Gas-liquid separators and air conditioning systems

Abstract

This utility model discloses a gas-liquid separator and an air conditioning system, relating to the field of air conditioning system technology. The gas-liquid separator includes a centrifugal separation bend, a liquid outlet pipe, and a gas outlet pipe. The gas outlet pipe is connected to the end of the centrifugal separation bend. The centrifugal separation bend has several liquid outlet positions, and the liquid outlet pipe is connected to each liquid outlet position. The extension direction of the end of the liquid outlet pipe closest to the liquid outlet position is close to the tangential direction of the centrifugal separation bend at the corresponding liquid outlet position. The technical solution provided by this utility model simplifies the structure of the gas-liquid separator.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning system technology, and in particular to a gas-liquid separator and an air conditioning system. Background Technology

[0002] With the continuous development of technology, air conditioning systems are being used more and more widely, and the performance requirements for these systems are also becoming increasingly stringent. To improve the performance of air conditioning systems, a gas-liquid separator can be added. This separator is primarily used to effectively separate the gaseous and liquid refrigerants within the system. However, the structure of existing gas-liquid separators is often quite complex. Utility Model Content

[0003] The main purpose of this invention is to propose a gas-liquid separator and an air conditioning system, which aims to simplify the structure of the gas-liquid separator.

[0004] To achieve the above objectives, the gas-liquid separator proposed in this utility model includes:

[0005] The centrifugal separation bend, liquid outlet pipe, and air outlet pipe are provided. The air outlet pipe is connected to the end of the centrifugal separation bend. The centrifugal separation bend is provided with several liquid outlet positions. The liquid outlet pipe is connected to the liquid outlet positions, and the extension direction of the end of the liquid outlet pipe near the liquid outlet position is close to the tangential direction of the centrifugal separation bend at the corresponding liquid outlet position.

[0006] In one embodiment, the bending radius of the centrifugal separation bend is greater than or equal to 15 mm.

[0007] In one embodiment, the plurality of liquid outlets include a first liquid outlet and a second liquid outlet, the centrifugal separation bend includes a first bend section and a second bend section, the first liquid outlet is located between the first bend section and the second bend section, the second liquid outlet is located at the end of the second bend section, and the liquid outlet pipe includes a first liquid outlet pipe section and a second liquid outlet pipe section, the first liquid outlet pipe section is connected to the first liquid outlet, and the second liquid outlet pipe section is connected to the second liquid outlet.

[0008] In one embodiment, the bending radius of the first bend is equal to the bending radius of the second bend; and / or,

[0009] The first bend and the second bend are configured as two arc-shaped pipe sections with opposite protrusion directions.

[0010] In one embodiment, the first outlet pipe section is a straight pipe section, and the extension direction of the end of the first outlet pipe section near the first outlet position is parallel to the tangential direction of the first bend pipe section at the first outlet position; and / or,

[0011] The second outlet pipe section is a curved pipe section, and the extension direction of the end of the second outlet pipe section near the second outlet position is close to the tangent direction of the second curved pipe section at the second outlet position.

[0012] In one embodiment, the outlet pipe further includes an outlet main pipe, which is connected to the end of the first outlet pipe section away from the outlet position and the end of the second outlet pipe section away from the outlet position.

[0013] In one embodiment, the diameter of the inlet end of the centrifugal separation bend is greater than or equal to 6 mm and less than or equal to 9 mm; and / or,

[0014] The diameter of the vent pipe is greater than or equal to 6 mm and less than or equal to 8 mm; and / or,

[0015] The diameter of the outlet pipe is greater than or equal to 6 mm and less than or equal to 8 mm.

[0016] In one embodiment, the diameter of the inlet end of the centrifugal separation bend is 9 mm; and / or,

[0017] The diameter of the vent pipe is 7 mm; and / or,

[0018] The diameter of the outlet pipe is 7 mm.

[0019] In one embodiment, the portion of the vent pipe near the end of the centrifugal separation bend is bent, the bending direction of the vent pipe is the same as that of the centrifugal separation bend, and the bending radius of the vent pipe is smaller than that of the centrifugal separation bend.

[0020] In one embodiment, the vent pipe is equipped with a one-way valve.

[0021] This utility model also proposes an air conditioning system, including a refrigerant circuit, wherein the compressor, four-way valve, first outdoor heat exchanger, second outdoor heat exchanger, expansion valve, indoor heat exchanger and the gas-liquid separator as described above can form a corresponding circuit according to requirements.

[0022] The gas-liquid separator is located between the first outdoor heat exchanger and the second outdoor heat exchanger, and the inlet end of the centrifugal separation bend is connected to the first outdoor heat exchanger, while the outlet pipe is connected to the second outdoor heat exchanger.

