WO2015162678A1 - 積層型ヘッダー、熱交換器、及び、空気調和装置 - Google Patents
積層型ヘッダー、熱交換器、及び、空気調和装置 Download PDFInfo
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- WO2015162678A1 WO2015162678A1 PCT/JP2014/061209 JP2014061209W WO2015162678A1 WO 2015162678 A1 WO2015162678 A1 WO 2015162678A1 JP 2014061209 W JP2014061209 W JP 2014061209W WO 2015162678 A1 WO2015162678 A1 WO 2015162678A1
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- refrigerant
- flow path
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- branch
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
- F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
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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
- F28F9/0219—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
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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
- F28F9/0278—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 a laminated header, a heat exchanger, and an air conditioner.
- a header provided with a plate-like body in which a distribution channel that distributes and flows out refrigerant flowing in from an inlet channel to a plurality of outlet channels.
- the distribution channel has a plurality of branch channels having a branch part, an inflow channel communicating with the branch part, and two outflow channels communicating with the branch part.
- the refrigerant repeats two branches in the branch channel a plurality of times, then flows into the plurality of distribution chambers, and is distributed to the plurality of outlet channels in each distribution chamber (for example, Patent Document 1). See).
- JP 10-267468 A paragraph [0033] to paragraph [0037], FIG. 6
- the refrigerant distributed to each outlet channel is made uniform by equalizing the number of branch passages through which the refrigerant passes before flowing into each distribution chamber and the number of branches in each branch passage.
- the number of outlet channels is limited to a multiple of 2. That is, in such a header, when used in a device such as a heat exchanger, there is a problem that the number of outlet channels cannot be freely changed according to the number of channels formed in the device.
- the present invention has been made against the background of the above-described problems, and an object thereof is to obtain a laminated header in which the degree of freedom of the number of outlet channels is expanded. Moreover, an object of this invention is to obtain the heat exchanger provided with such a laminated header. Moreover, an object of this invention is to obtain the air conditioning apparatus provided with such a heat exchanger.
- the laminated header according to the present invention includes a first plate-like body in which a plurality of outlet channels are formed, and a refrigerant that is attached to the first plate-like body and flows in from the inlet channel to the plurality of outlet channels.
- a second plate-like body formed with at least a part of a distribution flow path that flows out and distributes, and the distribution flow path includes a branch portion, an inflow flow path that communicates with the branch portion, and the branch portion.
- a plurality of outflow passages that communicate with each other, the plurality of outflow passages including a first outflow passage and a second outflow passage, and inflow from the inflow passage
- the number of curved portions where separation occurs in the flow of the refrigerant in the flow path through which the refrigerant that passes through the first outflow path to reach the outlet flow path is such that the refrigerant flowing in from the inflow path Compared with the number of the curved portions in the flow path that passes through the second outflow flow path to reach the outlet flow path, it is small.
- Ku wherein at least a portion of the equivalent diameter of the first outlet channel is small compared to at least a portion of the equivalent diameter of the second outlet channel.
- the plurality of outflow channels include a first outflow channel and a second outflow channel, and the refrigerant flowing in from the inflow channel passes through the first outflow channel.
- the number of curved portions where separation occurs in the flow of the refrigerant in the flow path that passes up to the outlet flow path is such that the refrigerant flowing in from the inflow flow path reaches the outlet flow path via the second outflow flow path.
- the equivalent diameter of at least a part of the 1st outflow channel is the equivalent diameter of at least a part of the 2nd outflow channel Small compared. Therefore, it is possible to change the number of outlet channels to a number other than a multiple of 2 while suppressing deterioration in the uniformity of refrigerant distribution, so that the number of outlet channels of the multilayer header can be freely set. The degree is expanded.
- FIG. 3 is a drawing in which each flow path of the branch flow path of the heat exchanger according to Embodiment 1 is overlapped and drawn. It is a Baker diagram which shows the relationship between the flow state of a refrigerant
- FIG. 6 is a drawing in which each flow path of a branch flow path is drawn by overlapping the heat exchanger according to the second embodiment. It is a perspective view in the state which decomposed
- FIG. 6 is a perspective view in the state which decomposed
- FIG. It is a perspective view in the state which decomposed
- the laminated header according to the present invention will be described with reference to the drawings.
- the laminated header according to the present invention distributes the refrigerant flowing into the heat exchanger
- a refrigerant may be distributed.
- the configuration, operation, and the like described below are merely examples, and the laminated header according to the present invention is not limited to such a configuration, operation, and the like.
- symbol is attached
- symbol is abbreviate
- the illustration of the fine structure is simplified or omitted as appropriate.
- overlapping or similar descriptions are appropriately simplified or omitted.
- FIG. 1 is a diagram illustrating a configuration of a heat exchanger according to the first embodiment.
- the heat exchanger 1 includes a laminated header 2, a header 3, a plurality of heat transfer tubes 4, a holding member 5, and a plurality of fins 6.
- the laminated header 2 has a refrigerant inflow portion 2A and a plurality of refrigerant outflow portions 2B.
- the header 3 has a plurality of refrigerant inflow portions 3A and a refrigerant outflow portion 3B.
- Refrigerant piping is connected to the refrigerant inflow portion 2A of the stacked header 2 and the refrigerant outflow portion 3B of the header 3.
- a heat transfer tube 4 is connected between the refrigerant outflow portion 2B of the stacked header 2 and the refrigerant inflow portion 3A of the header 3.
- the heat transfer tube 4 is a flat tube in which a plurality of flow paths are formed.
- the heat transfer tube 4 is made of aluminum, for example.
- the end of the heat transfer tube 4 on the side of the laminated header 2 is connected to the refrigerant outflow portion 2B of the laminated header 2 while being held by the plate-like holding member 5.
- the holding member 5 is made of aluminum, for example.
- a plurality of fins 6 are joined to the heat transfer tube 4.
- the fin 6 is made of aluminum, for example.
- FIG. 1 although the case where the number of the heat exchanger tubes 4 is six is shown, it is not limited to such a case. For example, two may be used. Further, the heat transfer tube 4 may not be a flat tube.
- the refrigerant flowing through the refrigerant pipe flows into the stacked header 2 through the refrigerant inflow portion 2A and is distributed, and flows out to the plurality of heat transfer tubes 4 through the plurality of refrigerant outflow portions 2B.
