Air conditioner outdoor unit

Abstract

The application discloses an outdoor unit of an air conditioner, which comprises a casing, a heat exchanger arranged in the casing, and a plurality of groups of heat exchange pipes. The heat exchange pipes comprise a straight pipe section arranged between a first end plate and a second end plate opposite to the first end plate, a bent pipe section connected to two adjacent straight pipe sections and located outside the first end plate and the second end plate, and an inlet section connected to one end of the straight pipe section and located outside the first end plate. Each fluid distributor comprises a main flow pipe with a refrigerant inlet at one end, and a plurality of branch flow pipes connected to one end of the main flow pipe away from the refrigerant inlet and each provided with a refrigerant outlet. The branch flow pipes provide refrigerant to the inlet section through the refrigerant outlets. At least one branch flow pipe forms an avoiding portion configured to avoid the bent pipe section. The technical scheme can avoid interference between the branch flow pipes and the bent pipe section, and reduce the assembly difficulty of the branch flow pipes.

Description

Technical Field

[0001] This application relates to the field of air conditioning equipment technology, and in particular to an outdoor air conditioning unit. Background Technology

[0002] An air conditioner, also known as an air conditioner, is a device that uses artificial means to regulate and control parameters such as temperature, humidity, and airflow of the air inside a building or structure.

[0003] Currently, more and more people are choosing to install air conditioners indoors to regulate the temperature of the indoor air. Air conditioners typically consist of an outdoor unit and an indoor unit. The outdoor unit refers to the part of the refrigeration cycle that includes the compressor and the outdoor heat exchanger, while the indoor unit includes the indoor heat exchanger. An expansion valve can be provided in either the indoor or outdoor unit. The indoor and outdoor heat exchangers function as either condensers or evaporators. When the indoor heat exchanger is used as a condenser, the air conditioner operates in heating mode; when it is used as an evaporator, the air conditioner operates in cooling mode.

[0004] In the existing technology, the heat exchanger of the outdoor unit distributes the refrigerant to each heat exchange tube of the heat exchanger through a distribution component. However, the length of the connecting pipe between the distribution component and the heat exchange tube is long, and the larger the size of the heat exchanger, the more heat exchange tubes there are and the denser the arrangement. This causes interference between the connecting pipe of the distribution component and the bend section of the heat exchange tube, increasing the difficulty of assembling the branch pipe and the heat exchange tube. Utility Model Content

[0005] This application discloses an outdoor air conditioning unit that can avoid interference between the branch pipe and the bend section, and reduce the assembly difficulty of the branch pipe and the heat exchange pipe.

[0006] To achieve the above objectives, some embodiments of this application provide an outdoor unit for an air conditioner, comprising: a casing; a heat exchanger disposed within the casing, the heat exchanger comprising: a first end plate; a second end plate opposite to the first end plate; multiple sets of heat exchange tubes, each heat exchange tube comprising: a straight pipe section disposed between the first end plate and the second end plate; a bent pipe section connecting two adjacent straight pipe sections and located outside the first end plate and the second end plate; and an inlet section connected to one end of each straight pipe section. Located outside the first end plate; multiple fluid distributors for distributing refrigerant to the inlet sections of the multiple sets of heat exchange tubes, each fluid distributor including: a main pipe with a refrigerant inlet at one end; multiple branch pipes connected to the end of the main pipe away from the refrigerant inlet, each branch pipe having a refrigerant outlet, the branch pipe supplying refrigerant to the inlet section through the refrigerant outlet, at least one branch pipe forming a clearance section configured to avoid the bend section.

[0007] In related technologies, a flow distribution assembly for distributing refrigerant to multiple inlet sections of multiple heat exchange tubes consists of a flow distribution element and multiple flow distribution branches. The refrigerant is divided into multiple streams within the flow distribution element and then transported to each heat exchange tube through the multiple flow distribution branches. The length of the flow distribution branches is long, resulting in significant flow losses of the refrigerant within them. Furthermore, the flow distribution branches interfere with the bends in the heat exchange tubes, making assembly difficult when connecting the flow distribution branches to the heat exchange tubes. If the flow distribution branches are forcibly connected to the heat exchange tubes, the bends in the flow distribution branches and the heat exchange tubes will be squeezed against each other, causing deformation of the bends and affecting the flow stability of the refrigerant in the heat exchange tubes.

[0008] In this embodiment, the refrigerant is distributed using a fluid distributor. Because the branch pipe of the fluid distributor has a clearance section that avoids the bends in the heat exchanger pipes, when connecting the branch pipe to the inlet section of the heat exchanger pipes, the clearance section of the branch pipe can avoid the bends between the inlet sections of adjacent sets of heat exchanger pipes. This prevents interference between the branch pipe and the bends in the heat exchanger pipes, reduces the assembly difficulty of the branch pipe and the inlet section of the heat exchanger pipes, makes the layout between the branch pipe and the heat exchanger pipes more compact, and avoids mutual compression and deformation of the bends in the branch pipe and the heat exchanger pipes, ensuring the flow stability of the refrigerant in the heat exchanger pipes.

[0009] Furthermore, in the related technology, after the refrigerant is diverted by the flow divider, the flow path of the flow divider branch between the flow divider and the inlet section of the heat exchange tube is long, resulting in a long flow path for the refrigerant in the flow divider branch and a large flow loss in the flow divider branch, which makes it impossible to guarantee the amount of refrigerant distributed to the heat exchange tube.

[0010] In this embodiment, the main flow pipe of the fluid distributor is directly connected to the compressor, which supplies refrigerant into the main flow pipe. Multiple branch pipes are connected to the end of the main flow pipe furthest from the refrigerant inlet (i.e., the end closest to the first end plate). The refrigerant first flows in the main flow pipe, and then branches into the branch pipes at the end closest to the first end plate. The short pipe length between each branch pipe and the inlet section of the heat exchange tubes reduces refrigerant flow losses within each branch pipe and increases the amount of refrigerant flowing in each group of heat exchange tubes.

[0011] In some embodiments of this application, the plane in which the avoidance portion is located is perpendicular to the first end plate.

[0012] This allows for a more compact and rational arrangement of the branch pipes in space, avoiding interference between the branch pipes and bends, and improving the overall structural compactness and space utilization of the heat exchanger. At the same time, this helps maintain the relative stability and reliable connections between the components of the heat exchanger, reducing the risk of structural deformation or damage caused by mutual compression or collision between components, thereby improving the stability and service life of the entire outdoor air conditioning unit.

[0013] In some embodiments of this application, the avoidance section includes: an inclined section, a first end of which is connected to the end of the main flow pipe away from the refrigerant inlet, and a second end of which is inclined relative to the first end of the inclined section in a direction away from the first end plate; a straight section, a first end of which is connected to the second end of the inclined section, and the straight section extends in a direction parallel to the first end plate; the branch pipe includes: an outlet section, a first end of which is connected to the second end of the straight section, and a refrigerant outlet is disposed at the second end of the outlet section, the second end of which is connected to the inlet section through the refrigerant outlet; an avoidance space is formed between the straight section and the first end plate for avoiding the bend section.