[0023] In one embodiment, the air conditioning system has a cooling mode, and in the cooling mode, the refrigerant circuit has a first refrigerant circuit;

[0024] The first refrigerant circuit is a closed loop formed by a compressor, a four-way valve, a second outdoor heat exchanger, a gas-liquid separator, a first outdoor heat exchanger, an expansion valve, and an indoor heat exchanger connected in series, and the outlet pipe is blocked.

[0025] In one embodiment, the air conditioning system has a heating mode, and in the heating mode, the refrigerant circuit has a second refrigerant circuit;

[0026] The second refrigerant circuit is a closed loop formed by a compressor, a four-way valve, an indoor heat exchanger, an expansion valve, a first outdoor heat exchanger, a gas-liquid separator, and a second outdoor heat exchanger connected in series, and the outlet pipe is connected between the compressor and the second outdoor heat exchanger.

[0027] In one embodiment, the ratio of the heat exchange area of ​​the first outdoor heat exchanger to the sum of the heat exchange areas of the first outdoor heat exchanger and the second outdoor heat exchanger is in the range of 14% to 30%.

[0028] The technical solution of this utility model involves setting a centrifugal separation bend, which provides centrifugal force to the mixed refrigerant flowing through it, thereby separating the liquid and gaseous refrigerants. An outlet pipe connects to the end of the centrifugal separation bend, which has several liquid outlet positions. An outlet pipe is connected to each liquid outlet position, and the extension direction of the end of the outlet pipe closest to the liquid outlet position is close to the tangential direction of the centrifugal separation bend at the corresponding liquid outlet position. This is because the density of the gaseous refrigerant is much smaller than the density of the liquid refrigerant (ρ). g <<ρ □ This design allows the mixed refrigerant within the centrifugal separation bend to be separated into gaseous and liquid forms. Under the influence of centrifugal force (and gravity), the liquid refrigerant is thrown tangentially towards the liquid outlet pipe, while the less dense refrigerant continues to flow along the bend and exits through the gas outlet pipe. In other words, this design achieves gas-liquid separation of the mixed refrigerant using a simple centrifugal separation bend, simplifying the structure of the gas-liquid separator. Furthermore, this tubular gas-liquid separator reduces its overall volume, thus minimizing the space it occupies. Attached Figure Description

[0029] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0030] Figure 1A schematic diagram of an angle structure of an embodiment of the gas-liquid separator provided by this utility model;

[0031] Figure 2 for Figure 1 Another structural diagram of the gas-liquid separator;

[0032] Figure 3 A schematic diagram of the air conditioning system in cooling mode in one embodiment of the air conditioning system provided by this utility model;

[0033] Figure 4 for Figure 3 A schematic diagram of the air conditioning system in cooling mode.

[0034] Explanation of icon numbers:

[0035] 1. Gas-liquid separator; 11. Centrifugal separation bend; 111. Liquid outlet; 112. First liquid outlet; 113. Second liquid outlet; 114. First bend section; 115. Second bend section; 116. Inlet end; 12. Liquid outlet pipe; 121. First liquid outlet pipe section; 122. Second liquid outlet pipe section; 123. Main liquid outlet pipe; 13. Gas outlet pipe; 131. Check valve; 2. Compressor; 3. Four-way valve; 4. First outdoor heat exchanger; 5. Second outdoor heat exchanger; 6. Expansion valve; 7. Indoor heat exchanger.

[0036] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0037] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0038] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0039] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0040] This utility model proposes a gas-liquid separator 1 for use in an air conditioning system, which can improve the performance of the air conditioning system.

[0041] Please see Figure 1 and Figure 2 In one embodiment of this utility model, the gas-liquid separator 1 includes:

[0042] The centrifugal separation bend 11, the liquid outlet pipe 12, and the air outlet pipe 13 are provided. The air outlet pipe 13 is connected to the end of the centrifugal separation bend 11. The centrifugal separation bend 11 is provided with several liquid outlet positions 111. The liquid outlet pipe 12 is connected to the liquid outlet position 111, and the extension direction of the end of the liquid outlet pipe 12 near the liquid outlet position 111 is close to the tangential direction of the centrifugal separation bend 11 at the corresponding liquid outlet position 111.

[0043] Specifically, the centrifugal separation bend 11 can be arranged in a spiral or near-spiral shape, thereby providing centrifugal force to the mixed refrigerant flowing through it, thus separating the liquid and gaseous refrigerant. The centrifugal separation bend 11 has a starting end and an ending end. The starting end allows refrigerant to enter, and the ending end connects to the gas outlet pipe 13 to discharge gaseous refrigerant. The separation bend has several liquid outlet positions 111, and a liquid outlet pipe 12 is connected to each liquid outlet position 111. The extension direction of the end of the liquid outlet pipe 12 near the liquid outlet position 111 is close to the tangential direction of the centrifugal separation bend 11 at the corresponding liquid outlet position 111. This is because the density of the gaseous refrigerant is much smaller than that of the liquid refrigerant (ρ). g <<ρ □This allows the mixed refrigerant within the centrifugal separation bend 11 to be separated by centrifugal force (and gravity). The liquid refrigerant is thrown tangentially towards the liquid outlet pipe 12, while the less dense gaseous refrigerant continues to flow along the centrifugal separation bend 11 and is finally discharged through the gas outlet pipe 13, thus achieving the separation of gaseous and liquid refrigerant. In other words, this solution achieves gas-liquid separation of the mixed refrigerant using a simple centrifugal separation bend 11, simplifying the structure of the gas-liquid separator 1. Furthermore, this tubular gas-liquid separator 1 reduces its overall volume, thereby reducing the space it occupies.