- the refrigerant exchanges heat with, for example, air supplied by a fan in the plurality of heat transfer tubes 4.
- the refrigerant flowing through the plurality of heat transfer tubes 4 flows into and merges with the header 3 through the plurality of refrigerant inflow portions 3A, and flows out into the refrigerant pipe through the refrigerant outflow portion 3B.
- the refrigerant can flow backward.
- FIG. 2 is a perspective view of the heat exchanger according to Embodiment 1 in a state where the stacked header is disassembled.
- the stacked header 2 includes a first plate-like body 11 and a second plate-like body 12.
- the first plate-like body 11 is stacked on the refrigerant outflow side.
- the second plate-like body 12 is stacked on the refrigerant inflow side.
- the first plate-like body 11 includes a first plate-like member 21 and a clad material 24_5.
- the second plate-like body 12 includes a second plate-like member 22, a plurality of third plate-like members 23_1 to 23_3, and a plurality of clad materials 24_1 to 24_4.
- a brazing material is applied to both surfaces or one surface of the cladding materials 24_1 to 24_5.
- the first plate-like member 21 is laminated on the holding member 5 via the clad material 24_5.
- the plurality of third plate-like members 23_1 to 23_3 are stacked on the first plate-like member 21 via the clad materials 24_2 to 24_4.
- the second plate-like member 22 is laminated on the third plate-like member 23_1 via the clad material 24_1.
- the first plate member 21, the second plate member 22, and the third plate members 23_1 to 23_3 are, for example, about 1 to 10 mm in thickness and made of aluminum.
- the holding member 5, the first plate member 21, the second plate member 22, the third plate members 23_1 to 23_3, and the clad materials 24_1 to 24_5 may be collectively referred to as plate members.
- the third plate-like members 23_1 to 23_3 may be collectively referred to as the third plate-like member 23 in some cases.
- the cladding materials 24_1 to 24_5 may be collectively referred to as the cladding material 24 in some cases.
- the flow path 21 ⁇ / b> A and the flow path 24 ⁇ / b> _ ⁇ b> 5 ⁇ / b> A are through holes having an inner peripheral surface that follows the outer peripheral surface of the heat transfer tube 4.
- the end of the heat transfer tube 4 is joined and held to the holding member 5 by brazing.
- the holding member 5 may not be provided, and the outlet channel 11A and the heat transfer tube 4 may be directly joined. In such a case, parts costs and the like are reduced.
- the plurality of outlet channels 11A correspond to the plurality of refrigerant outflow portions 2B in FIG.
- the second plate-like member 22, the third plate-like members 23_1 to 23_3, and the clad members 24_1 to 24_4 are joined together, whereby the flow path 22A formed in the second plate-like member 22 and the third plate-like member 23_1.
- the flow paths 23_1A to 23_3A, 23_2B, and 23_3B formed in .about.23_3 and the flow paths 24_1A to 24_4A and 24_2B to 24_4B formed in the cladding materials 24_1 to 24_4 are communicated to form the distribution flow path 12A. .
- the distribution channel 12A includes an inlet channel 12a, branch channels 12b_11 to 12b_14, and a passage channel 12c.
- the number and order of the branch flow paths 12b_11 to 12b_14 and the passage flow path 12c are appropriately changed according to the number of heat transfer tubes 4 and the like.
- the branch flow paths 12b_11 to 12b_14 may be collectively referred to as a branch flow path 12b.
- the flow path 22A formed in the second plate-like member 22 and the flow path 24_1A formed in the clad material 24_1 are communicated with each other.
- An inlet channel 12a is formed.
- the channel 22A and the channel 24_1A are circular through holes.
- a refrigerant pipe is connected to the inlet channel 12a.
- the inlet channel 12a corresponds to the refrigerant inflow portion 2A in FIG.
- the third plate member 23_1 and the clad members 24_1 and 24_2 are joined to each other, whereby the flow path 24_1A formed in the clad material 24_1, the flow path 23_1A formed in the third plate member 23_1, and the clad material 24_2.
- the one flow path 24_2A and one flow path 24_2B formed in the above are communicated to form a branch flow path 12b_11.
- the flow path 23_1A is a linear through groove.
- the flow paths 24_2A and 24_2B are circular through holes.
- the third plate-like member 23_2 and the clad members 24_2 and 24_3 are joined to each other so that the flow path 24_2A formed in the clad material 24_2, the flow path 23_2A formed in the third plate-like member 23_2, and the clad material 24_3.
- the two flow paths 24_3A formed in the above are communicated to form a branch flow path 12b_12.
- the flow path 23_2A is a linear through groove.
- the flow path 24_3A is a circular through hole.
- the third plate member 23_3 and the clad members 24_3 and 24_4 are joined to each other, whereby the flow path 24_3A formed in the clad material 24_3, the flow path 23_3A formed in the third plate member 23_3, and the clad material 24_4.
- the two flow paths 24_4A formed in the above are communicated to form the branch flow path 12b_13.
- the flow path 23_3A is a linear through groove.
- the flow path 24_4A is a circular through hole.
- the third plate-like member 23_2 and the clad members 24_2 and 24_3 are joined to each other so that the flow path 24_2B formed in the clad material 24_2, the flow path 23_2B formed in the third plate-like member 23_2, and the clad material 24_3. And the one flow path 24_3B formed in the above are communicated to form the passage flow path 12c.
- the flow path 23_2B and the flow path 24_3B are circular through holes.
- the third plate member 23_3 and the clad members 24_3 and 24_4 are joined to each other, whereby the flow path 24_3B formed in the clad material 24_3, the flow path 23_3B formed in the third plate member 23_3, and the clad material 24_4.
- the two flow paths 24_4B formed in the above are communicated to form a branch flow path 12b_14.
- the flow path 23_3B is a linear through groove.
- the flow path 24_4B is a circular through hole.
- the flow paths 24_1A to 24_3A and 24_3B, which are circular through holes, formed in the laminated clad material 24 are formed at positions facing each other. Therefore, the flow paths 23_1A to 23_3A, 23_3B, which are linear through grooves formed in the third plate member 23, are clad materials laminated on the surface of the third plate member 23 on the side where the refrigerant flows. 24, except for a part between the end portions.
