Liquid separator structure, compressor and air conditioner

Abstract

The invention discloses a liquid separator structure, a compressor and an air conditioner. The liquid separator structure comprises a shell, an air inlet pipe, an air outlet pipe and a partition plate piece. The partition plate piece is connected to the interior of the shell and divides the interior of the shell into a first cavity and a second cavity in the longitudinal direction, and an air return part is arranged at the upper end of the partition plate piece and used for communicating the first cavity with the second cavity; an inlet of the air inlet pipe is located outside the shell and used for being communicated with an evaporator located outside the liquid separator, and an outlet of the air inlet pipe extends into the shell and is communicated with the first cavity. An inlet of the air outlet pipe is located in the shell and communicates with the second cavity, and an outlet of the air outlet pipe extends out of the shell and is used for communicating with an air inlet of the compressor body. The gravity center of the liquid separator can be reduced, excessive gathering of a gas-liquid mixture at the upper end of the liquid separator is effectively avoided, and the stability and vibration resistance of the liquid separator are enhanced; and the mechanical vibration transmitted from the liquid separator to the compressor is also reduced, so that the operation noise of the whole machine is greatly reduced.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more specifically to a liquid distributor structure, a compressor, and an air conditioner. Background Technology

[0002] In air conditioning technology, the refrigeration compressor is a core component, and its operating efficiency and reliability directly affect the performance and lifespan of the entire system. During actual compressor operation, the refrigerant typically enters the compression chamber as a gas-liquid two-phase mixture. If liquid refrigerant enters the compressor directly, it will not only significantly reduce compression efficiency but also cause severe impacts on moving parts such as pistons and connecting rods due to the incompressibility of liquids (i.e., "liquid slugging"), leading to mechanical damage, increased noise, and a shortened overall lifespan. Therefore, achieving efficient gas-liquid separation before the refrigerant enters the compressor is a key technical challenge to ensure stable compressor operation.

[0003] In existing technologies, the distributor, as the core device for gas-liquid separation, typically employs a design combining a filter assembly with an intermediate straight pipe for gas and oil return. Its working principle is as follows: after the gas and liquid refrigerants enter the distributor through the inlet, they undergo preliminary separation through the filter assembly. The liquid refrigerant settles at the bottom of the distributor due to gravity, while the gaseous refrigerant returns to the compressor through the intermediate straight pipe. However, this traditional structure suffers from the following significant technical drawbacks:

[0004] Center of gravity stability issue: When a large amount of gas-liquid mixture accumulates on the upper part of the distributor filter assembly, the uneven distribution of liquid refrigerant causes the overall center of gravity of the distributor to shift. Especially when the compressor is running at high frequency, the instability of the center of gravity will cause the distributor housing to vibrate, which will then be transmitted to the compressor body through the connecting pipeline, causing the vibration and noise of the whole machine to exceed the standard.

[0005] Flow-induced vibration problem: Traditional straight pipe structures lack effective flow guiding or baffle fixing devices, making it easy for turbulence and eddies to form when the refrigerant flows inside the straight pipe. This unsteady flow field not only increases fluid resistance but also causes low-frequency vibration of the distributor shell. Over long-term operation, this can lead to mechanical failure risks such as loosening of connecting parts and fatigue cracking of welds, while also exacerbating the wear of moving parts inside the compressor.

[0006] Although existing technologies attempt to improve separation performance by optimizing filter materials or increasing straight pipe length, they have not fundamentally solved the coupling problem between turbulent flow field and unstable center of gravity. Therefore, there is an urgent need for a new type of distributor structure that, through innovative flow channel design and dynamic balancing mechanisms, can achieve efficient gas-liquid separation while suppressing mechanical vibration, thereby improving the reliability and energy efficiency of refrigeration compressors. Summary of the Invention

[0007] The purpose of this invention is to overcome the shortcomings of the prior art and provide a liquid distributor structure, a compressor, and an air conditioner.

[0008] To achieve the above objectives, the present invention adopts the following technical solution:

[0009] In a first aspect, embodiments of the present invention provide a liquid dispenser structure, comprising: a housing, an inlet pipe, an outlet pipe, and a partition;

[0010] The partition is connected to the interior of the housing and divides the interior of the housing longitudinally into a first cavity and a second cavity. The upper end of the partition is provided with a return air section, which is used to connect the first cavity and the second cavity.

[0011] The inlet of the air inlet pipe is located outside the housing and is used to connect with the evaporator located outside the distributor. The outlet of the air inlet pipe extends into the housing and communicates with the first cavity.

[0012] The inlet of the outlet pipe is located inside the housing and communicates with the second cavity, while the outlet of the outlet pipe extends outside the housing and is used to communicate with the air inlet of the compressor body.

[0013] In one specific embodiment, the volume of the first cavity is greater than or equal to the volume of the second cavity.

[0014] In one specific embodiment, the return air section is circular in shape and is composed of a plurality of circular holes arranged in a circle.

[0015] In one specific embodiment, the diameter of the return air section is greater than or equal to 6 mm, and the diameter of the circular hole is greater than or equal to 0.3 mm.

