Distributor, heat exchanger and refrigeration cycle device

Abstract

The utility model relates to the technical field of fluid distribution, and discloses a distributor, a heat exchanger and a refrigeration cycle device. The distributor includes: an inflow plate on which an inflow portion is formed; at least one branch flow path plate in which at least one branch flow path, which has a branch inflow part and a branch outflow part, is formed, said branch flow path causing the refrigerant that has flowed in from the inflow part to branch and flow therethrough; the branch flow path plate closest to the heat exchange tube in the branch flow path plates is a downstream side branch flow path plate; on the downstream side branch flow path plate, the branch flow-out part extends in the third direction different from the first direction, and the connecting position of the branch flow-in part and the branch flow-out part is arranged close to the windward side of the heat exchanger. The heat exchange efficiency of the heat exchanger can be improved.

Description

Technical Field

[0001] The present application relates to the technical field of fluid distribution, and in particular to a distributor, a heat exchanger and a refrigeration cycle device. Background Art

[0002] After condensing, the refrigerant must pass through a throttling device to reduce its pressure before evaporating, forming a gas-liquid two-phase fluid with a certain dryness. Before this two-phase fluid is distributed to the heat exchange tubes, gas-liquid separation may occur, resulting in uneven distribution, which in turn leads to low heat exchange efficiency. Uniformly distributing the refrigerant within the heat exchange tubes to ensure optimal heat transfer is crucial. Utility Model Content

[0003] In one aspect of the present application, a dispenser is provided, comprising:

[0004] an inflow plate having an inflow portion formed thereon;

[0005] at least one branch flow path plate having at least one branch flow path formed thereon for branching the refrigerant flowing from the inlet portion and circulating it to the heat exchange tube, the branch flow path having a branch inlet portion for the refrigerant to flow in, and a plurality of branch outflow portions for the refrigerant to branch out; the one of the branch flow path plates closest to the heat exchange tube being the downstream branch flow path plate;

[0006] Wherein, on the downstream branch flow path plate, the branch outflow portion extends in a direction orthogonal to the first direction, and a connection position between the branch inflow portion and the branch outflow portion is arranged close to the windward side of the heat exchanger.

[0007] In the present application, the branch outflow portion of the downstream branch flow plate extends in a direction orthogonal to the first direction, and the connection position between the branch inflow portion and the branch outflow portion is arranged close to the windward side of the heat exchanger, so that the distance from the branch inflow portion to the windward side portion of the heat exchange tube is shorter than the distance to the leeward side portion of the heat exchange tube. Therefore, the refrigerant in the branch flow inflow portion will first flow to the windward side portion of the heat exchange tube, so that more refrigerant is obtained in the holes in the heat exchange tube close to the windward side. The temperature of the air gradually decreases when it flows from the windward end to the leeward end of the heat exchange tube (when the heat exchanger is an evaporator), and the refrigerant flow rate close to the windward side in the heat exchange tube is larger, which can adapt to the energy of the air in the windward direction, making the heat exchange efficiency of the heat exchanger higher.

[0008] In some embodiments, projected on the plate surface of the downstream branch flow path plate, the heat exchange tube is located in the branch flow outflow portion.

[0009] In one aspect of the present application, a heat exchanger comprises:

[0010] a plurality of heat exchange tubes arranged along a first direction for circulating a refrigerant, wherein the heat exchange tubes are flat tubes; and

[0011] a distributor, for distributing the refrigerant to the plurality of heat exchange tubes;

[0012] Wherein, the distributor comprises:

[0013] an inflow plate having an inflow portion formed thereon;

[0014] at least one branch flow path plate having at least one branch flow path formed thereon for branching and circulating the refrigerant flowing from the inlet portion, the branch flow path having a branch inlet portion for the refrigerant to flow in, and a plurality of branch outflow portions for the refrigerant to branch out, wherein the branch flow path plate closest to the heat exchange tube is a downstream branch flow path plate;

[0015] an outflow plate, on which a plurality of outflow portions are provided, wherein the outflow portions connect the branch outflow portions of the downstream branch flow plate and the heat exchange tubes in opposite directions;

[0016] Wherein, on the downstream branch flow path plate, the branch outflow portion has a branch outflow end for allowing the refrigerant to flow out; the branch outflow end is arranged close to the windward side of the heat exchanger;

[0017] In the present application, the branch outflow end of the downstream branch flow plate is arranged close to the windward side of the heat exchanger, so that the distance from the branch outflow end to the windward part of the heat exchange tube is shorter than the distance to the leeward part of the heat exchange tube. Therefore, the refrigerant at the branch outflow end will first flow to the windward part of the heat exchange tube, so that the holes in the heat exchange tube close to the windward side obtain more refrigerant. The temperature of the air gradually decreases when it flows from the windward end to the leeward end of the heat exchange tube (when the heat exchanger is an evaporator), and the refrigerant flow rate near the windward side in the heat exchange tube is larger, which can adapt to the energy of the air in the windward direction, making the heat exchange efficiency of the heat exchanger higher.

[0018] In some embodiments, on the downstream side branch flow plate, the branch outflow portion extends in a direction orthogonal to the first direction; the distributor also includes: a connecting plate, arranged between the downstream side branch flow plate and the outflow plate, and a plurality of connecting portions are formed on the connecting plate for connecting the branch outflow end and the outflow portion.

[0019] In the present application, since the outflow end of the branch is close to the windward side of the heat exchanger, the connecting portion connected to the outflow end of the branch is close to the windward side, thereby ensuring that the refrigerant first flows to the windward side of the heat exchanger.

[0020] In some embodiments, the branch inlet portion includes a first branch inlet portion and a second branch inlet portion that are spaced apart and arranged in a direction orthogonal to the first direction.

