EP3136039A1 - Collecteur stratifié, échangeur de chaleur et climatiseur - Google Patents

Collecteur stratifié, échangeur de chaleur et climatiseur Download PDF

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Publication number
EP3136039A1
EP3136039A1 EP14890287.7A EP14890287A EP3136039A1 EP 3136039 A1 EP3136039 A1 EP 3136039A1 EP 14890287 A EP14890287 A EP 14890287A EP 3136039 A1 EP3136039 A1 EP 3136039A1
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EP
European Patent Office
Prior art keywords
passage
refrigerant
outflow
passages
branching
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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.)
Granted
Application number
EP14890287.7A
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German (de)
English (en)
Other versions
EP3136039B1 (fr
EP3136039A4 (fr
Inventor
Shigeyoshi MATSUI
Shinya Higashiiue
Takashi Okazaki
Akira Ishibashi
Atsushi Mochizuki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3136039A1 publication Critical patent/EP3136039A1/fr
Publication of EP3136039A4 publication Critical patent/EP3136039A4/fr
Application granted granted Critical
Publication of EP3136039B1 publication Critical patent/EP3136039B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates

Definitions

  • the present invention relates to laminated headers, heat exchangers, and air-conditioning apparatuses.
  • a header in the related art includes, for example, a plate-like body including a distribution passage configured to distribute and deliver refrigerant inflowing from an inlet passage to a plurality of outlet passages.
  • the distribution passage includes a plurality of branching passages, each having a branching portion, an inflow passage communicating with the branching portion, and two outflow passages communicating with the branching portion.
  • the refrigerant is repeatedly branched off into two paths a plurality of times in the branching passages, subsequently flows into a plurality of distribution chambers, and is distributed to the plurality of outlet passages from the distribution chambers (e.g., see Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 10-267468 (paragraphs [0033] to [0037], Fig. 6 )
  • the number of branching passages through which the refrigerant passes before flowing into each distribution chamber and the number of branch paths in each branching passage are the same so that evenness in the refrigerant to be distributed to the outlet passages is achieved.
  • the number of outlet passages is limited to multiples of powers of 2. In other words, in a case where such a header is used in a device, such as a heat exchanger, there is a problem in that the number of outlet passages cannot be changed freely in accordance with the number of passages formed in the device.
  • the present invention has been made in view of the problem mentioned above, and an object thereof is to obtain a laminated header in which the degree of freedom in the number of outlet passages is increased. Another object of the present invention is to obtain a heat exchanger equipped with such a laminated header. Another object of the present invention is to obtain an air-conditioning apparatus equipped with such a heat exchanger.
  • a laminated header includes a first plate-like body including a plurality of outlet passages, and also includes a second plate-like body attached to the first plate-like body and including at least part of a distribution passage configured to distribute and deliver refrigerant inflowing from an inlet passage to the plurality of outlet passages.
  • the distribution passage includes a branching passage having a branching portion, an inflow passage communicating with the branching portion, and a plurality of outflow passages communicating with the branching portion.
  • the plurality of outflow passages include a first outflow passage and a second outflow passage.
  • the number of curves, at which flow separation of the refrigerant is to occur, in a flow path through which the refrigerant inflowing from the inflow passage passes via the first outflow passage before reaching the outlet passages is smaller than the number of curves, at which flow separation of the refrigerant is to occur, in a flow path through which the refrigerant inflowing from the inflow passage passes via the second outflow passage before reaching the outlet passages.
  • the equivalent diameter of at least part of the first outflow passage is smaller than the equivalent diameter of at least part of the second outflow passage.
  • the plurality of outflow passages include the first outflow passage and the second outflow passage.
  • the number of curves, at which flow separation of the refrigerant is to occur, in the flow path through which the refrigerant inflowing from the inflow passage passes via the first outflow passage before reaching the outlet passages is smaller than the number of curves, at which flow separation of the refrigerant is to occur, in the flow path through which the refrigerant inflowing from the inflow passage passes via the second outflow passage before reaching the outlet passages.
  • the equivalent diameter of at least part of the first outflow passage is smaller than the equivalent diameter of at least part of the second outflow passage.
  • the laminated header according to the present invention is described below as being configured to distribute refrigerant flowing into a heat exchanger, the laminated header according to the present invention may alternatively be configured to distribute refrigerant flowing into another device.
  • the configuration and the operation to be described below are merely examples, and the laminated header according to the present invention is not limited to the case of such a configuration or operation.
  • identical reference signs are given to identical or similar components among the drawings or such reference signs are omitted therefrom.
  • the illustrations of detailed structures are simplified or omitted, where appropriate.
  • redundant or similar descriptions are simplified or omitted, where appropriate.
  • Fig. 1 illustrates the configuration of the heat exchanger according to Embodiment 1.
  • a heat exchanger 1 has a laminated header 2, a header 3, a plurality of heat-transfer tubes 4, a support member 5, and a plurality of fins 6.
  • the laminated header 2 has a refrigerant inflow section 2A and a plurality of refrigerant outflow sections 2B.