[0016] In one specific embodiment, the lower end of the partition is further provided with an oil return hole, which is used to connect the first cavity and the second cavity.

[0017] In one specific embodiment, the diameter of the oil return hole is greater than or equal to 0.5 mm and less than or equal to 1 / 10 of the diameter of the gas return section.

[0018] In one specific embodiment, the cross-section of the partition member is curved or planar.

[0019] In one specific embodiment, the housing is composed of a first part and a second part, the first part being connected to the partition and the air inlet pipe, and the second part being connected to the air outlet pipe.

[0020] The beneficial effects of the distributor structure of the present invention compared with the prior art are as follows: The distributor is connected to the evaporator via an inlet pipe, and the outlet of the inlet pipe is connected to the first chamber. The gas-liquid mixture introduced from the evaporator can directly reach the lower part of the first chamber through the inlet pipe, which lowers the center of gravity of the distributor and effectively avoids excessive accumulation of the gas-liquid mixture at the upper end of the distributor. This solves the problem of equipment instability caused by the upward shift and offset of the center of gravity in traditional designs, and enhances the structural stability and vibration resistance of the distributor and even the entire refrigeration system. Furthermore, the use of a partition to divide the interior of the housing into a first chamber and a second chamber, and the gas flow between the two chambers through a return gas section, not only extends the flow path of the refrigerant fluid and increases the gas-liquid separation efficiency, but also makes the distributor act as a kind of reactive silencer, effectively absorbing and attenuating the vibration energy generated by the fluid flow, reducing the mechanical vibration transmitted from the distributor to the compressor, and thus significantly reducing the overall operating noise of the machine.

[0021] Secondly, embodiments of the present invention provide a compressor, including a compressor body and a liquid distributor structure as described above.

[0022] The compressor of this invention has the following advantages compared with the prior art: By setting a distributor structure and connecting the inlet pipe to the evaporator, with the outlet of the inlet pipe connected to the first cavity, the gas-liquid mixture introduced from the evaporator can directly reach the lower part of the first cavity through the inlet pipe. This lowers the center of gravity of the distributor, effectively preventing excessive accumulation of the gas-liquid mixture at the upper end of the distributor. This solves the problem of unstable equipment operation caused by the upward shift and offset of the center of gravity in traditional designs, and enhances the structural stability and vibration resistance of the distributor and even the entire refrigeration system. In addition, by using a partition to divide the interior of the housing into a first cavity and a second cavity, and realizing gas flow between the two cavities through the return gas section, this design not only extends the flow path of the refrigerant fluid and increases the gas-liquid separation efficiency, but also makes the distributor act as a kind of resistive silencer, effectively absorbing and attenuating the vibration energy generated by the fluid flow, reducing the mechanical vibration transmitted from the distributor to the compressor body, and thus significantly reducing the operating noise of the entire machine.

[0023] Thirdly, embodiments of the present invention provide an air conditioner, including the compressor described above.

[0024] The air conditioner of the present invention has the following advantages compared with the prior art: By setting up a compressor and connecting the intake pipe to the evaporator, with the outlet of the intake pipe connected to the first cavity, the gas-liquid mixture introduced from the evaporator can directly reach the lower part of the first cavity through the intake pipe. This lowers the center of gravity of the distributor, effectively preventing excessive accumulation of the gas-liquid mixture at the upper end of the distributor. This solves the problem of equipment instability caused by the upward shift and offset of the center of gravity in traditional designs, and enhances the structural stability and vibration resistance of the distributor and even the entire refrigeration system. In addition, by using a partition to divide the interior of the casing into a first cavity and a second cavity, and realizing gas flow between the two cavities through the return gas section, this design not only extends the flow path of the refrigerant fluid and increases the gas-liquid separation efficiency, but also makes the distributor act as a kind of resistive silencer, effectively absorbing and attenuating the vibration energy generated by the fluid flow, reducing the mechanical vibration transmitted from the distributor to the compressor body, and thus significantly reducing the operating noise of the whole machine, thereby improving the performance of the air conditioner.

[0025] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. Attached Figure Description

[0026] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] Figure 1 This is a front cross-sectional view of a liquid dispenser structure in the prior art;

[0028] Figure 2 This is a front cross-sectional view of the separator structure provided in an embodiment of the present invention;

[0029] Figure 3 This is a top view of the separator structure provided in an embodiment of the present invention;

[0030] Figure 4 This is a left-side view of the separator structure provided in an embodiment of the present invention;

[0031] Figure 5 This is a front view schematic diagram of the partition member provided in an embodiment of the present invention;

[0032] Figure 6 This is a top view of the partition member provided in an embodiment of the present invention;

[0033] Figure 7 A top view schematic diagram of another embodiment of the liquid dispenser structure provided in this invention;

[0034] Figure 8 A top view schematic diagram of another embodiment of the liquid dispenser structure provided in this invention;

[0035] Figure 9 for Figure 8 A schematic diagram of its breakdown.