[0044] It should be noted that the extension direction of the end of the outlet pipe 12 near the outlet position 111 is close to the tangent direction of the centrifugal separation bend 11 at the corresponding outlet position 111. That is, the extension direction of the end of the outlet pipe 12 near the outlet position 111 tends to the tangent direction of the centrifugal separation bend 11 at the corresponding outlet position 111. For example, the angle between the extension direction of the end of the outlet pipe 12 near the outlet position 111 and the tangent direction of the centrifugal separation bend 11 at the corresponding outlet position 111 is less than or equal to 20°; or, the extension direction of the end of the outlet pipe 12 near the outlet position 111 is parallel to the tangent direction of the centrifugal separation bend 11 at the corresponding outlet position 111. The centrifugal separation bend 11 can have only one liquid outlet 111, which can be located at the end of the centrifugal separation bend 11, that is, both the gas outlet pipe 13 and the liquid outlet pipe 12 are connected to the end of the centrifugal separation bend 11; or it can have multiple liquid outlets 111, which can be arranged at intervals along the axial direction of the centrifugal separation bend 11, that is, the gas-liquid separator 1 adopts a multi-stage separation method to achieve gas-liquid separation, so as to improve the gas-liquid separation effect.

[0045] To ensure the gas-liquid separation effect of the gas-liquid separator 1, in one embodiment, the bending radius of the centrifugal separation bend 11 is greater than or equal to 15 mm. Let the bending radius of the centrifugal separation bend 11 be R1, where R1 ≥ 15 mm. If R1 < 15 mm, the bending radius of the centrifugal separation bend 11 is too small, and the flow path of the mixed refrigerant within the centrifugal separation bend 11 may change drastically, leading to greater local resistance loss, excessive kinetic energy loss, and a significant reduction in the flow velocity of the mixed refrigerant. Furthermore, if the bending radius of the centrifugal separation bend 11 is too small, a flow separation zone (low-pressure vortex zone) may easily appear on the outside of the centrifugal separation bend 11, causing enhanced turbulence pulsation, resulting in a chaotic gas-liquid interface, hindering the stable coalescence and sedimentation of the liquid refrigerant, and affecting the gas-liquid separation effect. Therefore, controlling the bending radius of the centrifugal separation bend 11 to be no less than 15 mm ensures centrifugal force and gas-liquid separation effect. Optionally, the bending radius of the centrifugal separation bend 11 can be 15mm, 16mm, 17mm, 18mm, 19mm, 20mm, 22mm, 24mm, 25mm, 30mm, etc. However, the bending radius of the centrifugal separation bend 11 should not be too large. On the one hand, the installation space in the air conditioning system is limited, and on the other hand, an excessively large bending radius will further reduce the centrifugal force of the centrifugal separation bend 11.

[0046] Please refer to it again. Figure 1 and Figure 2In an embodiment of this utility model, a plurality of liquid outlets 111 include a first liquid outlet 112 and a second liquid outlet 113. The centrifugal separation bend 11 includes a first bend section 114 and a second bend section 115. The first liquid outlet 112 is located between the first bend section 114 and the second bend section 115, and the second liquid outlet 113 is located at the end of the second bend section 115. The liquid outlet pipe 12 includes a first liquid outlet pipe section 121 and a second liquid outlet pipe section 122. The first liquid outlet pipe section 121 is connected to the first liquid outlet 112, and the second liquid outlet pipe section 122 is connected to the second liquid outlet 113. Specifically, the centrifugal separation bend 11 has a two-stage gas-liquid separation function. Therefore, the centrifugal separation bend 11 is divided into two bend sections connected end to end, namely the first bend section 114 and the second bend section 115. The first liquid outlet 112 is located at the end of the first bend section 114. The second bend section 115 and the first liquid outlet section 121 are both connected to the first bend section 114 at the first liquid outlet 112. The second liquid outlet 113 is located at the end of the second bend section 115. The gas outlet pipe 13 and the second liquid outlet section 122 are both connected to the second bend section 115 at the second liquid outlet 113. Therefore, the mixed refrigerant can enter the first bend section 114 through the inlet end 116 of the centrifugal separation bend 11. Due to the bend of the first bend section 114, centrifugal force is generated. Under the action of centrifugal force (and gravity), the liquid refrigerant is thrown towards the first liquid outlet section 121 along the tangent of the first bend section 114, while the less dense gaseous refrigerant continues to flow towards the second bend section 115, thus achieving the first separation of gaseous and liquid refrigerant. Then, due to the bend of the second bend section 115, centrifugal force is generated. Under the action of centrifugal force (and gravity), the liquid refrigerant is thrown towards the second liquid outlet section 122 along the tangent of the second bend section 115, while the less dense gaseous refrigerant is discharged through the gas outlet pipe 13, thus achieving the second separation of gaseous and liquid refrigerant. This allows as much liquid refrigerant as possible to be separated, thereby improving the gas-liquid separation effect.