  • the header 3 has a plurality of refrigerant inflow sections 3A and a refrigerant outflow section 3B.
  • the refrigerant inflow section 2A of the laminated header 2 and the refrigerant outflow section 3B of the header 3 are connected to a refrigerant pipe.
  • the heat-transfer tubes 4 are connected between the refrigerant outflow sections 2B of the laminated header 2 and the refrigerant inflow sections 3A of the header 3.
  • a plurality of heat-transfer tubes 4 are flat tubes each having a passages.
  • the heat-transfer tubes 4 are composed of, for example, aluminum.
  • the laminated-header-2-side ends of the heat-transfer tubes 4 are connected to the refrigerant outflow sections 2B of the laminated header 2 in a state where the ends are supported by the support member 5, which is plate-like.
  • the support member 5 is composed of, for example, aluminum.
  • the heat-transfer tubes 4 are joined to the plurality of fins 6.
  • the fins 6 are composed of, for example, aluminum.
  • Fig. 1 illustrates a case where there are six heat-transfer tubes 4, the number thereof is not limited to such a case. For example, the number may be two. Furthermore, the heat-transfer tubes 4 do not have to be flat tubes.
  • the refrigerant flowing through the refrigerant pipe is distributed by flowing into the laminated header 2 via the refrigerant inflow section 2A, and outflows to the plurality of heat-transfer tubes 4 via the corresponding plurality of refrigerant outflow sections 2B.
  • the refrigerant exchanges heat with, for example, air supplied from a fan.
  • the refrigerant flowing through the plurality of heat-transfer tubes 4 merges together by flowing into the header 3 via the plurality of refrigerant inflow sections 3A, and outflows to the refrigerant pipe via the refrigerant outflow section 3B.
  • the refrigerant can be flowed backward.
  • Fig. 2 is a perspective view illustrating a state where the laminated header of the heat exchanger according to Embodiment 1 is disassembled.
  • the laminated header 2 includes a first plate-like body 11 and a second plate-like body 12.
  • the first plate-like body 11 is laminated at the outflow side of the refrigerant.
  • the second plate-like body 12 is laminated at the inflow side of the refrigerant.
  • the first plate-like body 11 has a first plate-like member 21 and a cladding member 24_5.
  • the second plate-like body 12 has a second plate-like member 22, a plurality of third plate-like members 23_1 to 23_3, and a plurality of cladding members 24_1 to 24_4.
  • a brazing material is applied to both surfaces or one surface of each of the cladding members 24_1 to 24_5.
  • the first plate-like member 21 is laminated on the support member 5 with the cladding member 24_5 interposed therebetween.
  • the plurality of third plate-like members 23_1 to 23_3 respectively intervened by the cladding members 24_2 to 24_4 are laminated on the first plate-like member 21.
  • the second plate-like member 22 is laminated on the third plate-like member 23_1 with the cladding member 24_1 interposed therebetween.
  • the first plate-like member 21, the second plate-like member 22, and the third plate-like members 23_1 to 23_3 each have a thickness of 1 mm to 10 mm and are composed of aluminum.
  • the support member 5, the first plate-like member 21, the second plate-like member 22, the third plate-like members 23_1 to 23_3, and the cladding members 24_1 to 24_5 are sometimes collectively referred to as plate-like members.
  • the third plate-like members 23_1 to 23_3 are sometimes collectively referred to as third plate-like members 23.
  • the cladding members 24_1 to 24_5 are sometimes collectively referred to as cladding members 24.
  • passages 21 A formed in the first plate-like member 21 and passages 24_5A formed in the cladding member 24_5 communicate with each other, whereby a plurality of outlet passages 11 A are formed.
  • the passages 21 A and the passages 24_5A are through-holes whose inner peripheral surfaces conform in shape to the outer peripheral surfaces of the heat-transfer tubes 4.
  • the ends of the heat-transfer tubes 4 are supported by being joined to the support member 5 by brazing.
  • outlet passages 11 A and the heat-transfer tubes 4 may be directly joined to each other without providing the support member 5. In that case, for example, the component cost is reduced.
  • the plurality of outlet passages 11 A correspond to the plurality of refrigerant outflow sections 2B in Fig. 1 .
  • the distribution passage 12A has an inlet passage 12a, branching passages 12b_11 to 12b_14, and a through-passage 12c.
  • the number and the order of the branching passages 12b_11 to 12b_14 and the through-passage 12c are changed, where appropriate, in accordance with, for example, the number of heat-transfer tubes 4.
  • the branching passages 12b_11 to 12b_14 are sometimes collectively referred to as branching passages 12b.
  • the passage 22A formed in the second plate-like member 22 and the passage 24_1 A formed in the cladding member 24_1 communicate with each other, whereby the inlet passage 12a is formed.
  • the passage 22A and the passage 24_1 A are circular through-holes.
  • the inlet passage 12a is connected to the refrigerant pipe.
  • the inlet passage 12a corresponds to the refrigerant inflow section 2A in Fig. 1 .