[0014] In this way, by designing the branch pipe as a combination of inclined section, straight section and outlet section, and making the straight section extend in a direction parallel to the first end plate, a clearance space is formed between the straight section and the first end plate, which effectively avoids the bend section in the direction perpendicular to the first end plate, so that the branch pipe will not interfere with the bend section in the direction perpendicular to the first end plate, thus improving the structural compactness of the entire heat exchanger.

[0015] In some embodiments of this application, the angle between the axis of the inclined segment and the extension line along the direction perpendicular to the first end plate is 30° to 45°.

[0016] In this way, the branch pipe can effectively avoid the bend section in space and provide sufficient clearance, while the inclined section will not be overly inclined and occupy too much space, thus better adapting to the limited space layout inside the casing and optimizing the relative positional relationship between the branch pipe and other components.

[0017] In some embodiments of this application, the plane in which the avoidance portion is located is parallel to the first end plate.

[0018] In this way, the bending direction of the branch pipe is coordinated with the layout parallel to the first end plate, avoiding excessive space occupation of the branch pipe in the direction perpendicular to the first end plate, thereby improving the structural compactness of the entire heat exchanger and reducing the volume of the outdoor unit of the air conditioner.

[0019] In some embodiments of this application, the avoidance section includes: an inclined section, a first end of which is connected to the end of the main flow pipe away from the refrigerant inlet, and a second end of which is inclined relative to the first end of which is inclined in a first direction parallel to the first end plate; a straight section, a first end of which is connected to the second end of the inclined section, and which extends in a direction parallel to the first end plate; and an outlet section, a first end of which is connected to the second end of the straight section, and a refrigerant outlet is disposed at the second end of the outlet section, the second end of which is connected to the inlet section through the refrigerant outlet; the straight section forms an avoidance space on a second side in a direction parallel to the first end plate for avoiding the bend section.

[0020] Thus, the straight section forms a clearance space on its second side in the direction parallel to the first end plate, effectively avoiding the bend section in the direction parallel to the first end plate and effectively preventing interference between the branch pipe and the bend section in the direction parallel to the first end plate. This allows for a more compact and rational layout between the branch pipe and the bend section of the heat exchanger, reducing the space occupied by the clearance portion of the branch pipe in the direction perpendicular to the first end plate, improving the overall structural compactness of the heat exchanger, and reducing the space occupied within the casing.

[0021] In some embodiments of this application, the length of the straight section is 35mm to 60mm.

[0022] This design ensures sufficient clearance between the branch pipes and the bends to prevent interference, while also avoiding excessive use of the internal space of the casing. This allows for a rational layout of the branch pipes within a limited space, improving space utilization and ensuring a compact overall structure of the heat exchanger. Furthermore, this length range allows for stable refrigerant flow in the straight sections, reducing refrigerant eddies and resistance losses, ensuring sufficient refrigerant is allocated to the inlet section of the heat exchange pipes, and improving heat exchange efficiency.

[0023] In some embodiments of this application, the second end of the inclined segment smoothly transitions to the first end of the straight segment; and / or, the second end of the straight segment smoothly transitions to the first end of the outlet segment.

[0024] In this way, a smooth transition surface can guide the refrigerant to change its flow direction smoothly, avoiding refrigerant flow separation and eddy current generation caused by sudden sharp corners or steps.

[0025] In some embodiments of this application, the axis of the main flow pipe extends in a direction perpendicular to the first end plate; the plurality of branch pipes include: a first branch pipe, which is connected to the end of the main flow pipe away from the refrigerant inlet and extends in a direction perpendicular to the first end plate; a second branch pipe, which is connected to the end of the main flow pipe away from the refrigerant inlet and extends in a direction parallel to the first end plate, and is located on one side of the first branch pipe; a third branch pipe, which is connected to the end of the main flow pipe away from the refrigerant inlet and extends in a direction parallel to the first end plate, and is located on the side of the first branch pipe away from the second branch pipe, and the clearance portion is disposed on the third branch pipe.

[0026] In this way, a single fluid distributor can simultaneously distribute refrigerant to the three inlet sections of three sets of heat exchange tubes. Furthermore, the clearance section on the third branch tube can be adjusted according to the structure of different heat exchangers and the layout of the bends in the heat exchange tubes, enabling the fluid distributor to adapt to heat exchangers of various sizes and shapes, thus improving its adaptability.

[0027] In some embodiments of this application, the axis of the main flow pipe extends in a direction perpendicular to the first end plate; the plurality of branch pipes include: a fourth branch pipe connected to the end of the main flow pipe away from the refrigerant inlet; and a fifth branch pipe connected to the end of the main flow pipe away from the refrigerant inlet and extending in a direction parallel to the first end plate. The main flow pipe is located between the fourth branch pipe and the fifth branch pipe, and the fifth branch pipe includes a horizontal section parallel to the first end plate and a vertical section perpendicular to the first end plate. The horizontal section extends away from the vertical section. One end of the straight section is connected to the main flow pipe, and the refrigerant outlet is located at the end of the vertical section away from the horizontal section; the sixth branch pipe is connected to the horizontal section of the fifth branch pipe, and in the direction perpendicular to the first end plate, the sixth branch pipe is staggered from the main flow pipe, and the main flow pipe is located between the sixth branch pipe and the fourth branch pipe in the direction parallel to the first end plate, forming the clearance portion between the sixth branch pipe and the fourth branch pipe, and the distance between the axis of the sixth branch pipe and the axis of the main flow pipe is 5mm to 50mm.

[0028] Thus, by staggering the sixth branch pipe with the main pipe, the branch pipes can be arranged more flexibly within the space of the first end plate, avoiding interference with other components. The distance between the axis of the sixth branch pipe and the axis of the main pipe is 5mm to 50mm. This not only provides more flexible space for the connection between the branch pipe and the inlet section of the heat exchange tube during installation, reducing installation difficulty, but also provides a reasonable offset range for the sixth branch pipe. This ensures that the sixth branch pipe avoids interference areas without excessive offset, increasing the utilization rate of the internal space of the entire casing and making the structure more compact.

[0029] In some embodiments of this application, the diameter of the main flow pipe is larger than the diameter of each of the branch pipes; and / or, the diameters of each of the branch pipes are equal.

[0030] In this way, the larger diameter of the main pipe reduces the flow resistance of the refrigerant before it enters the branch pipes, ensuring sufficient flow and pressure to distribute the refrigerant to each branch pipe. Furthermore, the equal diameter of each branch pipe helps to ensure that the refrigerant velocity, flow rate, and other parameters are basically the same in each branch pipe, thus achieving uniform refrigerant distribution.

