Air conditioner

Abstract

The utility model discloses an air conditioner, and belongs to the technical field of air treatment. The air conditioner comprises an outdoor heat exchanger assembly, and the outdoor heat exchanger assembly comprises a heat exchange pipe set; the supercooling section is connected to the bottom of the heat exchange tube set, the first end of the supercooling section is connected with the liquid collecting end of the heat exchange tube set, and the second end of the supercooling section is connected with the liquid side stop valve; the refrigerant radiator is connected between the supercooling section and the liquid side stop valve in series; the first bypass pipe and the second bypass pipe are respectively connected with the supercooling section in parallel and are used for bypassing a refrigerant; the one-way valve is connected to the second bypass pipe, the one-way valve is communicated when the refrigerant flows to the refrigerant radiator from the heat exchange pipe set, and the one-way valve is cut off when the refrigerant flows to the heat exchange pipe set from the refrigerant radiator; when the air conditioner is used for refrigerating, a refrigerant from the heat exchange tube group is divided into three paths and flows to the refrigerant radiator through the cold section, the first bypass tube and the one-way valve respectively. According to the air conditioner, the pressure loss of the supercooling section can be reduced in the refrigeration cycle, and the condensation risk of the base plate under the outdoor high-temperature and high-humidity working condition is avoided.

Description

Technical Field

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

[0002] In common large-capacity side-discharge outdoor units, a refrigerant radiator is often used near the electrical box. By connecting the radiator to the air conditioner's refrigerant circuit, the refrigerant flowing through the radiator removes heat from the electrical box. The radiator is typically connected to the baseboard within the electrical box. If the refrigerant flowing through the radiator is relatively cool, condensation can occur on the baseboard in high temperature and humidity conditions outdoors.

[0003] In addition, a subcooling section will be set at the bottom of the heat exchanger in the large-capacity side-outlet outdoor unit to prevent ice from forming at the bottom of the heat exchanger.

[0004] As the air conditioning capacity range increases, the length of the subcooling section of the heat exchanger increases significantly and the pressure loss increases. During cooling, the increase in the pressure loss in the subcooling section will cause the temperature of the refrigerant passing through the subcooling section to drop. The refrigerant radiator is located after the subcooling section, and the decrease in the temperature of the refrigerant flowing inside it will cause condensation on the substrate under high temperature and high humidity conditions outdoors. Utility Model Content

[0005] The present application provides an air conditioner that reduces the pressure loss in the supercooling section during a refrigeration cycle, thereby avoiding the risk of condensation on a substrate under outdoor high temperature and high humidity conditions.

[0006] In one aspect of the present application, an air conditioner comprises: an outdoor heat exchanger assembly, the outdoor heat exchanger assembly comprising: a heat exchange tube group; a subcooling section connected to the bottom of the heat exchange tube group, a first end of the subcooling section connected to a liquid collecting end of the heat exchange tube group, and a second end of the subcooling section connected to a liquid-side shut-off valve; a refrigerant radiator connected in series between the subcooling section and the liquid-side shut-off valve; a first bypass pipe and a second bypass pipe, each connected in parallel with the subcooling section for bypassing refrigerant; a one-way valve connected to the second bypass pipe, the one-way valve being connected when refrigerant flows from the outdoor heat exchanger assembly to the refrigerant radiator and being closed when refrigerant flows from the refrigerant radiator to the outdoor heat exchanger assembly;

[0007] When the air conditioner is cooling, the refrigerant from the heat exchange tube group is divided into three paths: one path flows through the cold section to the refrigerant radiator, one path flows through the first bypass pipe to the refrigerant radiator, and one path flows through the second bypass pipe to the refrigerant radiator;

[0008] When the air conditioner is heating, the refrigerant from the refrigerant radiator is divided into two paths, one path flows through the cold section to the heat exchange tube group; the other path flows through the first bypass pipe to the heat exchange tube group.

[0009] In this technical solution, a first bypass pipe and a second bypass pipe are arranged in parallel with the supercooling section, and a one-way valve for controlling the on-off of the pipeline is arranged on the second bypass pipe, so that the second bypass pipe is connected during cooling, and most of the refrigerant flows directly to the refrigerant radiator through the two bypass pipes, which can avoid the reduction of refrigerant temperature due to pressure loss in the supercooling section and the risk of condensation on the substrate under high temperature and high humidity conditions.

[0010] In some embodiments, it also includes: an indoor heat exchanger, one end of which is connected to the gas side stop valve and the other end is connected to the liquid side stop valve; an indoor expansion valve, connected in series between the indoor heat exchanger and the liquid side stop valve; an outdoor expansion valve, connected in series between the refrigerant radiator and the subcooling section; the outdoor expansion valve is in a fully open state when the air conditioner is cooling.