[0021] In the present application, there are two branch inflow parts arranged at intervals, so that the refrigerant is directly divided into two parts at the branch inflow part. There is no need to increase the lateral size of the branch flow path part in order to achieve horizontal diversion, which solves the problem of the branch flow path being large in the lateral size when the branch inflow part is a horizontal straight segment in the prior art. In the present application, the lateral size of the branch flow path is more compact.

[0022] In some embodiments, the length w of the first branch inflow portion and the second branch inflow portion in a direction perpendicular to the first direction is not greater than the length u of the branch outflow portion in a direction perpendicular to its extending direction.

[0023] In the present application, the size of the branch inflow portion is limited so that the lateral sizes of the first branch inflow portion and the second branch inflow portion are relatively small.

[0024] In some embodiments, there are at least two branch flow plates; the distributor also includes: a connecting plate, arranged between the two branch flow plates, and a plurality of connecting parts are formed on the connecting plate to connect the branch outflow part of the upstream branch flow plate with the branch inflow part of the downstream branch flow plate; projected on the plate surface of the connecting plate, the areas of the first branch inflow part and the second branch inflow part on the downstream branch flow plate overlapping with the connecting part are equal.

[0025] In the present application, the overlapping areas of the first branch inflow portion, the second branch inflow portion and the connecting portion are equal, which can ensure uniform flow diversion at the two locations and avoid biased flow of the refrigerant at the branch inflow portions.

[0026] In some embodiments, the branch flow plate includes an upstream branch flow plate located between the downstream branch flow plate and the inflow plate; on the upstream branch flow plate, the branch outflow portion extends in a direction orthogonal to the first direction, and a transition portion is connected between the branch inflow portion and the branch outflow portion, and the transition portion extends along the first direction.

[0027] In some embodiments, the outer end surface P of the branch inlet portion extending along the first direction is coplanar with the transition portion, so that the shape of the branch flow path is relatively regular, which is conducive to processing and manufacturing.

[0028] In other embodiments, a refrigeration cycle device includes the above-mentioned heat exchanger, wherein the heat exchanger serves as at least one of an evaporator and a condenser.

[0029] In this application, the number of heat exchange tubes connected to the distributor increases from top to bottom. The fewer the number of outlets of the distributor, the greater the refrigerant flow in the corresponding heat exchange tube, so that the refrigerant flow on the heat exchanger increases from bottom to top, which matches the distribution trend of increasing wind speed as the height increases on the heat exchanger, thereby optimizing the heat exchange efficiency of the heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 A diagram showing the appearance of a refrigeration cycle device according to some embodiments;

[0031] Figure 2 A diagram illustrating a refrigerant system in a refrigeration cycle device according to some embodiments;

[0032] Figure 3 shows a cross-sectional view of a refrigeration cycle device according to some embodiments;

[0033] Figure 4 A schematic structural diagram of a heat exchanger in a refrigeration cycle device according to some embodiments is shown;

[0034] Figure 5 A side view of a heat exchanger in a refrigeration cycle device according to some embodiments is shown;

[0035] Figure 6 A partial schematic diagram of a microchannel heat exchanger in a refrigeration cycle device according to some embodiments is shown;

[0036] Figure 7 shows a cross-sectional view of a gas header in a heat exchanger according to some embodiments;

[0037] Figure 8 shows a perspective view of a dispenser in an exploded state according to some embodiments;

[0038] Figure 9 shows a diagram of a dispenser in an exploded, flattened state according to some embodiments;

[0039] Figure 10 Schematic diagram of branch flow paths according to some embodiments Figure 1 ;

[0040] Figure 11 A partial front view of a downstream branch flow path and heat exchange tubes of a distributor according to some embodiments is shown;

[0041] Figure 12 Schematic diagram showing branch flow paths according to some embodiments Figure 2 ;

[0042] Figure 13 shows diagrams of dispensers in an exploded and flattened state according to other embodiments;

[0043] Figure 14 shows a schematic diagram of branch flow paths according to other embodiments;

[0044] Figure 15 A partial front view of a downstream branch flow path and heat exchange tubes of a distributor according to some embodiments is shown;

[0045] Figure 16 shows a schematic diagram of branch flow paths according to yet other embodiments;

[0046] Figure 17 shows a top view of a dispenser according to other embodiments;

[0047] Figure 18 A line graph showing the heat exchanger height versus wind speed / refrigerant flow rate is shown;

[0048] Figure 19 Shown is a partial view of a heat exchanger according to some embodiments.

[0049] In the above figures, 100, outdoor unit 111, compressor 112, outdoor heat exchanger 113, four-way valve; 114, outdoor throttling device 115, liquid accumulator 116, outdoor fan 200, indoor unit 211, indoor heat exchanger 212, indoor throttling device 213, indoor fan 300, heat exchanger 310, heat exchange tube; 310a, hole; 320, fin; 330, gas header 331, converging flow path 340, heat exchanger body; 400, distributor; 410, inflow plate; 411, inflow portion; 420, heat exchange tube mounting plate; 421, heat exchange tube insertion portion; 430, branch flow plate; 431, branch flow; 432, branch inflow; 432a, first branch inflow; 432b, second branch inflow; 433, branch outflow; 433a, branch outflow end; 434, partition; 435, transition; 440, downstream branch flow plate; 441, downstream branch flow; 450, upstream branch flow plate; 451, upstream branch flow; 460, connecting plate; 461, connecting portion; 470, outflow plate; 471, outflow; 510, fan; 600, diverter; 610, capillary. DETAILED DESCRIPTION

[0050] In order to make the purpose and implementation of this application clearer, the exemplary implementation of this application will be clearly and completely described below in conjunction with the drawings in the exemplary embodiments of this application. Obviously, the described exemplary embodiments are only part of the embodiments of this application, not all of the embodiments.

[0051] In the description of this application, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application.

[0052] The terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, features specified as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of this application, unless otherwise specified, "plurality" means two or more.