[0031] In some embodiments of this application, the fluid distributor is integrally formed by a cold extrusion process.

[0032] Thus, the fluid distributor is formed by cold extrusion, which allows for precise shaping and the creation of the desired form and size. Because the process is performed in a cold state, the material used to make the distributor has good flowability, enabling it to better fill all parts of the mold, thereby reducing material waste and lowering production costs. Furthermore, cold extrusion can complete complex forming processes in a single operation, reducing the processing time of multiple steps. Compared to traditional machining, cold extrusion significantly shortens the production cycle and improves the production efficiency of fluid distributors.

[0033] In some embodiments of this application, the fluid distributor further includes: a plurality of welding aids, each of which corresponds to a plurality of branch pipes, the welding aids being disposed at one end of the branch pipe near the refrigerant outlet, and the welding aids being configured to provide a welding position for automatic welding equipment to weld the branch pipe and the inlet section.

[0034] In related technologies, the branch pipes of the splitter assembly need to be connected to the inlet section of the heat exchange tube by manual welding. However, the heat exchanger has a large number of inlet sections of multiple heat exchange tubes, which leads to a large number of weld points that need to be welded manually, resulting in low assembly efficiency of the branch pipes and heat exchange tubes.

[0035] In this embodiment, the welding auxiliary component installed at the end of the branch pipe near the refrigerant outlet provides a clear and fixed welding position for the automatic welding equipment. The automatic welding equipment can quickly identify and locate the welding position provided by the welding auxiliary component, and perform welding operations continuously and stably according to the preset program and welding position, thus automating the welding process, reducing reliance on manual operation, and improving the assembly efficiency of the branch pipe and the inlet section of the heat exchange tube. Furthermore, the welding auxiliary component enables the automatic welding equipment to accurately align the connection between the branch pipe and the inlet section, avoiding welding deviations caused by inaccurate positioning, improving welding accuracy, ensuring the quality and reliability of the weld, thereby enhancing the connection strength between the branch pipe and the inlet section. This allows the fluid distributor to better withstand refrigerant pressure and vibration loads, reducing the risk of weld cracking or loosening during operation, and improving the reliability and safety of the outdoor air conditioning unit. Attached Figure Description

[0036] To more clearly illustrate the technical solutions in the embodiments of this application, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0037] Figure 1 This is a front view of the outdoor unit of an air conditioner disclosed in an embodiment of this application;

[0038] Figure 2 This is a schematic diagram of the structure of the heat exchanger disclosed in the embodiments of this application;

[0039] Figure 3 This is a side view of the heat exchanger disclosed in an embodiment of this application;

[0040] Figure 4 for Figure 3 Sectional view at point AA;

[0041] Figure 5 This is a front view of the heat exchanger disclosed in the embodiments of this application;

[0042] Figure 6 for Figure 5 A magnified view of a section at point A in the middle;

[0043] Figure 7 This is a schematic diagram of the structure of a fluid distributor disclosed in one embodiment of this application;

[0044] Figure 8 This is a front view of a fluid dispenser disclosed in one embodiment of this application;

[0045] Figure 9This is a schematic diagram of the structure of a fluid distributor disclosed in another embodiment of this application;

[0046] Figure 10 This is a top view of a fluid dispenser disclosed in another embodiment of this application;

[0047] Figure 11 This is a schematic diagram of a fluid distributor disclosed in another embodiment of this application.

[0048] Explanation of reference numerals in the attached figures:

[0049] 100 - Air conditioner outdoor unit;

[0050] 1-Casing;

[0051] 2-Heat exchanger; 2a-First end plate; 2b-Second end plate; 21-Heat exchange tube; 211-Straight tube section; 212-Bend section; 213-Inlet section;

[0052] 3-Fluid distributor; 31-Main stream pipe; 31a-Refrigerant inlet; 32-Branch pipe; 32a-Refrigerant outlet; 321-Breakthrough section; 3211-Inclined section; 3212-Straight section; 322-Outlet section; 323-First branch pipe; 324-Second branch pipe; 325-Third branch pipe; 326-Fourth branch pipe; 327-Fifth branch pipe; 3271-Horizontal section; 3272-Vertical section; 328-Sixth branch pipe; 33-Welding auxiliary parts. Detailed Implementation

[0053] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0054] In this application, the terms "upper," "lower," "left," "right," "front," "rear," "top," "bottom," "inner," "outer," "vertical," "horizontal," "lateral," and "longitudinal" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for the purpose of better describing this application and its embodiments, and are not intended to limit the indicated device, element, or component to having a specific orientation, or to be constructed and operated in a specific orientation.

[0055] Furthermore, in addition to indicating location or positional relationship, some of the aforementioned terms may also have other meanings. For example, the term "above" may also be used in some cases to indicate a certain dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0056] Furthermore, the terms "installation," "setup," "equipped with," "connection," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral structure; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium, or an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0057] Furthermore, the terms "first," "second," etc., are primarily used to distinguish different devices, elements, or components (which may be the same or different in specific type and construction), and are not intended to indicate or imply the relative importance or quantity of the indicated devices, elements, or components. Unless otherwise stated, "a plurality of" means two or more.

[0058] As people increasingly pursue higher quality indoor environments, air conditioning has become an essential device to meet these needs. Air conditioning, or air conditioner, uses artificial means to regulate and control parameters such as temperature, humidity, and airflow within a building or structure, thereby adjusting indoor air parameters and bringing convenience to daily life.

[0059] Air conditioners are typically divided into outdoor and indoor units. The outdoor unit refers to the part of the refrigeration cycle that includes the compressor and the outdoor heat exchanger. The indoor unit includes the indoor heat exchanger, and an expansion valve can be provided in either the indoor or outdoor unit. The indoor and outdoor heat exchangers function as condensers or evaporators. When the indoor heat exchanger is used as a condenser, the air conditioner operates in heating mode; when it is used as an evaporator, the air conditioner operates in cooling mode.

[0060] In related technologies, the outdoor unit's heat exchanger distributes refrigerant to each heat exchange tube through a distributor. However, the length of the pipes connecting the distributor and the heat exchange tubes is long. As the size of the heat exchanger increases, the number of heat exchange tubes inside the heat exchanger also increases, and the denser the arrangement of the heat exchange tubes, interference will occur between the pipes connecting the distributor and the heat exchange tubes and the bends in the heat exchange tubes. This increases the difficulty of assembling the pipes connected to the distributor and the heat exchange tubes. After installation, the pipes connected to the distributor will be squeezed between the pipes connected to the distributor and the bends in the heat exchange tubes, causing the bends to deform and affecting the flow of refrigerant in the heat exchange tubes.