- the third plate-like member 23 is laminated on the end portions of the flow paths 23_1A to 23_3A, 23_3B, which are linear through grooves, and the surface of the third plate-like member 23 on the side where the refrigerant flows out.
- the flow paths 24_2A to 24_4A and 24_4B, which are circular through holes, formed in the clad material 24 are formed at positions facing each other. Therefore, the flow paths 23_1A to 23_3A, 23_3B, which are linear through grooves formed in the third plate member 23, are clad materials stacked on the surface of the third plate member 23 on the side from which the refrigerant flows out. 24, except for the end, is closed.
- the laminated header 2 may include a plurality of sets of a plurality of outlet channels 11A and distribution channels 12A. Further, the inlet channel 12 a may be formed in a plate-like member other than the second plate-like member 22. That is, the inlet channel 12a may be formed in the first plate member 21, the third plate member 23, and the like.
- the refrigerant that has passed through the flow path 24_2A flows into a part between the end portions of the flow path 23_2A, branches into two by hitting the surface of the clad material 24_3, and reaches both end portions of the flow path 23_2A. It flows into the two branch flow paths 12b_13.
- the refrigerant that has passed through the flow path 24_3A flows into a part between the end portions of the flow path 23_3A, hits the surface of the clad material 24_4, branches into two, and reaches both end portions of the flow path 23_3A. Then, it flows into the heat transfer tube 4 through the outlet channel 11A.
- the refrigerant that has passed through the channel 24_2B passes through the channel 23_2B and flows into the branch channel 12b_14.
- the refrigerant that has passed through the flow path 24_3B flows into a part between the end portions of the flow path 23_3B, branches into two by hitting the surface of the clad material 24_4, and reaches both end portions of the flow path 23_3B. Then, it flows into the heat transfer tube 4 through the outlet channel 11A.
- FIG. 3 is a perspective view of the main part of the distribution channel in a state where the stacked header is disassembled in the heat exchanger according to the first embodiment.
- FIG. 4 is a drawing in which each flow path of the branch flow path is drawn by overlapping the heat exchanger according to the first embodiment.
- the equivalent diameter of the flow path 24_2B communicating with the flow path 23_2B that is a circular through hole of the passage flow path 12c is the linear shape of the branch flow path 12b_12. It is smaller than the equivalent diameter of the flow path 24_2A communicating with the flow path 23_2A, which is a through groove.
- the intersection 31 that intersects the flow path 24_1A of the flow path 23_1A is the branching section 41 of the branch flow path 12b
- the flow path 24_1A is the inflow flow path 42 of the branch flow path 12b
- the connecting portion 33 connecting the intersecting portion 31 and the upper end portion 32 of the flow passage 23_1A and the flow passage 24_2B are used as the first outflow passage 43 of the branch flow passage 12b
- the intersecting portion 31 and the lower end portion 34 of the flow passage 23_1A are
- the equivalent diameter of at least a part of the first outflow flow path 43 is at least that of the second outflow flow path 44.
- the branch part 41 of the branch flow path 12b separation occurs in the refrigerant flow.
- a bent portion 36 is formed in the connecting portions 33 and 35 of the linear through groove of the branch flow path 12b, and the refrigerant flows at the bent portion 36.
- separation occurs in the flow of the refrigerant. That is, the branch portion 41, the bent portion 36, the upper end portion 32, and the lower end portion 34 correspond to the “curved portion where separation occurs in the flow of the refrigerant” in the present invention.
- the refrigerant flowing out from the end on the side not communicating with the branch unit 41 passes through the passage channel 12c and the branch channel 12b_14 before reaching the outlet channel 11A. Since it passes, the number of times it passes through the curved portion where the refrigerant flows is separated is small.
- the refrigerant flowing out from the end on the side not communicating with the branch unit 41 passes through the branch channel 12b_12 and the branch channel 12b_13 before reaching the outlet channel 11A. In order to pass, there are many frequency
- coolant there are many frequency
- coolant there are many frequency
- coolant there are many frequency
- coolant there are many frequency
- the equivalent diameter of the first outflow passage 43 and the equivalent diameter of the second outflow passage 44 are equal, the pressure loss generated in the refrigerant flowing out of the first outflow passage 43 and the second outflow passage 44.
- the pressure loss generated in the refrigerant flowing out of the refrigerant causes a difference, and the refrigerant distributed to the outlet channel 11A becomes non-uniform.
- the equivalent diameter of at least a part of the first outflow channel 43 is smaller than the equivalent diameter of at least a part of the second outflow channel 44, the refrigerant distributed to the outlet channel 11A is not sufficient. It is suppressed that it becomes uniform.
- the equivalent diameter is calculated by the following formula 1.
- the equivalent diameters and the like of the flow paths 24_2A and 24_2B are set so that the refrigerant flows in the same manner before and after passing through the flow paths 24_2A and 24_2B. If the flow pattern of the refrigerant changes before and after passing through each of the flow paths 24_2A and 24_2B, the pressure loss generated in the refrigerant greatly varies depending on the flow rate. Therefore, when the flow rate of the refrigerant flowing into the distribution flow path 12A varies, the balance of pressure loss in each of the flow paths 24_2A and 24_2B varies, and the refrigerant distributed to the outlet flow path 11A becomes uneven. Will occur.
- each of the flow paths 24_2A and 24_2B is such that the refrigerant flows into the distribution flow path 12A at the maximum flow rate and is evenly distributed to the outlet flow paths 11A. It is good to set to the hole diameter which the flow pattern of a refrigerant
- the equivalent diameters and the like of the flow paths 24_2A and 24_2B are set so that the refrigerant flow forms an annular flow or an annular spray flow. Good. With such a configuration, the flow state of the refrigerant after passing through each of the flow paths 24_2A and 24_2B is homogenized, and the uniformity of branching in the next branch flow path 12b is improved. .
- FIG. 5 is a Baker diagram showing the relationship between the flow state of the refrigerant and the flow mode.
- the flow mode of the refrigerant before and after passing through each of the flow paths 24_2A and 24_2B can be calculated using the Baker diagram shown in FIG.
- the Baker diagram is a characteristic diagram showing the flow mode of the refrigerant in the gas-liquid two-phase state.
- the vertical axis and the horizontal axis are values representing the refrigerant flow state, the vertical axis is Gg / ⁇ , and the horizontal axis is ⁇ ⁇ ⁇ ⁇ Gl / Gg.