[0011] In this technical solution, the outdoor expansion valve is in a fully open state during cooling, which can avoid the risk of condensation at the refrigerant radiator caused by the refrigerant temperature dropping after throttling by the outdoor expansion valve.

[0012] In some embodiments, the outdoor heat exchanger assembly further includes: a diverter, wherein the diverter end of the diverter is connected to the liquid collecting end of the heat exchange tube group through a capillary tube, and the converging end of the diverter is connected to the subcooling section.

[0013] In this technical solution, when heating, the refrigerant first passes through the subcooling section, and then flows to the heat exchange tube group after capillary throttling, so that the temperature of the subcooling section can be higher than the heat exchange tube group, thereby avoiding the problem of ice forming at the bottom of the outdoor heat exchanger due to the low temperature.

[0014] In some embodiments, the diameter of the second bypass pipe is larger than the diameter of the first bypass pipe, and the diameter of the second bypass pipe is larger than the diameter of the supercooling section.

[0015] In this technical solution, the second bypass pipe has a larger diameter, which can bypass most of the refrigerant during refrigeration, greatly reducing the amount of refrigerant passing through the supercooling section, thereby avoiding the reduction in refrigerant temperature due to large pressure loss in the supercooling section.

[0016] In some embodiments, the diameter of the first bypass pipe is the same as that of the supercooling section, and the length L1 of the first bypass pipe and the length L0 of the supercooling section satisfy: L1 / L0=15%-25%.

[0017] In this technical solution, under these conditions, the diameter and length of the first bypass pipe can reduce the pressure loss of the supercooling section by about 89% to 92%, which can reduce the heating heat loss while ensuring the anti-freezing of the supercooling section.

[0018] In some embodiments, the diameter of the second bypass pipe is 5-6 mm larger than the diameter of the supercooling section, and the length L2 of the second bypass pipe and the length L0 of the supercooling section satisfy: L2 / LO=5%-15%.

[0019] In this technical solution, under this condition, the diameter and length of the second bypass pipe can reduce the pressure loss in the supercooling section by 90% or more, which can better prevent the refrigerant from passing through the supercooling section and causing the temperature to drop further due to pressure loss, resulting in the refrigerant temperature at the refrigerant radiator being too low and the risk of condensation on the substrate.

[0020] In some embodiments, during heating, the bypass flow rate accounts for 66% to 72%.

[0021] In this technical solution, the bypass flow ratio during heating is within this range, which can reduce the pressure loss of the supercooling section by about 89% to 92%, thereby ensuring the anti-freezing of the supercooling section while reducing the heat loss during heating.

[0022] In some embodiments, during cooling, the bypass flow rate accounts for no less than 90%.

[0023] In this technical solution, the bypass flow rate during cooling is within this range, which can reduce the pressure loss in the supercooling section by 90% or more. This can effectively prevent the refrigerant from passing through the supercooling section and causing the temperature to drop further due to pressure loss, resulting in the refrigerant temperature at the refrigerant radiator being too low and the risk of condensation on the substrate.

[0024] In some embodiments, it further includes: a plate heat exchanger connected in series between the refrigerant radiator and the liquid side stop valve.

[0025] In this technical solution, during cooling, the temperature of the refrigerant rises after passing through the refrigerant radiator, and continues to be supercooled through the plate heat exchanger, which can maximize the capacity of the unit.

[0026] Another aspect of the present application provides an air conditioner, comprising: an outdoor heat exchanger assembly, the outdoor heat exchanger assembly comprising: a heat exchange tube group; a subcooling section connected to the bottom of the heat exchange tube group, a first end of the subcooling section connected to a liquid collecting end of the heat exchange tube group, and a second end of the subcooling section connected to a liquid-side shut-off valve; a refrigerant radiator connected in series between the subcooling section and the liquid-side shut-off valve; a first bypass pipe and a second bypass pipe, each connected in parallel with the subcooling section for bypassing the refrigerant; a control valve connected to the second bypass pipe, the control valve being connected when the refrigerant flows from the outdoor heat exchanger assembly to the refrigerant radiator, and being shut off when the refrigerant flows from the refrigerant radiator to the outdoor heat exchanger assembly;

[0027] When the air conditioner is cooling, the refrigerant from the heat exchange tube group is divided into three paths: one path flows through the cold section to the refrigerant radiator, one path flows through the first bypass pipe to the refrigerant radiator, and one path flows through the second bypass pipe to the refrigerant radiator;

[0028] When the air conditioner is heating, the refrigerant from the refrigerant radiator is divided into two paths, one path flows through the cold section to the heat exchange tube group; the other path flows through the first bypass pipe to the heat exchange tube group.