[0061] Based on this, the present application provides an outdoor air conditioning unit that can avoid interference between the branch pipe and the bend section of the fluid distributor, reduce the assembly difficulty of the branch pipe and the heat exchange pipe, and prevent the branch pipe and the bend section from squeezing each other after installation.

[0062] The present technical solution will be further described below with reference to the embodiments and accompanying drawings.

[0063] Please see Figure 1 This application provides an outdoor unit 100 for an air conditioner, which works together with the indoor unit to regulate indoor air temperature. The air conditioner operates on a refrigeration cycle using a compressor, condenser, expansion valve, and evaporator. Low-temperature, low-pressure refrigerant enters the compressor, which compresses it into a high-temperature, high-pressure refrigerant gas and discharges the compressed gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, releasing heat to the surrounding environment during the condensation process. The expansion valve expands the high-temperature, high-pressure liquid refrigerant formed in the condenser into a low-pressure liquid refrigerant. The evaporator evaporates the expanded refrigerant in the expansion valve and returns the low-temperature, low-pressure refrigerant gas to the compressor. The evaporator achieves the cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material being cooled.

[0064] like Figure 1 As shown, the outdoor unit 100 of the air conditioner includes a housing 1, which is used to house components inside the outdoor unit 100, such as a compressor and a fan.

[0065] like Figure 2 and Figure 3 As shown, the outdoor unit 100 of the air conditioner also includes a heat exchanger 2, which is disposed inside the casing 1. The heat exchanger 2 includes a first end plate 2a and a second end plate 2b, with the second end plate 2b opposite to the first end plate 2a.

[0066] like Figure 4 As shown, the heat exchanger 2 also includes multiple sets of heat exchange tubes 21, and the heat exchange tubes 21 carry away the cold or heat released by the refrigerant inside the heat exchange tubes 21 through the air flow.

[0067] The heat exchange tube 21 includes a straight tube section 211, which is disposed between the first end plate 2a and the second end plate 2b. The straight tube section 211 is the main body of the heat exchange tube 21.

[0068] The heat exchange tube 21 also includes a bend section 212, which connects two adjacent straight tube sections 211 and is located outside the first end plate 2a and the second end plate 2b. The bend section 212 is used to connect the ends of two adjacent straight tube sections 211 to form a complete refrigerant flow path.

[0069] The heat exchange tube 21 also includes an inlet section 213, which is connected to one end of the straight tube section 211 and located outside the first end plate 2a. The inlet section 213 serves as the inlet for the refrigerant flow path in the heat exchanger 2, through which the refrigerant enters the heat exchange tube 21.

[0070] like Figure 5 and Figure 6 As shown, the outdoor unit 100 of the air conditioner also includes multiple fluid distributors 3, which are used to distribute refrigerant to the inlet sections 213 of multiple sets of heat exchange tubes 21.

[0071] Each fluid distributor 3 includes a main pipe 31, one end of which has a refrigerant inlet 31a. The refrigerant inlet 31a of the main pipe 31 is connected to a compressor to supply refrigerant to the main pipe 31 via the compressor.

[0072] Each fluid distributor 3 also includes a plurality of branch pipes 32 connected to the end of the main pipe 31 away from the refrigerant inlet 31a, and each branch pipe 32 is provided with a refrigerant outlet 32a. The branch pipe 32 provides refrigerant to the inlet section 213 of the heat exchange tube 21 through the refrigerant outlet 32a. At least one branch pipe 32 forms a clearance section 321, which is configured to avoid the bend section 212 of the heat exchange tube 21.

[0073] It should be noted that the formation of a clearance portion 321 on at least one branch pipe 32 means that the fluid distributor 3 may have a clearance portion 321 formed on one branch pipe 32, or two branch pipes 32, or even all three branch pipes 32. This embodiment does not make a specific limitation on this.

[0074] In related technologies, the flow distribution assembly for distributing refrigerant to multiple inlet sections 213 of multiple heat exchange tubes 21 consists of a flow distribution element and multiple flow distribution branches. The refrigerant is divided into multiple streams within the flow distribution element and then transported to each heat exchange tube 21 through the multiple flow distribution branches. The length of the flow distribution branches is long, resulting in significant flow losses of the refrigerant within them. Furthermore, the flow distribution branches interfere with the bends 212 of the heat exchange tubes 21, making assembly difficult when connecting the flow distribution branches to the heat exchange tubes 21. If the flow distribution branches are forcibly connected to the heat exchange tubes 21, they will cause mutual compression between the flow distribution branches and the bends 212 of the heat exchange tubes 21, resulting in deformation of the bends 212 and consequently affecting the flow stability of the refrigerant in the heat exchange tubes 21.

[0075] In this embodiment, the refrigerant is distributed through a fluid distributor 3. Because the branch pipe 32 of the fluid distributor 3 has a clearance portion 321 that avoids the bend section 212 of the heat exchange pipe 21, when connecting the branch pipe 32 to the inlet section 213 of the heat exchange pipe 21, the clearance portion 321 of the branch pipe 32 can avoid the bend section 212 between the inlet sections 213 of two adjacent sets of heat exchange pipes 21. This prevents interference between the branch pipe 32 and the bend section 212 of the heat exchange pipe 21, reduces the assembly difficulty of the branch pipe 32 and the inlet section 213 of the heat exchange pipe 21, makes the layout between the branch pipe 32 and the heat exchange pipe 21 more compact, and avoids mutual compression and deformation of the bend section 212 of the branch pipe 32 and the heat exchange pipe 21, ensuring the flow stability of the refrigerant in the heat exchange pipe 21.

[0076] Furthermore, in the related technology, after the refrigerant is diverted by the diverter, the flow path of the diverter branch pipe between the diverter and the inlet section 213 of the heat exchange tube 21 is long, resulting in a long flow path for the refrigerant in the diverter branch pipe. This leads to a large flow loss of the refrigerant in the diverter branch pipe, making it impossible to guarantee the amount of refrigerant distributed to the heat exchange tube 21.

[0077] In this embodiment, the main flow pipe 31 of the fluid distributor 3 is directly connected to the compressor, which supplies refrigerant into the main flow pipe 31. Multiple branch pipes 32 are connected to the end of the main flow pipe 31 furthest from the refrigerant inlet 31a (i.e., the end closest to the first end plate 2a). The refrigerant first flows in the main flow pipe 31, and then branches into the branch pipes 32 when it reaches the end closest to the first end plate 2a. The short pipe length between each branch pipe 32 and the inlet section 213 of the heat exchange tube 21 reduces refrigerant flow losses within each branch pipe 32 and increases the amount of refrigerant flowing in each group of heat exchange tubes 21.

[0078] It should be noted that the heat exchanger in this embodiment can be a finned heat exchanger. The heat exchange tube 21 is inserted into the fins. The airflow direction through the fins is perpendicular to the flow direction of the refrigerant through the heat exchange tube 21. The heat / cold energy released by the refrigerant in the heat exchange tube 21 is carried away by the heat dissipation of the fins and the airflow, thereby enhancing the heat exchange with the air.