[0036] Figure label:

[0037] 1. Intake straight pipe; 2. Cylinder; 3. Bend; 4. Filter assembly; 5. Intermediate straight pipe;

[0038] The components include: housing 10, first cavity 11, second cavity 12, first part 13, second part 14, air inlet pipe 20, air outlet pipe 30, partition 40, air return part 41, and oil return hole 42. Detailed Implementation

[0039] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0040] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0041] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0042] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0043] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0044] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0045] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. The illustrative expressions of the above terms in this specification should not be construed as necessarily referring to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0046] See Figure 1 As shown, the conventional liquid distributor structure provided by the prior art consists of a straight suction pipe 1, a cylinder 2, and a bend 3. In addition, conventional liquid distributors usually also use a filter assembly 4 and an intermediate straight pipe 5. Among them, the intermediate straight pipe 5 is not fixed or has only a few baffles for fixing, which makes it easy for a large amount of gas-liquid mixture to accumulate at the upper end of the filter assembly 4, causing instability of the upper center of gravity of the liquid distributor. In addition, the impact and eddy current of the refrigerant in the intermediate straight pipe 5 will cause the cylinder 2 to vibrate, which will then be transmitted to the compressor, exacerbating the noise and mechanical wear of the whole machine.

[0047] See Figures 2 to 9 As shown, the present invention discloses a specific embodiment of a liquid dispenser structure, including: a housing 10, an air inlet pipe 20, an air outlet pipe 30, and a partition 40;

[0048] The partition 40 is connected to the interior of the housing 10 and divides the interior of the housing 10 longitudinally into a first cavity 11 and a second cavity 12. The upper end of the partition 40 is provided with a return air section 41, which is used to connect the first cavity 11 and the second cavity 12.

[0049] The inlet of the air inlet pipe 20 is located outside the housing 10 and is used to connect with the evaporator located outside the liquid separator. The outlet of the air inlet pipe 20 extends into the housing 10 and communicates with the first cavity 11.

[0050] The inlet of the outlet pipe 30 is located inside the housing 10 and communicates with the second cavity 12, and the outlet of the outlet pipe 30 extends outside the housing 10 and is used to communicate with the air inlet of the compressor body.

[0051] Specifically, the housing 10 is made of high-strength, corrosion-resistant metal materials (such as stainless steel or aluminum alloy), and a closed cavity structure is formed through processes such as stamping and welding to ensure good sealing and structural strength, capable of withstanding pressure and temperature changes during the operation of the refrigeration system. Additionally, a partition 40 is installed inside the housing 10, made of the same or compatible material as the housing 10. The partition 40 is vertically connected to the inside of the housing 10, with precise control of its installation position, dividing the interior of the housing 10 longitudinally into a first cavity 11 and a second cavity 12. The connection between the partition 40 and the housing 10 can be welded to ensure a strong and airtight connection, preventing refrigerant leakage. Furthermore, a return gas section 41 is provided at the upper end of the partition 40. The return gas section 41 can be multiple evenly distributed small holes or a channel of a specific shape, its function being to connect the first cavity 11 and the second cavity 12, while also guiding and throttling the gas flow, optimizing the gas flow state.

[0052] The inlet pipe 20 is a metal pipe of appropriate diameter. Its inlet is located outside the housing 10 and is connected to the evaporator outlet located outside the distributor via flange connection or welding, ensuring a tight connection and preventing refrigerant leakage. The outlet of the inlet pipe 20 extends into the housing 10, with its insertion depth precisely controlled so that the outlet reaches the area of ​​the first cavity 11, generally at 1 / 6 to 1 / 3 of the height of the first cavity 11. This allows the gas-liquid mixture introduced from the evaporator to directly enter the lower part of the first cavity 11, avoiding accumulation at the top. The outlet pipe 30 is also a metal pipe of appropriate diameter. Its inlet is located inside the housing 10 and connects to the second cavity 12. The inlet position is optimized according to the structure and gas flow characteristics of the second cavity 12 to ensure sufficient collection of gaseous refrigerant from the return gas section 41. The outlet of the outlet pipe 30 extends outside the housing 10 and is connected to the air inlet of the compressor body via flange connection or welding, ensuring a reliable connection and providing a stable supply of gaseous refrigerant to the compressor.