[0029] In this technical solution, a first bypass pipe and a second bypass pipe are arranged in parallel with the supercooling section, and a control valve for controlling the on / off of the pipeline is arranged on the second bypass pipe, so that the second bypass pipe is connected during cooling, and most of the refrigerant flows directly to the refrigerant radiator through the two bypass pipes, which can avoid the reduction of refrigerant temperature due to pressure loss in the supercooling section and the risk of condensation on the substrate under high temperature and high humidity conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 shows a schematic diagram of a refrigerant cycle of an air conditioner according to some embodiments;

[0031] Figure 2 A partial schematic diagram of a refrigerant cycle of an air conditioner according to some embodiments is shown;

[0032] Figure 3 shows a schematic diagram of the interior of an electrical box of an air conditioner according to some embodiments;

[0033] Figure 4 A partial schematic diagram of a refrigerant cycle of an air conditioner during cooling according to some embodiments is shown;

[0034] Figure 5 A partial schematic diagram of a refrigerant cycle of an air conditioner during heating according to some embodiments is shown;

[0035] Figure 6 A partial schematic diagram of a refrigerant cycle of an air conditioner according to some other embodiments is shown.

[0036] In the above figures, 100, outdoor heat exchanger assembly; 110, heat exchange tube group; 120, subcooling section; 130, gas collecting pipe; 140, liquid collecting pipe group; 141, diverter; 142, capillary tube; 150, first bypass pipe; 160, second bypass pipe; 170, one-way valve; 210, compressor; 220, four-way valve; 230, gas-liquid separator; 241, liquid side stop valve; 242, gas side stop valve; 250, indoor heat exchanger; 260, indoor expansion valve; 270, outdoor expansion valve; 280, refrigerant radiator; 290, plate heat exchanger. DETAILED DESCRIPTION

[0037] In order to make the purpose and implementation of this application clearer, the exemplary implementation of this application will be clearly and completely described below in conjunction with the drawings in the exemplary embodiments of this application. Obviously, the described exemplary embodiments are only part of the embodiments of this application, not all of the embodiments.

[0038] In the description of this application, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application.

[0039] The terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, features specified as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of this application, unless otherwise specified, "plurality" means two or more.

[0040] In the description of this application, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; direct or indirect connections through an intermediate medium; and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on the specific circumstances.

[0041] In this application, the air conditioner 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 the air that has been conditioned and heat exchanged.

[0042] The compressor compresses the low-temperature, low-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 into the surrounding environment through the condensation process.

[0043] The expansion valve expands the high-temperature, high-pressure liquid refrigerant condensed in the condenser to a lower-pressure liquid. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the low-temperature, low-pressure refrigerant gas to the compressor. The evaporator achieves cooling by utilizing the latent heat of evaporation to exchange heat with the material being cooled. Throughout this cycle, the air conditioner regulates the temperature of the indoor space.

[0044] The outdoor unit of the air conditioner refers to a portion of a refrigeration cycle including a compressor and an outdoor heat exchanger, the indoor unit of the air conditioner includes an indoor heat exchanger, and an expansion valve may be provided in the indoor unit or the outdoor unit.

[0045] 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 heating mode, and when the indoor heat exchanger functions as an evaporator, the air conditioner functions as a cooler in cooling mode.

[0046] The outdoor unit and indoor unit of the air conditioner can be an integrated unit or a two-body unit. When the air conditioner is a two-body unit, the outdoor unit is also called an outdoor unit and the indoor unit is also called an indoor unit.

[0047] Reference Figure 1 As shown, the air conditioner according to the embodiment of the present application includes an outdoor unit located in an outdoor space and used to perform heat exchange between a refrigerant and outdoor air; and an indoor unit located in an indoor space and used to perform heat exchange between a refrigerant and indoor air.

[0048] The outdoor unit includes: a compressor 210 for compressing the refrigerant; an outdoor heat exchanger assembly 100 for performing heat exchange between the outdoor air and the refrigerant; a four-way valve 220 for selectively guiding the refrigerant compressed by the compressor 210 to the outdoor heat exchanger assembly 100 or the indoor unit according to the heating mode or the cooling mode; an outdoor expansion valve 270 for decompressing the refrigerant; and a gas-liquid separator 230 for preventing unevaporated liquid refrigerant from flowing to the compressor 210.

[0049] The exhaust end of the compressor 210 is connected to the D pipe of the four-way valve 220, and the C pipe of the four-way valve 220 is connected to the gas collecting end of the outdoor heat exchanger assembly 100; the S pipe of the four-way valve 220 is connected to the input end of the gas-liquid separator 230, and the output end of the gas-liquid separator 230 is connected to the suction end of the compressor 210; the E pipe of the four-way valve 220 is connected to the gas side stop valve 242.

[0050] The liquid collecting end of the outdoor heat exchanger assembly 100 is connected in series to the outdoor expansion valve 270 and then to the liquid side stop valve 241 .

[0051] The indoor unit includes an indoor heat exchanger 250 for performing heat exchange between indoor air and refrigerant. One end of the indoor heat exchanger 250 is connected to a gas-side stop valve 242, and the other end is connected to a liquid-side stop valve 241.