[0079] In some embodiments, such as Figure 7 and Figure 8As shown, the plane containing the clearance portion 321 is perpendicular to the first end plate 2a. That is, the clearance portion 321 avoids the bend section 212 of the heat exchange pipe 21 in a direction perpendicular to the first end plate 2a. When the plane containing the clearance portion 321 of the branch pipe 32 is perpendicular to the first end plate 2a, the bending direction of the branch pipe 32 is clear and consistent with the layout of the heat exchanger 2 perpendicular to the first end plate 2a. This allows the branch pipe 32 to be arranged more compactly and rationally in space, avoiding interference between the branch pipe 32 and the bend section 212, and improving the overall structural compactness and space utilization of the heat exchanger 2. Simultaneously, this helps maintain the relative stability and reliable connection between the components of the heat exchanger 2, reducing the risk of structural deformation or damage caused by mutual compression or collision between components, thereby improving the stability and service life of the entire outdoor air conditioning unit 100.

[0080] In some embodiments, combined with Figure 6 and Figure 8 The clearance section 321 includes an inclined section 3211. The first end of the inclined section 3211 is connected to the end of the main pipe 31 away from the refrigerant inlet 31a. The second end of the inclined section 3211 is inclined away from the first end plate 2a relative to the first end of the inclined section 3211.

[0081] The clearance section 321 also includes a straight section 3212, the first end of which is connected to the second end of the inclined section 3211, and the straight section 3212 extends in a direction parallel to the first end plate 2a.

[0082] The branch pipe 32 includes an outlet section 322, the first end of which is connected to the second end of the straight section 3212, and a refrigerant outlet 32a is located at the second end of the outlet section 322. The second end of the outlet section 322 is connected to the inlet section 213 through the refrigerant outlet 32a.

[0083] A clearance space M is formed between the straight section 3212 and the first end plate 2a to avoid the bend section 212.

[0084] By designing the branch pipe 32 as a combination of an inclined section 3211, a straight section 3212, and an outlet section 322, and by making the straight section 3212 extend in a direction parallel to the first end plate 2a, a clearance space M is formed between the straight section 3212 and the first end plate 2a. This effectively avoids the bend section 212 in the direction perpendicular to the first end plate 2a, so that the branch pipe 32 will not interfere with the bend section 212 in the direction perpendicular to the first end plate 2a, thereby improving the structural compactness of the entire heat exchanger 2.

[0085] It should be noted that in this embodiment, the compressor provides high-pressure gaseous refrigerant to the refrigerant inlet 31a of the main pipe 31, with a pressure between 1.5MPa and 3MPa, thereby ensuring that the high-pressure gaseous refrigerant can smoothly enter the straight section 3212 from the main pipe 31 through the inclined section 3211.

[0086] In some embodiments, such as Figure 8 As shown, the angle α between the axis of the inclined segment 3211 and the extension line along the direction perpendicular to the first end plate 2a is 30° to 45°.

[0087] The angle α between the axis of the inclined section 3211 and the extension line perpendicular to the first end plate 2a indicates the degree of inclination of the second end of the inclined section 3211 relative to the first end in a direction away from the first end plate 2a. If the angle α between the axis of the inclined section 3211 and the extension line perpendicular to the first end plate 2a is less than 30°, it means that the inclination of the inclined section 3211 is too large, resulting in excessive occupation of the space perpendicular to the first end plate 2a; if the angle α between the axis of the inclined section 3211 and the extension line perpendicular to the first end plate 2a is greater than 45°, it means that the inclination of the inclined section 3211 is too small, resulting in the inclined section 3211 being unable to effectively avoid the bend section 212 of the heat exchange tube 21 in the direction perpendicular to the first end plate 2a.

[0088] Therefore, when the axis of the inclined section 3211 forms an angle α of 30° to 45° with the extension line perpendicular to the first end plate 2a, it means that the inclined section 3211 is inclined to a moderate degree away from the first end plate 2a. This ensures that the branch pipe 32 effectively avoids the bend section 212 in space, providing sufficient clearance space M, while preventing the inclined section 3211 from being over-inclined and occupying too much space. This better adapts to the limited space layout inside the housing 1 and optimizes the relative positional relationship between the branch pipe 32 and other components.

[0089] In some embodiments, such as Figure 9 and Figure 10 As shown, the plane containing the clearance portion 321 is parallel to the first end plate 2a. That is, the clearance portion 321 avoids the bend section 212 of the heat exchange pipe 21 within a plane parallel to the first end plate 2a; in other words, the clearance portion 321 changes within a plane parallel to the first end plate 2a. When the plane containing the clearance portion 321 is parallel to the first end plate 2a, the bending direction of the branch pipe 32 is coordinated with the layout parallel to the first end plate 2a, avoiding excessive space occupation by the branch pipe 32 in the direction perpendicular to the first end plate 2a. This improves the overall structural compactness of the heat exchanger 2 and reduces the volume of the outdoor unit 100.

[0090] In some embodiments, such as Figure 10As shown, the clearance section 321 includes an inclined section 3211. The first end of the inclined section 3211 is connected to the end of the main pipe 31 away from the refrigerant inlet 31a. The second end of the inclined section 3211 is inclined to a first side in a direction parallel to the first end plate 2a relative to the first end of the inclined section 3211.

[0091] The clearance section 321 also includes a straight section 3212, the first end of which is connected to the second end of the inclined section 3211, and the straight section 3212 extends in a direction parallel to the first end plate 2a.

[0092] The branch pipe 32 includes an outlet section 322, the first end of which is connected to the second end of the straight section 3212, and a refrigerant outlet 32a is located at the second end of the outlet section 322. The second end of the outlet section 322 is connected to the inlet section 213 through the refrigerant outlet 32a.

[0093] The straight section 3212 forms a clearance space M on its second side in a direction parallel to the first end plate 2a to avoid the bend section 212.

[0094] In this embodiment, the first side and the second side in the direction parallel to the first end plate 2a are opposite sides. That is, when the second end of the inclined segment 3211 is inclined relative to the first end of the inclined segment 3211 towards the first side in the direction parallel to the first end plate 2a, the straight segment 3212 forms a clearance space M on the second side in the direction parallel to the first end plate 2a; when the second end of the inclined segment 3211 is inclined relative to the first end of the inclined segment 3211 towards the second side in the direction parallel to the first end plate 2a, the straight segment 3212 forms a clearance space M on the first side in the direction parallel to the first end plate 2a. In other words, when the second end of the inclined segment 3211 is inclined relative to the first end of the inclined segment 3211 towards any side in the direction parallel to the first end plate 2a, the straight segment 3212 forms a clearance space M on the opposite side in the direction parallel to the first end plate 2a. In this embodiment, as shown... Figure 10 As shown, the upper side of the straight section 3212 is the first side in the direction parallel to the first end plate 2a, and the lower side of the straight section 3212 is the second side in the direction parallel to the first end plate 2a.