  • the passage 24_1 A formed in the cladding member 24_1, the passage 23_1A formed in the third plate-like member 23_1, and the one passage 24_2A and the one passage 24_2B formed in the cladding member 24_2 communicate with one another, whereby the branching passage 12b_11 is formed.
  • the passage 23_1A is a linear through-groove.
  • the passages 24_2A and 24_2B are circular through-holes.
  • the passage 24_2A formed in the cladding member 24_2 By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3, the passage 24_2A formed in the cladding member 24_2, the passage 23_2A formed in the third plate-like member 23_2, and the two passages 24_3A formed in the cladding member 24_3 communicate with one another, whereby the branching passage 12b_12 is formed.
  • the passage 23_2A is a linear through-groove.
  • the passages 24_3A are circular through-holes.
  • the passages 24_3A formed in the cladding member 24_3, the passages 23_3A formed in the third plate-like member 23_3, and the two pairs of passages 24_4A formed in the cladding member 24_4 communicate with one another, whereby the branching passages 12b_13 are formed.
  • the passages 23_3A are linear through-grooves.
  • the passages 24_4A are circular through-holes.
  • the passage 24_2B formed in the cladding member 24_2 By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3, the passage 24_2B formed in the cladding member 24_2, the passage 23_2B formed in the third plate-like member 23_2, and the one passage 24_3B formed in the cladding member 24_3 communicate with one another, whereby the through-passage 12c is formed.
  • the passage 23_2B and the passage 24_3B are circular through-holes.
  • the passage 24_3B formed in the cladding member 24_3, the passage 23_3B formed in the third plate-like member 23_3, and the two passages 24_4B formed in the cladding member 24_4 communicate with one another, whereby the branching passage 12b_14 is formed.
  • the passage 23_3B is a linear through-groove.
  • the passages 24_4B are circular through-holes.
  • the ends of the passages 23_1 A to 23_3A and 23_3B being linear through-grooves formed in the third plate-like members 23 and the passages 24_2A to 24_4A and 24_4B being circular through-holes formed in the cladding members 24 laminated on the refrigerant outflow surfaces of the third plate-like members 23 are formed at positions facing each other. Therefore, the passages 23_1 A to 23_3A and 23_3B being linear through-grooves formed in the third plate-like members 23 are blocked, except for the ends, by the cladding members 24 laminated on the refrigerant outflow surfaces of the third plate-like members 23.
  • the laminated header 2 may include a plurality of combinations of outlet passages 11 A and distribution passages 12A. Furthermore, the inlet passage 12a may be formed in a plate-like member other than the second plate-like member 22. In other words, the inlet passage 12a may be formed in, for example, the first plate-like member 21 or the third plate-like member 23.
  • the refrigerant passing through the inlet passage 12a flows into the branching passage 12b_11.
  • the refrigerant passing through the passage 24_1 A flows into the part between the ends of the passage 23_1 A, branches off into two paths by hitting against the surface of the cladding member 24_2, reaches the opposite ends of the passage 23_1A, and flows into the branching passage 12b_12 and the through-passage 12c.
  • the refrigerant passing through the passage 24_2A flows into the part between the ends of the passage 23_2A, branches off into two paths by hitting against the surface of the cladding member 24_3, reaches the opposite ends of the passage 23_2A, and flows into the two branching passages 12b_13.
  • each branching passage 12b_13 the refrigerant passing through the passage 24_3A flows into the part between the ends of the passage 23_3A, branches off into two paths by hitting against the surface of the cladding member 24_4, reaches the opposite ends of the passage 23_3A, and flows into the heat-transfer tubes 4 via the outlet passages 11 A.
  • the refrigerant passing through the passage 24_2B passes through the passage 23_2B and flows into the branching passage 12b_14.
  • the refrigerant passing through the passage 24_3B flows into the part between the ends of the passage 23_3B, branches off into two paths by hitting against the surface of the cladding member 24_4, reaches the opposite ends of the passage 23_3B, and flows into the heat-transfer tubes 4 via the outlet passages 11 A.
  • Fig. 3 is a perspective view of a relevant part of the distribution passage, illustrating a state where the laminated header of the heat exchanger according to Embodiment 1 is disassembled.
  • Fig. 4 is a diagram illustrating an overlapped state of the passages of a branching passage in the heat exchanger according to Embodiment 1.
  • the equivalent diameter of the passage 24_2B communicating with the passage 23_2B being a circular through-hole of the through-passage 12c is smaller than the equivalent diameter of the passage 24_2A communicating with the passage 23_2A being a linear through-groove of the branching passage 12b_12.
  • an intersection portion 31 where the passage 23_1A intersects the passage 24_1A is defined as a branching portion 41 of the branching passage 12b
  • the passage 24_1A is defined as an inflow passage 42 of the branching passage 12b
  • a connecting portion 33 connecting the intersection portion 31 and an upper end 32 of the passage 23_1 A
  • the passage 24_2B are defined as a first outflow passage 43 of the branching passage 12b
  • a connecting portion 35 connecting the intersection portion 31 and a lower end 34 of the passage 23_1 A
  • the passage 24_2A are defined as a second outflow passage 44 of the branching passage 12b
  • the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44.