[0053] In other words, the gas-liquid mixture introduced from the evaporator is connected to the inlet pipe 20, and the outlet of the inlet pipe 20 is connected to the first cavity 11. The gas-liquid mixture can be directly introduced from the evaporator through the inlet pipe 20 to the lower part of the first cavity 11. This can lower the center of gravity of the distributor, effectively avoid excessive accumulation of the gas-liquid mixture at the upper end of the distributor, solve the problem of unstable equipment operation caused by the upward shift and offset of the center of gravity in traditional designs, and enhance the structural stability and vibration resistance of the distributor and even the entire refrigeration system. Furthermore, the concentration of the gas-liquid mixture at the upper end not only leads to instability of the center of gravity but also causes significant vibration due to fluid impact and turbulence. This distributor guides the gas-liquid mixture to the lower part of the first chamber 11, changing the flow path and distribution of the fluid, reducing fluid impact and turbulence at the upper end, and thus effectively mitigating the vibration of the distributor itself. At the same time, the straight pipe structure, which has a significant impact on vibration in the prior art, is eliminated, avoiding the transmission of vibration caused by fluid impact and eddies in the straight pipe. The design of the baffle 40 makes the fluid flow path longer, and the energy of the fluid gradually decreases during the flow process. Moreover, the distributor at this time acts as a resistive silencer, which can absorb and consume some vibration energy, further reducing the intensity of vibration transmitted to the compressor. Therefore, the overall noise and vibration of the compressor are significantly reduced, the operation is more stable and quiet, the user's comfort is improved, and the wear of internal compressor components caused by vibration is reduced, extending the service life of the compressor. In addition, the liquid separator structure ensures that the refrigerant entering the compressor is a relatively pure gaseous refrigerant. After the gas-liquid mixture undergoes initial separation in the lower part of the first chamber 11, the liquid refrigerant gradually settles, and the gaseous refrigerant enters the second chamber 12 through the return gas section 41, and is then transported to the compressor body through the outlet pipe 30. This effective gas-liquid separation mechanism avoids liquid refrigerant from entering the compressor, prevents liquid slugging, and protects the compressor's compression components from damage caused by liquid refrigerant impact. At the same time, the optimized fluid flow path and stable gas supply reduce pressure fluctuations and load changes during compressor operation, enabling the compressor to operate in a more stable state, improving the overall operational stability and reliability of the system, reducing the system failure rate, and reducing maintenance costs and downtime.

[0054] On another front, in traditional distributors, the gas-liquid mixture is transported from the curved tube to the compressor body through only one cylindrical container cavity. This short path results in limited residence time for the gas-liquid mixture within the container, leading to insufficient vaporization and a higher proportion of liquid components in the refrigerant entering the compressor. This new distributor, however, uses two chambers. The gas-liquid mixture first enters the first chamber 11, where it has ample space and time for initial vaporization and separation. The liquid refrigerant gradually evaporates, while the gaseous refrigerant rises. Then, the gaseous refrigerant enters the second chamber 12 through the return gas section 41, where it is further stabilized and homogenized, ensuring a more complete vaporization process. After processing through both chambers, the liquid component in the refrigerant entering the compressor body is significantly reduced, improving the quality and purity of the refrigerant and promoting optimal compressor operation. In addition, at the moment the compressor starts, the system pressure and flow rate change drastically. Traditional distributors, due to insufficient vaporization, easily lead to a large amount of gas-liquid mixture, especially liquid refrigerant, entering the compressor directly and rapidly. However, the two-chamber structure of this distributor provides a buffer and vaporization transition space for the gas-liquid mixture. At the moment of startup, the gas-liquid mixture first enters the first chamber 11, where it undergoes preliminary vaporization and energy exchange, and its speed is slowed down to a certain extent. Then, the vaporized gaseous refrigerant slowly enters the second chamber 12 through the return gas section 41, and finally enters the compressor body. This staged buffering and vaporization process effectively slows down the speed at which the liquid refrigerant enters the compressor, avoiding sudden impact of the liquid refrigerant on the compressor's interior. If liquid refrigerant accumulates excessively after entering the compressor, it can soak the compressor motor, affecting its heat dissipation and normal operation, and even causing motor damage. This distributor reduces the amount of liquid refrigerant entering the compressor at startup by fully vaporizing and slowing down the entry rate, thus reducing the possibility of the mixture soaking the motor. Even if a small amount of liquid refrigerant enters the compressor, it will not accumulate rapidly like with traditional distributors. The motor has sufficient time to evaporate the small amount of liquid refrigerant, ensuring normal motor operation and heat dissipation, and improving the compressor's reliability and lifespan. When liquid refrigerant soaks the compressor motor, it may cause a decrease in the motor's insulation performance, increasing leakage current. Increased leakage current can damage the compressor's electrical system and even cause safety accidents. This distributor effectively alleviates the problem of the mixture soaking the motor at startup, maintains the motor's good insulation performance, reduces leakage current at startup, and improves the compressor's electrical safety and operational stability.

[0055] See Figures 2 to 3 As shown, in one embodiment, the volume of the first cavity 11 is greater than or equal to the volume of the second cavity 12.

[0056] Specifically, after determining the total volume, the volume is allocated according to the principle that the volume of the first cavity 11 is greater than or equal to the volume of the second cavity 12. For example, if the total volume is V, the volume V1 of the first cavity 11 can be set to 50%-75% of V, and the volume V2 of the second cavity 12 can be set to 25%-50% of V, that is, V1≥V2 and V=V1+V2. The specific allocation ratio can be determined through experimental optimization, taking into account the vaporization of the gas-liquid mixture under different operating conditions and the operational stability of the system.