[0095] In this embodiment, the straight section 3212 forms a clearance space M on its second side in the direction parallel to the first end plate 2a, which can effectively avoid the bend section in the direction parallel to the first end plate 2a and effectively avoid mutual interference between the branch pipe and the bend section in the direction parallel to the first end plate 2a. This makes the layout between the branch pipe 32 and the bend section 212 of the heat exchange pipe 21 more compact and reasonable, reduces the space occupied by the clearance part 321 of the branch pipe 32 in the direction perpendicular to the first end plate 2a, improves the structural compactness of the entire heat exchanger 2, and reduces the space occupied inside the casing 1.

[0096] It should be noted that in this embodiment, the angle α of the inclined section 3211 is 30° to 45°, so as to ensure that the inclined section 3211 and the straight section 3212 can effectively avoid the bend section 212 of the heat exchange tube 21.

[0097] In some embodiments, combined with Figure 8 and Figure 10 The length L of the straight section 3212 is 35mm to 60mm.

[0098] The length L of the straight section 3212 is determined by a comprehensive consideration of the spatial layout of the bend section 212 of the heat exchange tube 21 of the heat exchanger 2 and the refrigerant flow requirements. If the length L of the straight section 3212 is less than 35mm, it may not provide enough clearance space, resulting in the straight section 3212 and the bend section 212 being too close, increasing the risk of interference. If the length L of the straight section 3212 exceeds 60mm, it may cause the branch pipe 32 to extend too much, occupying too much space, affecting the layout of other components, and reducing the space utilization rate inside the casing 1.

[0099] Furthermore, from the perspective of refrigerant flow, a length L of 35mm to 60mm for the straight section 3212 ensures that the refrigerant has sufficient time and path for stable flow within the straight section 3212. If the length L of the straight section 3212 is too short, the change in refrigerant flow direction will be too abrupt, which may cause eddies and increased resistance; if the length L of the straight section 3212 is too long, it will lengthen the refrigerant flow path, increasing the refrigerant flow resistance and energy loss.

[0100] Therefore, the length L of the straight section 3212 is within the range of 35mm to 60mm. This ensures sufficient clearance between the branch pipe 32 and the bend section 212 to avoid interference, while also preventing excessive occupation of the internal space of the casing 1. This allows for a reasonable layout of the branch pipe 32 within the limited space, improving space utilization and ensuring a compact overall structure of the heat exchanger 2. Furthermore, this length range allows for stable refrigerant flow within the straight section 3212, reducing refrigerant eddies and resistance losses, ensuring sufficient refrigerant is distributed to the inlet section 213 of the heat exchange pipe 21, and improving heat exchange efficiency.

[0101] In some embodiments, such as Figure 8 and Figure 10 As shown, there is a smooth transition between the second end of the inclined segment 3211 and the first end of the straight segment 3212.

[0102] The smooth transition between the second end of the inclined section 3211 and the first end of the straight section 3212 reduces eddies and disturbances generated when the refrigerant flows through the connection between the two sections. As the refrigerant flows from the inclined section 3211 into the straight section 3212, the smooth transition surface guides the refrigerant to change its flow direction smoothly, avoiding refrigerant flow separation and eddy current generation caused by sudden angles or steps. This helps reduce the flow resistance of the refrigerant in the branch pipe 32, improves the refrigerant flow efficiency, thereby enhancing the performance of the entire heat exchange system and reducing energy consumption.

[0103] In some embodiments, such as Figure 8 and Figure 10 As shown, there is a smooth transition between the second end of the straight section 3212 and the first end of the outlet section 322.

[0104] The smooth transition between the second end of the straight section 3212 and the first end of the outlet section 322 reduces eddies and disturbances generated when the refrigerant flows through the connection between the straight section 3212 and the outlet section 322. When the refrigerant flows from the straight section 3212 into the outlet section 322, the smooth transition surface guides the refrigerant to smoothly change its flow direction, avoiding refrigerant flow separation and eddy current generation caused by sudden angles or steps. This helps reduce flow losses of the refrigerant as it flows from the straight section 3212 into the outlet section 322, improving the refrigerant flow efficiency and ensuring the amount of refrigerant flowing from the outlet section 322 into the inlet section 213 of the heat exchange tube 21. This ensures that each heat exchange tube 21 can effectively exchange heat, fully utilizing the performance of the heat exchanger 2.

[0105] In some embodiments, combined with Figure 6 and Figure 8 The axis of the main flow pipe 31 extends in a direction perpendicular to the first end plate 2a. The multiple branch pipes 32 also include a first branch pipe 323, which is connected to the end of the main flow pipe 31 away from the refrigerant inlet 31a and extends in a direction perpendicular to the first end plate 2a.

[0106] The multiple branch pipes 32 also include a second branch pipe 324, which is connected to the end of the main pipe 31 away from the refrigerant inlet 31a and is located on one side of the first branch pipe 323 in a direction parallel to the first end plate 2a.

[0107] The multiple branch pipes 32 also include a third branch pipe 325, which is connected to the end of the main pipe 31 away from the refrigerant inlet 31a and is located in a direction parallel to the first end plate 2a. The third branch pipe 325 is located on the side of the first branch pipe 323 away from the second branch pipe 324, and the clearance part 321 is provided on the third branch pipe 325.

[0108] That is to say, a fluid distributor 3 consists of a main flow pipe 31, a first branch pipe 323, a second branch pipe 324 and a third branch pipe 325.

[0109] In this embodiment, refrigerant is distributed from the main pipe 31 to the first branch pipe 323, the second branch pipe 324, and the third branch pipe 325, respectively. Then, the first branch pipe 323, the second branch pipe 324, and the third branch pipe 325 deliver refrigerant to the three inlet sections 213 of the three sets of heat exchange tubes 21. This allows a single fluid distributor 3 to simultaneously distribute refrigerant to the three inlet sections 213 of the three sets of heat exchange tubes 21. Furthermore, the clearance portion 321 on the third branch pipe 325 can be adjusted according to different heat exchanger structures 2 and the layout of the bends 212 of the heat exchange tubes 21, enabling the fluid distributor 3 to adapt to heat exchangers 2 of various sizes and shapes, thus improving the adaptability of the fluid distributor 3.

[0110] In some embodiments, combined with Figure 6 and Figure 11 The axis of the main pipe 31 extends in a direction perpendicular to the first end plate 2a. Multiple branch pipes 32 include a fourth branch pipe 326, which is connected to the end of the main pipe 31 away from the refrigerant inlet 31a.