[0053] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0054] <Structure of Refrigeration Cycle Device>

[0055] Reference Figure 1 According to an embodiment of the present application, a refrigeration cycle device includes: an outdoor unit 100, located in an outdoor space, for performing heat exchange between a refrigerant and outdoor air; and an indoor unit 200, located in an indoor space, for performing heat exchange between a refrigerant and indoor air.

[0056] Figure 1 The multi-split system is used as an example for demonstration. In this embodiment, there are multiple indoor units 200. However, the refrigeration cycle device of the present application is also applicable to the case of a single indoor unit 200.

[0057] Reference Figure 2 The outdoor unit 100 includes: a compressor 111 for compressing the refrigerant; an outdoor heat exchanger 112 for performing heat exchange between the outdoor air and the refrigerant; a four-way valve 113 for selectively guiding the refrigerant compressed by the compressor 111 to the outdoor heat exchanger 112 or the indoor unit 200 according to the heating mode or the cooling mode; an outdoor throttling device 114 for decompressing the refrigerant guided to the outdoor heat exchanger 112 in the heating mode; and a liquid accumulator 115 for preventing the unevaporated liquid refrigerant from flowing to the compressor 111.

[0058] The compressor 111 compresses low-pressure gaseous refrigerant to high pressure using the rotational force of a compressor motor (not shown) when energized.

[0059] The four-way valve 113 guides the refrigerant compressed in the compressor 111 to the outdoor heat exchanger 112 in the cooling mode, and guides the refrigerant compressed in the compressor 111 to the indoor unit 200 in the heating mode.

[0060] The outdoor heat exchanger 112 condenses the refrigerant compressed by the compressor 111 in a cooling mode, and evaporates the refrigerant decompressed by the indoor unit 200 in a heating mode.

[0061] The outdoor fan 116 blows outdoor air to the outdoor heat exchanger 112 .

[0062] The outdoor throttling device 114 reduces the refrigerant pressure by throttling the refrigerant. As the refrigerant passes through a narrow passage, the refrigerant pressure decreases without exchanging heat with the outside. Specifically, the outdoor throttling device 114 may be an expansion valve or a capillary tube.

[0063] The indoor unit 200 includes an indoor heat exchanger 211 for performing heat exchange between a refrigerant and indoor air, and an indoor throttle device 212 for decompressing the refrigerant supplied to the indoor heat exchanger 211 in a cooling mode.

[0064] The indoor heat exchanger 211 evaporates gas-liquid two-phase refrigerant in a cooling mode, and condenses high-pressure gas refrigerant in a heating mode.

[0065] Hereinafter, the flow of refrigerant in the refrigeration cycle device in the cooling mode or the heating mode will be described.

[0066] When the refrigeration cycle device operates in a cooling mode, the refrigerant is compressed to a high pressure by the compressor 111 of the outdoor unit 100. As the refrigerant is compressed, the pressure and temperature of the refrigerant increase.

[0067] The compressed refrigerant is guided to the outdoor heat exchanger 112 through the four-way valve 113. The refrigerant is condensed in the outdoor heat exchanger 112, and heat exchange is performed between the refrigerant and the outdoor air while the refrigerant is condensed. Specifically, the state of the refrigerant changes from gas to liquid.

[0068] After passing through the outdoor throttle device 124 , the condensed refrigerant is supplied to the indoor unit 200 .

[0069] The refrigerant supplied to the indoor unit 200 is decompressed by the indoor throttling device 212, and the refrigerant is converted into a two-phase refrigerant with low temperature, low pressure and a certain dryness.

[0070] The decompressed refrigerant is evaporated by the indoor heat exchanger 222, and heat exchange between the refrigerant and the indoor air is performed while the refrigerant is evaporated. Specifically, the state of the refrigerant changes to a gaseous state.

[0071] After passing through the indoor heat exchanger 222, the evaporated gaseous refrigerant is supplied to the outdoor unit 100 and is supplied to the accumulator 115 via the four-way valve 113. In the accumulator 115, the refrigerant is separated into non-evaporated liquid refrigerant and evaporated gaseous refrigerant, and the gaseous refrigerant is again supplied to the compressor 111, completing one refrigerant cycle.

[0072] As described above, in the cooling mode, the refrigeration cycle device may cool the indoor air using heat exchange between the refrigerant generated in the indoor heat exchanger 211 and the indoor air.

[0073] When the refrigeration cycle device operates in a heating mode, the refrigerant is compressed to a high pressure by the compressor 111 of the outdoor unit 100 , and the temperature of the refrigerant increases with the pressure of the refrigerant.

[0074] After passing through the four-way valve 113 , the compressed refrigerant is guided to the indoor unit 200 .

[0075] The refrigerant is condensed by the indoor heat exchanger 211, and heat is exchanged between the refrigerant and the indoor air while the refrigerant is condensed. Specifically, the state of the refrigerant changes from a gaseous state to a liquid state.

[0076] After passing through the indoor heat exchanger 211 , the condensed refrigerant is supplied to the outdoor unit 100 again.

[0077] The refrigerant supplied to the outdoor unit 100 is decompressed by the outdoor throttling device 114, and at the same time, the refrigerant becomes a two-phase state with low temperature, low pressure and a certain dryness.

[0078] The decompressed refrigerant is evaporated by the outdoor heat exchanger 112, and heat is exchanged between the refrigerant and the outdoor air while the refrigerant is evaporated. Specifically, the state of the refrigerant changes to a gaseous state.

[0079] The gaseous refrigerant evaporated by the outdoor heat exchanger 112 is supplied to the accumulator 115 via the four-way valve 113. In the accumulator 115, the refrigerant is separated into non-evaporated liquid refrigerant and evaporated gaseous refrigerant, and the gaseous refrigerant is supplied to the compressor 111 again, completing one refrigerant cycle.