- the vertical axis corresponds to the mass flow rate of the refrigerant gas phase.
- the mass flow rate of the gas phase of the refrigerant increases toward the upper side.
- the horizontal axis corresponds to the mass flow ratio between the gas phase and the liquid phase of the refrigerant, that is, the dryness. In FIG. 5, the degree of dryness becomes smaller toward the right side.
- each of the flow paths 24_2A and 24_2B is set so that the refrigerant flows into a flow state satisfying the relationship of the following Expression 2 or Expression 3.
- An equivalent diameter or the like may be set.
- the mass velocity of the refrigerant gas phase is Gg [kg / (m 2 ⁇ h)]
- the mass velocity of the refrigerant liquid phase is G 1 [kg / (m 2 ⁇ h)].
- the density of the gas phase of the refrigerant is ⁇ g [kg / m 3 ]
- the density of the liquid phase of the refrigerant is ⁇ l [kg / m 3 ]
- the density of air is ⁇ a [kg / m 3 ]
- the density of water is ⁇ w [kg / m 3 ]
- the surface tension of the liquid phase of the refrigerant is ⁇ l [N / m]
- the surface tension of water is ⁇ w [N / m]
- the viscosity coefficient of the liquid phase of the refrigerant is ⁇ l [ ⁇ Pa ⁇ s]
- the viscosity coefficient of water is ⁇ w [ ⁇ Pa ⁇ s].
- the flow rate 23_1A is set as the flow rate, the maximum flow rate of the refrigerant flowing into the distribution flow channel 12A, and the equivalent diameter of the flow channel before passing through the flow channels 24_2A and 24_2B.
- the equivalent diameter of the flow paths 24_2A and 24_2B may be used as the equivalent diameter of the flow paths after passing through the flow paths 24_2A and 24_2B.
- the other flow channels constituting the distribution flow channel 12A are similarly configured. It is good to set to the equivalent diameter in which the pressure loss which arises in a refrigerant
- the equivalent diameter of the flow path 24_3B may be smaller than the equivalent diameter of the flow path 24_3A.
- the equivalent diameter of the flow path 23_3B and the flow path 24_4B may be smaller than the equivalent diameter of the flow path 23_3A and the flow path 24_4A.
- branch channels 12b similar to the branch channel 12b_11
- the above-described configuration may be employed for all of them, and the above-described configuration may be employed for a part thereof. .
- the equivalent branch diameter of at least a portion of 43 is smaller than the equivalent diameter of at least a portion of the second outflow passage 44.
- the branch passage 12b is a branch passage 12b upstream of the distribution passage 12A. Good. That is, the first outflow passage 43 and the first outflow passage 43b have a smaller equivalent diameter of at least a portion of the first outflow passage 43 than the equivalent diameter of at least a portion of the second outflow passage 44.
- the refrigerant flowing out from at least one of the two outflow channels 44 may be further branched by the other branch channel 12b.
- the branch channel 12b is such that the branch portion 41 is formed in a linear region that is not parallel to the gravity direction of the channels 23_1A to 23_3A and 23_3B has been described.
- the branch channel 12b may not be used.
- the branch channel 12b is such that the branch part 41 is formed in a linear region that is not parallel to the gravitational direction of the channels 23_1A to 23_3A and 23_3B, the refrigerant branches in the branch part 41 are made uniform. .
- the angle of each branching direction in the branching portion 41 with respect to the direction of gravity is made uniform, and the distribution of the refrigerant becomes nonuniform due to the influence of gravity. Is suppressed.
- the branch flow path 12b has different heights in the gravitational direction at the end portions of the first outflow flow path 43 and the second outflow flow path 44 on the side not communicating with the branching section 41, the effect is obtained. Becomes prominent.
- branch channel 12b is located such that the end of the first outlet channel 43 that does not communicate with the branch unit 41 is located above the branch unit 41 in the gravity direction, and the branch unit of the second outlet channel 44 Although the case where the end portion on the side not communicating with 41 is located below the branch portion 41 in the direction of gravity is described, such a branch channel 12b may not be used.
- the end of the branch flow path 12b that does not communicate with the branch section 41 of the first outflow path 43 is located above the branch section 41 in the gravity direction, and the side that does not communicate with the branch section 41 of the second outflow path 44 If the end of the first outlet channel is located below the branching portion 41 in the direction of gravity, the difference in channel length between the first outlet channel 43 and the second outlet channel 44 can be reduced. Thus, the refrigerant distribution can be made uniform without complicating the flow path shapes of the first outflow path 43 and the second outflow path 44.
- the straight line connecting the branch channel 12 b to the end portion of the first outflow channel 43 that does not communicate with the branch portion 41 and the end portion of the second outflow channel 44 that does not communicate with the branch portion 41 may not be used.
- a straight line connecting the end of the first outflow passage 43 that does not communicate with the branch portion 41 and the end of the second outflow passage 44 that does not communicate with the branch portion 41 is a straight line of the plate-like member. In the case of being parallel to the longitudinal direction, it is possible to reduce the dimension in the short direction of the plate-like member, and the parts cost, weight and the like are reduced.
- a straight line connecting the end of the branch flow path 12b that does not communicate with the branch 41 of the first outflow path 43 and the end of the second outflow path 44 that does not communicate with the branch 41 is a heat transfer tube.
- the heat exchanger 1 is parallel to the arrangement direction of 4, the heat exchanger 1 is saved in space.
- the straight line connecting the end of the first outflow passage 43 that does not communicate with the branch portion 41 and the end of the second outflow passage 44 that does not communicate with the branch portion 41, the longitudinal direction of the plate-like member, and The arrangement direction of the heat transfer tubes 4 may not be parallel to the direction of gravity.
- FIG. 6 is a diagram illustrating a configuration of an air-conditioning apparatus to which the heat exchanger according to Embodiment 1 is applied.
- the air conditioner 91 includes a compressor 92, a four-way valve 93, an outdoor heat exchanger (heat source side heat exchanger) 94, an expansion device 95, and an indoor heat exchanger (load side).
- 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 to form a refrigerant circulation circuit.
- a compressor 92, a four-way valve 93, a throttle device 95, an outdoor fan 97, an indoor fan 98, various sensors, and the like are connected to the control device 99.
- the control device 99 By switching the flow path of the four-way valve 93 by the control device 99, the cooling operation and the heating operation are switched.
