Air conditioner

Abstract

The utility model discloses an air conditioner, and belongs to the technical field of air treatment. The air conditioner comprises a heat exchanger; the heat exchanger comprises a plurality of flat pipes which are arranged in the height direction and used for circulation of refrigerants; the collecting pipe is connected with the ends of the flat pipes and used for distributing refrigerants to the flat pipes, the inner side face, opposite to the flat pipes and away from the flat pipes, of the collecting pipe is an arc side face, and the collecting pipe is provided with a refrigerant inflow cavity, a refrigerant outflow cavity and a refrigerant outflow cavity. The flow dividing cavity is formed in the upper side of the refrigerant inflow cavity, and the flow dividing cavity communicates with the flat pipes; and the circulation hole is communicated between the refrigerant inflow cavity and the flow dividing cavity, and the circulation hole is close to the arc side face, so that when the refrigerant flows to the flow dividing cavity from the circulation hole, the coanda effect is generated, and the refrigerant climbs to the top of the flow dividing cavity along the arc side face. The air conditioner can solve the problem of poor refrigerant distribution uniformity of the micro-channel heat exchanger.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air treatment, in particular to an air conditioner. BACKGROUND

[0002] The heat exchanger is an important component of the heat exchange cycle of the air conditioner. The commonly used heat exchanger forms include the tube-fin type and the micro-channel type. The tube-fin type heat exchanger includes a plurality of fins and a circular tube penetrating the fins. The micro-channel type heat exchanger includes a plurality of flat tubes and a plurality of fins connected to the flat tubes. In the tube-fin type heat exchanger and the micro-channel type heat exchanger, the refrigerant flowing through the circular tube or the flat tube exchanges heat with the external air. The fins can increase the heat exchange area between the refrigerant in the circular tube or the flat tube and the external air.

[0003] Since the height of the heat exchanger of the large air conditioner outdoor unit is large, the number of flat tubes in the vertical direction is large. Whether the refrigerant can be evenly distributed into these flat tubes becomes a bottleneck problem that restricts the performance of the micro-channel type heat exchanger. CONTENT OF THE UTILITY MODEL

[0004] The present application provides an air conditioner, which can solve the problem of poor refrigerant distribution uniformity of the micro-channel heat exchanger.

[0005] In one aspect of the present application, an air conditioner comprises: a heat exchanger; the heat exchanger comprises: a plurality of flat tubes arranged along a height direction and used for flowing refrigerant; and a header pipe connected to end portions of the flat tubes and used for distributing the refrigerant to the plurality of flat tubes, an inner side surface of a portion of the header pipe opposite to and away from the flat tubes is a circular arc side surface, the header pipe is provided with: a refrigerant inflow cavity; a distribution cavity provided on an upper side of the refrigerant inflow cavity and in communication with the flat tubes; and a flow-through hole communicated between the refrigerant inflow cavity and the distribution cavity and close to the circular arc side surface, so that the refrigerant generates a Coanda effect when flowing from the flow-through hole to the distribution cavity and climbs along the circular arc side surface to a top portion of the distribution cavity.

[0006] In the technical solution, the flow-through hole is arranged close to the circular arc side surface, the Coanda effect is utilized, the refrigerant stably climbs along the circular arc side surface to the top portion of the distribution cavity, and thus the refrigerant in the distribution cavity can be distributed into the flat tubes at the top portion. Compared with the principle of spraying the refrigerant to the top portion, the pressure drop of the present application is smaller, and the refrigerant is more evenly distributed among the flat tubes.

[0007] In some embodiments, a plane parallel to an inlet end surface of the flat tube and passing through an axis of the header pipe is defined as a dividing surface S; the flow-through hole and the flat tube are respectively located on two sides of the dividing surface S; and a minimum distance L1 from the flow-through hole to the circular arc side surface is smaller than a distance L2 from the flow-through hole to the dividing surface S.

[0008] In the technical solution, by setting L1 smaller than L2, the distance from the flow-through hole to the circular arc side surface is limited, so that the two are relatively close and the Coanda effect can be generated.

[0009] In some embodiments, the manifold is cylindrical.

[0010] In some embodiments, the flow-through hole has a diameter D≥4mm.

[0011] If the diameter D is too small, it will cause a large pressure drop. D≥4mm can avoid too large pressure drop and ensure that the refrigerant can rise to the top of the distribution chamber.

[0012] In some embodiments, the diameter D of the flow-through hole increases as the height H of the distribution chamber increases.