[0047] Furthermore, the first bend section 114 and the second bend section 115 are configured as two arc-shaped pipe sections with opposite protruding directions. For example, the first bend section 114 is an upwardly protruding arc-shaped pipe section, and the second bend section 115 is a downwardly protruding arc-shaped pipe section, thus making the first bend section 114 and the second bend section 115 approximately circular or elliptical in shape. The first bend section 114 and the second bend section 115 can be set at an angle, making the centrifugal separation bend 11 approximately spiral-shaped. Of course, in other embodiments, the first bend section 114 can also be a downwardly protruding arc-shaped pipe section, and the second bend section 115 can be an upwardly protruding arc-shaped pipe section. The vertical direction mentioned here refers to the vertical direction of the air conditioner when the gas-liquid separator 1 is installed vertically; of course, the gas-liquid separator 1 can also be installed horizontally inside the air conditioner.

[0048] The first bend section 114, the second bend section 115, and the first liquid outlet section 121 can be connected by a tee pipe, which can be configured as a Y-type tee pipe to ensure gas-liquid separation effect. The second bend section 115, the gas outlet pipe 13, and the second liquid outlet section 122 can be connected by a Y-type tee pipe.

[0049] Optionally, the bending radius of the first bend section 114 is equal to the bending radius of the second bend section 115. Of course, in other embodiments, the bending radius of the first bend section 114 may also be greater than the bending radius of the second bend section 115; or, the bending radius of the first bend section 114 may be less than the bending radius of the second bend section 115.

[0050] In one embodiment, the liquid outlet pipe 12 further includes a main liquid outlet pipe 123, which is connected to the end of the first liquid outlet pipe section 121 away from the liquid outlet position 111 and the end of the second liquid outlet pipe section 122 away from the liquid outlet position 111. Specifically, the ends of the first liquid outlet pipe section 121 and the second liquid outlet pipe section 122 away from the liquid outlet position 111 are both connected to the main liquid outlet pipe 123 via Y-shaped tee pipes, thereby realizing the convergence of liquid refrigerant and facilitating the connection of the liquid outlet pipe 12 with external equipment.

[0051] Furthermore, since the extension direction of the first bend section 114 is from top to bottom (forming an upwardly convex arc-shaped pipe section), when the mixed refrigerant flows to the first liquid outlet 112, centrifugal force and gravity can be used to throw the liquid refrigerant into the first liquid outlet pipe section 121. Therefore, in order to further increase the liquid output at the first liquid outlet 112, the first liquid outlet pipe section 121 is a straight pipe section, and the extension direction of the end of the first liquid outlet pipe section 121 near the first liquid outlet 112 is parallel to the tangent direction of the first bend section 114 at the first liquid outlet 112. That is, the first liquid outlet pipe section 121 extends downward as a whole, so the connection position between the main liquid outlet pipe 123 and the first liquid outlet pipe 12 is located below the first liquid outlet 112. Then, the second bend section 115 extends in a downward-to-upward direction (forming a downward-protruding arc-shaped pipe section). Therefore, at the second liquid outlet 113, the mixed refrigerant is thrown upward to displace the liquid refrigerant into the second liquid outlet pipe section 122. Since the second liquid outlet pipe section 122 extends upward and then needs to extend downward to connect to the liquid outlet main pipe 123, the second liquid outlet pipe section 122 is a bend section. The extension direction of the end of the second liquid outlet pipe section 122 near the second liquid outlet 113 is close to the tangent direction of the second bend section 115 at the second liquid outlet 113. This allows the second liquid outlet pipe section 122 to smoothly transition to the connection position of the first liquid outlet pipe section 121 and the liquid outlet main pipe 123, so as to simultaneously take into account the liquid output at the second liquid outlet 113 and the overall volume of the gas-liquid separator 1, and at the same time help to control the flow rate of the liquid refrigerant in the liquid outlet pipe 12. Optionally, the extension direction of the second outlet pipe section 122 near the second outlet position 113 is parallel to the tangential direction of the second bend pipe section 115 at the second outlet position 113.