  • the branching portion 41 of the branching passage 12b separation occurs in the flow of the refrigerant. Furthermore, the connecting portions 33 and 35 being linear through-grooves of the branching passage 12b each have a bent portion 36. At each bent portion 36, separation occurs in the flow of the refrigerant. Moreover, separation occurs in the flow of the refrigerant at the upper end 32 and the lower end 34 being linear through-grooves of the branching passage 12b. In other words, the branching portion 41, the bent portions 36, the upper end 32, and the lower end 34 correspond to "curves at which flow separation of the refrigerant is to occur".
  • the refrigerant outflowing from the end not communicating with the branching portion 41 passes through the through-passage 12c and the branching passage 12b_14 before reaching the outlet passages 11 A. Therefore, the number of times the refrigerant passes through the curves at which separation occurs in the flow of the refrigerant is small.
  • the refrigerant outflowing from the end not communicating with the branching portion 41 passes through the branching passage 12b_12 and the branching passages 12b_13 before reaching the outlet passages 11 A.
  • the equivalent diameter of the first outflow passage 43 and the equivalent diameter of the second outflow passage 44 are equal to each other, a difference occurs between pressure loss in the refrigerant outflowing from the first outflow passage 43 and pressure loss in the refrigerant outflowing from the second outflow passage 44, causing the refrigerant distributed to the outlet passages 11A to become uneven.
  • the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44, unevenness in the refrigerant distributed to the outlet passages 11 A is suppressed.
  • the equivalent diameters of the passages 24_2A and 24_2B are set such that the flow pattern of the refrigerant is the same before and after passing through the passages 24_2A and 24_2B. If the flow pattern of the refrigerant changes before and after passing through the passages 24_2A and 24_2B, the pressure loss occurring in the refrigerant is dependent on the flow rate and fluctuates significantly. Thus, the balance in pressure loss in each of the passages 24_2A and 24_2B changes in accordance with fluctuations in the flow rate of the refrigerant flowing into the distribution passage 12A, causing the refrigerant distributed to the outlet passages 11 A to become uneven. In the case where, for example, the equivalent diameters of the passages 24_2A and 24_2B are set such that the flow pattern of the refrigerant is the same, unevenness in the refrigerant distributed to the outlet passages 11 A is suppressed.
  • the hole diameters of the passages 24_2A and 24_2B may be set such that the flow pattern of the refrigerant does not change before and after passing through the passages 24_2A and 24_2B under a condition in which the refrigerant flows into the distribution passage 12A at the maximum flow rate and is uniformly distributed to the outlet passages 11 A.
  • the equivalent diameters of the passages 24_2A and 24_2B may be set such that the flow pattern of the refrigerant becomes an annular flow pattern or an annular spray flow pattern before and after passing through the passages 24_2A and 24_2B.
  • the flow state of the refrigerant after passing through the passages 24_2A and 24_2B is made uniform, thereby achieving improved evenness in the branching process in the subsequent branching passage 12b.
  • Fig. 5 is a Baker diagram illustrating the relationship between the flow state and the flow pattern of the refrigerant.
  • the flow pattern of the refrigerant before and after passing through the passages 24_2A and 24_2B can be calculated by using the Baker diagram shown in Fig. 5 .
  • the Baker diagram is a characteristic diagram showing the flow pattern of the refrigerant in a two-phase gas-liquid state.
  • the ordinate axis and the abscissa axis indicate values expressing the flow state of the refrigerant.
  • the ordinate axis is Gg/ ⁇
  • the abscissa axis is ⁇ Gl/Gg.
  • the ordinate axis corresponds to the magnitude of the mass flow rate of the gaseous phase of the refrigerant.
  • the mass flow rate of the gaseous phase of the refrigerant increases toward the upper side.
  • the abscissa axis corresponds to the ratio of the mass flow rate between the gaseous phase and the liquid phase of the refrigerant, that is, the quality. In Fig. 5 , the quality decreases toward the right side.
  • the equivalent diameters of the passages 24_2A and 24_2B may be set such that the flow state of the refrigerant before and after passing through the passages 24_2A and 24_2B satisfies the relationship indicated by expression 2 or 3 below.
  • the mass velocity of the gaseous phase of the refrigerant is defined as Gg [kg/(m 2 ⁇ h)]
  • the mass velocity of the liquid phase of the refrigerant is defined as Gl [kg/(m 2 ⁇ h)]
  • the density of the gaseous phase of the refrigerant is defined as pg [kg/m 3 ]
  • the density of the liquid phase of the refrigerant is defined as ⁇ l [kg/m 3 ]
  • the density of air is defined as pa [kg/m 3 ]
  • the density of water is defined as ⁇ w [kg/m 3 ]
  • the surface tension of the liquid phase of the refrigerant is defined as ⁇ l [N/m]
  • the surface tension of water is defined as ⁇ w [N/m]
  • the viscosity coefficient of the liquid phase of the refrigerant is defined as ⁇ l [ ⁇ Pa ⁇ s]
  • the viscosity coefficient of water is defined as ⁇ w [ ⁇ Pa ⁇ s].
