fin 50 may be arranged between thetubes 60 and joined to thetubes 60 by brazing. -
Headers tubes 60 placed therebetween. Hereinafter, for simplicity of illustration, theheader 20 disposed on the right side of thetubes 60 inFIG. 1 will be defined as afirst header 20 and theheader 30 disposed on the left side of thetubes 60 will be defined as asecond header 30. - The
first header 20 and thesecond header 30 may be formed approximately in the shape of a cylinder having an inner space. Accordingly, the cross sections of thefirst header 20 and thesecond header 30 are approximately formed in the shape of a circle. However, embodiments of the present invention are not limited thereto. The cross sections may be formed approximately in a "D" shape or other shapes. - The
first header 20 and thesecond header 30 may be respectively formed by couplingcylindrical bodies 21 and 31 withinner spaces 22 and 32 and open opposites ends toupper caps lower caps bodies 21 and 31. Thebodies 21 and 31, theupper caps lower caps -
Tube insertion holes tubes 60 to be inserted thereinto are formed on one side surface of each of thebodies 21 and 31. Opposite ends of each of thetubes 60 may be inserted into and joined to thetube insertion holes microchannels 61 of thetubes 60 may communicate with theinner space 22 and 32 of thefirst header 20 and thesecond header 30, and the refrigerant may flow between theheaders tubes 60. - The other side surfaces of the
bodies 21 and 31 are provided withbaffle insertion holes 24 and 34 allowingbaffles passage defining baffles 70 may be inserted into the baffle insertion holes 24 of thefirst header 20. A flowpassage defining baffle 70, a flowspeed boosting baffle 100, andflow distribution baffles baffle insertion holes 34 of thesecond header 30. - Configurations and functions of the flow
passage defining baffle 70, the flowspeed boosting baffle 100, and theflow distribution baffles baffles first header 20 or thesecond header 30 in the direction inwardly extending from the exterior of theheat exchanger 10. - The
baffles first header 20 may be provided with aninlet pipe 27 and anoutlet pipe 28 through which the refrigerant flows into and out of thefirst header 20. Theinlet pipe 27 may be provided to a lower portion of thefirst header 20, and theoutlet pipe 28 may be provided to an upper portion of thefirst header 20. - When the
heat exchanger 10 operates as an evaporator of the outdoor unit in this embodiment, the refrigerant in a liquid state or gaseous state may be introduced through theinlet pipe 27. The introduced refrigerant may be evaporated after absorbing heat from external air while passing through thetubes 60. There, it may be discharged through theoutlet pipe 28 in the gaseous state. - When the
heat exchanger 10 operates as a condenser of the outdoor unit in this embodiment, the refrigerant in the gaseous state may be introduced through theoutlet pipe 28. The introduced refrigerant may lose heat to the external air while passing through thetubes 60. Then, the refrigerant may be condensed into the liquid state and discharged through theinlet pipe 27. - The
heat exchanger 10, which may operate as an evaporator and condenser of the outdoor unitvertical headers heat exchanger 10 operates as the evaporator of the outdoor unit, the flow distribution baffles 80 and 90 and flowspeed boosting baffle 100 provided to thesecond header 30 may ensure that the refrigerant is evenly distributed, thereby enhancing heat exchange efficiency. - Hereinafter, a detailed description will be given of configurations and functions of the flow
passage defining baffle 70, the flow distribution baffles 80 and 90 and the flowspeed boosting baffle 100. -
FIG. 4 is a front view illustrating the heat exchanger ofFIG. 1 ,FIG. 5 is a view illustrating main parts of the heat exchanger ofFIG. 1 , andFIG. 6 is a cross-sectional view taken along line I-I ofFIG. 1 .FIGS. 7 to 11 are cross-sectional views illustrating flow distribution baffles according to other embodiments of the present invention.FIG. 12 is a cross-sectional view illustrating a flow speed boosting baffle of the heat exchanger ofFIG. 1 .FIG. 13 is a cross-sectional view illustrating a header and a flow distribution baffle according to another embodiment of the present invention. - The arrows shown in
FIGS. 4 and5 indicate flow of the refrigerant when theheat exchanger 10 operates as the evaporator of the outdoor unit. - Referring to
FIGS. 4 to 6 , two flowpassage defining baffles 70 are mounted to thefirst header 20, and one flowpassage defining baffles 70 is mounted to thesecond header 30. Thereby, theheat exchanger 10 is provided with three flowpassage defining baffles 70, which are disposed at different vertical levels. - The three flow