[0052] In some embodiments, the indoor unit may include an indoor expansion valve 260 , which is connected in series between the indoor heat exchanger 250 and the liquid-side stop valve 250 .

[0053] In some embodiments, the air conditioner can be a multi-split unit with multiple indoor units. The indoor heat exchanger 250 of each indoor unit is connected in parallel between the gas side stop valve 242 and the liquid side stop valve 241. The branch where each indoor heat exchanger 250 is located is connected in series with an indoor expansion valve 260.

[0054] The indoor expansion valve 260 is in a throttling state in cooling mode to reduce the pressure of the refrigerant directed to the indoor heat exchanger 150. The outdoor expansion valve 270 is in a throttling state in heating mode to reduce the pressure of the refrigerant directed to the outdoor heat exchanger assembly 100.

[0055] In some embodiments, reference Figure 1 and Figure 2 The outdoor heat exchanger assembly 100 includes a heat exchange tube group 110, which is mainly used for heat exchange between refrigerant and outdoor air.

[0056] The heat exchange tube group 100 may include heat exchange tubes for circulating refrigerant; fins are connected to the heat exchange tubes to increase the surface area of ​​the heat exchange tubes to improve the heat exchange efficiency between the refrigerant and the air.

[0057] The heat exchange tubes have a gas collecting end and a liquid collecting end. The gas collecting end of the heat exchange tube group 110 can be connected to the C tube of the four-way valve 220 through the gas collecting pipe 130.

[0058] The outdoor heat exchanger assembly 100 may include a header pipe group 140. The header pipe group 140 is connected to the liquid collecting end of the heat exchange tube group 110.

[0059] The liquid collecting tube group 140 has a flow divider 141. The flow divider 141 has a converging end and multiple flow dividing ends. The multiple flow dividing ends of the flow divider 141 are respectively connected to the liquid collecting end of the heat exchange tube group 110 through capillary tubes 142.

[0060] In cooling mode, the refrigerant in the heat exchange tube group 110 flows through the capillary tubes 142 to the splitter 141 and flows out of the confluence end of the splitter 141. In heating mode, the refrigerant at the confluence end is divided into multiple paths and flows through the capillary tubes 142 to the heat exchange tube group 110.

[0061] Because the bottom of the outdoor heat exchanger assembly 100 is farther from the outdoor fan, the wind speed and volume passing through the bottom of the outdoor heat exchanger assembly 100 are lower. Therefore, when the air conditioner is operating in heating mode, the bottom of the outdoor heat exchanger assembly 100 absorbs less heat from the wind than the top of the outdoor heat exchanger assembly 100. Condensed water on the outdoor heat exchanger assembly 100 flows to the bottom, making the bottom fins more susceptible to frost and ice.

[0062] In order to prevent ice from forming on the bottom of the outdoor heat exchanger assembly 100 , a supercooling section 120 may be provided in the outdoor heat exchanger assembly 100 .

[0063] The outdoor heat exchanger assembly 100 includes a subcooling section 120. The subcooling section 120 is connected to the bottom end of the heat exchange tube group 110. The two ends of the subcooling section 120 are a first end of the subcooling section 120 and a second end of the subcooling section 120.

[0064] In some embodiments, the first end of the subcooling section 120 is connected to the confluence end of the diverter 141. The second end of the subcooling section 120 is connected in series to the outdoor expansion valve 270 and then to the liquid-side stop valve 241.

[0065] Reference Figure 1 During heating, the compressor 210 discharges high-temperature and high-pressure refrigerant, which flows to the gas-side stop valve 242 through the four-way valve 220; then enters the indoor heat exchanger 250 of the indoor unit, is condensed into a medium-temperature and high-pressure state at the indoor heat exchanger 250, and then returns to the liquid-side stop valve 241 through the indoor expansion valve 260; then passes through the outdoor expansion valve 140 for throttling, pressure reduction, and temperature reduction, and enters the subcooling section 120, and then passes through the capillary tube 142 of the liquid collecting pipe group 140 for secondary throttling and temperature reduction, and enters the heat exchange tube group 110, and flows out from the gas collecting end of the heat exchange tube group 110 to the four-way valve 220; then returns to the gas-liquid separator 230, and returns to the compressor 210 from the gas-liquid separator 230, completing a cycle.

[0066] During the heating process, since the refrigerant flowing out of the supercooling section 120 flows into the heat exchange tube group 110 after secondary throttling of the capillary tube 142, the temperature at the supercooling section 120 is higher than that at the heat exchange tube group 110, thereby increasing the temperature at the bottom of the outdoor heat exchanger assembly 100. Therefore, when the condensed water at the top of the outdoor heat exchanger assembly 110 flows to the bottom of the outdoor heat exchanger assembly 110, it will not freeze due to the excessively low temperature at this location.