[0013] In some embodiments, assuming the longitudinal axis is the diameter D of the flow-through hole and the transverse axis is the height H of the distribution chamber, the relationship between the diameter D and the height H is represented as a hole height line, and the hole height line is a convex curve.

[0014] In this technical solution, when the diameter D is large, it can increase the amount of refrigerant flowing to the flat tube, but if the diameter D is too large, the refrigerant cannot reach the top of the manifold, therefore, the hole height line is a convex curve, although the diameter D can increase as the height H of the distribution chamber increases, but the amplitude of the diameter D that can increase gradually decreases.

[0015] In some embodiments, the manifold further comprises: a plurality of flat tube connection cavities arranged along the height direction, the plurality of flat tube connection cavities are arranged transversely with the distribution chamber and located on the upper side of the refrigerant inflow cavity, and the flat tube connection cavities are in communication with the flat tubes; and a plurality of distribution holes for connecting the distribution chamber and the flat tube connection cavities.

[0016] In this technical solution, by separating the middle and upper parts of the manifold into the distribution chamber and the flat tube communication cavity, the transverse size of the distribution chamber can be reduced, avoiding the separation of the liquid phase and the gas phase of the refrigerant caused by the too large volume of the distribution chamber.

[0017] In some embodiments, a second separation part is arranged in the manifold to separate the distribution chamber and the plurality of flat tube connection cavities, and the distribution holes are arranged on the second separation part; the minimum distance L1 from the flow-through hole to the side of the circular arc is less than the distance L3 from the flow-through hole to the second separation part.

[0018] In this technical solution, L1 is less than L3, so that the flow-through hole is close to the side of the circular arc, ensuring the effect of the Coanda effect.

[0019] In some embodiments, the side of the manifold away from the flat tube is provided with a refrigerant inlet, the refrigerant inlet is in communication with the refrigerant inflow cavity, and the axis of the flow-through hole intersects with the axis of the refrigerant inlet.

[0020] In another aspect of the present application, an air conditioner comprises: a heat exchanger; the heat exchanger comprises: a plurality of flat tubes arranged in a height direction for circulating refrigerant; and a header connected to end portions of the flat tubes for distributing refrigerant to the plurality of flat tubes, the header comprising: a header body, an inner side surface of a portion of the header body opposite to the flat tubes and away from the flat tubes being a circular arc side surface; a first partition portion for partitioning an internal space of the header body into a refrigerant inflow cavity and a distribution cavity located on an upper side of the refrigerant inflow cavity, the distribution cavity being in communication with the flat tubes, the first partition portion being provided with: a flow-through hole, the flow-through hole being close to the circular arc side surface, so that when the refrigerant flows from the flow-through hole to the distribution cavity, the refrigerant generates a Coanda effect and climbs along the circular arc side surface to a top portion of the distribution cavity.

[0021] In this technical solution, the flow-through hole is arranged close to the circular arc side surface, and the Coanda effect is utilized to make the refrigerant stably climb along the circular arc side surface to the top portion of the distribution cavity, so that the refrigerant in the distribution cavity can be distributed into the flat tubes at the top portion. Compared with the principle of using injection to make the refrigerant be injected to the top portion, the pressure drop of the present application is smaller, and the distribution between the flat tubes is more uniform. BRIEF DESCRIPTION OF DRAWINGS

[0022] Figure 1 A schematic diagram of a refrigerant circuit of an air conditioner according to some embodiments is shown;

[0023] Figure 2 A perspective view of a heat exchanger in an air conditioner according to some embodiments is shown;

[0024] Figure 3 A perspective view of a header and a flat tube in an air conditioner according to some embodiments is shown;

[0025] Figure 4 A sectional view of a header and a flat tube in an air conditioner according to some embodiments is shown;

[0026] Figure 5 And Figure 6 A sectional view of a header in an air conditioner according to some embodiments is shown;

[0027] Figure 7 A linear graph of a hole diameter of a flow-through hole of a header and a height of a distribution cavity in an air conditioner according to some embodiments is shown;

[0028] Figure 8 And Figure 9 A fluid simulation diagram of a header in an air conditioner according to some embodiments is shown.