[0111] The multiple branch pipes 32 also include a fifth branch pipe 327, which is connected to the end of the main pipe 31 away from the refrigerant inlet 31a and is located in a direction parallel to the first end plate 2a. The main pipe 31 is located between the fourth branch pipe 326 and the fifth branch pipe 327. The fifth branch pipe 327 includes a horizontal section 3271 parallel to the first end plate 2a and a vertical section 3272 perpendicular to the first end plate 2a. The end of the horizontal section 3271 away from the vertical section 3272 is connected to the main pipe 31. The refrigerant outlet 32a is located at the end of the vertical section 3272 away from the horizontal section 3271.

[0112] The plurality of branch pipes 32 also includes a sixth branch pipe 328, which is connected to the horizontal section 3271 of the fifth branch pipe 327. In the direction perpendicular to the first end plate 2a, the sixth branch pipe 328 is staggered with the main pipe 31. The main pipe 31 is located between the sixth branch pipe 328 and the fourth branch pipe 326 in the direction parallel to the first end plate 2a. A clearance portion 321 is formed between the sixth branch pipe 328 and the fourth branch pipe 326. The distance N between the axis of the sixth branch pipe 328 and the axis of the main pipe 31 is 5mm to 50mm.

[0113] It should be noted that the direction perpendicular to the first end plate 2a is... Figure 11 The direction from top to bottom or bottom to top, parallel to the first end plate 2a, is... Figure 11 The direction from left to right or from right to left.

[0114] It should be noted that the distance between the axis of the sixth branch pipe 328 and the axis of the main flow pipe 31 indicates the degree to which the sixth branch pipe 328 and the main flow pipe 31 are offset in a direction perpendicular to the first end plate 2a.

[0115] If the distance N between the axis of the sixth branch pipe 328 and the axis of the main pipe 31 is less than 5mm, it means that the sixth branch pipe 328 and the main pipe 31 are slightly misaligned in the direction perpendicular to the first end plate 2a, and the sixth branch pipe 328 cannot effectively avoid the bend section 212.

[0116] If the distance N between the axis of the sixth branch pipe 328 and the axis of the main pipe 31 is greater than 50mm, it means that the sixth branch pipe 328 and the main pipe 31 are significantly misaligned in the direction perpendicular to the first end plate 2a, which will result in additional space occupation and is not conducive to the compact layout inside the housing 1.

[0117] In this embodiment, the staggered arrangement of the sixth branch pipe 328 and the main pipe 31 allows the fluid distributor 3 to be arranged more flexibly throughout the space of the first end plate 2a, avoiding interference with other components (such as the bend section 212 or other branch pipes 32). The distance N between the axis of the sixth branch pipe 328 and the axis of the main pipe 31 is 5mm to 50mm. This not only provides more flexible space for the connection between the fluid distributor 3 and the inlet section 213 of the heat exchange tube 21 during installation, reducing installation difficulty, but also provides a reasonable offset range for the sixth branch pipe 328. This ensures that the sixth branch pipe 328 avoids interference areas without excessive offset, thus improving the utilization rate of the internal space of the entire casing 1 and making the structure more compact.

[0118] It should be noted that, as Figure 11 As shown, in this embodiment, the avoidance section 321, the fourth branch pipe 326, and the sixth branch pipe 328 form an avoidance space M to avoid the bend section 212 of the heat exchange pipe 21.

[0119] In some embodiments, such as Figure 8 As shown, the diameter of the main flow pipe 31 is larger than the diameter of each branch pipe 32.

[0120] As the main channel for refrigerant, the larger diameter of the main channel 31 effectively reduces the refrigerant velocity within it. According to fluid mechanics principles, reduced velocity significantly decreases flow resistance, thereby reducing pressure loss throughout the system caused by refrigerant flow. Furthermore, the lower flow resistance before the refrigerant enters the branch pipes 32 ensures sufficient flow and pressure for distribution to each branch pipe 32. Just as a wide main road can accommodate more traffic, this facilitates the even distribution of refrigerant to each branch pipe 32, preventing insufficient or uneven refrigerant supply due to an excessively small diameter of the main channel 31.

[0121] In some embodiments, such as Figure 8 As shown, the diameter of each branch pipe 32 is the same.

[0122] The diameter of each branch pipe 32 is equal, ensuring consistent refrigerant flow characteristics across all branch pipes 32. This helps guarantee that parameters such as refrigerant velocity and flow rate are essentially the same in each branch pipe 32, thereby achieving uniform refrigerant distribution. This ensures that each heat exchanger tube 21 receives the same and stable refrigerant supply, improving the uniformity and efficiency of heat exchange. It also prevents the overall performance of the outdoor unit 100 from being affected by excessively high or low refrigerant flow rates in some heat exchanger tubes 21 due to differences in the diameter of the branch pipes 32.

[0123] In this embodiment, the diameter of the main pipe 31 and the branch pipe 32 can be 4mm to 30mm, and the length of the main pipe 31 can be 3mm to 50mm, so as to adapt to heat exchangers 2 of different specifications and layouts.

[0124] In some embodiments, the fluid distributor 3 is integrally formed by a cold extrusion process.

[0125] Cold extrusion is a process that plastically processes metal materials in a cold state. High pressure forces the metal material to flow within a mold, shaping it into the desired form and size. In this embodiment, the fluid distributor 3 is formed using cold extrusion, which allows for precise shaping to the required dimensions. Because the process is performed in a cold state, the material used to make the fluid distributor 3 has good flowability, enabling it to better fill the various parts of the mold, thus reducing material waste and lowering the production cost of the fluid distributor 3. Furthermore, cold extrusion can complete complex forming processes in a single operation, reducing the processing time of multiple steps. Compared to traditional machining, cold extrusion significantly shortens the production cycle and improves the production efficiency of the fluid distributor 3.

[0126] It should be noted that the fluid distributor 3 in this embodiment is made of copper tube by cold extrusion process. In addition to copper, the material of the fluid distributor 3 can also be aluminum alloy, stainless steel or other metal materials. This embodiment does not make specific limitations on this.

[0127] In some embodiments, such as Figure 8 As shown, the fluid distributor 3 also includes a plurality of welding aids 33, which correspond to a plurality of branch pipes 32 respectively. The welding aids 33 are disposed at one end of the branch pipe 32 near the refrigerant outlet 32a. The welding aids 33 are configured to provide a welding position for the automatic welding equipment to weld the branch pipe 32 and the inlet section 213.

[0128] In related technologies, the branch pipes of the branch assembly need to be connected to the inlet section 213 of the heat exchange tube 21 by manual welding. However, the heat exchanger 2 has a large number of inlet sections 213 of multiple heat exchange tubes 21, resulting in a large number of weld points that need to be welded by manual welding, which leads to low assembly efficiency of the branch pipes and heat exchange tubes 21.