  • the maximum flow rate of the refrigerant flowing into the distribution passage 12A may be used as the flow rate
  • the equivalent diameter of the passage 23_1 A may be used as the equivalent diameter of a passage before the refrigerant passes through the passage 24_2A or 24_2B
  • the equivalent diameter of the passage 24_2A or 24_2B may be used as the equivalent diameter of a passage before the refrigerant passes through the passage 24_2A or 24_2B.
  • other passages constituting the distribution passage 12A may similarly be set to equivalent diameters with which the pressure loss occurring in the refrigerant becomes even.
  • the equivalent diameter of the passage 24_3B may be smaller than the equivalent diameter of each passage 24_3A.
  • the equivalent diameters of the passage 23_3B and the passages 24_4B may be smaller than the equivalent diameters of the passages 23_3A and the passages 24_4A.
  • branching passages 12b similar to the branching passage 12b_11, the above-described configuration may be employed in all of the branching passages, or the above-described configuration may be employed in one or more of the branching passages.
  • the branching passage 12b in which the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44 may be the branching passage 12b at the upstream side of the distribution passage 12A.
  • the refrigerant outflowing from at least one of the first outflow passage 43 and the second outflow passage 44 in the branching passage 12b in which the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44 may be further branched off at another branching passage 12b.
  • each branching passage 12b has different heights, in the direction of gravitational force, at the ends not communicating with the branching portion 41 between the first outflow passage 43 and the second outflow passage 44
  • the branching passage 12b is not limited to such a case.
  • the advantage of employing the above-described configuration is noteworthy since it is particularly difficult to evenly distribute the refrigerant.
  • the branching passages 12b are not limited to such a case.
  • the branching passages 12b are not limited to such a case.
  • the refrigerant is evenly branched off at the branching portion 41.
  • each branching passage 12b has different heights, in the direction of gravitational force, at the ends not communicating with the branching portion 41 between the first outflow passage 43 and the second outflow passage 44.
  • each branching passage 12b the end of the first outflow passage 43 not communicating with the branching portion 41 is positioned at the upper side of the branching portion 41 in the direction of gravitational force and the end of the second outflow passage 44 not communicating with the branching portion 41 is positioned at the lower side of the branching portion 41 in the direction of gravitational force
  • the branching passages 12b are not limited to such a case.
  • each branching passage 12b the end of the first outflow passage 43 not communicating with the branching portion 41 is positioned at the upper side of the branching portion 41 in the direction of gravitational force and the end of the second outflow passage 44 not communicating with the branching portion 41 is positioned at the lower side of the branching portion 41 in the direction of gravitational force, the difference in passage length between the first outflow passage 43 and the second outflow passage 44 can be reduced, thereby achieving even distribution of the refrigerant without making the passage shapes of the first outflow passage 43 and the second outflow passage 44 complex.
  • each branching passage 12b a line connecting the end of the first outflow passage 43 not communicating with the branching portion 41 and the end of the second outflow passage 44 not communicating with the branching portion 41 is parallel to the longitudinal direction of the plate-like member
  • the branching passages 12b are not limited to such a case.
  • the plate-like member can be reduced in size in the lateral direction so that, for example, the component cost and the weight are reduced.
  • each branching passage 12b the line connecting the end of the first outflow passage 43 not communicating with the branching portion 41 and the end of the second outflow passage 44 not communicating with the branching portion 41 is parallel to the direction in which the heat-transfer tubes 4 are arranged, a space-saving heat exchanger 1 can be achieved.
  • the line connecting the end of the first outflow passage 43 not communicating with the branching portion 41 and the end of the second outflow passage 44 not communicating with the branching portion 41, the longitudinal direction of the plate-like member, and the direction in which the heat-transfer tubes 4 are arranged do not have to be parallel to the direction of gravitational force.
  • the heat exchanger according to Embodiment 1 is applied to an air-conditioning apparatus
  • the application is not limited thereto.
  • the heat exchanger according to Embodiment 1 may be applied to another refrigeration cycle apparatus having a refrigerant circuit.
  • the air-conditioning apparatus may alternatively be configured to only perform the cooling operation or the heating operation.
  • Fig. 6 illustrates the configuration of the air-conditioning apparatus to which the heat exchanger according to Embodiment 1 is applied.
  • the flow of the refrigerant during the cooling operation is indicated by a solid arrow, whereas the flow of the refrigerant during the heating operation is indicated by a dotted arrow.
  • an air-conditioning apparatus 91 has a compressor 92, a four-way valve 93, an outdoor heat exchanger (heat-source-side heat exchanger) 94, an expansion device 95, an indoor heat exchanger (load-side heat exchanger) 96, an outdoor fan (heat-source-side fan) 97, an indoor fan (load-side fan) 98, and a controller 99.