[0080] As described above, in the heating mode, the refrigeration cycle device may heat the indoor air using heat exchange between the refrigerant and the indoor air generated in the indoor heat exchanger 211 .

[0081] In this application, the outdoor heat exchanger 112 and the indoor heat exchanger 211 are collectively referred to as the heat exchanger 300. The outdoor fan 116 and the indoor fan 213 are collectively referred to as the fan 510. The outdoor throttling device 114 and the indoor throttling device 212 are collectively referred to as the throttling device.

[0082] Figure 3 The demonstration is conducted by taking a top-outlet outdoor unit as an example, that is, the fan 510 is located above the heat exchanger 300 . Figure 3 The middle arrow indicates the direction of air flow. When the fan 510 is running, air enters the outdoor unit from the lower side, exchanges heat with the heat exchanger 300, and then flows out from the top of the outdoor unit.

[0083] Extending from the end of the heat exchanger 300 are a plurality of heat exchange tubes 310 (to be described later) arranged from top to bottom, serving as a refrigerant inlet and a refrigerant outlet.

[0084] When the heat exchanger 300 is used as an evaporator, the refrigerant entering the evaporator is two-phase refrigerant throttled by the throttling device. When the two-phase refrigerant is in a large space or the flow rate is reduced, phase separation will occur, which will lead to uneven distribution. Figure 3 The outdoor unit shown, Figure 3 The middle heat exchanger 300 is large and high, and the number of heat exchange tubes 310 in the vertical direction is very large. Therefore, this type of refrigeration cycle device is more prone to uneven distribution problems.

[0085] Hereinafter, the present application will be described in detail in conjunction with the structure of the heat exchanger 300 .

[0086] <Structure of Heat Exchanger 300>

[0087] Reference Figures 4 to 7 The heat exchanger 300 includes a heat exchanger body 340 . The heat exchanger body 340 has a plurality of heat exchange tubes 310 and fins 320 .

[0088] The heat exchange tube 310 has the refrigerant flowing thereon, and the fin 320 is connected to the heat exchange tube 310 to increase the surface area of the heat exchange tube 310 to improve the heat exchange efficiency between the refrigerant and the air.

[0089] The heat exchange tube 310 may be a flat tube or a round tube.

[0090] When the heat exchange tube 310 is a circular tube, the heat exchanger 300 is a through-fin heat exchanger. When viewed from the side of the heat exchanger 300 , the heat exchange tube 300 extends in an "S" shape from top to bottom. The heat exchange tube 310 is passed through the fin 320 .

[0091] When the heat exchange tubes 310 are flat tubes, the heat exchanger 300 is a microchannel heat exchanger. The plurality of flat tubes are arranged at intervals in the first direction (the vertical direction Z). Fins 320 are connected between the flat tubes.

[0092] The following description will be made using a microchannel heat exchanger as an example: the heat exchange tubes 310 may be made of aluminum, and the fins 320 may be made of aluminum. The heat exchange tubes 310 and the fins 320 are connected by welding.

[0093] Heat exchange tube 310 is a porous tube having a plurality of holes 310a that form a refrigerant flow path. The refrigerant exchanges heat with the air as it flows through each hole 310a of heat exchange tube 310. The holes 310a are arranged within heat exchange tube 310 along the direction of air flow relative to heat exchanger body 340.

[0094] At both transverse ends of the heat exchanger body 340 , a plurality of heat exchange tubes 310 extend relative to the fins 320 for connection to a refrigerant system.

[0095] The heat exchanger 300 includes a pair of headers connected to both ends of the heat exchanger body 340 , and the headers are respectively connected to the extended heat exchange tubes 310 .

[0096] One header is a distributor 400 through which gas-liquid two-phase refrigerant flows. The other header is a gas header 330 through which gas refrigerant flows. A flow splitter 600 having a plurality of capillary tubes 610 is connected to the distributor 400.

[0097] The refrigerant needs to be divided and flowed into the plurality of heat exchange tubes 310 of the heat exchanger 300. If the refrigerant entering the heat exchange tubes 310 is unevenly distributed, the heat exchange efficiency of the heat exchanger 300 will be affected.

[0098] The distributor 400 is connected to the heat exchange tubes 310 to ensure that the refrigerant distributed to each heat exchange tube 310 of the heat exchanger 300 is substantially consistent, so as to maximize the effectiveness of the heat exchanger 300.

[0099] When heat exchanger 300 functions as a condenser, because the refrigerant entering the condenser is superheated gas compressed by compressor 111, refrigerant is generally evenly distributed at the condenser inlet. Specifically, when the end of heat exchanger 300 connected to four-way valve 113 serves as the inlet, uneven distribution generally does not occur. Therefore, a conventional gas manifold 330 can be installed at this end of heat exchanger 300, with distributor 400 installed only at the end of heat exchanger 300 connected to throttling device 520. In other embodiments, gas manifold 330 can also adopt a distributor structure.

[0100] The distributor 400 is provided with a refrigerant inlet as a refrigerant inflow portion and a plurality of refrigerant outflow portions as refrigerant outflow portions.

[0101] Specific reference Figure 6 and Figure 7 The gas manifold 330 can be in the shape of a closed cylinder or a rectangular cylinder. The cavity within the gas manifold 330 forms a converging flow path 331. Multiple heat exchange tubes 310 are connected to the inflow side of the converging flow path 331. A refrigerant pipe is connected to the outflow side of the converging flow path 331.

[0102] The gas header 330 is provided with multiple refrigerant inlets and one or more refrigerant outlets. Refrigerant piping of the refrigerant system is connected to the refrigerant inlets of the distributor 400 and the refrigerant outlets of the gas header 330. Heat exchange tubes 310 are also connected to the refrigerant outlets of the distributor 400 and the refrigerant inlet of the gas header 330.