[0029] In the above figures, 100, outdoor unit; 111, compressor; 112, four-way valve; 113, outdoor heat exchanger; 114, outdoor throttling device; 115, outdoor fan; 120, shell; 121, air inlet; 122, air outlet; 130, flow divider; 131, capillary tube; 200, indoor unit; 210, indoor heat exchanger; 211, indoor fan; 220, indoor throttling device; 300, heat exchanger; 310, flat tube; 311, inlet end face; 320, fin; 330, header; 330a, refrigerant inlet; 331, header body; 331a, circular arc side face; 3311, insertion slot; 332, first partition; 3321, flow-through hole; 333, refrigerant inflow cavity; 335, second partition; 3351, flow division hole; 336, flow division cavity; 338, third partition; 339, flat tube connection cavity; 340, gas collecting pipe. DETAILED DESCRIPTION

[0030] For the purpose of making the purpose and implementation of the present application more clear, the exemplary implementation of the present application will be described clearly and completely in the following with reference to the drawings in the exemplary implementation of the present application. Obviously, the described exemplary implementation is only a part of the implementation of the present application, but not all the implementation.

[0031] In the description of the present application, it needs to be understood that the orientation or position relationship indicated by the terms “center”, “upper”, “lower”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inner”, “outer” and the like is based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, and is not intended to indicate or imply that the indicated device or element must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application.

[0032] The terms “first”, “second” are only for the purpose of description, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined with “first”, “second” can explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise specified, the meaning of “a plurality of” is two or more.

[0033] In the description of the present application, it needs to be explained that, unless otherwise explicitly specified and limited, the terms “mounting”, “connection”, “connection” should be understood in a broad sense, for example, it can be fixed connection, or detachable connection, or integrally connected; it can be mechanical connection, or electrical connection; it can be directly connected, or indirectly connected through intermediate medium; it can be the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0034] The air conditioner in the present application performs a refrigeration cycle of the air conditioner by using a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and supplies refrigerant to air that has been adjusted and heat-exchanged.

[0035] The compressor compresses refrigerant gas in a low-temperature and low-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.

[0036] The expansion valve expands the liquid-phase refrigerant in a high-temperature and high-pressure state condensed in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a refrigeration effect by heat-exchanging with a material to be cooled using latent heat of evaporation of the refrigerant. Throughout the cycle, the air conditioner can adjust the temperature of an indoor space.

[0037] The outdoor unit of the air conditioner refers to a portion of the refrigeration cycle including the compressor and the outdoor heat exchanger, the indoor unit of the air conditioner includes the indoor heat exchanger, and the expansion valve can be provided in the indoor unit or the outdoor unit.

[0038] The indoor heat exchanger and the outdoor heat exchanger function as a condenser or an evaporator. When the indoor heat exchanger functions as a condenser, the air conditioner functions as a heater in a heating mode, and when the indoor heat exchanger functions as an evaporator, the air conditioner functions as a cooler in a cooling mode.

[0039] When the outdoor unit and the indoor unit of the air conditioner are in a split structure, the outdoor unit is also referred to as an outdoor machine, and the indoor unit is also referred to as an indoor machine.

[0040] Embodiments of the present application will be described in detail with reference to the accompanying drawings:

[0041] Referring to Figure 1 , the air conditioner according to the embodiments of the present application includes an outdoor machine 100 located in an outdoor space to perform heat exchange between refrigerant and outdoor air, and an indoor machine 200 located in an indoor space to perform heat exchange between refrigerant and indoor air.

[0042] The outdoor machine 100 is provided with a compressor 111 to compress refrigerant, a four-way valve 112 to guide the refrigerant compressed by the compressor to an outdoor heat exchanger 113 or an indoor heat exchanger 210, the outdoor heat exchanger 113 to condense the refrigerant introduced thereto when cooling and evaporate the refrigerant flowing thereto when heating, and an outdoor throttling device 114 to decompress the refrigerant introduced to the outdoor heat exchanger 113.

[0043] The indoor unit 200 is provided with an indoor heat exchanger 210 for evaporating the refrigerant flowing thereto in cooling and condensing the refrigerant introduced thereto in heating, and an indoor throttling device 220 for decompressing the refrigerant introduced to the indoor heat exchanger 210.

[0044] The compressor 111, the four-way valve 112, the outdoor heat exchanger 113, the outdoor throttling device 114, the indoor throttling device 220 and the indoor heat exchanger 210 are connected in series by refrigerant pipes to form a refrigerant circulation loop.

[0045] In the outdoor unit 100, an outdoor fan 115 is disposed opposite the outdoor heat exchanger 113. The outdoor fan 115 includes an outdoor fan and a motor for driving the outdoor fan to rotate. The rotation of the outdoor fan causes outdoor air to flow, and the outdoor air exchanges heat with the refrigerant in the outdoor heat exchanger 113 as it passes through the outdoor heat exchanger 113.