  • the compressor 92, the four-way valve 93, the outdoor heat exchanger 94, the expansion device 95, and the indoor heat exchanger 96 are connected by a refrigerant pipe, so that a refrigerant circuit is formed.
  • the controller 99 is connected to, for example, the compressor 92, the four-way valve 93, the expansion device 95, the outdoor fan 97, the indoor fan 98, and various types of sensors.
  • the controller 99 changes the passage of the four-way valve 93 to switch between the cooling operation and the heating operation.
  • the refrigerant in a high-pressure high-temperature gas state discharged from the compressor 92 flows into the outdoor heat exchanger 94 via the four-way valve 93 and condenses by exchanging heat with air supplied by the outdoor fan 97.
  • the condensed refrigerant turns into a high-pressure liquid state, outflows from the outdoor heat exchanger 94, and is turned into a low-pressure two-phase gas-liquid state by the expansion device 95.
  • the refrigerant in the low-pressure two-phase gas-liquid state flows into the indoor heat exchanger 96 and evaporates by exchanging heat with air supplied by the indoor fan 98, thereby cooling the interior.
  • the evaporated refrigerant turns into a low-pressure gas state, outflows from the indoor heat exchanger 96, and is suctioned into the compressor 92 via the four-way valve 93.
  • the refrigerant in a high-pressure high-temperature gas state discharged from the compressor 92 flows into the indoor heat exchanger 96 via the four-way valve 93 and condenses by exchanging heat with air supplied by the indoor fan 98, thereby heating the interior.
  • the condensed refrigerant turns into a high-pressure liquid state, outflows from the indoor heat exchanger 96, and is turned into refrigerant in a low-pressure two-phase gas-liquid state by the expansion device 95.
  • the refrigerant in the low-pressure two-phase gas-liquid state flows into the outdoor heat exchanger 94 and evaporates by exchanging heat with air supplied by the outdoor fan 97.
  • the evaporated refrigerant turns into a low-pressure gas state, outflows from the outdoor heat exchanger 94, and is suctioned into the compressor 92 via the four-way valve 93.
  • the heat exchanger 1 is used as at least one of the outdoor heat exchanger 94 and the indoor heat exchanger 96. When functioning as an evaporator, the heat exchanger 1 is connected such that the refrigerant inflows from the laminated header 2 and the refrigerant outflows to the header 3. In other words, when the heat exchanger 1 functions as an evaporator, the refrigerant in a two-phase gas-liquid state flows into the laminated header 2 from the refrigerant pipe. When the heat exchanger 1 functions as a condenser, the refrigerant flows backward through the laminated header 2.
  • the laminated header 2 achieves improved evenness in the distribution of the refrigerant owing to the above-described configuration, evenness in the flow rate and the quality of the refrigerant outflowing to the plurality of heat-transfer tubes 4 can be achieved even when refrigerant in a two-phase gas-liquid state, which is relatively difficult to distribute evenly, flows in.
  • the laminated header 2 is suitable for a refrigeration cycle apparatus, such as the air-conditioning apparatus 91.
  • each branching passage 12b has the first outflow passage 43 having a small number of curves, at which flow separation of the refrigerant is to occur, in a flow path through which the refrigerant inflowing from the inflow passage 42 passes before reaching the outlet passages 11 A, and also has the second outflow passage 44 having a large number of curves, at which flow separation of the refrigerant is to occur, in a flow path through which the refrigerant inflowing from the inflow passage 42 passes before reaching the outlet passages 11 A.
  • the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44.
  • the distribution passage 12A is formed by laminating plate-like members. Therefore, regardless of the fact that the laminated header 2 is capable of suppressing reduction in the evenness of the distribution of the refrigerant while also allowing for a change in the number of outlet passages 11 A to a number other than multiples of powers of 2, for example, the equivalent diameter of each passage, the shape of each passage, the number of distributions, and the number of branch paths in the branching portion 41 can be easily changed by changing, for example, the hole diameter of each plate-like member, the groove width of each plate-like member, the hole shape or the groove shape of each plate-like member, the number of plate-like members, and the thickness of each plate-like member.
  • Embodiment 1 Redundant or similar descriptions as those in Embodiment 1 are simplified, where appropriate, or are omitted.
  • Fig. 7 is a perspective view illustrating a state where the laminated header of the heat exchanger according to Embodiment 2 is disassembled.
  • the distribution passage 12A has an inlet passage 12a and branching passages 12b_21 to 12b_23.
  • the number and the order of the branching passages 12b_21 to 12b_23 are changed, where appropriate, in accordance with, for example, the number of heat-transfer tubes 4.
  • the branching passages 12b_21 to 12b_23 are sometimes collectively referred to as branching passages 12b.
  • the passage 24_1 A formed in the cladding member 24_1, the passage 23_1 A formed in the third plate-like member 23_1, and the two passages 24_2A and the one passage 24_2B formed in the cladding member 24_2 communicate with one another, whereby a branching passage 12b_21 is formed.