passage defining baffles 70 interrupt flow of the refrigerant in theheaders headers first header 20 through theinlet pipe 27 provided to a lower portion of thefirst header 20 rises in a zigzag form, repeatedly passing through thefirst header 20, thetubes 60 and thesecond header 30 as indicated by arrows inFIG. 4 . - That is, the flow
passage defining baffles 70 define a flow passage of the refrigerant. At this time, thetubes 60 are classified into a plurality of groups A, B, C and D. Tubes classified into the same group adjoin each other and allow the refrigerant to flow therethrough in the same direction. - In this embodiment, the
tubes 60 are divided into tubes of one group (hereinafter, group A) disposed adjacent to each other at the lowest position and causing the refrigerant to flow from thefirst header 20 to thesecond header 30 therethrough, tubes of another group (hereinafter, group B) disposed adjacent to each other on the tubes of group A and causing the refrigerant to flow from thesecond header 30 to thefirst header 20 therethrough, tubes of another group (hereinafter, group C) disposed adjacent to each other on the tubes of group B and causing the refrigerant to flow from thefirst header 20 to thesecond header 30 therethrough, and tubes of the other group (hereinafter, group D) disposed adjacent to each other on the tubes of group C and causing the refrigerant to flow from thesecond header 30 to thefirst header 20 therethrough. Herein, each of the groups may include 2 to 15 tubes. - As described above, the
heat exchanger 10 of this embodiment is provided with three flowpassage defining baffles 70, and thetubes 60 are divided into four groups by the three flowpassage defining baffles 70. - Herein, the
first header 20 of the pair ofheaders inlet pipe 27 and theoutlet pipe 28. In this context, when the number of the flowpassage defining baffles 70 is n - 1, the number of groups of tubes is n, where n is an even number greater than 2. The number of the flowpassage defining baffles 70 may be greater or less than 3, and the number of groups of the tubes may also be greater or less than the number illustrated inFIG. 4 . - In short, the heat exchanger according to an embodiment of the present invention may have n - 1 flow passage defining baffles that divide the
tubes 60 into n (n ≥ 2, where n is an even number) groups, each of which has tubes adjoining each other and causing the refrigerant to flow in one direction. - Meanwhile, the flow distribution baffles 80 and 90 are provided to ensure that the refrigerant in the
header 30 is evenly distributed to thetubes 60. In this embodiment, two flow distribution baffles 80 and 90 are mounted to an upper portion of thesecond header 30. - The number of the flow distribution baffles is not limited. Depending upon various factors such as the number and length of the
tubes 60 and pressure of the refrigerant, one flow distribution baffle may be provided, or two, three or more flow distribution baffles may be provided. - The two flow distribution baffles 80 and 90 of this embodiment substantially have the same shape and function, and therefore only the
flow distribution baffle 80 disposed at a lower position of the two flow distribution baffles 80 and 90 will be described. - The shape of the
flow distribution baffle 80 will be discussed first. As shown inFIG. 6 , theflow distribution baffle 80 may include aninterruption wall 89 arranged perpendicular to the longitudinal direction of the header to interrupt flow of the refrigerant in the header in the longitudinal direction of the header, a distribution hole 81 (91 for the flow distribution baffle 90) formed in theinterruption wall 89 to allow the refrigerant to flow in the header in the longitudinal direction of the header, and astopper 88 protruding from opposite sides of theinterruption wall 89 to restrict the insertion depth of theflow distribution baffle 80. - The
interruption wall 89 may closely contact the inner side surface of the header to interrupt flow of the refrigerant, and thus the refrigerant directed to theflow distribution baffle 80 may be allowed to flow via theflow distribution baffle 80 only by passing through thedistribution hole 81. - Particularly, the
distribution hole 81 needs to be spaced a predetermined distance G from theinner side surface 37 on the opposite side facing the tubes in the header such that flow of the liquid refrigerant along theinner side surface 37 on the opposite side facing the tubes is interrupted. - The