- the flow of the refrigerant during the cooling operation will be described.
- the high-pressure and high-temperature gas refrigerant discharged from the compressor 92 flows into the outdoor heat exchanger 94 through the four-way valve 93, exchanges heat with the air supplied by the outdoor fan 97, and condenses.
- the condensed refrigerant enters a high-pressure liquid state, flows out of the outdoor heat exchanger 94, and enters a low-pressure gas-liquid two-phase state by the expansion device 95.
- the low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 96 and evaporates by heat exchange with the air supplied by the indoor fan 98, thereby cooling the room.
- the evaporated refrigerant enters a low-pressure gas state, flows out of the indoor heat exchanger 96, and is sucked into the compressor 92 via the four-way valve 93.
- the flow of the refrigerant during the heating operation will be described.
- the high-pressure and high-temperature gaseous refrigerant discharged from the compressor 92 flows into the indoor heat exchanger 96 through the four-way valve 93 and is condensed by heat exchange with the air supplied by the indoor fan 98. Heat up.
- the condensed refrigerant enters a high-pressure liquid state, flows out of the indoor heat exchanger 96, and becomes a low-pressure gas-liquid two-phase refrigerant by the expansion device 95.
- the low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 94, exchanges heat with the air supplied by the outdoor fan 97, and evaporates.
- the evaporated refrigerant enters a low-pressure gas state, flows out of the outdoor heat exchanger 94, and is sucked into the compressor 92 through the four-way valve 93.
- the heat exchanger 1 is used for at least one of the outdoor heat exchanger 94 and the indoor heat exchanger 96.
- the heat exchanger 1 acts as an evaporator
- the heat exchanger 1 is connected so that the refrigerant flows from the stacked header 2 and flows out to the header 3. That is, when the heat exchanger 1 acts as an evaporator, the gas-liquid two-phase refrigerant flows into the laminated header 2 from the refrigerant pipe. Further, when the heat exchanger 1 acts as a condenser, the refrigerant flows back through the stacked header 2.
- the laminated header 2 has improved distribution uniformity of the refrigerant by the above-described configuration. Therefore, even when a gas-liquid two-phase refrigerant that is relatively difficult to distribute uniformly flows in, the plurality of heat transfer tubes 4 are arranged. It is possible to make the flow rate and the dryness of the refrigerant flowing out of each of them uniform. That is, the laminated header 2 is suitable for a refrigeration cycle apparatus such as the air conditioner 91.
- the branch flow path 12 b has a small number of curved portions where separation of the refrigerant flow occurs in the flow path through which the refrigerant flowing from the inflow flow path 42 reaches the outlet flow path 11 ⁇ / b> A.
- the equivalent diameter of at least a part of the first outflow channel 43 is smaller than the equivalent diameter of at least a part of the second outflow channel 44. Therefore, it is possible to change the number of outlet channels 11A to a number other than a multiple of 2 while suppressing a decrease in the uniformity of refrigerant distribution. Number of degrees of freedom is extended.
- the distribution channel 12A is formed by laminating plate-like plate materials. Therefore, despite the fact that the number of outlet channels 11A can be changed to a number other than a multiple of 2 while suppressing a decrease in the uniformity of refrigerant distribution, Change the equivalent diameter of the path, the shape of each flow path, the number of distributions, the number of branches in the branch portion 41, etc., the hole diameter of each plate member, the groove width of each plate member, the hole or groove of each plate member This can be easily realized by changing the shape, the number of plate members, the thickness of the plate members, and the like.
- FIG. A heat exchanger according to Embodiment 2 will be described. Note that description overlapping or similar to that in Embodiment 1 is appropriately simplified or omitted.
- FIG. 7 is a perspective view of the heat exchanger according to Embodiment 2 in a state where the stacked header is disassembled. As shown in FIG. 7, the flow path 22A formed in the second plate member 22 by joining the second plate member 22, the third plate members 23_1, 23_2, and the cladding materials 24_1 to 24_3.
- the distribution channel 12A includes an inlet channel 12a and branch channels 12b_21 to 12b_23.
- the number and order of the branch flow paths 12b_21 to 12b_23 are appropriately changed according to the number of the heat transfer tubes 4 and the like.
- the branch flow paths 12b_21 to 12b_23 may be collectively referred to as a branch flow path 12b.
- the third plate member 23_1 and the clad members 24_1 and 24_2 are joined to each other, whereby the flow path 24_1A formed in the clad material 24_1, the flow path 23_1A formed in the third plate member 23_1, and the clad material 24_2.
- the two flow paths 24_2A and one flow path 24_2B formed in the above are communicated to form a branch flow path 12b_21.
- the flow path 23_1A is a linear through groove.
- the flow paths 24_2A and 24_2B are circular through holes.
- the third plate-like member 23_2 and the clad members 24_2 and 24_3 are joined to each other so that the flow path 24_2A formed in the clad material 24_2, the flow path 23_2A formed in the third plate-like member 23_2, and the clad material 24_3.
- the two flow paths 24_3A formed in the above are communicated to form a branch flow path 12b_22.
- the flow path 23_2A is a linear through groove.
- the flow path 24_3A is a circular through hole.
- the third plate-like member 23_2 and the clad members 24_2 and 24_3 are joined to each other so that the flow path 24_2B formed in the clad material 24_2, the flow path 23_2B formed in the third plate-like member 23_2, and the clad material 24_3.
- the two flow paths 24_3B formed in the above are communicated to form a branch flow path 12b_23.
- the flow path 23_2B is a linear through groove.
- the flow path 24_3B is a circular through hole.
- the flow paths 23_1A, 23_2A, and 23_2B that are linear through grooves formed in the third plate-like member 23 are clad materials that are stacked on the surface of the third plate-like member 23 on the side into which the refrigerant flows. 24, except for a part between the end portions.
- the third plate-like member 23 is laminated on the end portions of the flow paths 23_1A, 23_2A, 23_2B, which are linear through grooves, and the surface of the third plate-like member 23 on the side where the refrigerant flows out.
- the flow paths 24_2A, 24_3A, and 24_3B, which are circular through holes, formed in the clad material 24 are formed at positions facing each other.
- the flow path 24_1A which is a circular through hole, formed in the clad material 24_1 laminated on the surface of the third plate member 23_1 on the side where the refrigerant flows, and the refrigerant of the third plate member 23_1 flow out.