[0046] In the indoor unit 200, an indoor fan 211 is disposed opposite the indoor heat exchanger 210. The indoor fan 211 includes an indoor fan and a motor for driving the indoor fan to rotate. The rotation of the indoor fan causes indoor air to flow, and the indoor air exchanges heat with the refrigerant in the indoor heat exchanger 210 as it passes through the indoor heat exchanger 210.

[0047] In cooling, the compressor 111 discharges high-temperature and high-pressure gaseous refrigerant, which flows into the outdoor heat exchanger 113 via the four-way valve 112. At the outdoor heat exchanger 113, the gaseous refrigerant exchanges heat with outdoor air and is cooled, and the refrigerant gradually changes from a gaseous state to a liquid state as it flows through the outdoor heat exchanger 113.

[0048] The liquid refrigerant discharged from the outdoor heat exchanger 113 is guided to the indoor unit 200 via the outdoor throttling device 114.

[0049] In the indoor unit 200, the refrigerant is decompressed by the indoor throttling device 220 to become a gas-liquid two-phase state.

[0050] The refrigerant flowing out of the indoor throttling device 220 is further guided to the indoor heat exchanger 210, where it exchanges heat with indoor air driven by the indoor fan 211 and evaporates. The temperature of the indoor air decreases and is blown into the room. In the indoor heat exchanger 210, the refrigerant changes from a gas-liquid two-phase state to a gaseous state.

[0051] The gaseous refrigerant exiting the indoor heat exchanger 210 returns to the compressor 111, thereby forming a cooling cycle.

[0052] During the heating operation, the four-way valve 112 is reversed. The compressor 111 discharges high-temperature and high-pressure gas refrigerant, which flows into the indoor heat exchanger 210 via the four-way valve 112. At the indoor heat exchanger 210, the gas refrigerant is heated by heat exchange with indoor air, and the temperature of the indoor air is increased to be blown into the room. The refrigerant gradually changes from a gas state to a liquid state while flowing through the indoor heat exchanger 210.

[0053] The liquid refrigerant discharged from the indoor heat exchanger 210 flows to the outdoor unit 100 via the indoor throttling device 220.

[0054] In the outdoor unit 100, the refrigerant is decompressed by the outdoor throttling device 114 to become a gas-liquid two-phase state.

[0055] The refrigerant flowing out of the outdoor throttling device 114 is continuously guided to the outdoor heat exchanger 113, and is evaporated by heat exchange with outdoor air driven by the outdoor fan 115. In the outdoor heat exchanger 113, the refrigerant changes from a gas-liquid two-phase state to a gas state.

[0056] The gas refrigerant coming out of the outdoor heat exchanger 113 returns to the compressor 111, thereby forming a heating cycle.

[0057] Figure 1 The above description is based on a multi-split air conditioner, but the present application is also applicable to an air conditioner having only one indoor unit.

[0058] In the present application, the outdoor heat exchanger 113 and the indoor heat exchanger 210 are collectively referred to as a heat exchanger. The outdoor fan 115 and the indoor fan 211 are collectively referred to as a fan. The outdoor throttling device 114 and the indoor throttling device 220 are collectively referred to as a throttling device.

[0059] Referring to Figure 2 The heat exchanger 300 includes a refrigerant pipe through which refrigerant flows, and a fin 320 coupled to the refrigerant pipe to increase a heat exchange area.

[0060] In some embodiments, the heat exchanger 300 can be a micro-channel heat exchanger, and the refrigerant pipe is a flat tube 310. The fin 320 is connected to the flat tube 310 to increase the surface area of the flat tube 310, thereby improving the heat exchange efficiency between the refrigerant and the air.

[0061] The flat tube 310 extends in a horizontal direction. A plurality of flat tubes 310 are arranged in a vertical direction (height direction) at intervals. The flat tube 310 can be an aluminum tube.

[0062] The fin 320 is in the shape of a sheet, and a plurality of fins 320 are stacked at a predetermined micro gap and are inserted into the flat tube 310.

[0063] In other embodiments, the fin 320 is connected in a corrugated shape between the flat tubes 310.

[0064] The flat tubes 310 are multi-hole tubes having a plurality of holes that form refrigerant flow paths. The refrigerant exchanges heat with air as it flows through each hole of the flat tubes 310. The plurality of holes are arranged in the flat tubes 310 in the direction of air flow relative to the heat exchanger 300.

[0065] The heat exchanger 300 includes a header 330. The header 330 is connected to one end of the flat tubes 310 in the lateral direction.