[0057] In other words, the first chamber 11 has a larger volume, capable of holding more gas-liquid mixture. During the operation of the refrigeration system, after the gas-liquid mixture enters the first chamber 11, there is sufficient space for diffusion and distribution, allowing the liquid refrigerant to fully contact the gaseous refrigerant, increasing the heat exchange area, and thus improving vaporization efficiency. For example, under the same inlet flow rate and temperature conditions, the larger volume of the first chamber 11 allows more liquid refrigerant to evaporate, reducing the amount of liquid entering the second chamber 12. Furthermore, due to the larger volume of the first chamber 11, the residence time of the gas-liquid mixture within it is relatively longer. This longer residence time provides more time for the liquid refrigerant to evaporate, resulting in a more complete vaporization process. This is particularly important for systems operating in low-temperature environments or using low-boiling-point refrigerants, effectively preventing liquid refrigerant from entering the compressor due to insufficient vaporization, thus protecting the compressor's normal operation. Additionally, the large volume of the first chamber 11 acts as a buffer, preventing pressure fluctuations within the system caused by changes in the refrigeration system load or compressor start-up and shutdown. The first chamber 11 can absorb and release a portion of the refrigerant, mitigating rapid pressure changes and stabilizing the system pressure. For example, at the moment the compressor starts, the system pressure drops rapidly. The refrigerant in the first chamber 11 can replenish the system in time, maintaining relative pressure stability and reducing the impact on the compressor and other components. After the refrigerant has been fully vaporized in the first chamber 11, it enters the second chamber 12, where it further stabilizes and homogenizes the gas. The relatively small volume of the second chamber 12 helps to make the gas flow smoother, reducing the generation of turbulence and eddies, thereby providing a more uniform gas supply to the compressor. This helps to improve the compressor's operating efficiency, reduce energy consumption, and reduce compressor vibration and noise problems caused by uneven gas supply.

[0058] See Figure 2 and Figure 5 As shown, in one embodiment, the return air section 41 is circular in shape and is composed of a plurality of circular holes arranged in a circular pattern.

[0059] Specifically, based on the structural design, volume, and overall dimensions of the first chamber 11 and the second chamber 12 of the distributor, the installation position of the return gas section 41 on the partition 40 is determined. It is typically placed near the upper part of the partition 40 to ensure that the pre-vaporized gaseous refrigerant in the first chamber 11 can pass smoothly. Simultaneously, based on the flow rate requirements and expected vaporization effect of the distributor, the overall diameter or side length of the return gas section 41 is determined. For example, for a distributor used in a small household refrigeration system, the overall diameter of the return gas section 41 may be designed to be 20-50 mm. Furthermore, considering the uniformity of airflow and resistance distribution, the arrangement of multiple circular holes is planned. Common arrangement methods include regular matrix arrangements (such as square matrices and triangular matrices) and ring arrangements. Taking a square matrix arrangement as an example, first determine the number of rows and columns of the circular holes, and then calculate the diameter of each circular hole and the spacing between adjacent holes based on the dimensions of the return gas section 41 and the required opening area ratio. For example, if the diameter of the return gas section 41 is 30mm and it is designed as a 3x3 square matrix, the diameter of the circular holes can be initially set to 5mm. Then, the spacing can be adjusted by calculation to ensure that the circular holes are evenly distributed within the area of ​​the return gas section 41. Furthermore, the return gas section 41 and the partition plate 40 can be manufactured as a single piece or separately and then connected. The selected material should be the same as that of the partition plate 40, generally a high-strength, corrosion-resistant metal material, such as stainless steel 304 or 316, to ensure good stability and durability in the working environment of the refrigeration system.

[0060] In other words, the return gas section 41, composed of multiple circular holes, allows for a more uniform distribution of gaseous refrigerant during passage. A regular arrangement (such as a matrix or ring arrangement) prevents airflow concentration in a specific area, reducing localized excessively fast or slow airflow velocities. For example, in a square matrix arrangement, the airflow from each hole is relatively uniform, allowing the gaseous refrigerant entering the second chamber 12 from the first chamber 11 to flow smoothly, improving the uniformity of airflow throughout the distributor and facilitating stable gas intake and compression by the subsequent compressor. Furthermore, the circular shape of the return gas section 41, compared to irregular shapes, reduces turbulence and frictional resistance during airflow. The smooth inner walls of the circular holes allow for smoother passage of gaseous refrigerant, reducing energy loss. Simultaneously, a well-planned diameter and spacing of the circular holes can further optimize the airflow channel while ensuring sufficient opening area (to meet gas flow requirements), minimizing airflow resistance. This helps improve the efficiency of the refrigeration system and reduce compressor energy consumption. Furthermore, the uniform airflow distribution and low airflow resistance facilitate better heat exchange and separation between the gaseous refrigerant and liquid refrigerant within the first chamber 11. The gaseous refrigerant can smoothly enter the second chamber 12 through the return gas section 41 without backflow or eddies occurring near the return gas section 41, thus providing a more stable vaporization environment for the liquid refrigerant within the first chamber 11. The liquid refrigerant can fully evaporate under the influence of a more uniform airflow, improving the vaporization effect, reducing the amount of liquid refrigerant entering the compressor, and protecting the normal operation of the compressor.

[0061] See Figure 2 and Figure 5 As shown, in one embodiment, the diameter of the return air section 41 is greater than or equal to 6 mm, and the diameter of the circular hole is greater than or equal to 0.3 mm.