[0052] In the embodiments of this utility model, the diameter D1 of the inlet end 116 of the centrifugal separation bend 11 is greater than or equal to 6 mm and less than or equal to 9 mm; the diameter D2 of the outlet pipe 13 is greater than or equal to 6 mm and less than or equal to 8 mm; and the diameter D3 of the outlet pipe 12 is greater than or equal to 6 mm and less than or equal to 8 mm. That is, the diameter of the inlet end 116 of the centrifugal separation bend 11 is greater than or equal to the diameter of the outlet pipe 13 and the diameter of the liquid outlet pipe 12, respectively. Since the refrigerant flowing into the centrifugal separation bend 11 is a mixed state, while the refrigerant flowing out from the outlet pipe 13 and the liquid outlet pipe 12 is the phase-separated gaseous and liquid refrigerant, the volume of the gaseous and liquid refrigerant is smaller than that of the mixed state. Therefore, controlling the diameter of the inlet end 116 of the centrifugal separation bend 11 to be greater than or equal to the diameter of the outlet pipe 13 and the diameter of the liquid outlet pipe 12 can reduce the sudden drop in flow velocity caused by the decrease in volume and increase in pipe diameter after phase separation of the mixed refrigerant, thus helping to ensure the outflow rate of the gaseous and liquid refrigerant. The diameters of the outlet pipe 13 and the liquid outlet pipe 12 can be equal or unequal.

[0053] Optionally, the diameter D1 of the inlet end 116 of the centrifugal separation bend 11 can be 6mm, 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, etc.; the diameter D2 of the outlet pipe 13 can be 6mm, 6.5mm, 7mm, 7.5mm, 8mm, etc.; and the diameter D3 of the liquid outlet pipe 12 can be 6mm, 6.5mm, 7mm, 7.5mm, 8mm, etc. Of course, in other embodiments, the diameter of the inlet end 116 of the centrifugal separation bend 11 can also be less than 6mm or greater than 9mm. Designers can adjust the diameter of the inlet end 116 of the centrifugal separation bend 11 according to the bending radius of the centrifugal separation bend 11 to achieve a better separation effect; the diameter of the outlet pipe 13 can also be less than 6mm or greater than 8mm; and the diameter of the liquid outlet pipe 12 can also be less than 6mm or greater than 8mm. The diameter of the outlet pipe 12 is greater than or equal to 6 mm and less than or equal to 8 mm. That is, the diameters of the first outlet pipe section 121, the second outlet pipe section 122, and the main outlet pipe 123 are all greater than or equal to 6 mm and less than or equal to 8 mm. However, the diameters of the first outlet pipe section 121, the second outlet pipe section 122, and the main outlet pipe 123 can be equal or unequal.

[0054] In this embodiment of the invention, the exhaust pipe 13 is equipped with a one-way valve 131. Specifically, the operator can control the operation of the gas-liquid separator 1 by controlling the opening and closing of the one-way valve 131. Furthermore, the presence of the one-way valve 131 reduces the possibility of gaseous refrigerant backflow during exhaust, which could cause airflow turbulence within the gas-liquid separator 1, thus ensuring the gas-liquid separation effect of the gas-liquid separator 1.

[0055] This utility model also proposes an air conditioning system, which includes a refrigerant circuit, a compressor 2, a four-way valve 3, a first outdoor heat exchanger 4, a second outdoor heat exchanger 5, an expansion valve 6, an indoor heat exchanger 7, and a gas-liquid separator 1. The specific structure of the gas-liquid separator 1 is as described in the above embodiments. Since this air conditioning system adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here. The compressor 2, four-way valve 3, first outdoor heat exchanger 4, second outdoor heat exchanger 5, expansion valve 6, indoor heat exchanger 7, and the gas-liquid separator 1 in the refrigerant circuit can form corresponding circuits according to requirements.

[0056] Specifically, compressor 2, four-way valve 3, first outdoor heat exchanger 4, second outdoor heat exchanger 5, expansion valve 6, indoor heat exchanger 7, and gas-liquid separator 1 are connected to form the refrigerant circuit of the air conditioning system. The air conditioning system controls the connection between different components through the four-way valve 3 and changes the flow direction of the refrigerant in the refrigerant circuit, thereby switching between different operating modes. Furthermore, the air conditioning system has two outdoor heat exchangers, allowing the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5 to divide the refrigerant circuit of the outdoor unit into multiple branches, thus collectively improving the performance of the air conditioning system.

[0057] The gas-liquid separator 1 is located between the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5. The inlet end 116 of the centrifugal separation bend 11 is connected to the first outdoor heat exchanger 4, and the outlet pipe 12 is connected to the second outdoor heat exchanger 5. That is, the gas-liquid separator 1 can control the dryness of the refrigerant system flowing into the second outdoor heat exchanger 5, thereby controlling the refrigerant flow rate and the heat transfer coefficient of the refrigerant circuit at the second outdoor heat exchanger 5.