- the channel 24_2B which is a circular through hole, formed in the clad material 24_2 laminated on the surface on the side to be formed is formed at a position facing the channel 24_2B. Therefore, the flow paths 23_2A and 23_2B, which are linear through grooves, formed on the third plate-like member 23 other than the third plate-like member 23_1 are surfaces of the third plate-like member 23 on the side where the refrigerant flows out. The portions other than the end portions are closed by the clad material 24 laminated on the substrate.
- the flow path 23_1A which is a linear through groove, formed in the third plate member 23_1 has an end portion by a clad material 24_2 laminated on the surface of the third plate member 23_1 on the side where the refrigerant flows out. A part other than the end and the end are blocked.
- the refrigerant that has passed through the flow path 24_2A flows into a part between the end portions of the flow path 23_2A, and hits the surface of the clad material 24_3 to branch into two to reach both end portions of the flow path 23_2A. Then, it flows into the heat transfer tube 4 through the outlet channel 11A.
- the refrigerant that has passed through the flow path 24_2B flows into a part between the end portions of the flow path 23_2B, and hits the surface of the clad material 24_3 to branch into two to reach both end portions of the flow path 23_2B. Then, it flows into the heat transfer tube 4 through the outlet channel 11A.
- FIG. 8 is a perspective view of the main part of the distribution channel in a state where the stacked header is disassembled in the heat exchanger according to the second embodiment.
- FIG. 9 is a drawing in which each flow path of the branch flow path is drawn by overlapping the heat exchanger according to the second embodiment.
- a part between the ends of the channel 23_1A and the equivalent diameter of the channel 24_2B facing the channel 24_1A are equal to the channel facing the end of the channel 23_1A. Small compared to the equivalent diameter of 24_2A.
- the intersection 31 that intersects the flow path 24_1A of the flow path 23_1A is the branching section 41 of the branch flow path 12b
- the flow path 24_1A is the inflow flow path 42 of the branch flow path 12b
- the flow path 24_2B is used as the first outflow flow path 43 of the branch flow path 12b
- the connecting portions 33 and 35 that connect the intersection 31 and the upper end 32 or the lower end 34 of the flow path 23_1A and the flow path 24_2A are branched.
- the equivalent diameter of at least a part of the first outflow channel 43 is smaller than the equivalent diameter of at least a part of the second outflow channel 44.
- the refrigerant that has flowed into the branch portion 41 from the inflow channel 42 is likely to flow into the first outflow channel 43 and is difficult to flow into the second outflow channel 44. That is, in the flow path connecting the inflow flow path 42 and the second outflow flow path 44, the branch portion 41 corresponds to the “curved portion where separation occurs in the flow of the refrigerant” in the present invention.
- the refrigerant flows from the inflow channel 42 without being bent at the branch part 41, and the bent portion 36 of the channel 23_1A and the upper end of the channel 23_1A. Since the refrigerant flows into the next branch flow path 12b_23 without passing through the lower end part 34 or the lower end part 34, the refrigerant flowing from the inflow path 42 passes through the curved portion where the refrigerant flow is separated before reaching the outlet flow path 11A. There are few times to do.
- the refrigerant is bent from the inflow channel 42 at the branch part 41 and flows in, and the bent portion 36 of the channel 23_1A and the upper end 32 of the channel 23_1A.
- the equivalent diameter of the first outflow passage 43 and the equivalent diameter of the second outflow passage 44 are equal, the pressure loss generated in the refrigerant passing through the first outflow passage 43 and the second outflow passage 44.
- the pressure loss that occurs in the refrigerant that passes through the refrigerant causes a difference, and the refrigerant that is distributed to the outlet channel 11A becomes non-uniform.
- the equivalent diameter of at least a part of the first outflow channel 43 is smaller than the equivalent diameter of at least a part of the second outflow channel 44, the refrigerant distributed to the outlet channel 11A is not sufficient. It is suppressed that it becomes uniform.
- the other flow channels constituting the distribution flow channel 12A are similarly configured. It is good to set to the equivalent diameter in which the pressure loss which arises in a refrigerant
- coolant is equalized.
- the equivalent diameters of the flow paths 23_2B and 24_3B may be smaller than the equivalent diameters of the flow paths 23_2A and 24_3A.
- branch flow paths 12b similar to the branch flow path 12b_21
- the above-described configuration may be employed for all of them, and the above-described configuration may be employed for a part thereof. .
- the branch flow path 12 b has a small number of curved portions where separation of the refrigerant flow occurs in the flow path through which the refrigerant flowing from the inflow flow path 42 reaches the outlet flow path 11 ⁇ / b> A.
- the equivalent diameter of at least a part of the first outflow channel 43 is smaller than the equivalent diameter of at least a part of the second outflow channel 44. Therefore, it is possible to change the number of outlet channels 11A to a number other than a multiple of 2 while suppressing a decrease in the uniformity of refrigerant distribution. Number of degrees of freedom is extended.
- the distribution flow path 12A has a branch flow path 12b_21 that branches the incoming refrigerant into three branches, that is, branches the incoming refrigerant with a larger number of branches. Therefore, it is possible to reduce the thickness of the multilayer header 2, thereby reducing the size of the multilayer header 2 and reducing the cost. Further, the number of plate-like members constituting the laminated header 2 can be reduced, and the manufacturing cost and the like are reduced.
- FIG.10 and FIG.11 is a perspective view in the state which decomposed
- FIG. 10 the refrigerant that has flowed out from the first outflow channel 43 of the branch channel 12b_21 may flow into the passage channel 12c. That is, the configuration of the heat exchanger according to the first embodiment and the configuration of the heat exchanger according to the second embodiment may be combined. In such a case, the outlet flow path 11A in the stacked header 2 may be combined. The number of degrees of freedom is further expanded.
- the refrigerant that has flowed out from the first outflow channel 43 of the branch channel 12b_21 flows into the branch channel 12b_22 and out of the second outflow channel 44 of the branch channel 12b_21.
- the refrigerated refrigerant may flow into the passage channel 12c.
- the equivalent diameter of at least a part of the first outflow channel 43 is set to at least a part of the second outflow channel 44 in order to make the refrigerant distributed to each outlet channel 11A uniform. It may be larger than the equivalent diameter.