[0062] Specifically, the return gas section 41, with a diameter of 6 mm or greater, provides a sufficiently large flow channel for the gaseous refrigerant, meeting the gas flow requirements of the refrigeration system under different operating conditions. For example, in high-temperature environments or when the system is operating under high load, the refrigerant evaporation rate increases, requiring a larger gas flow rate through the return gas section 41 to enter subsequent stages. The larger diameter of the return gas section 41 prevents airflow blockage caused by an insufficiently small channel, ensuring smooth passage of the gaseous refrigerant and maintaining normal system operation. The diameter of the circular orifice, ≥0.3 mm, also ensures that each orifice can pass a certain amount of gaseous refrigerant. The combined effect of multiple orifices further increases the gas passage area and improves the overall gas flow rate. Simultaneously, a reasonable selection of the circular orifice diameter avoids problems such as excessively high airflow velocity and excessive pressure loss caused by an excessively small orifice. Furthermore, the larger diameter of the return gas section 41 and the appropriate circular orifice diameter effectively reduce the airflow resistance of the gaseous refrigerant when passing through the return gas section 41. According to fluid mechanics principles, the larger the diameter of the pipe or orifice, the lower the flow resistance within it. The optimized diameter of the return gas section 41 allows gaseous refrigerant to pass through with relatively low pressure loss. The selection of the orifice diameter also considers airflow uniformity and resistance balance. While a smaller orifice diameter increases airflow uniformity, it also increases airflow resistance; conversely, a larger orifice diameter has the opposite effect. By optimizing the orifice diameter, airflow resistance can be controlled within a reasonable range while ensuring airflow uniformity, reducing energy loss and improving the efficiency of the refrigeration system.

[0063] In one embodiment, a filter screen is also provided on one side of the air return section 41 to perform a filtering function.

[0064] Specifically, stainless steel filter screens can be selected. Stainless steel has advantages such as corrosion resistance, high strength, and long service life. It can effectively resist trace impurities in the refrigerant and possible moisture corrosion, ensuring that the filter screen will not rust or deform during long-term use, thus maintaining good filtration performance. The filter screen and the return air section 41 can be connected by snap-fit, bolt fixing, or welding.

[0065] In other words, the filter can effectively intercept impurities in the gaseous refrigerant entering the return gas section 41, such as dust, metal shavings, and oil. Through the filtering effect of the filter, the amount of impurities entering the refrigeration system can be greatly reduced, keeping the system clean and ensuring that the refrigeration system can operate efficiently and stably.

[0066] See Figure 2 , Figure 4 and Figure 5 As shown, in one embodiment, the lower end of the partition 40 is further provided with an oil return hole 42, which is used to connect the first cavity 11 and the second cavity 12.

[0067] Specifically, the number of oil return holes 42 needs to be determined based on factors such as the system size, compressor lubrication requirements, and refrigerant flow rate. For small refrigeration systems, such as household air conditioners, 1-2 oil return holes 42 are generally sufficient to meet the compressor's lubrication requirements. However, for large industrial refrigeration equipment, due to the higher compressor power and larger lubricant requirements, 3-5 or even more oil return holes 42 may be needed to ensure sufficient lubricant returns to the compressor in a timely manner. Common shapes for oil return holes 42 include circular, elliptical, and oblong. Circular oil return holes 42 are easy to manufacture and offer relatively low resistance to fluid flow, making them suitable for most refrigeration systems. Elliptical and oblong oil return holes 42 can increase the flow area to some extent and guide the fluid flow direction, helping to improve oil return efficiency, but they are relatively more difficult to manufacture. The diameter or equivalent diameter of the oil return hole 42 should be calculated and determined based on the lubricant flow rate and velocity. Generally, the diameter of the oil return hole 42 should not be too large, otherwise excessive liquid refrigerant may enter the second chamber 12 through the oil return hole 42, affecting the normal operation of the compressor; nor should it be too small, to avoid poor oil return and insufficient lubrication of the compressor. The appropriate size of the oil return hole 42 can be determined through experimental or theoretical calculations, combined with the actual operating parameters of the system. For example, for small household air conditioning systems, the diameter of the oil return hole 42 can be designed to be 1-5mm; for large industrial refrigeration equipment, the diameter of the oil return hole 42 may be around 5-10mm. In addition, in the first chamber 11, the liquid refrigerant and lubricating oil will separate to a certain extent. Since the density of lubricating oil is usually greater than that of liquid refrigerant, under the action of gravity, the lubricating oil will gradually sink to the bottom of the first chamber 11. To ensure that the lubricating oil at the bottom of the first chamber 11 can flow smoothly into the second chamber 12 through the oil return hole 42, a certain slope or guide structure can be set at the bottom of the first chamber 11. For example, the bottom of the first cavity 11 can be designed as an inclined surface sloping towards the oil return hole 42, allowing the lubricating oil to flow naturally towards the oil return hole 42 under the influence of gravity. In addition, some guide plates or baffles can be set near the oil return hole 42 to guide the flow direction of the lubricating oil and improve the oil return efficiency.

[0068] In other words, the oil return hole 42 can promptly deliver the lubricating oil separated in the first chamber 11 to the second chamber 12, and then enter the compressor along the outlet pipe 30, providing sufficient lubrication for the compressor's moving parts. This reduces wear on internal compressor parts, lowers frictional resistance, extends the compressor's service life, and improves the compressor's operational reliability and efficiency. Furthermore, an effective oil return design can prevent compressor malfunctions caused by insufficient lubrication, such as bearing wear and seizure. It also reduces the possibility of excessive lubricating oil mixing in the refrigerant affecting the normal operation of other system components (such as the expansion valve and evaporator), thereby lowering the overall refrigeration system failure rate, reducing maintenance costs and downtime, and improving the system's operational economy and reliability.