[0058] In one embodiment, see Figure 3 The air conditioning system has a heating mode. In the heating mode, the refrigerant circuit has a second refrigerant circuit. The second refrigerant circuit is a closed loop formed by the compressor 2, four-way valve 3, indoor heat exchanger 7, expansion valve 6, first outdoor heat exchanger 4, gas-liquid separator 1, and second outdoor heat exchanger 5 connected in series. The outlet pipe 13 is connected between the compressor 2 and the second outdoor heat exchanger 5.

[0059] Specifically, in heating mode, the refrigerant is compressed by compressor 2, increasing its temperature and pressure. The refrigerant then flows into indoor heat exchanger 7, where it is cooled and forms high-pressure condensate. During condensation, the refrigerant releases heat, thus raising the indoor temperature. Simultaneously, the refrigerant's temperature and pressure decrease. After condensation, the refrigerant enters expansion valve 6 for expansion. During expansion, the refrigerant pressure drops sharply, but the temperature remains relatively constant. Then, as the refrigerant continues to flow into the first outdoor heat exchanger 4, at the evaporation inlet, due to the low dryness of the mixed refrigerant and its low flow velocity, the heat transfer coefficient within the refrigerant circuit dominates. Therefore, the refrigerant absorbs external heat, generating low-temperature, low-pressure evaporating gas. As the refrigerant continues to flow, its dryness gradually increases. If the gas-liquid separator 1 is not installed, and the refrigerant continues to flow into the second outdoor heat exchanger 5, the average flow velocity within the refrigerant circuit increases with the increase in dryness, corresponding to an increase in the heat transfer coefficient of the wall surface. When it enters the mist flow stage, the shear force of the high-speed airflow tears apart the liquid film on the wall surface, causing a sharp drop in the heat transfer coefficient and a sharp decrease in the refrigerant's heat transfer performance. This results in a reduction in the overall heating capacity of the air conditioning system, a decrease in heating efficiency, and an impact on the overall performance of the air conditioning system.

[0060] Therefore, in this scheme, by setting up a gas-liquid separator 1, after the refrigerant flows out of the first outdoor heat exchanger 4, it flows in through the inlet end 116 of the centrifugal separation bend 11. When the mixed refrigerant enters the bend through the centrifugal separation bend 11, it will be subjected to gravity and centrifugal force in the bend. Furthermore, since the density of the gaseous refrigerant is much smaller than the density of the liquid refrigerant (ρ... g The force of <<ρ1) causes the denser liquid refrigerant to be thrown towards the liquid outlet pipe 12, while the less dense gaseous refrigerant flows into the compressor 2 in advance for the next round of operation. This reduces the dryness of the refrigerant entering the second outdoor heat exchanger 5, thus delaying the time for the refrigerant to enter the mist flow stage. As a result, the refrigerant maintains a state with a better heat transfer coefficient when flowing through the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5, thereby improving the performance of the air conditioning system. According to the whole unit test results, by setting up the gas-liquid separator 1, its heating capacity can be increased by 2.23%, while the pressure loss of the air conditioning system can be reduced by 28.31%.

[0061] Furthermore, in the heating mode of the air conditioning system, this evaporation process is an accelerated process, and its pressure drop is generally several times that of the condensation process. Excessive pressure drop will reduce the average heat transfer temperature difference in the evaporation process. In order to improve the pressure drop, this solution sets up a first outdoor heat exchanger 4 and a second outdoor heat exchanger 5, thereby dividing the evaporation process into multiple paths, which helps to solve the pressure drop and frosting problems and improve the overall working performance of the outdoor evaporator.

[0062] For further details, please refer to [link / reference]. Figure 4 The air conditioning system has a cooling mode. In the cooling mode, the refrigerant circuit has a first refrigerant circuit. The first refrigerant circuit is a closed loop formed by the compressor 2, four-way valve 3, second outdoor heat exchanger 5, gas-liquid separator 1, first outdoor heat exchanger 4, expansion valve 6, and indoor heat exchanger 7 connected in series, and the outlet pipe 13 is blocked.

[0063] Specifically, in cooling mode, the refrigerant is compressed by compressor 2, increasing its temperature and pressure. The refrigerant then flows to the second outdoor heat exchanger 5, where it is cooled and forms a high-pressure condensate. During condensation, the refrigerant releases heat, thus dissipating it outdoors. Simultaneously, the refrigerant's temperature and pressure decrease, making this second heat exchanger similar to a subcooling pipe. Its purpose is to further cool the condensed liquid refrigerant below its saturation temperature, providing further subcooling to the outdoor heat exchanger; in other words, this second heat exchanger undertakes the primary condensation function. Afterward, the refrigerant flows to gas-liquid separator 1. At this point, the one-way valve 131 closes, and gas-liquid separator 1 no longer performs gas-liquid separation. However, it still acts as a liquid receiver, storing the refrigerant, reducing the amount of refrigerant circulating in the air conditioning system, and thus improving the system's energy efficiency.