- the first outflow channel 43 corresponds to the “second outflow channel” in the present invention
- the second outflow channel 44 corresponds to the “first outflow channel” in the present invention. .
- Embodiment 1 and Embodiment 2 were demonstrated, this invention is not limited to description of each embodiment. For example, it is possible to combine all or a part of each embodiment, each modification, and the like.
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Abstract
Description
なお、以下では、本発明に係る積層型ヘッダーが、熱交換器に流入する冷媒を分配するものである場合を説明しているが、本発明に係る積層型ヘッダーが、他の機器に流入する冷媒を分配するものであってもよい。また、以下で説明する構成、動作等は、一例にすぎず、本発明に係る積層型ヘッダーは、そのような構成、動作等である場合に限定されない。また、各図において、同一又は類似するものには、同一の符号を付すか、又は、符号を付すことを省略している。また、細かい構造については、適宜図示を簡略化又は省略している。また、重複又は類似する説明については、適宜簡略化又は省略している。
実施の形態1に係る熱交換器について説明する。
<熱交換器の構成>
以下に、実施の形態1に係る熱交換器の構成について説明する。
図1は、実施の形態1に係る熱交換器の、構成を示す図である。
図1に示されるように、熱交換器1は、積層型ヘッダー2と、ヘッダー3と、複数の伝熱管4と、保持部材5と、複数のフィン6と、を有する。
以下に、実施の形態1に係る熱交換器における冷媒の流れについて説明する。
冷媒配管を流れる冷媒は、冷媒流入部2Aを介して積層型ヘッダー2に流入して分配され、複数の冷媒流出部2Bを介して複数の伝熱管4に流出する。冷媒は、複数の伝熱管4において、例えば、ファンによって供給される空気等と熱交換する。複数の伝熱管4を流れる冷媒は、複数の冷媒流入部3Aを介してヘッダー3に流入して合流し、冷媒流出部3Bを介して冷媒配管に流出する。冷媒は、逆流することができる。
以下に、実施の形態1に係る熱交換器の積層型ヘッダーの構成について説明する。
図2は、実施の形態1に係る熱交換器の、積層型ヘッダーを分解した状態での斜視図である。
図2に示されるように、積層型ヘッダー2は、第1板状体11と、第2板状体12と、を備える。第1板状体11は、冷媒の流出側に積層される。第2板状体12は、冷媒の流入側に積層される。
以下に、実施の形態1に係る熱交換器の積層型ヘッダーにおける冷媒の流れについて説明する。
図2に示されるように、入口流路12aを通過した冷媒は、分岐流路12b_11に流入する。分岐流路12b_11において、流路24_1Aを通過した冷媒は、流路23_1Aの端部間の一部に流入し、クラッド材24_2の表面に当たって2つに分岐して、流路23_1Aの両端部に至り、分岐流路12b_12と通過流路12cに流入する。
以下に、実施の形態1に係る熱交換器の積層型ヘッダーの分岐流路及び通過流路の詳細について説明する。
図3は、実施の形態1に係る熱交換器の、積層型ヘッダーを分解した状態での分配流路の要部の斜視図である。図4は、実施の形態1に係る熱交換器の、分岐流路の各流路を重ねて描画した図である。
冷媒の、流路24_2A、24_2Bのそれぞれを通過する前後の流動様式は、図5に示されるBaker線図を用いて算出することができる。なお、Baker線図は、気液二相状態の冷媒の流動様式を示す特性図である。縦軸及び横軸は、それぞれ冷媒の流動状態を表す値であり、縦軸は、Gg/λ、横軸は、λ×φ×Gl/Ggである。縦軸は、冷媒のガス相の質量流量の大きさに相当する。図5中、上側ほど、冷媒のガス相の質量流量が大きくなる。横軸は、冷媒のガス相と液相との質量流量の比、つまり乾き度に相当する。図5中、右側ほど、乾き度が小さくなる。
以下に、実施の形態1に係る熱交換器の使用態様の一例について説明する。
なお、以下では、実施の形態1に係る熱交換器が、空気調和装置に使用される場合を説明しているが、そのような場合に限定されず、例えば、冷媒循環回路を有する他の冷凍サイクル装置に使用されてもよい。また、空気調和装置が、冷房運転と暖房運転とを切り替えるものである場合を説明しているが、そのような場合に限定されず、冷房運転又は暖房運転のみを行うものであってもよい。
図6に示されるように、空気調和装置91は、圧縮機92と、四方弁93と、室外熱交換器(熱源側熱交換器)94と、絞り装置95と、室内熱交換器(負荷側熱交換器)96と、室外ファン(熱源側ファン)97、室内ファン(負荷側ファン)98、制御装置99と、を有する。圧縮機92と四方弁93と室外熱交換器94と絞り装置95と室内熱交換器96とが冷媒配管で接続されて、冷媒循環回路が形成される。
圧縮機92から吐出される高圧高温のガス状態の冷媒は、四方弁93を介して室外熱交換器94に流入し、室外ファン97によって供給される空気と熱交換を行い、凝縮する。凝縮した冷媒は、高圧の液状態となり、室外熱交換器94から流出し、絞り装置95によって、低圧の気液二相状態となる。低圧の気液二相状態の冷媒は、室内熱交換器96に流入し、室内ファン98によって供給される空気との熱交換によって蒸発することで、室内を冷却する。蒸発した冷媒は、低圧のガス状態となり、室内熱交換器96から流出し、四方弁93を介して圧縮機92に吸入される。
圧縮機92から吐出される高圧高温のガス状態の冷媒は、四方弁93を介して室内熱交換器96に流入し、室内ファン98によって供給される空気との熱交換によって凝縮することで、室内を暖房する。凝縮した冷媒は、高圧の液状態となり、室内熱交換器96から流出し、絞り装置95によって、低圧の気液二相状態の冷媒となる。低圧の気液二相状態の冷媒は、室外熱交換器94に流入し、室外ファン97によって供給される空気と熱交換を行い、蒸発する。蒸発した冷媒は、低圧のガス状態となり、室外熱交換器94から流出し、四方弁93を介して圧縮機92に吸入される。