[0067] By controlling the opening of the outdoor expansion valve 270 to control the temperature of the refrigerant after throttling through the outdoor expansion valve 270 , ice formation at the bottom of the outdoor heat exchanger assembly 110 can be avoided.

[0068] During cooling, the compressor 210 discharges high-temperature and high-pressure refrigerant, which flows into the heat exchange tube group 110 through the four-way valve 220, is cooled by the heat exchange tube group 110, and flows to the subcooling section 120 after throttling, reducing pressure and cooling through the capillary tube 142, and then returns to the liquid side stop valve 241 through the cold section 120 and the outdoor expansion valve 270; continues to flow into the indoor heat exchanger 250 after throttling, reducing pressure and cooling through the indoor expansion valve 260, evaporates into gas at the indoor heat exchanger 250, and then returns to the gas-liquid separator 230 through the four-way valve 220, and returns to the compressor 210 from the gas-liquid separator 230.

[0069] The subcooling section 120 is connected closely to the bottom of the heat exchange tube group 110 , so that the subcooling section 120 and the heat exchange tube group 110 are connected to form an integral component.

[0070] In some embodiments, in conjunction with reference Figure 3 The air conditioner includes a refrigerant radiator 280. The refrigerant radiator 280 is usually installed in the electrical box 300 of the outdoor unit and dissipates heat from the electrical box 300 through the flowing low-temperature refrigerant.

[0071] The electrical box 300 includes a base plate 310, on which components are electrically connected. The refrigerant radiator 280 is connected to the drive module on the base plate 310 to dissipate heat for the drive module.

[0072] The refrigerant radiator 280 includes a metal block and a refrigerant pipe connected together. The refrigerant pipe is connected to a refrigerant circuit for circulating the refrigerant.

[0073] The refrigerant radiator 280 is connected in series between the liquid-side stop valve 241 and the outdoor expansion valve 270. Specifically, the second end of the subcooling section 120 is connected to the first end of the outdoor expansion valve 270, the second end of the outdoor expansion valve 270 is connected to the first end of the refrigerant radiator 280, and the second end of the refrigerant radiator 280 is connected to the liquid-side stop valve 241.

[0074] With the introduction of G-type heat exchangers, outdoor unit heat exchangers have gradually evolved toward monolithic heat exchangers. Monolithic heat exchangers cover an increasingly wide range of heat exchange capacities, and their lengths are also increasing. The pressure drop in the subcooling section 120 increases significantly with increasing capacity. At this point, the temperature of the refrigerant flowing within the refrigerant radiator 280 is lower than before the increased pressure drop in the subcooling section 120. In high-temperature and high-humidity outdoor conditions, the risk of condensation on the base plate 310 within the electrical box 300 increases.

[0075] To avoid this problem, in an embodiment of the present application, the air conditioner includes a first bypass pipe 150. The first bypass pipe 150 is connected in parallel with the subcooling section 120 and is used to bypass the refrigerant. This can reduce the pressure loss of the subcooling section 120 during cooling, thereby preventing condensation on the base plate 310 caused by the low temperature of the refrigerant flowing from the subcooling section 120 to the refrigerant radiator 280 during cooling.

[0076] In addition, since the heat exchange capacity at the subcooling section 120 is lower than that of the heat exchange tube group 110 during heating, the increase in pressure loss in the subcooling section 120 will also result in a loss of part of the heat exchange capacity of the heat exchanger during heating. Therefore, part of the refrigerant is bypassed through the first bypass pipe 150 and does not pass through the subcooling section 120 but directly enters the collecting pipe group 140, which can ensure that the subcooling section 120 is prevented from freezing during heating while reducing the heat loss during heating.

[0077] If the bypass flow of the first bypass pipe 150 is small, the pressure loss of the supercooling section 120 during cooling is not significantly reduced, which will still cause the temperature of the refrigerant flowing to the refrigerant radiator 280 to be low. If the bypass flow of the first bypass pipe 150 is large, the amount of refrigerant flowing to the supercooling section 120 is greatly reduced, which will affect the anti-freezing function of the supercooling section 120 during heating.

[0078] To avoid this technical problem, in an embodiment of the present application, the air conditioner further includes a second bypass pipe 160. The second bypass pipe 160 is connected in parallel with the supercooling section 120.

[0079] A control valve is provided on the second bypass pipe 160. This control valve can control the flow or disconnection of the second bypass pipe 160. The control valve can be, for example, an expansion valve, a solenoid valve, or a one-way valve 170. Since expansion valves and solenoid valves are more expensive than one-way valves 170 and require software to open or close them, the preferred control valve in this application is a one-way valve 170.

[0080] The one-way valve 170 is connected in the refrigerant flow path in the cooling mode to connect the second bypass pipe 160 , and is not connected in the refrigerant flow path in the heating mode to disconnect the second bypass pipe 160 .