distribution hole 81 may be formed in any shape. In addition, the number of the distribution holes is not limited. That is, the distribution hole shown inFIG. 6 has a rectangular cross section. However, embodiments of the present invention are not limited thereto. For example, theflow distribution baffle 82 may be provided with adistribution hole 82a having a circular cross section as shown inFIG. 7 . Alternatively, aflow distribution baffle 83 may be provided with adistribution hole 83a whose cross section is formed in the shape of multiple slits, as shown inFIG. 8 . Alternatively, aflow distribution baffle 84 may be provided with adistribution hole 84a whose cross section has the shape of a closed figure different from a circle and a rectangle, as shown inFIG. 9 . Alternatively, aflow distribution baffle 85 may have aporous distribution hole 85a as shown inFIG. 10 . - The distribution hole of the
flow distribution baffle 82 may include not only the hole formed in theflow distribution baffle 82 but also a hole defined between theflow distribution baffle 82 and the header. That is, ahole 86a defined between onesurface 86b of theflow distribution baffle 82 and theinner side surface 38 of theheader 31 by mounting theflow distribution baffle 86 to theheader 31 is also provided as adistribution hole 86a of theflow distribution baffle 86, as shown inFIG. 11 . - Meanwhile, the
flow distribution baffle 80 is applicable not only to a header having a circular cross section but also to a header having a cross section formed in a shape different from a circle. - That is, even in the case that the cross section of the
header 39 is approximately formed in a "D" shape as shown inFIG. 13 , aflow distribution baffle 87 with adistribution hole 87a may be mounted to theheader 39.
The sum of the cross-sectional area of thedistribution hole 81 in theflow distribution baffle 80 may be 1 to 40 % of the cross-sectional area of the inner space of the header. - Hereinafter, the mounting position and function of the
flow distribution baffle 80 will be described with reference toFIG. 5 . - For simplicity of illustration, a portion of the inner space of the
second header 30 that supplies the refrigerant to the tubes of group D will be defined as asupply section 40. Thereby, the lower end of thesupply section 40 in the second header is limited by the flowspeed boosting baffle 100, and the upper end thereof is limited by theupper cap 35. In thesupply section 40, the refrigerant generally rapidly flows upward. Particularly, the liquid refrigerant rapidly rises along the inner side surface of thesecond header 30 facing thetube 60. Accordingly, the refrigerant is not evenly distributed to the tubes of the group D in thesupply section 40. That is, most of the refrigerant is distributed to some of the tubes of group D which are positioned at the upper side, and little refrigerant is distributed to the other tubes of group D positioned at the lower side. - The
flow distribution baffle 80 according to one embodiment is mounted in thesupply section 40 to ensure that the refrigerant of thesupply section 40 is evenly distributed to all the tubes of group D. - Specifically, the
flow distribution baffle 80 is mounted to thesecond header 30 such that it is positioned between the tubes of group D. Herein, positioning theflow distribution baffle 80 between the tubes of group D means that at least one of the tubes of group D is positioned over theflow distribution baffle 80, and at least one of the tubes of group D is positioned under theflow distribution baffle 80. - The
supply section 40 is partitioned into two spaces by theflow distribution baffle 80. For simplicity of illustration, one of the two spaces positioned over theflow distribution baffle 80 is defined as anupper section 41, and the other space positioned under theflow distribution baffle 80 is defined as alower section 42. - Flow of the refrigerant is directed upward in the
supply section 40, and thus the refrigerant flows from thelower section 42 to theupper section 41. At this time, the refrigerant flowing from thelower section 42 to theupper section 41 is interrupted by theflow distribution baffle 80 since theflow distribution baffle 80 is installed between thelower section 42 and theupper section 41. Thereby, only a portion of the refrigerant flows into theupper section 41 through thedistribution hole 81, the other portion of the refrigerant fails to pass through thedistribution hole 81 and is caused to horizontally flow into the tubes communicating with thelower section 42. - Particularly, the liquid refrigerant rising fast along the inner side surface of the header facing the tubes is resisted by the
flow distribution baffle 80, and mixing of the refrigerant may occur in thelower section 42. - Through the above structural configuration, the