[0103] When the heat exchanger 300 functions as an evaporator, the refrigerant flows into the distributor 400 through the refrigerant inlet, where it is divided and then flows out through the multiple refrigerant outlets to the multiple heat exchange tubes 310. The refrigerant exchanges heat with the air driven by the fan 510 in the multiple heat exchange tubes 310. The refrigerant flowing through the multiple heat exchange tubes 310 flows into the gas header 330 through the multiple refrigerant inlets, where it merges and then flows out through the refrigerant outlets to the refrigerant piping.

[0104] When the heat exchanger 300 functions as a condenser, the refrigerant flows in a direction opposite to this flow.

[0105] <Structure of Distributor 400>

[0106] Hereinafter, the structure of the dispenser 400 will be described in detail.

[0107] First, the dispenser 400 is taken as a laminated dispenser as an example for description.

[0108] Reference Figure 8 、 Figure 9 The dispenser 400 is formed by stacking multiple layers of plates. In this application, the longitudinal direction of the plates is referred to as the first direction Z, the direction of the plates stacked perpendicular to the first direction is referred to as the second direction X, and the direction perpendicular to the first and second directions Z and X is referred to as the third direction Y. The dispenser 400 of this embodiment is arranged in the vertical direction of the first direction Z, in the front-to-back direction of the second direction X, and in the left-to-right direction of the third direction Y. Therefore, in the following description, the first direction Z can be converted to the vertical direction, the second direction X can be converted to the front-to-back direction, and the third direction Y can be converted to the left-to-right direction.

[0109] The multi-layer board body includes an inflow board 410. The inflow board 410 is a rectangular board that is long in the up-down direction Z. In the inflow board 410, the board surface is arranged along the up-down direction Z and the left-right direction Y.

[0110] The inlet plate 410 is provided with a through hole extending in the front-rear direction X to form an inlet flow path 411 . The inlet flow path 411 corresponds to a refrigerant inflow portion of the distributor 400 .

[0111] The inflow plate 410 may include one or a plurality of inflow plates 410 arranged in a stacked manner.

[0112] The inlet flow path 411 has a circular cross-section and can be connected to the capillary tube 610 (or refrigerant piping). The inlet flow path 411 can be directly connected to the capillary tube 610 (or refrigerant piping) by welding; alternatively, a pipe joint can be connected to the inlet flow path 411, connecting it to the capillary tube 610 via the pipe joint. The flow path cross-section here refers to the cross-section obtained by cutting the flow path perpendicular to the refrigerant flow direction. The refrigerant flow direction refers to the direction of refrigerant flow within the inlet flow path 411.

[0113] <Heat exchange tube mounting plate 420>

[0114] Reference Figure 8 and Figure 9 The multi-layer plate body includes a heat exchange tube mounting plate 420. The heat exchange tube mounting plate 420 is a rectangular plate that is elongated in the vertical direction Z. The length of the heat exchange tube mounting plate 420 in the vertical direction Z and the length of the left-right direction Y are approximately the same as those of the inflow plate 410 in the vertical direction Z and the left-right direction Y. The plate surface is arranged along the vertical direction Z and the left-right direction Y.

[0115] The heat exchange tube mounting plate 420 is provided with a plurality of through grooves to form a plurality of heat exchange tube insertion portions 421 .

[0116] The heat exchange tube 310 may be installed to the heat exchange tube mounting plate 420 from the heat exchange tube insertion portion 421. The heat exchange tube 310 may be connected to the heat exchange tube mounting plate 420 by welding.

[0117] The heat exchange tube 310 communicates with a branch flow path 431 of a branch flow path plate 430 to be described later.

[0118] In other embodiments, the heat exchange tube mounting plate 420 may be omitted, that is, the distributor 400 does not include the heat exchange tube mounting plate 420 , and the heat exchange tube 310 is directly connected to the branch flow path plate 430 or the outflow plate 470 described later.

[0119] <Branch Flow Path Plate 430>

[0120] The multilayer plate body includes a branching flow path plate 430. The branching flow path plate 430 is a rectangular plate that is long in the vertical direction Z. The vertical length Z and the horizontal length Y of the branching flow path plate 430 are approximately the same as the vertical length Z and the horizontal length Y of the inlet plate 410, and the plate surface is arranged along the vertical direction Z and the horizontal direction Y.

[0121] The branch flow channel plate 430 is provided with at least one through groove penetrating in the front-to-back direction X. The through groove forms a branch flow channel 431 .

[0122] There may be at least one branching flow path plate 430 , and the one closest to the heat exchange tube 310 among the branching flow path plates 430 is a downstream-side branching flow path plate 440 .

[0123] If there is only one branching flow path plate 430 , then this branching flow path plate 430 is the downstream branching flow path plate 440 . If there are multiple branching flow path plates 430 , then the branching flow path plate located between the inlet plate 410 and the downstream branching flow path plate 440 is the upstream branching flow path plate 450 .

[0124] For easy distinction, the branched flow paths of the downstream branched flow path plate 440 are also referred to as downstream branched flow paths 441 . The branched flow paths of the upstream branched flow path plate 450 are also referred to as upstream branched flow paths 451 .

[0125] Reference Figure 10 、 Figure 14 and Figure 16 The branch flow path 431 has a branch inlet 432 and at least two branch outlets 433. The branch outlets 433 of the branch flow path 431 are connected to the heat exchange pipe 310. The two branch outlets 433 are connected to both sides of the branch inlet 432 in the vertical direction Z.

[0126] For the convenience of description in this application, the side of the distributor 400 on the same side as the windward side of the heat exchanger 300 is also referred to as the windward side of the distributor 400 .

[0127] In some embodiments, reference Figure 11 , the arrows in the figure indicate the air flow direction, and the branch outflow portion 433 of the downstream branch flow path 441 extends roughly along the left-right direction Y.