[0069] See Figure 2 , Figure 4 and Figure 5 As shown, in one embodiment, the diameter of the oil return hole 42 is greater than or equal to 0.5 mm and less than or equal to 1 / 10 of the diameter of the gas return section 41.

[0070] Specifically, when the diameter of the oil return hole 42 is greater than or equal to 0.5 mm, it provides sufficient flow channels for lubricating oil, allowing the lubricating oil separated in the first chamber 11 to flow smoothly into the second chamber 12 and enter the compressor along the outlet pipe 30. This ensures that the compressor always has a sufficient supply of lubricating oil, reducing wear on parts caused by insufficient oil and extending the compressor's service life. For example, in a large refrigeration system, if the diameter of the oil return hole 42 is too small, it may lead to slow oil return, causing dry friction of the bearings after prolonged operation. An oil return hole 42 with the required diameter can effectively prevent this from happening. In addition, sufficient oil return ensures that the compressor operates normally under good lubrication conditions, keeping the compressor's compression ratio stable. If the diameter of the oil return hole 42 is too small, poor oil return will lead to increased internal friction in the compressor, abnormal compression ratio, and consequently affect the system's pressure stability. An oil return hole 42 with a diameter greater than or equal to 0.5 mm ensures that the lubricating oil returns to the compressor in a timely manner, maintaining the system pressure within the normal range and improving the system's operational stability and reliability. In addition, a suitable diameter for the oil return hole 42 helps the refrigerant and lubricating oil to separate fully in the first chamber 11. If the diameter of the oil return hole 42 is too large, too much refrigerant will enter the second chamber 12 through the oil return hole 42, affecting the refrigerant separation effect; while if the diameter is too small, lubricating oil may accumulate in the first chamber 11 and fail to return to the compressor in time. An oil return hole 42 with a diameter of 0.5 mm or greater can ensure smooth lubricating oil return while minimizing the amount of refrigerant passing through, improving the purity of the refrigerant, and thus improving the heat exchange efficiency of the refrigeration system.

[0071] In one embodiment, the cross-section of the partition member 40 is curved or planar.

[0072] See Figure 3 and Figure 6As shown, the cross-section of the baffle 40 is curved and S-shaped. The S-shaped rotating curved surface design conforms to the gas flow law. As the gas flows along the curved surface, it can gradually change its flow direction, avoiding sudden changes in direction and velocity, reducing the generation of eddies. This makes the refrigerant flow within the system more stable, reduces flow resistance, and thus improves system operating efficiency. Furthermore, the smooth refrigerant flow helps maintain stable pressure within the system. Due to the reduction of eddies and velocity abrupt changes, the pressure change of the refrigerant during flow is more uniform, avoiding drastic pressure fluctuations. This is crucial for the normal operation of the compressor; stable pressure reduces the compressor load, energy consumption, and wear, extending the compressor's service life. Additionally, the special shape of the S-shaped curved surface provides some obstruction and buffering effect when the gas-liquid mixture passes through the baffle 40. Because of its higher density, the liquid refrigerant is more easily separated from the gaseous refrigerant under the guidance of the curved surface and flows slowly along the surface, rather than directly and rapidly entering the compressor. This effectively prevents liquid slugging in the compressor and protects its safe operation.

[0073] See Figure 7 As shown, the planar partition 40 has a simple design, relatively easy manufacturing process, and low material and processing costs. For small refrigeration equipment that does not require high refrigerant flow smoothness and pressure stability and is cost-sensitive, such as small refrigerators and freezers, using the planar partition 40 can reduce manufacturing costs while meeting basic functional requirements. Furthermore, due to its simple structure, the planar partition 40 is easy to install and disassemble. When system maintenance or cleaning is required, the partition 40 can be quickly removed and installed, reducing maintenance time and workload. This is a significant advantage for refrigeration equipment that requires regular maintenance.

[0074] See Figure 8 and Figure 9 As shown, in one embodiment, the housing 10 is composed of a first part 13 and a second part 14, the first part 13 being connected to the partition 40 and the air inlet pipe 20, and the second part 14 being connected to the air outlet pipe 30.

[0075] Specifically, the first part 13 and the second part 14 are combined together by welding, strong adhesive bonding or other means to form the liquid dispenser as a whole.