flow distribution baffle 80 may improve distribution of the refrigerant to thetubes 60 in theheader 30. - While the
flow distribution baffle 80 of this embodiment is illustrated as being mounted to an upper portion of the second header communicating with the tubes of group D, embodiments of the present invention are not limited thereto. The flow distribution baffle may be mounted to any portion of the second header where fast flow causes uneven distribution of the refrigerant, according to the specifications of the heat exchanger refrigerant. - Meanwhile, the flow
speed boosting baffle 100 is provided to increase the flow speed of the refrigerant in theheader 30 to improve distribution of the refrigerant. In this embodiment, one flowspeed boosting baffle 100 is mounted to the middle portion of thesecond header 30. - The number of the flow
speed boosting baffles 100 is not limited thereto. Depending upon the specifications of the heat exchanger, two or more flow speed boosting baffles may be provided. If unnecessary, they may not be provided. - Regarding the configuration of the flow
speed boosting baffle 100, the flowspeed boosting baffle 100 has at least one boostinghole 101 allowing the refrigerant to pass therethrough, as shown inFIG. 12 . The flowspeed boosting baffle 100 has almost the same shape as theflow distribution baffle 80. - The sum of the cross-sectional area of the at least one boosting
hole 101 in the flowspeed boosting baffle 100 may occupy 5 % to 70 % of the cross-sectional area of the inner space of the header. Accordingly, the sum of the cross-sectional area of the at least one boostinghole 101 in the flowspeed boosting baffle 100 is generally greater than the sum of the cross-sectional area of the at least onedistribution hole 81 in theflow distribution baffle 80. - The shape of the boosting
hole 101 in the flowspeed boosting baffle 100 is not limited. Unlike thedistribution hole 81 in theflow distribution baffle 80, the boostinghole 101 in the flowspeed boosting baffle 100 is not necessarily spaced from the inner side surface of the header facing the tubes. - Hereinafter, the mounting position and function of the flow
speed boosting baffle 100 will be described with reference toFIG. 5 . - For simplicity of illustration, a portion of the inner space of the
second header 30 positioned under thesupply section 40 to receive the refrigerant from the tubes of group C will be defined as anintroduction section 43. - The flow
speed boosting baffle 100 is mounted to thesecond header 30 such that it is positioned between thesupply section 40 and theintroduction section 43. That is, the flowspeed boosting baffle 100 is mounted to thesecond header 30 such that it is positioned between the tubes of group D and the tubes of group C. - In the
introduction section 43, the refrigerant is caused to flow upward to thesupply section 40 by the refrigerant introduced from the tubes of group C. At this time, the refrigerant flowing from theintroduction section 43 to thesupply section 40 is interrupted since the flowspeed boosting baffle 100 is installed between thesupply section 40 and theintroduction section 43. Thereby, the pressure of the refrigerant in theintroduction section 43 increases. - Accordingly, the flow speed of the refrigerant flowing from the
introduction section 43 to thesupply section 40 is boosted when the refrigerant passes through the boostinghole 101 in the flowspeed boosting baffle 100. - As such, in the case that the refrigerant flows in the
header 30 at low speed and is thus insufficiently supplied to the upper end of theheader 30 and concentrated at the lower portion of the header, the flow speed may be increased by installing the flow speed boosting baffle. In the case that the refrigerant is sufficiently supplied to the upper end, the flow speed boosting baffle may not be necessary. -
FIG. 14 is a view illustrating overall flow of a refrigerant in a cooling and heating system according to an embodiment of the present invention,FIG. 15 is a view illustrating flow of the refrigerant when the heat exchanger ofFIG. 1 operates as a condenser, andFIG. 16 is a view illustrating flow of the refrigerant when the heat exchanger ofFIG. 1 operates as an evaporator. - Hereinafter, operation of a cooling and heating system with the heat exchanger according to an embodiment of the present invention will be described with reference to
FIGS. 14 to 16 . - A two-way heat pump cooling and heating system may include an
outdoor unit 1 and anindoor unit 2. Theoutdoor unit 1 may include afirst heat exchanger 10 according to one embodiment, acompressor 3 to compress the refrigerant, and anexpansion unit 4 to expand the refrigerant and a switchingvalve 5 to switch the flow passage of the refrigerant, and theindoor unit 2 may include a second heat exchanger 11. - In a cooling mode, the refrigerant flows sequentially through the