[0128] The connection between the branch inlet 432 and the branch outlet 433 of the downstream branch flow path 441 is located near the windward side of the distributor 400. This allows the refrigerant to flow first toward the windward-facing holes 310a of the heat exchange tube 310. Consequently, a greater amount of refrigerant flow is received by the windward-facing holes 310a in the heat exchange tube 310.

[0129] Due to the heat exchange between the air and the refrigerant in the heat exchange tube 310, the air temperature gradually decreases as it flows from the windward end of the heat exchange tube 310 to the leeward end (when the heat exchanger is an evaporator). The refrigerant flow rate near the windward side of the heat exchange tube 310 is higher, which can adapt to the energy of the windward air, thereby improving the heat exchange efficiency of the heat exchanger 300.

[0130] According to an embodiment of the present application, the shape of the branch outflow portion 433 may be the same as that of the heat exchange tube 310 .

[0131] Reference Figure 12 The branched inflow portion 432 includes a first branched inflow portion 432a and a second branched inflow portion 432b separated by a partition portion 434. The first branched inflow portion 432a and the second branched inflow portion 432b are arranged along the left-right direction Y.

[0132] The length w of the first branch inlet 432a in the left-right direction is not greater than the length u of the branch outlet 433 in the vertical direction Z. Since the length w of the first branch inlet 432a in the left-right direction Y is relatively small, the refrigerant flows along the vertical direction Z to the branch outlet 433 after entering the first branch inlet 432a.

[0133] The length w of the second branch inlet 432b in the left-right direction is not greater than the length u of the branch outlet 433 in the vertical direction Z. Since the length w of the second branch inlet 432b in the left-right direction Y is relatively small, the refrigerant flows along the vertical direction Z to the branch outlet 433 after entering the first branch inlet 432a.

[0134] In some embodiments, reference Figure 13 and Figure 14 The free end of the branch outflow portion 433 is the branch outflow end 433a. The refrigerant flows along the branch outflow portion 433 to the branch outflow end 433a, and then flows from the branch outflow end 433a to the next plate.

[0135] Reference Figure 15 The arrows in the figure indicate the direction of air flow. The branch outlet end 433a is positioned near the windward side of the distributor 400 in the left-right direction Y. Thus, the refrigerant flows from the cooling outlet end 433a first into the holes 310a of the heat exchange tube 310, which are located near the windward side. Consequently, a larger amount of refrigerant flows into the holes 310a of the heat exchange tube 310, which are located near the windward side.

[0136] Due to the heat exchange between the air and the refrigerant in the heat exchange tube 310, the air temperature gradually decreases as it flows from the windward end of the heat exchange tube 310 to the leeward end (when the heat exchanger is an evaporator). The refrigerant flow rate near the windward side of the heat exchange tube 310 is higher, which can adapt to the energy of the windward air, thereby improving the heat exchange efficiency of the heat exchanger 300.

[0137] In this embodiment, the plurality of plates may include a connecting plate 460 .

[0138] <Connecting plate 460>

[0139] Reference Figure 13 The multi-layer plate body includes a connecting plate 460. The connecting plate 460 is a rectangular plate that is long in the vertical direction Z. The connecting plate 460 has a length in the vertical direction Z and a length in the horizontal direction Y that is approximately the same as the length of the inflow plate 410 in the vertical direction Z and the horizontal direction Y. The plate surface is arranged along the vertical direction Z and the horizontal direction Y.

[0140] The connecting plate 460 is provided with a plurality of through holes penetrating in the front-to-back direction X to form a plurality of connecting portions 461 .

[0141] The connecting plate 460 can be disposed between the downstream branching flow channel plate 440 and the outlet plate 470 (described later). The connecting portion 461 is connected to the branch outlet end 433a of the downstream branching flow channel plate 440. The connecting portion 461 is connected to the outlet portion 471 of the outlet plate 470. Thus, the connecting portion 461 connects the branch outlet end 433a of the downstream branching flow channel plate 440 with the outlet portion 471 of the outlet plate 470.

[0142] Reference Figure 8 、 Figure 9 、 Figure 13 When there are multiple branch flow path plates 430 , the communication plate 460 may be disposed between two adjacent branch flow path plates 430 . The communication portion 461 connects the branch flow outflow portion 433 of the preceding branch flow path plate 430 with the branch flow inflow portion 432 of the following branch flow path plate 430 .

[0143] The shape of the flow path cross section of the communication portion 461 may be the same as that of the branch outflow end 402 a .

[0144] It should be noted that the flow path cross section herein refers to a cross section obtained by cutting the flow path perpendicular to the flow direction of the refrigerant. The flow direction of the refrigerant refers to the direction in which the refrigerant flows in the communicating portion 461 .

[0145] For the branch flow path plate 430 closest to the inflow plate 410, when projected on a plane perpendicular to the front-to-back direction X, the first branch inflow portion 401a and the second branch inflow portion 401b of the branch inflow portion 401 have the same overlapping area with the inflow portion 411 of the inflow plate 410.

[0146] For the branch flow path plate 430 excluding the one closest to the inflow plate 410 , when projected on a plane perpendicular to the front-to-back direction X, the first branch inflow portion 401a and the second branch inflow portion 401b of the branch inflow portion 401 have the same overlapping area with the connecting portion 461 of the connecting plate 460 .

[0147] The partition 434 at the branch inlet 432 allows the first branch inlet 432 a and the second branch inlet 432 b to be arranged in a horizontal direction, thereby preventing flow deviation caused by gas-liquid stratification in the capillary 610 .

[0148] Reference Figure 12For the downstream branch flow path 441, the length h of the branch inlet portion 432 in the vertical direction Z is approximately the same as the length of the connecting portion 461. Because the length h of the branch inlet portion 432 in the vertical direction Z is relatively short, the refrigerant flows directly to the branch outlet portion 433 after entering the branch inlet portion 432. Furthermore, because the length h of the branch inlet portion 432 in the vertical direction Z is relatively short, the distance between the two branch outlet portions 433 can be relatively close, allowing a greater number of heat exchange tubes 310 to be arranged in the vertical direction Z, thereby improving heat exchange efficiency.