[0081] That is, the one-way valve 170 is connected when the refrigerant flows from the header assembly 140 to the refrigerant radiator 280 , and is not connected when the refrigerant flows from the refrigerant radiator 280 to the header assembly 140 .

[0082] Reference Figure 4 In cooling mode, most of the liquid refrigerant flows directly to the refrigerant radiator 280 through the first bypass pipe 150 and the second bypass pipe 160 after merging from the liquid collecting pipe group 140, greatly reducing the pressure loss caused by the refrigerant flowing through the cold section 120, and preventing the refrigerant temperature at the refrigerant radiator 280 from being too low, which may cause condensation risk at the base plate 310 under outdoor high temperature and high humidity conditions.

[0083] Reference Figure 5 In heating mode, refrigerant flowing through outdoor expansion valve 270 cannot pass through check valve 170 and must return to manifold 140 via first bypass pipe 150 and subcooling section 120. The bypass refrigerant flow rate is kept low during heating to minimize heat loss while maintaining anti-freeze capability.

[0084] The selection and design of the bypass pipe will affect the distribution of the flow in the supercooling section 120. If the resistance is too small, the flow into the supercooling section 120 will be very small, which may cause the supercooling section 120 to freeze; if the resistance is too large, the flow into the supercooling section 120 will be too much, resulting in more heat loss. Therefore, its selection and design is of paramount importance.

[0085] The pressure loss calculation formula is as follows: ΔP=f*(L / D)*(ρ*V 2 / 2). Where ΔP is the pressure loss per unit length, f is the friction coefficient, L is the pipe length, D is the pipe inner diameter, ρ is the fluid density, and V is the flow velocity.

[0086] The bypass ratio ε of the bypass pipe is calculated as follows:

[0087]

[0088] Where ΔP1 is the subcooling section pressure loss, and ΔP2 is the bypass pipe pressure loss. Both pressure loss values ​​are calculated under the same inlet and outlet pressures and flow rates.

[0089] By calculating the pressure loss of the first bypass pipe 150 and the pressure loss of the subcooling section 120 under heating conditions, the flow ratio of the first bypass pipe 150 and the subcooling section 120 under different pipe diameters and pipe lengths can be obtained.

[0090] After determining the diameter and length of the first bypass pipe 150, the first bypass pipe 150 and the second bypass pipe 160 are regarded as an equivalent bypass pipe under refrigeration conditions. By calculating the pressure loss of the equivalent bypass pipe and the pressure loss of the subcooling section 120 under refrigeration conditions respectively, the flow ratio of the equivalent bypass pipe and the subcooling section 120 under different pipe diameters and lengths can be obtained.

[0091] In some embodiments, during heating, the bypass flow rate of the first bypass pipe 150 accounts for approximately 66% to 72%, and the pressure loss reduction rate is approximately 89% to 92%. This can prevent freezing of the subcooling section 120 while reducing heat loss during heating. The bypass flow rate of the first bypass pipe 150 during heating is also the bypass flow rate during heating.

[0092] The bypass flow ratio of the first bypass pipe 150 is the refrigerant flow in the first bypass pipe 150 / (refrigerant flow in the first bypass pipe 150 + refrigerant flow in the supercooling section 120 ).

[0093] In some embodiments, the diameter of the first bypass pipe 150 is the same as that of the subcooling section 120. This simplifies the calculation process by simply calculating the length of the first bypass pipe 150 based on the required pressure drop reduction rate of the subcooling section 120 during heating. Furthermore, selecting the same pipe diameter as the subcooling section 120 reduces the need for different pipe diameters and reduces the burden on material procurement and storage.

[0094] The length L1 of the first bypass pipe 150 and the length L0 of the subcooling section 120 satisfy the following relationship: L1 / LO=15%-25%. Under this condition, the bypass flow rate of the first bypass pipe 150 can be guaranteed to account for approximately 66%-72%.

[0095] In some embodiments, the diameter of the second bypass pipe 160 is larger than that of the first bypass pipe 150 , so that the second bypass pipe 160 can bypass more refrigerant, so that most of the refrigerant can flow to the refrigerant radiator 280 through the second bypass pipe 160 in the cooling mode.

[0096] The diameter of the first bypass pipe 150 is smaller than that of the second bypass pipe 160 , so that less refrigerant flows through the first bypass pipe 150 to the manifold assembly 140 during heating, thereby reducing heat loss during heating and preventing the supercooling section 120 from freezing.

[0097] In some embodiments, the bypass flow accounts for 90% or more during cooling, and the pressure loss reduction rate of the supercooling section 120 is 90% or more. This can better prevent the refrigerant from passing through the supercooling section 120, causing the temperature to drop further due to pressure loss, resulting in the refrigerant temperature at the refrigerant radiator 280 being too low and the risk of condensation on the substrate.