[0066] The header 330 extends in the vertical direction for a predetermined length. The header 330 is provided on the side of the heat exchanger 300 to which the throttling device is connected, and gas-liquid two-phase refrigerant flows therethrough.

[0067] The heat exchanger 300 includes a gas header 340. The gas header 340 and the header 330 are connected to both ends of the flat tubes 310 in the lateral direction, respectively.

[0068] The gas header 340 extends in the vertical direction for a predetermined length. The gas header 340 is provided on the side of the heat exchanger 300 to which the four-way valve 112 is connected, and gas refrigerant flows therethrough.

[0069] When the heat exchanger 300 functions as an evaporator, gas-liquid two-phase refrigerant flows into the header 330 and is distributed to the plurality of flat tubes 310, and the refrigerant flowing in the plurality of flat tubes 310 continues to flow out of the heat exchanger 300 through the gas header 340.

[0070] When the heat exchanger 300 functions as a condenser, gas refrigerant flows into the gas header 340 and is distributed to the plurality of flat tubes 310, and the refrigerant flowing in the plurality of flat tubes 310 continues to flow out of the heat exchanger 300 through the header 330.

[0071] In some embodiments, referring to Figure 1 The outdoor unit 100 can include a distributor 130. The distributor 130 can have a shower head shape. The plurality of capillary tubes 131 of the distributor 130 are connected to the header 330. The distributor 130 functions primarily as a first distributor here.

[0072] When the height of the heat exchanger 300 is large, for example, when the height of the heat exchanger 300 is 1 m or more, the header 330 needs to function as a second distributor in the case of uneven wind fields.

[0073] Hereinafter, a description is made of the flow of refrigerant when the heat exchanger 300 functions as an evaporator.

[0074] In some embodiments, referring to Figures 3 to 5 A flow space for refrigerant is defined in the header 330.

[0075] The manifold 330 is provided with a refrigerant inlet 330a. The refrigerant inlet 330a can be connected with the capillary tube 131, for allowing refrigerant to flow into the manifold 330.

[0076] The manifold 330 is provided with a refrigerant inflow cavity 333. The refrigerant inflow cavity 333 is in communication with the refrigerant inlet 330a.

[0077] The manifold 330 is provided with a distribution cavity 336. The distribution cavity 336 is located on the upper side of the refrigerant inflow cavity 333. The distribution cavity 336 is arranged above the refrigerant inflow cavity 333. The distribution cavity 336 is in communication with the flat tube 310.

[0078] In some embodiments, the manifold 330 is provided with a flow-through hole 3321. The flow-through hole 3321 connects the refrigerant inflow cavity 333 and the distribution cavity 336, so that when the heat exchanger 300 is used as an evaporator, refrigerant can flow from the refrigerant inflow cavity 333 to the distribution cavity 336 through the flow-through hole 3321.

[0079] The inner side of the portion of the manifold 330 opposite to the inlet end of the flat tube 310 is a circular arc side 331a. The circular arc side 331a is away from the flat tube 310. The flow-through hole 3321 is arranged close to the circular arc side 331a, so that when the refrigerant flows upward from the flow-through hole 3321, the Coanda effect is generated to make the refrigerant climb along the circular arc side 331a to the top of the distribution cavity 336.

[0080] When the heat exchanger 300 is used as an evaporator, the refrigerant enters the refrigerant inflow cavity 333 from the refrigerant inlet 330a, and is preliminarily mixed in the refrigerant inflow cavity 333, then flows upward into the distribution cavity 336 through the flow-through hole 3321, and is secondarily mixed in the distribution cavity 336, and then is distributed into each flat tube 310.

[0081] If the refrigerant cannot be sprayed to the top of the manifold 330, the refrigerant in the upper flat tube 310 will be less, and the refrigerant in the lower flat tube 310 will be more, resulting in uneven distribution of refrigerant at the heat exchanger 300.

[0082] In the related art, in order to make the refrigerant be able to spray to the top of the manifold 330, the flow-through hole 3321 is usually a small spray hole, the flow rate of the refrigerant entering the distribution cavity is increased by the small hole, and the refrigerant is sprayed in a conical shape from the small spray hole to the top. However, at the same time, the pressure drop is too large, and the negative pressure formed by the high-speed sprayed refrigerant makes it difficult for the refrigerant to flow into the flat tube 310.

[0083] In the present application, the flow-through hole 3321 is arranged close to the circular arc side 331a of the manifold 330, and the Coanda effect is utilized to realize that after the refrigerant enters the distribution cavity 336, the refrigerant with a relatively high speed stably climbs along the circular arc side 331a to the top.