  • the passage 23_1A is a linear through-groove.
  • the passages 24_2A and 24_2B are circular through-holes.
  • the passages 24_2A formed in the cladding member 24_2 By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3, the passages 24_2A formed in the cladding member 24_2, the passages 23_2A formed in the third plate-like member 23_2, and the two pairs of passages 24_3A formed in the cladding member 24_3 communicate with one another, whereby branching passages 12b_22 are formed.
  • the passages 23_2A are linear through-grooves.
  • the passages 24_3A are circular through-holes.
  • the passage 24_2B formed in the cladding member 24_2 By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3, the passage 24_2B formed in the cladding member 24_2, the passage 23_2B formed in the third plate-like member 23_2, and the two passages 24_3B formed in the cladding member 24_3 communicate with one another, whereby a branching passage 12b_23 is formed.
  • the passage 23_2B is a linear through-groove.
  • the passages 24_3B are circular through-holes.
  • the passage 24_1 A being a circular through-hole formed in the cladding member 24_1 laminated on the refrigerant inflow surface of the third plate-like member 23_1 and the passage 24_2B being a circular through-hole formed in the cladding member 24_2 laminated on the refrigerant outflow surface of the third plate-like member 23_1 are formed at positions facing each other. Therefore, the passages 23_2A and 23_2B being linear through-grooves formed in the third plate-like members 23 excluding the third plate-like member 23_1 are blocked, except for the ends, by the cladding members 24 laminated on the refrigerant outflow surfaces of the relevant third plate-like members 23.
  • the passage 23_1A being a linear through-groove formed in the third plate-like member 23_1 is blocked, except for the part between the ends and the ends, by the cladding member 24_2 laminated on the refrigerant outflow surface of the third plate-like member 23_1.
  • the refrigerant passing through the inlet passage 12a flows into the branching passage 12b_21.
  • the refrigerant passing through the passage 24_1 A passes through the part between the ends of the passage 23_1 A, reaches the opposite ends of the passage 23_1A, and flows into the two branching passages 12b_22 and the one branching passage 12b_23.
  • each branching passage 12b_22 the refrigerant passing through the passage 24_2A flows into the part between the ends of the passage 23_2A, branches off into two paths by hitting against the surface of the cladding member 24_3, reaches the opposite ends of the passage 23_2A, and flows into the heat-transfer tubes 4 via the outlet passages 11 A.
  • the refrigerant passing through the passage 24_2B flows into the part between the ends of the passage 23_2B, branches off into two paths by hitting against the surface of the cladding member 24_3, reaches the opposite ends of the passage 23_2B, and flows into the heat-transfer tubes 4 via the outlet passages 11 A.
  • Fig. 8 is a perspective view of a relevant part of the distribution passage, illustrating a state where the laminated header of the heat exchanger according to Embodiment 2 is disassembled.
  • Fig. 9 is a diagram illustrating an overlapped state of the passages of a branching passage in the heat exchanger according to Embodiment 2.
  • the equivalent diameter of the passage 24_2B facing the part between the ends of the passage 23_1A and also facing the passage 24_1 A is smaller than the equivalent diameter of each of the passages 24_2A facing the ends of the passage 23_1 A.
  • an intersection portion 31 where the passage 23_1A intersects the passage 24_1A is defined as a branching portion 41 of the branching passage 12b
  • the passage 24_1A is defined as an inflow passage 42 of the branching passage 12b
  • the passage 24_2B is defined as a first outflow passage 43 of the branching passage 12b
  • the passage 24_2A are defined as a second outflow passage 44 of the branching passage 12b
  • the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44.
  • the branching portion 41 corresponds to "a curve at which flow separation of the refrigerant is to occur".
  • the refrigerant inflowing from the inflow passage 42 is bent at the branching portion 41, travels through the bent portion 36 of the passage 23_1A and the upper end 32 or the lower end 34 of the passage 23_1 A, and subsequently flows into the subsequent branching passage 12b_22. Therefore, the number of times the refrigerant inflowing from the inflow passage 42 passes through curves at which separation occurs in the flow of the refrigerant before reaching the outlet passages 11 A is large.
  • the equivalent diameter of the first outflow passage 43 and the equivalent diameter of the second outflow passage 44 are equal to each other, a difference occurs between pressure loss in the refrigerant passing through the first outflow passage 43 and pressure loss in the refrigerant passing through the second outflow passage 44, causing the refrigerant distributed to the outlet passages 11 A to become uneven.
  • the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44, unevenness in the refrigerant distributed to the outlet passages 11 A is suppressed.
  • other passages constituting the distribution passage 12A preferably similarly be set to equivalent diameters with which the pressure loss occurring in the refrigerant becomes even.
  • the equivalent diameter of each of the passage 23_2B and the passages 24_3B may be smaller than the equivalent diameter of each of the passages 23_2A and the passages 24_3A, respectively.
  • branching passages 12b similar to the branching passage 12b_21, the above-described configuration may be employed in all of the branching passages, or the above-described configuration may be employed in one or more of the branching passages.