[0098] The bypass flow ratio during cooling is (refrigerant flow in the first bypass pipe 150 + refrigerant flow in the second bypass pipe 160) / (refrigerant flow in the first bypass pipe 150 + refrigerant flow in the second bypass pipe 160 + refrigerant flow in the supercooling section 120).

[0099] In some embodiments, when the diameter of the second bypass pipe 160 is 5 mm to 6 mm larger than the diameter of the subcooling section 120, and the pipe length L2 of the second bypass pipe 160 and the pipe length L0 of the subcooling section satisfy: L2 / LO = 5% to 15%, the bypass flow rate during cooling accounts for 90% or more, and the pressure loss reduction rate of the subcooling section 120 is 90% or more.

[0100] In some embodiments, the air conditioner may include a plate heat exchanger 290 , which is connected in series between the refrigerant radiator 280 and the liquid-side stop valve 241 .

[0101] Plate heat exchanger 290 has a first channel and a second channel. The first channel connects to the main refrigerant circuit, that is, between refrigerant radiator 280 and liquid-side cutoff 241. The second channel connects between refrigerant radiator 280 and compressor 210. An expansion valve is also connected in series between the inlet of the second channel and refrigerant radiator 280.

[0102] In cooling mode, the refrigerant passes through the refrigerant radiator 280 and is divided into two paths. One path passes through the first channel of the plate heat exchanger 290, and the other path flows to the second channel after being throttled and cooled by the expansion valve. The refrigerant in the first channel exchanges heat with the refrigerant in the second channel, thereby making the refrigerant passing through the plate heat exchanger 290 and flowing to the liquid side stop valve 241 supercooled.

[0103] In cooling mode, the refrigerant temperature rises after passing through the refrigerant radiator 280 and continues to exchange heat through the plate heat exchanger 290, which can control the subcooling degree of the refrigerant flowing to the liquid side stop valve 241 and maximize the unit capacity.

[0104] If the positions of the refrigerant radiator 280 and the plate heat exchanger 290 are swapped, although the temperature of the refrigerant flowing into the refrigerant radiator 280 can be prevented from being too low by controlling the subcooling or temperature of the refrigerant flowing out of the plate heat exchanger 290, since the heat absorption of the refrigerant radiator 280 occurs after the heat exchange of the plate heat exchanger 290, this method will affect the subcooling of the external unit refrigerant, and thus affect the unit capacity.

[0105] In some embodiments, the difference from the above embodiments is that: Figure 6 , the location of the outdoor expansion valve 270. The first end of the subcooling section 120 is connected in series with the outdoor expansion valve 270 and then connected to the confluence end of the diverter 141. The second end of the subcooling section 120 is connected to the refrigerant radiator 280.

[0106] Since the outdoor expansion valve 270 is in a fully open state during cooling, whether the outdoor expansion valve 270 is connected before the subcooling section 120 (i.e., between the collecting pipe group 140 and the first end of the subcooling section 120) or after the subcooling section 120 (i.e., between the second end of the subcooling section 120 and the refrigerant radiator 280) will not affect the temperature of the refrigerant.

[0107] During heating, the compressor 210 discharges high-temperature and high-pressure refrigerant, which enters the indoor heat exchanger 250 of the indoor unit through the four-way valve 220 and the gas-side stop valve 241. After condensing in the indoor heat exchanger 250, it flows to the outdoor unit through the indoor expansion valve 260 and the liquid-side stop valve 241; then it passes through the cold section 120 and enters the outdoor expansion valve 270 for throttling, pressure reduction and temperature reduction, and then enters the heat exchange tube group 110, flows out from the gas collecting end of the heat exchange tube group 110, and reaches the four-way valve 220; then it returns to the gas-liquid separator 230, and returns to the compressor 210 from the gas-liquid separator 230.

[0108] During the heating process, since the temperature of the refrigerant in the supercooling section 120 is relatively high, the bottom of the heat exchange tube group 110 will be heated, so that the bottom of the heat exchange tube group 110 will not freeze.

[0109] As can be seen from the above, according to the implementation mode of the present application, by connecting the first bypass pipe 150 and the second bypass pipe 160 in parallel in the supercooling section 120, and providing a control valve for controlling the on-off of the pipeline on the second bypass pipe 160, the second bypass pipe 160 is connected during cooling, and most of the refrigerant flows directly to the refrigerant radiator 280 through the two bypass pipes, which can avoid the reduction of refrigerant temperature due to pressure loss in the supercooling section 120 and the risk of condensation on the substrate under high temperature and high humidity conditions.

[0110] In addition, the second bypass valve 150 is not connected during heating, and relatively less refrigerant flows through the first bypass pipe 150 to the manifold group 140 during cooling, which can reduce heat loss while retaining the heating anti-freezing function.

[0111] In addition, by connecting the first bypass pipe 150 and the second bypass pipe 160 in parallel in the supercooling section 120 and providing a control valve on the second bypass pipe 160 to control the on-off of the pipe, different bypass flow requirements during the cooling / heating cycle can be balanced.