以下に、実施の形態1に係る熱交換器の作用について説明する。
積層型ヘッダー2では、分岐流路12bが、流入流路42から流入する冷媒が出口流路11Aに至るまでに通過する流路において、冷媒の流れに剥離が生じる曲部の数が少ない第1流出流路43と、流入流路42から流入する冷媒が出口流路11Aに至るまでに通過する流路において、冷媒の流れに剥離が生じる曲部の数が多い第2流出流路44と、を有し、第1流出流路43の少なくとも一部の等価直径が、第2流出流路44の少なくとも一部の等価直径と比較して小さい。そのため、冷媒の分配の均一性の低下を抑制しつつ、出口流路11Aの数を2の累乗の倍数以外の数に変更することが可能となって、積層型ヘッダー2における出口流路11Aの数の自由度が拡張される。
実施の形態2に係る熱交換器について説明する。
なお、実施の形態1と重複又は類似する説明は、適宜簡略化又は省略している。
以下に、実施の形態2に係る熱交換器の積層型ヘッダーの構成について説明する。
図7は、実施の形態2に係る熱交換器の、積層型ヘッダーを分解した状態での斜視図である。
図7に示されるように、第2板状部材22と第3板状部材23_1、23_2とクラッド材24_1~24_3とが接合されることによって、第2板状部材22に形成された流路22Aと、第3板状部材23_1、23_2に形成された流路23_1A、23_2A、23_2Bと、クラッド材24_1~24_3に形成された流路24_1A~24_3A、24_2B、24_3Bと、が連通されて、分配流路12Aが形成される。
以下に、実施の形態2に係る熱交換器の積層型ヘッダーにおける冷媒の流れについて説明する。
図7に示されるように、入口流路12aを通過した冷媒は、分岐流路12b_21に流入する。分岐流路12b_21において、流路24_1Aを通過した冷媒は、流路23_1Aの端部間の一部を通過すると共に、流路23_1Aの両端部に至り、2つの分岐流路12b_22と1つの分岐流路12b_23に流入する。
以下に、実施の形態2に係る熱交換器の積層型ヘッダーの分岐流路及び通過流路の詳細について説明する。
図8は、実施の形態2に係る熱交換器の、積層型ヘッダーを分解した状態での分配流路の要部の斜視図である。図9は、実施の形態2に係る熱交換器の、分岐流路の各流路を重ねて描画した図である。
以下に、実施の形態2に係る熱交換器の作用について説明する。
積層型ヘッダー2では、分岐流路12bが、流入流路42から流入する冷媒が出口流路11Aに至るまでに通過する流路において、冷媒の流れに剥離が生じる曲部の数が少ない第1流出流路43と、流入流路42から流入する冷媒が出口流路11Aに至るまでに通過する流路において、冷媒の流れに剥離が生じる曲部の数が多い第2流出流路44と、を有し、第1流出流路43の少なくとも一部の等価直径が、第2流出流路44の少なくとも一部の等価直径と比較して小さい。そのため、冷媒の分配の均一性の低下を抑制しつつ、出口流路11Aの数を2の累乗の倍数以外の数に変更することが可能となって、積層型ヘッダー2における出口流路11Aの数の自由度が拡張される。
図10及び図11は、実施の形態2に係る熱交換器の変形例の、積層型ヘッダーを分解した状態での斜視図である。
図10に示されるように、分岐流路12b_21の第1流出流路43から流出した冷媒が、通過流路12cに流入してもよい。つまり、実施の形態1に係る熱交換器の構成と実施の形態2に係る熱交換器の構成とが組み合わされてもよく、そのような場合には、積層型ヘッダー2における出口流路11Aの数の自由度が更に拡張される。
Claims (10)
- 複数の出口流路が形成された第1板状体と、
前記第1板状体に取り付けられ、入口流路から流入する冷媒を前記複数の出口流路に分配して流出する分配流路の少なくとも一部が形成された第2板状体と、を備え、
前記分配流路は、分岐部と、該分岐部に連通する流入流路と、該分岐部に連通する複数の流出流路と、を有する分岐流路を有し、
前記複数の流出流路は、第1流出流路と、第2流出流路と、を含み、
前記流入流路から流入する冷媒が前記第1流出流路を経由して前記出口流路に至るまでに通過する流路における、冷媒の流れに剥離が生じる曲部の数は、
前記流入流路から流入する冷媒が前記第2流出流路を経由して前記出口流路に至るまでに通過する流路における、前記曲部の数と比較して、少なく、
前記第1流出流路の少なくとも一部の等価直径は、前記第2流出流路の少なくとも一部の等価直径と比較して小さい、積層型ヘッダー。 - 前記分配流路は、前記分岐流路以外の他の分岐流路を有し、
前記第1流出流路及び前記第2流出流路のうちの少なくとも一方から流出する冷媒は、前記他の分岐流路で更に分岐する、請求項1に記載の積層型ヘッダー。 - 前記第1流出流路及び前記第2流出流路のうちのいずれか一方の流出流路の、前記分岐部と連通する側の端部は、前記流入流路の前記分岐部と連通する側の端部と、対向する、請求項1又は2に記載の積層型ヘッダー。
- 複数の出口流路が形成された第1板状体と、
前記第1板状体に取り付けられ、入口流路から流入する冷媒を前記複数の出口流路に分配して流出する分配流路の少なくとも一部が形成された第2板状体と、を備え、
前記分配流路は、分岐部と、該分岐部に連通する流入流路と、該分岐部に連通する複数の流出流路と、を有する分岐流路を有し、
前記複数の流出流路のうちの1つの流出流路の前記分岐部と連通する側の端部は、前記流入流路の前記分岐部と連通する側の端部と、対向する、積層型ヘッダー。 - 前記複数の流出流路のそれぞれの前記分岐部と連通しない側の端部の、重力方向における高さは、互いに異なる、請求項1~4のいずれか一項に記載の積層型ヘッダー。
- 前記複数の流出流路のうちの少なくとも一部を通過する前後において、
冷媒の流動様式は、同一である、請求項1~5のいずれか一項に記載の積層型ヘッダー。 - 請求項1~8のいずれか一項に記載の積層型ヘッダーと、
前記複数の出口流路のそれぞれに接続された複数の伝熱管と、を備えた、熱交換器。 - 請求項9に記載の熱交換器を備え、
前記分配流路は、前記熱交換器が蒸発器として作用する際に、前記複数の出口流路に冷媒を流出する、空気調和装置。
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EP3136039B1 (en) | 2019-11-27 |
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