[0076] In other words, dividing the housing 10 into a first part 13 and a second part 14 and manufacturing them separately reduces manufacturing difficulty. For complex housing 10 shapes, modular manufacturing makes it easier to achieve the required machining precision for each part. For example, when the housing 10 has special flow channels or structures inside, modular manufacturing allows each part to be machined separately and then assembled, avoiding machining difficulties and precision problems that may occur during overall manufacturing. In addition, the modular housing 10 design makes it easier to install the partition 40, the inlet pipe 20, and the outlet pipe 30. The partition 40 and the inlet pipe 20 can be installed on the first part 13 of the housing 10 first, and the outlet pipe 30 can be installed on the second part 14 of the housing 10 first, and then the two parts can be assembled together, reducing the operational space restrictions during installation. At the same time, when system maintenance or cleaning is required, the housing 10 can be easily disassembled for inspection and repair of internal components, improving maintenance efficiency. The welded assembly method provides high connection strength and sealing performance, making it suitable for applications with high strength and sealing requirements, such as high-pressure refrigeration systems. The welded housing 10 exhibits good overall integrity and can withstand significant pressure and vibration. Strong adhesive bonding offers advantages such as not damaging the housing 10 material and ensuring uniform stress distribution, making it suitable for plastic housings or applications with specific welding requirements. The adhesive can fill minor surface defects of the housing 10, improving sealing. Mechanical and clamp connections facilitate installation and disassembly, enabling system maintenance and component replacement.

[0077] The present invention also discloses a compressor, including a compressor body and a liquid separator structure as described above.

[0078] Specifically, by setting up a distributor structure and connecting the inlet pipe 20 to the evaporator, with the outlet of the inlet pipe 20 connected to the first chamber 11, the gas-liquid mixture introduced from the evaporator can directly reach the lower part of the first chamber 11 through the inlet pipe 20. This lowers the center of gravity of the distributor, effectively preventing excessive accumulation of the gas-liquid mixture at the upper end of the distributor. This solves the problem of unstable equipment operation caused by the upward shift and offset of the center of gravity in traditional designs, and enhances the structural stability and vibration resistance of the distributor and even the entire refrigeration system. In addition, the partition 40 divides the interior of the housing 10 into the first chamber 11 and the second chamber 12, and the gas flow between the two chambers is achieved through the return gas section 41. This design not only extends the flow path of the refrigerant fluid and increases the gas-liquid separation efficiency, but also makes the distributor act as a kind of resistive silencer, effectively absorbing and attenuating the vibration energy generated by the fluid flow, reducing the mechanical vibration transmitted from the distributor to the compressor body, and thus significantly reducing the operating noise of the entire machine.

[0079] The present invention also discloses an air conditioner, including the compressor described above.

[0080] Specifically, by setting up a compressor and connecting the intake pipe 20 to the evaporator, with the outlet of the intake pipe 20 connected to the first cavity 11, the gas-liquid mixture introduced from the evaporator can directly reach the lower part of the first cavity 11 through the intake pipe 20. This lowers the center of gravity of the distributor, effectively preventing excessive accumulation of the gas-liquid mixture at the upper end of the distributor. This solves the problem of unstable equipment operation caused by the upward shift and offset of the center of gravity in traditional designs, and enhances the structural stability and vibration resistance of the distributor and even the entire refrigeration system. In addition, the partition 40 divides the interior of the housing 10 into the first cavity 11 and the second cavity 12, and the gas flow between the two cavities is achieved through the return gas section 41. This design not only extends the flow path of the refrigerant fluid and increases the gas-liquid separation efficiency, but also makes the distributor act as a kind of resistive silencer, effectively absorbing and attenuating the vibration energy generated by the fluid flow, reducing the mechanical vibration transmitted from the distributor to the compressor body, and thus significantly reducing the operating noise of the whole machine, thereby improving the performance of the air conditioner.

[0081] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and these modifications or substitutions should all be covered within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A liquid dispenser structure, characterized in that, include: Housing, air inlet pipe, air outlet pipe, and partition components; The partition is connected to the interior of the housing and divides the interior of the housing longitudinally into a first cavity and a second cavity. The upper end of the partition is provided with a return air section, which is used to connect the first cavity and the second cavity. The inlet of the air inlet pipe is located outside the housing and is used to connect with the evaporator located outside the distributor. The outlet of the air inlet pipe extends into the housing and communicates with the first cavity. The inlet of the outlet pipe is located inside the housing and communicates with the second cavity, while the outlet of the outlet pipe extends outside the housing and is used to communicate with the air inlet of the compressor body.

2. The separator structure according to claim 1, characterized in that, The volume of the first cavity is greater than or equal to the volume of the second cavity.

3. The separator structure according to claim 1, characterized in that, The return air section is circular in shape and consists of a plurality of circular holes arranged in a circle.

4. The separator structure according to claim 3, characterized in that, The diameter of the return air section is greater than or equal to 6 mm, and the diameter of the circular hole is greater than or equal to 0.3 mm.

5. The separator structure according to claim 3, characterized in that, The lower end of the partition is also provided with an oil return hole, which is used to connect the first cavity and the second cavity.

6. The separator structure according to claim 5, characterized in that, The diameter of the oil return hole is greater than or equal to 0.5 mm and less than or equal to 1 / 10 of the diameter of the gas return section.

7. The separator structure according to claim 1, characterized in that, The cross-section of the partition is curved or planar.

8. The separator structure according to claim 1, characterized in that, The housing consists of a first part and a second part, the first part being connected to the partition and the air inlet pipe, and the second part being connected to the air outlet pipe.

9. A compressor, characterized in that, It includes a compressor body and a distributor structure as described in any one of claims 1-8.

10. An air conditioner, characterized in that, Includes the compressor as described in claim 9.

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