[0112] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them. Although the present application has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some or all of the technical features therein. These modifications or replacements do not deviate the essence of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present application.

[0113] For ease of explanation, the above description has been presented in conjunction with specific embodiments. However, the above exemplary discussion is not intended to be exhaustive or to limit the embodiments to the specific forms disclosed above. Based on the above teachings, various modifications and variations are possible. The above embodiments have been selected and described to better explain the principles and practical applications, thereby enabling those skilled in the art to better utilize the embodiments and various different variations of the embodiments suitable for specific use considerations.

Claims

1. An air conditioner, characterized in that: include: An outdoor heat exchanger assembly, comprising: Heat exchange tube group; a subcooling section connected to the bottom of the heat exchange tube group, a first end of the subcooling section connected to the liquid collecting end of the heat exchange tube group, and a second end of the subcooling section connected to the liquid side stop valve; A refrigerant radiator is connected in series between the subcooling section and the liquid side stop valve; A first bypass pipe and a second bypass pipe are respectively connected in parallel with the subcooling section and are used to bypass the refrigerant; a one-way valve connected to the second bypass pipe, the one-way valve being connected when the refrigerant flows from the heat exchange tube group to the refrigerant radiator, and being closed when the refrigerant flows from the refrigerant radiator to the heat exchange tube group; When the air conditioner is in cooling mode, the refrigerant from the heat exchange tube group is divided into three paths: one path flows to the refrigerant radiator through the subcooling section, one path flows to the refrigerant radiator through the first bypass pipe, and one path flows to the refrigerant radiator through the second bypass pipe; When the air conditioner is heating, the refrigerant from the refrigerant radiator is divided into two paths, one path flows to the heat exchange tube group through the supercooling section; the other path flows to the heat exchange tube group through the first bypass pipe.

2. The air conditioner according to claim 1, characterized in that Also includes: an indoor heat exchanger, one end of which is connected to the gas-side stop valve and the other end of which is connected to the liquid-side stop valve; An indoor expansion valve connected in series between the indoor heat exchanger and the liquid side stop valve; An outdoor expansion valve is connected in series between the refrigerant radiator and the supercooling section; the outdoor expansion valve is in a fully open state when the air conditioner is cooling.

3. The air conditioner according to claim 1, characterized in that The outdoor heat exchanger assembly further comprises: A flow divider, wherein the flow dividing end of the flow divider is connected to the liquid collecting end of the heat exchange tube group through a capillary tube, and the flow converging end of the flow divider is connected to the supercooling section.

4. The air conditioner according to claim 1, wherein: The diameter of the second bypass pipe is larger than that of the first bypass pipe, and the diameter of the second bypass pipe is larger than that of the supercooling section.

5. The air conditioner according to claim 1, characterized in that The diameter of the first bypass pipe is the same as that of the supercooling section, and the length L1 of the first bypass pipe and the length L0 of the supercooling section satisfy the following relationship: 15%≤L1 / L0≤25%.

6. The air conditioner according to claim 1, characterized in that The diameter of the second bypass pipe is 5 mm to 6 mm larger than the diameter of the supercooling section. The length L2 of the second bypass pipe and the length L0 of the supercooling section satisfy the following relationship: 5%≤L2 / L0≤15%.

7. The air conditioner according to claim 1, wherein: During heating, the bypass flow rate accounts for 66% to 72%.

8. The air conditioner according to claim 1, wherein: During cooling, the bypass flow rate shall not be less than 90%.

9. The air conditioner according to claim 1, wherein: Also includes: A plate heat exchanger is connected between the refrigerant radiator and the liquid-side stop valve.

10. An air conditioner, characterized in that: include: An outdoor heat exchanger assembly, comprising: Heat exchange tube group; a subcooling section connected to the bottom of the heat exchange tube group, a first end of the subcooling section connected to the liquid collecting end of the heat exchange tube group, and a second end of the subcooling section connected to the liquid side stop valve; A refrigerant radiator is connected in series between the subcooling section and the liquid side stop valve; A first bypass pipe and a second bypass pipe are respectively connected in parallel with the subcooling section and are used to bypass the refrigerant; a control valve connected to the second bypass pipe, the control valve being connected when the refrigerant flows from the heat exchange tube group to the refrigerant radiator, and being closed when the refrigerant flows from the refrigerant radiator to the heat exchange tube group; When the air conditioner is in cooling mode, the refrigerant from the heat exchange tube group is divided into three paths: one path flows to the refrigerant radiator through the subcooling section, one path flows to the refrigerant radiator through the first bypass pipe, and one path flows to the refrigerant radiator through the second bypass pipe; When the air conditioner is heating, the refrigerant from the refrigerant radiator is divided into two paths, one path flows to the heat exchange tube group through the supercooling section; the other path flows to the heat exchange tube group through the first bypass pipe.

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