[0064] The refrigerant then continues to flow to the first outdoor heat exchanger 4, further dissipating heat outdoors. After the condensation process, the refrigerant enters the expansion valve 6 for expansion. During expansion, the refrigerant pressure drops sharply, but the temperature remains essentially constant, forming a low-temperature, low-pressure evaporating gas. After the expansion process, the refrigerant enters the indoor heat exchanger 7 for evaporation, where both the temperature and pressure rise. It then re-enters the compressor to begin the next refrigeration cycle.

[0065] Understandably, in heating mode, the degree to which the outdoor heat exchanger improves performance depends primarily on the capacity of the air conditioning system and the distribution of the refrigerant. Therefore, setting up a first outdoor heat exchanger 4 and a second outdoor heat exchanger 5 reduces the overall pressure drop of the outdoor heat exchanger, thereby reducing the area of ​​the heat transfer degradation zone, improving the uniformity of refrigerant distribution, and ultimately increasing evaporative heat exchange. However, this type of outdoor heat exchanger also reduces the average flow velocity of the refrigerant within the outdoor heat exchanger. That is, when the overall pressure drop of the outdoor heat exchanger is small, the average flow velocity is the main factor limiting its performance. When the pressure drop is large, it leads to a small average heat transfer temperature difference in the evaporation process. Furthermore, excessive pressure drop can also cause frosting in the air conditioning system, thus restricting the performance of the air conditioning system in low-temperature environments. Therefore, reducing the area of ​​the heat transfer degradation zone and increasing the area of ​​the two-phase heat exchange zone, while maintaining a high heat transfer coefficient and reducing the pressure drop of the outdoor heat exchanger, is an important method to improve its performance. Therefore, the heat exchange area ratio of the first and second heat exchangers needs to be rationally designed to ensure that the gas-liquid separator 1 can function better in the air conditioning system.

[0066] In one embodiment, the ratio of the heat exchange area of ​​the first outdoor heat exchanger 4 to the sum of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5 is in the range of 14% to 30%. This controls the ratio of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5, thereby controlling the overall pressure drop of the heat exchangers and maintaining the performance of the outdoor heat exchangers within a relatively optimal range. In this scheme, the performance of the air conditioning system is characterized by detecting key parameters such as rated cooling capacity, EER (Energy Efficiency Ratio), rated heating capacity, and COP (Coefficient of Performance) of the air conditioning system with different ratios of the heat exchange areas of the first outdoor heat exchanger 4 and the sum of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5. EER is mainly used to characterize the energy consumption in the air conditioning mode, and COP is also mainly used to characterize the energy consumption in the air conditioning mode. To make the detection more intuitive, this scheme provides relevant parameters for two models of air conditioning systems. By comparing these parameters, the air conditioning system with the optimal ratio can be selected more intuitively. In Model 1, the ratio of the heat exchange area of ​​the first outdoor heat exchanger 4 to the sum of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5 is a first preset ratio. Under this first preset ratio, the rated cooling capacity is 3547, the EER is 3.80, the rated heating capacity is 5307, and the COP is 3.61. In Model 2, the ratio of the heat exchange area of ​​the first outdoor heat exchanger 4 to the sum of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5 is a second preset ratio. Under this second preset ratio, the rated cooling capacity is 3499, the EER is 3.80, the rated heating capacity is 5147, and the COP is 3.54. The following table is obtained by comparing air conditioning systems with different heat exchange area ratios:

[0067] Optimization table for different heat exchange area ratios of outdoor heat exchangers

[0068] According to the table above, users can select an outdoor heat exchanger with a suitable heat exchange area ratio based on actual product needs. Considering the four parameters, the overall performance of the air conditioning system is best when the ratio of the heat exchange area of ​​the first outdoor heat exchanger 4 to the sum of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5 is within the range of 14.3%. Optionally, the ratio range of the heat exchange area of ​​the first outdoor heat exchanger 4 to the sum of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5 can be 14%, 14.3%, 16%, 18%, 20%, 22%, 24%, 26%, 28%, 28.3%, 30%, etc. In other embodiments, the ratio range of the heat exchange area of ​​the first outdoor heat exchanger 4 to the sum of the heat exchange areas of the first outdoor heat exchanger 4 and the second outdoor heat exchanger 5 can also be less than 14% or greater than 30%.

[0069] The above are merely exemplary embodiments of this utility model and are not intended to limit the scope of this utility model. Any equivalent structural transformations made based on the technical concept of this utility model and the contents of this utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the protection scope of this utility model.