compressor 3, thefirst heat exchanger 10,expansion unit 4, and the second heat exchanger 11 along the solid arrows. Accordingly, thefirst heat exchanger 10 operates as a condenser, and the second heat exchanger 11 operates as an evaporator. - As shown in
FIG. 15 , in the cooling mode, the gaseous refrigerant turned to a high-temperature and high-pressure refrigerant by being compressed in thecompressor 3 is introduced into theoutlet pipe 28 of thefirst heat exchanger 10. The introduced refrigerant is condensed by losing heat to the external air as it flows down in a zigzag pattern. The condensed refrigerant is discharged through theinlet pipe 27. - In a heating mode, the refrigerant flows sequentially through the
compressor 3, the second heat exchanger 11,expansion unit 4, and thefirst heat exchanger 10 along the dotted arrows. Accordingly, thefirst heat exchanger 10 operates as an evaporator, and the second heat exchanger 11 operates as a condenser. - As shown in
FIG. 16 , in the heating mode, the liquid or gaseous refrigerant turned into a low-temperature and low-pressure refrigerant by being expanded in theexpansion unit 4 is introduced into theinlet pipe 27 of thefirst heat exchanger 10. The introduced refrigerant is evaporated by absorbing heat as it flows upward in a zigzag pattern. The evaporated refrigerant is discharged through theoutlet pipe 28. - When the
first heat exchanger 10 of the parallel flow type having vertical headers operates as an evaporator, distribution of the refrigerant may become unbalanced due to the physical properties of the liquid refrigerant and gravity. - Particularly, the flow speed of the refrigerant rising up in the
second header 30 may be high and thus the refrigerant may show a tendency of being concentrated at the upper end of thesecond header 30. To prevent this unbalanced flow, at least oneflow distribution baffle second header 30 of thefirst heat exchanger 10. - In addition, the flow speed of the refrigerant rising up in the
second header 30 may be low and thus the refrigerant may not be sufficiently supplied to the upper end of thesecond header 30. To prevent this unbalanced flow, at least one flowspeed boosting baffle 100 may be mounted to thesecond header 30 of thefirst heat exchanger 10. - Thereby, even when the
first heat exchanger 10 operates as the evaporator of the outdoor unit, the refrigerant is smoothly distributed. The unbalanced performance of the heat pump cooling and heating system in the cooing mode and the heating mode may be addressed. - As is apparent from the above description, a parallel flow type heat exchanger with vertical headers according to an embodiment of the present invention may ensure balanced distribution of a refrigerant from the headers to the tubes even when the heat exchanger operates as an evaporator of an outdoor unit. Thereby, degradation of heat exchange performance may not occur.
- Therefore, when the parallel flow type heat exchanger with vertical headers is used in an outdoor unit of a heat pump type heating and cooling system, it may exhibit constant performance in both cooling and heating.
- Although specific embodiments of the present invention have been described above, the scope of the present invention is not limited thereto.
- It would be appreciated by those skilled in the art that changes may be made to the embodiments without departing from the principles of the invention, the scope of which is defined in the claims.
Claims (15)
- A heat exchanger comprising:a plurality of tubes, each having first and second ends;a first header disposed to communicate with the first end of each of the tubes;a second header disposed to communicate with the second end of each of the tubes;one or more flow passage defining baffles mounted to at least one of the first header and the second header to prevent flow of the refrigerant in the at least one header in a longitudinal direction and to divide the tubes into n groups (n ≥ 2, where n is an even number), each of the groups having tubes allowing the refrigerant to flow in one direction therethrough and the number of the one or more flow passage defining baffles being n-1; andone or more flow distribution baffles mounted to at least one of the first header and the second header and arranged at one group of the n groups such that the one or more flow distribution baffles are positioned between the tubes belonging to the one group, each of the one or more flow distribution baffles being provided with at least one distribution hole allowing the refrigerant to pass therethrough.