[0084] Since the present application utilizes the Coanda effect to enable the refrigerant to climb to the top of the distribution chamber 336, the flow-through hole 3321 does not need to be arranged in the form of a small jet hole, so the pressure drop loss is small, and the problem that the refrigerant is difficult to flow into the flat tube 310 can be avoided, while ensuring that the refrigerant at the flat tube 310 can be uniformly distributed.

[0085] In the embodiments of the present application, the size of the flow-through hole 3321 and the distance from the flow-through hole 3321 to the circular-arc side wall 331a are configured to enable the Coanda effect.

[0086] In some embodiments, the collecting pipe 330 can be cylindrical.

[0087] Since the collecting pipe 330 is cylindrical, the side walls surrounding the refrigerant inflow chamber 333 are all circular-arc side walls. When the refrigerant enters the refrigerant inflow chamber 333, it first impacts on the circular-arc side wall opposite the refrigerant inlet 330a. After the refrigerant impacts on the circular-arc side wall, it disperses and rotates, so that the gas-liquid phase of the refrigerant is mixed, ensuring the uniformity of the refrigerant.

[0088] In some embodiments, in combination Figure 6 , a plane passing through the axis of the collecting pipe 330 and parallel to the inlet end surface 311 of the flat tube 310 is defined as a boundary surface S.

[0089] The flow-through hole 3321 and the inlet end surface 311 of the flat tube 310 are respectively located on both sides of the boundary surface S.

[0090] The minimum distance L1 from the flow-through hole 3321 to the circular-arc side wall 331a is less than the distance L2 from the flow-through hole 3321 to the boundary surface S.

[0091] In this way, it can be ensured that the flow-through hole 3321 is closer to the circular-arc side wall 331a and farther away from the flat tube 310.

[0092] In some embodiments, the aperture D of the flow-through hole 3321 is ≥4mm. The aperture of the flow-through hole 3321 in this range can avoid excessive pressure drop caused by the flow-through hole 3321 being too small.

[0093] In some embodiments, in combination Figure 7 , the aperture D of the flow-through hole 3321 increases as the height H of the distribution chamber 336 increases. That is, the greater the height of the distribution chamber 336, the greater the aperture D of the flow-through hole 3321.

[0094] The relationship between the aperture D and the height H is expressed as a hole-height line, where the longitudinal axis is the aperture D of the flow-through hole 3321, and the transverse axis is the height H of the distribution chamber 336. The hole-height line is a convex curve.

[0095] When the aperture D is larger, the amount of refrigerant flowing to the flat tube 310 in the same time can be increased. However, when the aperture D is too large, the refrigerant cannot reach the top of the header 330. Therefore, the hole height line is a convex curve. Although the aperture D can be increased as the height H of the distribution chamber 336 increases, the increase of the aperture D gradually decreases.

[0096] The convex hole height line can ensure a small pressure drop and the refrigerant can climb to the top of the distribution chamber 336.

[0097] In some embodiments, continuing to refer to Figures 3 to 6 The header 330 is provided with a plurality of flat tube connection chambers 339. The plurality of flat tube connection chambers 339 are arranged vertically.

[0098] The plurality of flat tube connection chambers 339 are arranged transversely to the distribution chamber 336. The plurality of flat tube connection chambers 339 are located on the upper side of the refrigerant inflow chamber 333.

[0099] Part of the refrigerant inflow chamber 333 is located on the lower side of the distribution chamber 336, and another part of the refrigerant inflow chamber 333 is located on the lower side of the flat tube connection chamber 339.

[0100] The distribution chamber 336 communicates with the plurality of flat tube connection chambers 339, so that the refrigerant can flow from the distribution chamber 336 to the plurality of flat tube connection chambers 339.

[0101] If there is no flat tube connection chamber 339 in the header 330, the distribution chamber 336 is directly communicated with the flat tube 310. In the case that the lateral dimension of the header 330 is constant, the lateral dimension of the distribution chamber 336 will be relatively large, and the refrigerant in the distribution chamber 336 can be separated into liquid and gas phases.

[0102] In the embodiments of the present application, the middle and upper parts of the header 330 are separated into the distribution chamber 336 and the flat tube connection chamber 339, so that the width of the flow path of the refrigerant can be limited to be relatively small, and the separation of the refrigerant in a large space can be avoided.