[0149] <Outflow board 470>

[0150] Continue to refer to Figure 8 、 Figure 9 、 Figure 13 The multi-layer plate body includes an outflow plate 470. The outflow plate 470 is a rectangular plate that is long in the vertical direction Z. The outflow plate 470 has a length in the vertical direction Z and a length in the horizontal direction Y that is substantially the same as the lengths in the vertical direction Z and the horizontal direction Y of the inflow plate 410. The plate surface is arranged along the vertical direction Z and the horizontal direction Y.

[0151] The outflow plate 470 is provided with a plurality of through grooves extending therethrough, forming an outflow portion 471 .

[0152] The outflow plate 470 is located on the upstream side of the heat exchanger mounting plate 420 , and the outflow portion 471 is in communication with the heat exchange tubes 310 on the heat exchange tube mounting plate 460 .

[0153] The flow path cross-sectional shape of the outflow portion 471 may be the same as the shape of the heat exchange tube 310 .

[0154] It should be noted that the flow path cross section herein refers to a cross section obtained by cutting the flow path perpendicular to the flow direction of the refrigerant. The flow direction of the refrigerant refers to the direction in which the refrigerant flows in the outflow portion 471 .

[0155] In some embodiments, reference Figure 16 The branch outflow portion 433a of the upstream branch flow path 451 extends substantially in the left-right direction Y. The upstream branch flow path 451 includes a transition portion 435 connecting the branch inflow portion 432 and the branch outflow portion 433a. The transition portion 435 extends substantially in the up-down direction Z.

[0156] In the upstream branch flow path 451, the outer side surface P of the branch inlet portion 432 in the left-right direction Y is coplanar with the outer side surface of the transition portion 435. The shape of the branch flow path 451 is relatively regular, which is convenient for processing and manufacturing.

[0157] In the above embodiment, the dispenser 400 is in the shape of a rectangular parallelepiped. However, in other embodiments, referring to Figure 17The outer shape of the distributor 400 can also be made into a cylindrical shape. The outer side surface of each plate in the plate body is a cylindrical arc surface.

[0158] Therefore, the present application does not limit the appearance of the dispenser.

[0159] Next, the dispenser 400 is taken as an example of an integrated structure.

[0160] In this embodiment, the distributor 400 is made using a mold. A first mold with the same shape as the distribution flow path is placed into a second mold with the same shape as the distributor 400. Molten aluminum is then poured into the second mold. After the aluminum solidifies, the first mold is melted and discharged.

[0161] In this embodiment, the distributor 400 is an integrated structure, which is the same as the above embodiment except that the distributor 400 is formed by stacking a plurality of plates.

[0162] For top-out refrigeration cycle devices, refer to Figure 3 and Figure 18 The fan 510 is located above the heat exchanger 300 , which causes the wind speed at the upper part of the heat exchanger 300 closer to the fan 510 to be higher than the wind speed at the lower part farther from the fan 510 .

[0163] As the height of the heat exchanger 300 increases, the wind speed on the heat exchanger 300 also tends to increase. Only when the refrigerant flow rate on the heat exchanger 300 matches the wind speed distribution can the heat exchange efficiency of the heat exchanger 300 be optimized.

[0164] In the examples of this application, refer to Figure 19 In the heat exchanger 300 , the distributor 400 includes at least one first distributor 400_1 , at least one second distributor 400_2 , …, and at least one Nth distributor 400n , which are distributed from top to bottom.

[0165] The number of heat exchange pipes 310 connected to the first distributor 400_1 , the second distributor 400_2 , . . . , and the Nth distributor 400_n increases in sequence.

[0166] Illustratively, the first distributor 400_1 is a four-outlet distributor connected to four heat exchange tubes 310 , the second distributor 400_2 is an eight-outlet distributor connected to eight heat exchange tubes 310 , and the Nth distributor 400_n is a sixteen-outlet distributor connected to sixteen heat exchange tubes 310 .

[0167] From top to bottom, the number of heat exchange tubes 310 connected to the distributor 400 increases, which can make the refrigerant flow rate of each capillary tube 610 at the first diversion point of the diverter 600 close, the refrigerant dryness at the heat exchanger outlet close, and the heat exchange efficiency of the heat exchanger optimal.

[0168] As described above, according to the embodiment of the present application, the distributor 400 includes an inflow plate 410, on which an inflow portion 411 is formed; at least one branch flow path plate 430, on which at least one branch flow path 431 is formed for branching and circulating the refrigerant flowing from the inflow portion 411, the one closest to the heat exchange tube 310 among the branch flow path plates 430 is the downstream side branch flow path plate 440, and the branch flow path on the downstream side branch flow path plate 440 is the downstream side branch flow path 441; wherein, the branch outflow portion of the downstream side branch flow path 441 is 433 extends in a direction different from the first direction, and the connection position of the branch inlet portion 432 and the branch outflow portion 433 is arranged close to the windward side of the heat exchanger 300, so that more refrigerant can be obtained in the hole 310a close to the windward side in the heat exchange tube 310. The temperature of the air gradually decreases when it flows from the windward end to the leeward end of the heat exchange tube 310 (when the heat exchanger is an evaporator), and the refrigerant flow rate close to the windward side in the heat exchange tube 310 is larger, which can adapt to the energy of the air in the windward direction, making the heat exchange efficiency of the heat exchanger 300 higher.