  • each branching passage 12b has the first outflow passage 43 having a small number of curves, at which flow separation of the refrigerant is to occur, in a flow path through which the refrigerant inflowing from the inflow passage 42 passes before reaching the outlet passages 11 A, and also has the second outflow passage 44 having a large number of curves, at which flow separation of the refrigerant is to occur, in a flow path through which the refrigerant inflowing from the inflow passage 42 passes before reaching the outlet passages 11 A.
  • the equivalent diameter of at least part of the first outflow passage 43 is smaller than the equivalent diameter of at least part of the second outflow passage 44.
  • the distribution passage 12A has the branching passage 12b_21 that causes the inflowing refrigerant to branch off into three paths, that is, causes the inflowing refrigerant to branch off into a large number of branch paths. Therefore, the laminated header 2 can be reduced in thickness, so that the laminated header 2 is reduced in size and cost. Moreover, the number of plate-like members constituting the laminated header 2 can be reduced, thereby reducing, for example, the manufacturing costs.
  • Figs. 10 and 11 are perspective views illustrating a state where the laminated header in modifications of the heat exchanger according to Embodiment 2 is disassembled.
  • the refrigerant outflowing from the first outflow passage 43 of the branching passage 12b_21 may flow into the through-passage 12c.
  • the configuration of the heat exchanger according to Embodiment 1 and the configuration of the heat exchanger according to Embodiment 2 may be combined. In that case, the degree of freedom in the number of outlet passages 11 A in the laminated header 2 is further increased.
  • the refrigerant outflowing from the first outflow passage 43 of the branching passage 12b_21 may flow into the branching passage 12b_22, and the refrigerant outflowing from the second outflow passage 44 of the branching passage 12b_21 may flow into the through-passage 12c.
  • the equivalent diameter of at least part of the first outflow passage 43 may possibly be set to be larger than the equivalent diameter of at least part of the second outflow passage 44.
  • the first outflow passage 43 corresponds to a "second outflow passage” according to the present invention
  • the second outflow passage 44 corresponds to a "first outflow passage” according to the present invention.
  • Embodiment 1 and Embodiment 2 have been described above, the present invention is not to be limited to Embodiment 1 and Embodiment 2.
  • Embodiment 1 and Embodiment 2 may be entirely or partially combined, or may be combined with the modifications.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP14890287.7A 2014-04-21 2014-04-21 Collecteur stratifié, échangeur de chaleur et climatiseur Active EP3136039B1 (fr)

Applications Claiming Priority (1)

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PCT/JP2014/061209 WO2015162678A1 (fr) 2014-04-21 2014-04-21 Collecteur stratifié, échangeur de chaleur et climatiseur

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EP3136039A1 true EP3136039A1 (fr) 2017-03-01
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Cited By (2)

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Publication number Priority date Publication date Assignee Title
US11629896B2 (en) 2018-05-01 2023-04-18 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US11740026B2 (en) 2019-06-28 2023-08-29 Daikin Industries, Ltd. Heat exchanger and heat pump apparatus

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Publication number Priority date Publication date Assignee Title
CN114127488B (zh) * 2019-06-28 2023-01-13 大金工业株式会社 热交换器和热泵装置
JP6767606B1 (ja) * 2019-12-09 2020-10-14 日立ジョンソンコントロールズ空調株式会社 分配装置、分配装置を備えた熱交換器およびその熱交換器を備えた空気調和機
CN111059642A (zh) * 2019-12-31 2020-04-24 海信（山东）空调有限公司 一种空调器
JPWO2023148841A1 (fr) * 2022-02-02 2023-08-10

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US5241839A (en) * 1991-04-24 1993-09-07 Modine Manufacturing Company Evaporator for a refrigerant
US5242016A (en) * 1992-04-02 1993-09-07 Nartron Corporation Laminated plate header for a refrigeration system and method for making the same
JPH09189463A (ja) * 1996-02-29 1997-07-22 Mitsubishi Electric Corp 熱交換器の分配装置及びその製造方法
JPH11118295A (ja) * 1997-10-17 1999-04-30 Hitachi Ltd プレート型分流器およびその製造方法
JP3960233B2 (ja) * 2002-04-03 2007-08-15 株式会社デンソー 熱交換器
US6892805B1 (en) * 2004-04-05 2005-05-17 Modine Manufacturing Company Fluid flow distribution device
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JP5784215B2 (ja) * 2012-03-07 2015-09-24 三菱電機株式会社 熱交換器および冷凍サイクル装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11629896B2 (en) 2018-05-01 2023-04-18 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US11740026B2 (en) 2019-06-28 2023-08-29 Daikin Industries, Ltd. Heat exchanger and heat pump apparatus

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EP3136039B1 (fr) 2019-11-27
EP3136039A4 (fr) 2018-01-10
WO2015162678A1 (fr) 2015-10-29
JPWO2015162678A1 (ja) 2017-04-13
JP6188926B2 (ja) 2017-08-30

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