[0103] In some embodiments, the header 330 includes a plurality of distribution holes 3351. The plurality of distribution holes 3351 are arranged one by one corresponding to the flat tube connection chamber 339. The distribution hole 3351 communicates the flat tube connection chamber 339 with the distribution chamber 336. The refrigerant in the distribution chamber 336 flows to the flat tube connection chamber 339 through the distribution hole 3351.

[0104] In some embodiments, the side wall of the header 330 surrounding the flat tube connection chamber 339 can be provided with a plurality of insertion slots 3311 arranged in the height direction.

[0105] The flat tube 310 is inserted into the insertion slot 3311. The flat tube 310 and the header 330 can be fixed by welding.

[0106] The flat tube 310 is in communication with the flat tube connecting cavity 339, so that the refrigerant in the flat tube connecting cavity 339 can flow to the flat tube 310.

[0107] The distribution hole 3351, the flat tube connecting cavity 339, and the flat tube 310 are correspondingly arranged.

[0108] The refrigerant in the distribution cavity 336 is distributed into multiple streams, respectively enters the flat tube connecting cavity 339 through the multiple distribution holes 3351, and then flows into the flat tube 310 from the flat tube connecting cavity 339.

[0109] The present application can ensure that the refrigerant uniformly distributed to the distribution hole 3351 can flow to the corresponding flat tube 310 by arranging the flat tube connecting cavity 339 corresponding to the multiple distribution holes 3351, thereby ensuring the uniform distribution of the refrigerant.

[0110] In some embodiments, the distribution hole 3351 is arranged opposite to the inlet end of the flat tube 310, so that the refrigerant flowing out of the distribution hole 3351 can flow to the flat tube 310 in a straight path.

[0111] The distribution hole 3351 and the flat tube 310 are arranged at the vertical middle part of the flat tube connecting cavity 339.

[0112] After the refrigerant enters the header 330 through the refrigerant inlet 330a, the refrigerant is preliminarily mixed in the refrigerant flow-in cavity 333, then is secondarily mixed in the distribution cavity 336 through the flow-through hole 3321, and finally flows into the flat tube 310 through the distribution hole 3351.

[0113] In some embodiments, the header 330 includes a header body 331. The header body 331 is internally hollow to form a cavity for limiting the flow of the refrigerant.

[0114] The header 330 can include a first partition 332. The first partition 332 is in the form of a plate and is arranged transversely in the cavity of the header body 331.

[0115] The first partition 332 divides the cavity of the header body 331 into the refrigerant flow-in cavity 333 located at the lower side and the distribution cavity 336 located at the upper side.

[0116] The first partition 332 is provided with holes penetrating therethrough to form the flow-through hole 3321.

[0117] The first partition 332 can be integrally formed with the header body 331, or the first partition 332 and the header body 331 are two-body structures and can be connected together by means such as welding.

[0118] In some embodiments, the manifold 330 comprises a second partition 335. The second partition 335 is plate-shaped and vertically arranged in the manifold body 331.

[0119] The second partition 335 separates the shunt cavity 336 and the flat tube connecting cavity 339.

[0120] The second partition 335 is provided with a plurality of shunt holes 3351 arranged in the height direction.

[0121] In some embodiments, in the transverse direction, the minimum distance L1 from the flow-through hole 3321 to the circular arc side surface 331a is smaller than the distance L3 from the flow-through hole 3321 to the second partition 335.

[0122] L1 < L3, so that the flow-through hole 3321 is closer to the circular arc side surface 331a, ensuring the effect of the Coanda effect.

[0123] In some embodiments, the manifold 330 comprises a plurality of third partitions 338. The plurality of third partitions 338 are arranged in the vertical direction and used to separate a plurality of flat tube connecting cavities 339.

[0124] In some embodiments, the refrigerant inlet 330a is arranged on the side of the manifold 330 away from the flat tube 310.

[0125] In some embodiments, the axis of the flow-through hole 3321 intersects the axis of the refrigerant inlet 330a, so that the flow-through hole 3321 is closer to the refrigerant inlet 330a and farther from the flat tube 310.

[0126] The plane perpendicular to the inlet end surface 311 of the flat tube 310 and passing through the axis of the manifold 330 is plane P, and the axis of the refrigerant inlet 330 and the axis of the flow-through hole 3321 are both located on the plane P.

[0127] The present application simulates the fluid at the manifold 330, and obtains Figure 8 and Figure 9 As can be seen from the figure, after the refrigerant flows into the refrigerant inlet cavity 333, it first flows horizontally and then circulates near the position away from the refrigerant inlet 330a, and then the refrigerant flowing out of the flow-through hole 3321 climbs along the circular arc side surface 331a to the top.