- The heat exchanger according to claim 1, wherein the flow distribution baffle positioned between the tubes belonging to the last group of the n groups is arranged in a direction of flow of the refrigerant when the heat exchanger operates as an evaporator.
- The heat exchanger according to claim 1 or 2, wherein the distribution hole is spaced from an inner side surface of the at least one header at an opposite side to the tubes of the at least one header such that flow of the refrigerant along the inner side surface at the opposite side is prevented.
- The heat exchanger according to any one of the preceding claims, wherein a cross section of each of the at least one distribution hole is a polygon, circle, or other closed figure.
- The heat exchanger according to any one of the preceding claims, wherein the at least one distribution hole comprises either a hole formed in the flow distribution baffle or a hole formed between the flow distribution baffle and an inner side surface of the at least one header.
- The heat exchanger according to any one of the preceding claims, wherein the total cross-sectional area of the at least one distribution hole is 1 % to 40 % of the cross-sectional area of an inner surface of the at least one header.
- The heat exchanger according to any one of the preceding claims, wherein each of the groups has 2 to 15 tubes.
- The heat exchanger according to any one of the preceding claims, wherein n = 4, there are three flow passage defining baffles and the tubes are divided into four groups.
- The heat exchanger according to any one of the preceding claims, wherein:the first header is provided with an inlet pipe and an outlet pipe; andthe flow distribution baffle is mounted to the second header.
- The heat exchanger according to any one of the preceding claims, wherein:the refrigerant flows upward in the first header and the second header when the heat exchanger operates as an evaporator; andthe refrigerant flows downward in the first header and the second header when the heat exchanger operates as a condenser.
- The heat exchanger according to any one of the preceding claims, further comprising one or more flow speed boosting baffles mounted to at least one header of the first header and the second header arranged at an inlet of one group of the n groups such that the flow speed boosting baffle is positioned between the one group and another group positioned immediately ahead of the one group in a direction of flow of the refrigerant when the heat exchanger operates as an evaporator, each of the one or more flow speed boosting baffles being provided with at least one boosting hole allowing the refrigerant to pass therethrough.
- The heat exchanger according to claim 11, wherein the one or more flow speed boosting baffles are positioned between the last group of the n groups arranged in the direction of flow of the refrigerant and another group immediately ahead of the last group when the heat exchanger operates as the evaporator.
- The heat exchanger according to claim 11 or 12, wherein the cross section of each of the one or more boosting holes is a polygon, circle, or other closed figure.
- The heat exchanger according to claim 11, 12 or 13, wherein a total cross-sectional area of the one or more boosting holes is 5 % to 70 % of a cross-sectional area of an inner space of the at least one header.
- The heat exchanger according to claim 11, 12, 13 or 14, wherein the total cross-sectional area of the one or more boosting holes is greater than the total cross-sectional area of the at least one distribution hole.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR20130083460A KR101462176B1 (en) | 2013-07-16 | 2013-07-16 | Heat exchanger |
Publications (1)
Publication Number | Publication Date |
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EP2865980A1 true EP2865980A1 (en) | 2015-04-29 |
Family
ID=51205274
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20140177274 Withdrawn EP2865980A1 (en) | 2013-07-16 | 2014-07-16 | Heat exchanger |
Country Status (8)
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US (1) | US20150021003A1 (en) |
EP (1) | EP2865980A1 (en) |
KR (1) | KR101462176B1 (en) |
CN (1) | CN104296425A (en) |
AU (1) | AU2014291046B2 (en) |
BR (1) | BR112015032473A2 (en) |
RU (1) | RU2643566C2 (en) |
WO (1) | WO2015009028A1 (en) |
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Also Published As
Publication number | Publication date |
---|---|
AU2014291046A1 (en) | 2015-12-10 |
CN104296425A (en) | 2015-01-21 |
KR101462176B1 (en) | 2014-11-21 |
RU2016101060A (en) | 2017-07-20 |
US20150021003A1 (en) | 2015-01-22 |
BR112015032473A2 (en) | 2017-07-25 |
RU2643566C2 (en) | 2018-02-02 |
AU2014291046B2 (en) | 2016-09-22 |
WO2015009028A1 (en) | 2015-01-22 |
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