[0169] In addition, according to an embodiment of the present application, the distributor 400 includes an inlet plate 410, on which an inlet portion 411 is formed; at least one branch flow path plate 430, on which at least one branch flow path 431 is formed for branching and circulating the refrigerant flowing in from the inlet portion 411, the one of the branch flow path plates 430 closest to the heat exchange tube 310 is the downstream side branch flow path plate 440, and the branch flow path on the downstream side branch flow path plate 440 is the downstream side branch flow path 441; the downstream side branch flow path 441 has a branch outflow portion 433, and the downstream side branch flow path 441 allows the refrigerant to flow out from the branch outflow end 433a of the branch outflow portion 433; the branch outflow end 433a is arranged close to the windward side of the distributor 400, so that more refrigerant can be obtained in the hole 310a close to the windward side in the heat exchange tube 310. The temperature of the air gradually decreases when it flows from the windward end to the leeward end of the heat exchange tube 310 (when the heat exchanger is an evaporator), and the refrigerant flow rate near the windward side of the heat exchange tube 310 is larger, which can adapt to the energy of the air in the windward direction, making the heat exchange efficiency of the heat exchanger 300 higher.

[0170] In some embodiments, the refrigeration cycle device may be a water heater, a refrigerator, an air conditioner, a refrigerator, etc. In any case, the performance of the heat exchanger can be maximized and the heat exchange efficiency can be improved.

[0171] For ease of explanation, the above description has been presented in conjunction with specific embodiments. However, the above exemplary discussion is not intended to be exhaustive or to limit the embodiments to the specific forms disclosed above. Based on the above teachings, various modifications and variations are possible. The above embodiments have been selected and described to better explain the principles and practical applications, thereby enabling those skilled in the art to better utilize the embodiments and various different variations of the embodiments suitable for specific use considerations.

Claims

1. A dispenser, characterized in that: include: an inflow plate having an inflow portion formed thereon; at least one branch flow path plate having at least one branch flow path formed thereon for branching the refrigerant flowing from the inlet portion and circulating it to the heat exchange tube, the branch flow path having a branch inlet portion for the refrigerant to flow in, and a plurality of branch outflow portions for the refrigerant to branch out; the one of the branch flow path plates closest to the heat exchange tube being the downstream branch flow path plate; Wherein, on the downstream branch flow path plate, the branch outflow portion extends in a direction orthogonal to the first direction, and a connection position between the branch inflow portion and the branch outflow portion is arranged close to the windward side of the heat exchanger.

2. The dispenser according to claim 1, characterized in that Projected on the plate surface of the downstream side branch flow path plate, the heat exchange tube is located in the branch flow outflow portion.

3. The dispenser according to claim 2, characterized in that On the downstream branch flow path plate, the branch flow outflow portion extends in a direction perpendicular to the first direction, and the branch flow outflow portion has a branch flow outflow end for allowing the refrigerant to flow out; The dispenser further comprises: The connecting plate is arranged between the downstream branch flow path plate and the outflow plate, and the outflow plate is provided with a plurality of outflow parts. The connecting plate is formed with a plurality of connecting parts for connecting the branch outflow end and the outflow part.

4. The dispenser according to any one of claims 1 to 3, characterized in that The branch inlet portion includes a first branch inlet portion and a second branch inlet portion that are spaced apart and arranged in a direction perpendicular to the first direction.

5. The dispenser according to claim 4, characterized in that The lengths w of the first branch inflow portion and the second branch inflow portion in a direction perpendicular to the first direction are not greater than the length u of the branch outflow portion in a direction perpendicular to its extending direction.

6. The dispenser according to claim 4, characterized in that The branch flow path plates have at least two; The dispenser further comprises: a connecting plate provided between the two branch flow path plates, wherein a plurality of connecting portions are formed on the connecting plate so as to connect the branch flow outflow portion of the upstream branch flow path plate with the branch flow inflow portion of the downstream branch flow path plate; Projected onto the plate surface of the communicating plate, the areas of the first branch inflow portion and the second branch inflow portion on the downstream branch flow path plate that overlap with the communicating portion are equal.

7. The dispenser according to any one of claims 1 to 3, characterized in that: The branch flow path plate includes an upstream branch flow path plate located between the downstream branch flow path plate and the inflow plate; On the upstream branch flow channel plate, the branch outflow portion extends in a direction perpendicular to the first direction, a transition portion is connected between the branch inflow portion and the branch outflow portion, and the transition portion extends in the first direction.

8. The dispenser according to claim 7, characterized in that An outer end surface P of the branch inlet portion extending along the first direction is coplanar with the transition portion.

9. A heat exchanger, characterized in that: include: A plurality of heat exchange tubes are arranged along a first direction and are used for circulating the refrigerant, wherein the heat exchange tubes are flat tubes; and a distributor, for distributing the refrigerant to the plurality of heat exchange tubes; Wherein, the distributor comprises: an inflow plate having an inflow portion formed thereon; at least one branch flow path plate having at least one branch flow path formed thereon for branching and circulating the refrigerant flowing from the inlet portion, the branch flow path having a branch inlet portion for the refrigerant to flow in, and a plurality of branch outflow portions for the refrigerant to branch out, wherein the branch flow path plate closest to the heat exchange tube is a downstream branch flow path plate; an outflow plate, on which a plurality of outflow portions are provided, wherein the outflow portions connect the branch outflow portions of the downstream branch flow plate and the heat exchange tubes in opposite directions; Wherein, on the downstream branch flow path plate, the branch outflow portion has a branch outflow end for allowing the refrigerant to flow out; the branch outflow end is arranged close to the windward side of the heat exchanger; The heat exchanger is connected to a plurality of distributors; the number of the heat exchange tubes connected to the distributor is the number of outlets of the distributor; for a plurality of distributors with different numbers of outlets, the number of outlets of the distributor increases from top to bottom.

10. A refrigeration cycle device, characterized in that: The heat exchanger according to claim 9 is included, and the heat exchanger serves as at least one of an evaporator and a condenser.

Images