[0129] In this embodiment, the welding auxiliary component 33, located at the end of the branch pipe 32 near the refrigerant outlet 32a, provides a clear and fixed welding position for the automatic welding equipment. The automatic welding equipment can quickly identify and position the welding position provided by the welding auxiliary component 33, and perform welding operations continuously and stably according to a preset program and welding position. This automates the welding process, reduces reliance on manual operation, and improves the assembly efficiency of the branch pipe 32 and the inlet section of the heat exchange tube 21. Furthermore, the welding auxiliary component 33 enables the automatic welding equipment to accurately align the connection between the branch pipe 32 and the inlet section 213, avoiding welding deviations caused by inaccurate positioning, improving welding accuracy, ensuring weld quality and reliability, thereby enhancing the connection strength between the branch pipe 32 and the inlet section 213. This allows the fluid distributor 3 to better withstand refrigerant pressure and vibration loads, reducing the risk of weld cracking or loosening during operation, and improving the reliability and safety of the outdoor air conditioning unit 100.

[0130] It should be noted that, in this embodiment, the welding auxiliary component 33 can be a welding ring, clamp, or other component that can provide a welding position for the automatic welding equipment.

[0131] For example, the welding aid 33 is a welding ring. The welding ring can increase the rigidity of the connection between the branch pipe 32 and the inlet section 213, preventing the components from shifting or shaking due to external forces or thermal deformation during the welding process, making the welding process more stable, helping to form a uniform and continuous weld, and improving the welding quality. Furthermore, the welding ring can increase the amount of metal in the welding area between the branch pipe 32 and the inlet section 213 of the heat exchange tube 21, allowing the weld to better fill and connect the branch pipe and the inlet section, thereby enhancing the strength and load-bearing capacity of the weld joint. This enables the fluid distributor to withstand higher pressures and loads during operation, reducing the risk of weld cracking or leakage.

[0132] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. An air conditioner outdoor unit characterized by comprising: include: chassis; A heat exchanger, disposed within the housing, comprises: First end plate; The second end plate is opposite to the first end plate; Multiple sets of heat exchange tubes, wherein the heat exchange tubes include: A straight pipe section is disposed between the first end plate and the second end plate; A bend in the pipe, which connects to two adjacent straight pipe sections and is located outside the first end plate and the second end plate; An inlet section is connected to one end of the straight pipe section and is located outside the first end plate; Multiple fluid distributors for distributing refrigerant to the inlet sections of the multiple sets of heat exchange tubes, each of the fluid distributors comprising: Mainstream pipe, one end of which has a refrigerant inlet; Multiple branch pipes are connected to the end of the main pipe away from the refrigerant inlet, and each branch pipe is provided with a refrigerant outlet. The branch pipe provides refrigerant to the inlet section through the refrigerant outlet. At least one branch pipe forms a clearance section, which is configured to avoid the bend section.

2. The air conditioner outdoor unit according to claim 1, characterized by The plane containing the avoidance part is perpendicular to the first end plate.

3. The air conditioner outdoor unit according to claim 2, characterized by The avoidance part includes: An inclined section, the first end of which is connected to the end of the main pipe away from the refrigerant inlet, and the second end of which is inclined relative to the first end of which is in a direction away from the first end plate; A straight section, the first end of which is connected to the second end of the inclined section, and the straight section extends in a direction parallel to the first end plate; The branch pipe includes: An outlet section, wherein a first end of the outlet section is connected to a second end of the straight section, and a refrigerant outlet is located at the second end of the outlet section, and the second end of the outlet section is connected to the inlet section via the refrigerant outlet; A clearance space is formed between the straight section and the first end plate to avoid the curved section.

4. The air conditioner outdoor unit according to claim 3, characterized by The angle between the axis of the inclined segment and the extension line in the direction perpendicular to the first end plate is 30° to 45°.

5. The air conditioner outdoor unit according to claim 1, characterized by The plane containing the avoidance part is parallel to the first end plate.

6. The air conditioner outdoor unit according to claim 5, characterized by The avoidance part includes: An inclined section, the first end of which is connected to the end of the main pipe away from the refrigerant inlet, and the second end of which is inclined relative to the first end of which is inclined in a direction parallel to the first end plate; A straight section, the first end of which is connected to the second end of the inclined section, and the straight section extends in a direction parallel to the first end plate; The branch pipe includes: An outlet section, wherein a first end of the outlet section is connected to a second end of the straight section, and a refrigerant outlet is located at the second end of the outlet section, and the second end of the outlet section is connected to the inlet section via the refrigerant outlet; The straight section forms a clearance space on its second side in a direction parallel to the first end plate to avoid the bend section.

7. The outdoor unit of the air conditioner according to claim 3 or 6, characterized in that, The length of the straight section is 35mm to 60mm.

8. The outdoor unit of the air conditioner according to claim 3 or 6, characterized in that, The axis of the main tube extends in a direction perpendicular to the first end plate; The plurality of branch pipes include: The first branch pipe is connected to the end of the main pipe away from the refrigerant inlet, and the first branch pipe extends in a direction perpendicular to the first end plate. The second branch pipe is connected to the end of the main pipe away from the refrigerant inlet and is located on one side of the first branch pipe in a direction parallel to the first end plate. The third branch pipe is connected to the end of the main pipe away from the refrigerant inlet and is located in a direction parallel to the first end plate. The third branch pipe is located on the side of the first branch pipe away from the second branch pipe, and the clearance part is provided on the third branch pipe.

9. The outdoor unit of the air conditioner according to claim 1, characterized in that, The axis of the main tube extends in a direction perpendicular to the first end plate; The plurality of branch pipes include: The fourth branch pipe is connected to the end of the main pipe away from the refrigerant inlet; The fifth branch pipe is connected to the end of the main pipe away from the refrigerant inlet and runs parallel to the first end plate. The main pipe is located between the fourth branch pipe and the fifth branch pipe. The fifth branch pipe includes a horizontal section parallel to the first end plate and a vertical section perpendicular to the first end plate. The end of the horizontal section away from the vertical section is connected to the main pipe. The refrigerant outlet is located at the end of the vertical section away from the horizontal section. The sixth branch pipe is connected to the horizontal section of the fifth branch pipe. In the direction perpendicular to the first end plate, the sixth branch pipe is staggered from the main flow pipe. The main flow pipe is located between the sixth branch pipe and the fourth branch pipe in the direction parallel to the first end plate. The sixth branch pipe and the fourth branch pipe form a clearance portion. The distance between the axis of the sixth branch pipe and the axis of the main flow pipe is 5mm to 50mm.

10. The outdoor unit of an air conditioner according to any one of claims 1-6, characterized in that, The fluid distributor also includes: Multiple welding aids are provided, each corresponding to a plurality of branch pipes. The welding aids are disposed at one end of the branch pipe near the refrigerant outlet and are configured to provide a welding position for automatic welding equipment to weld the branch pipe and the inlet section.

Images