Claims

1. A gas-liquid separator, characterized in that, include: The centrifugal separation bend, liquid outlet pipe, and air outlet pipe are provided. The air outlet pipe is connected to the end of the centrifugal separation bend. The centrifugal separation bend is provided with several liquid outlet positions. The liquid outlet pipe is connected to the liquid outlet positions, and the extension direction of the end of the liquid outlet pipe near the liquid outlet position is close to the tangential direction of the centrifugal separation bend at the corresponding liquid outlet position.

2. The gas-liquid separator as described in claim 1, characterized in that, The bending radius of the centrifugal separation bend is greater than or equal to 15 mm.

3. The gas-liquid separator as described in claim 1, characterized in that, The plurality of liquid outlet positions include a first liquid outlet position and a second liquid outlet position. The centrifugal separation bend includes a first bend section and a second bend section. The first liquid outlet position is located between the first bend section and the second bend section, and the second liquid outlet position is located at the end of the second bend section. The liquid outlet pipe includes a first liquid outlet pipe section and a second liquid outlet pipe section. The first liquid outlet pipe section is connected to the first liquid outlet position, and the second liquid outlet pipe section is connected to the second liquid outlet position.

4. The gas-liquid separator as described in claim 3, characterized in that, The bending radius of the first bend is equal to the bending radius of the second bend; and / or, The first bend and the second bend are configured as two arc-shaped pipe sections with opposite protrusion directions.

5. The gas-liquid separator as described in claim 3, characterized in that, The first outlet pipe section is a straight pipe section, and the extension direction of the end of the first outlet pipe section near the first outlet position is parallel to the tangential direction of the first bend pipe section at the first outlet position; and / or, The second outlet pipe section is a curved pipe section, and the extension direction of the end of the second outlet pipe section near the second outlet position is close to the tangent direction of the second curved pipe section at the second outlet position.

6. The gas-liquid separator as described in claim 3, characterized in that, The outlet pipe also includes an outlet main pipe, which is connected to the end of the first outlet pipe section away from the outlet position and the end of the second outlet pipe section away from the outlet position.

7. The gas-liquid separator as described in claim 1, characterized in that, The diameter of the inlet end of the centrifugal separation bend is greater than or equal to 6 mm and less than or equal to 9 mm; and / or, The diameter of the vent pipe is greater than or equal to 6 mm and less than or equal to 8 mm; and / or, The diameter of the outlet pipe is greater than or equal to 6 mm and less than or equal to 8 mm.

8. The gas-liquid separator as described in claim 1, characterized in that, The diameter of the inlet end of the centrifugal separator bend is 9 mm; and / or, The diameter of the vent pipe is 7 mm; and / or, The diameter of the outlet pipe is 7 mm.

9. The gas-liquid separator as described in claim 1, characterized in that, The portion of the vent pipe near the end of the centrifugal separation bend is bent, the bending direction of the vent pipe is the same as that of the centrifugal separation bend, and the bending radius of the vent pipe is smaller than that of the centrifugal separation bend.

10. The gas-liquid separator according to any one of claims 1 to 9, characterized in that, The air outlet pipe is equipped with a one-way valve.

11. An air conditioning system, characterized in that, Includes a refrigerant circuit, wherein the compressor, four-way valve, first outdoor heat exchanger, second outdoor heat exchanger, expansion valve, indoor heat exchanger, and gas-liquid separator as described in any one of claims 1 to 10 can form a corresponding circuit as required; The gas-liquid separator is located between the first outdoor heat exchanger and the second outdoor heat exchanger, and the inlet end of the centrifugal separation bend is connected to the first outdoor heat exchanger, while the outlet pipe is connected to the second outdoor heat exchanger.

12. The air conditioning system as described in claim 11, characterized in that, The air conditioning system has a cooling mode, and in the cooling mode, the refrigerant circuit has a first refrigerant circuit. The first refrigerant circuit is a closed loop formed by a compressor, a four-way valve, a second outdoor heat exchanger, a gas-liquid separator, a first outdoor heat exchanger, an expansion valve, and an indoor heat exchanger connected in series, and the outlet pipe is blocked.

13. The air conditioning system as described in claim 11, characterized in that, The air conditioning system has a heating mode, and in the heating mode, the refrigerant circuit has a second refrigerant circuit. The second refrigerant circuit is a closed loop formed by a compressor, a four-way valve, an indoor heat exchanger, an expansion valve, a first outdoor heat exchanger, a gas-liquid separator, and a second outdoor heat exchanger connected in series, and the outlet pipe is connected between the compressor and the second outdoor heat exchanger.

14. The air conditioning system as described in claim 11, characterized in that, The ratio of the heat exchange area of ​​the first outdoor heat exchanger to the sum of the heat exchange areas of the first outdoor heat exchanger and the second outdoor heat exchanger is in the range of 14% to 30%.

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