[0128] As can be seen from the above, in the present application, by designing the flow-through hole 3321 in cooperation with the circular arc side surface 331a, the Coanda effect is utilized to make the refrigerant stably climb along the circular arc side surface 331a to the top of the manifold 330, and reach the flat tube 310 at the top. Compared with using a small injection hole to enable the refrigerant to be injected to the top, the pressure drop of the present application is smaller and the distribution between the flat tubes 310 is more uniform.

[0129] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, and are not intended to limit the present application; although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that the technical solutions recorded in the foregoing embodiments can still be modified, or some or all of the technical features can be replaced by equivalents; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present application.

[0130] The foregoing description has been presented for the purpose of illustration and description. It is not intended to be exhaustive or to limit the embodiments to the precise forms disclosed. Modifications and variations are possible in light of the above teachings or can be acquired from practice of the embodiments. The described embodiments were chosen and described in order to best explain the principles of the application and its practical application to thereby enable others skilled in the art to best use the application in various embodiments and with various modifications as are suited to the particular use contemplated.

Claims

1. An air conditioner, characterized in that, The heat exchanger comprises: a plurality of flat tubes arranged in a height direction for flowing refrigerant; a header connected with end portions of the flat tubes for distributing refrigerant to the plurality of flat tubes, an inner side surface of a portion of the header opposite to and away from the flat tubes being a circular arc side surface, the header being provided with: a refrigerant inflow cavity; a distribution cavity provided on an upper side of the refrigerant inflow cavity, the distribution cavity being in communication with the flat tubes; a flow-through hole in communication between the refrigerant inflow cavity and the distribution cavity, the flow-through hole being close to the circular arc side surface, so that when refrigerant flows from the flow-through hole to the distribution cavity, the refrigerant produces a Coanda effect and climbs along the circular arc side surface to a top portion of the distribution cavity. A plane passing through an axis of the header and parallel to an inlet end surface of the flat tubes is defined as a boundary surface S, the flow-through hole and the flat tubes being located on two sides of the boundary surface S respectively; a minimum distance L1 from the flow-through hole to the circular arc side surface is less than a distance L2 from the flow-through hole to the boundary surface S.

2. The air conditioner of claim 1, wherein The header is in a cylindrical shape. A hole diameter D of the flow-through hole is greater than or equal to 4 mm.

3. The air conditioner of claim 1, wherein The hole diameter D of the flow-through hole increases with an increase in a height H of the distribution cavity.

4. The air conditioner of claim 1, wherein A relationship between the hole diameter D and the height H is expressed as a hole-height line, the hole-height line being a convex curve.

5. The air conditioner of claim 4, wherein The header is further provided with:

6. The air conditioner of claim 5, wherein a plurality of flat tube connection cavities arranged in a height direction, the plurality of flat tube connection cavities being arranged transversely to the distribution cavity and located on an upper side of the refrigerant inflow cavity, the flat tube connection cavities being in communication with the flat tubes; 7. The air conditioner according to any one of claims 1 to 6, wherein a plurality of distribution holes in communication between the distribution cavity and the flat tube connection cavities. The header is provided with a second partition portion for separating the distribution cavity and the plurality of flat tube connection cavities, the distribution holes being provided on the second partition portion; the minimum distance L1 from the flow-through hole to the circular arc side surface is less than a distance L3 from the flow-through hole to the second partition portion.

8. The air conditioner of claim 7, wherein A refrigerant inlet is provided on a side of the header away from the flat tubes, the refrigerant inlet being in communication with the refrigerant inflow cavity; an axis of the flow-through hole intersects an axis of the refrigerant inlet.

9. The air conditioner of claim 1, wherein The heat exchanger comprises: a plurality of flat tubes arranged in a height direction for flowing refrigerant; 10. An air conditioner characterized by comprising: a header connected with end portions of the flat tubes for distributing refrigerant to the plurality of flat tubes, the header comprising: a header body, an inner side surface of a portion of the header body opposite to and away from the flat tubes being a circular arc side surface; a first partition portion separating an internal space of the header body into a refrigerant inflow cavity and a distribution cavity located on an upper side of the refrigerant inflow cavity, the distribution cavity being in communication with the flat tubes, the first partition portion being provided with: a flow-through hole, the flow-through hole being close to the circular arc side surface, so that when refrigerant flows from the flow-through hole to the distribution cavity, the refrigerant produces a Coanda effect and climbs along the circular arc side surface to a top portion of the distribution cavity. ​ ​ ​

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