Compressor and air conditioner

Abstract

The compressor comprises a compressor body and a gas-liquid separator, the compressor body comprises a compression mechanism, the gas-liquid separator comprises a gas outlet pipe, the gas outlet pipe is configured to input a gaseous refrigerant in the gas-liquid separator into a compression cavity of the compression mechanism, M liquid return holes are formed in the gas outlet pipe in the height direction of the gas outlet pipe, the diameter of each liquid return hole is D, the distance between every two adjacent liquid return holes is Nn, n is equal to (1,..., M-1), and D * M / (N1 +... + NM-1) belongs to (0.15, 0.20), so that the liquid return rate and the compressor efficiency are improved.

Description

Technical Field

[0001] The present disclosure relates to the technical field of air conditioning, and particularly to a compressor and an air conditioner. Background Art

[0002] An air conditioner includes an outdoor unit and an indoor unit, and the outdoor unit is connected to the indoor unit. The air conditioner performs a refrigeration and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve, and an evaporator. The compressor is fixedly arranged in the outdoor unit. In a rotary compressor, the compressor is composed of a compressor body and a gas-liquid separator. The compressor body includes a compression mechanism configured to compress a refrigerant. The gas-liquid separator is configured to supply gaseous refrigerant to the compression chamber of the compression mechanism, and the gas-liquid separator completes the separation of liquid refrigerant and gaseous refrigerant to prevent liquid refrigerant from entering the compression chamber of the compressor body and causing the compressor to malfunction.

[0003] The gas-liquid separator includes an outlet pipe configured to input the gaseous refrigerant in the inner cavity of the gas-liquid separator into the compression chamber of the compression mechanism. A liquid return hole is provided on the outlet pipe, and the liquid return hole is configured to discharge the liquid accumulated in the gas-liquid separator to prevent excessive liquid accumulation from reducing the gas-liquid separation effect of the gas-liquid separator. The liquid return hole of the existing gas-liquid separator is either too large, which is likely to cause liquid slugging in the compressor; or too small, resulting in excessive liquid accumulation in the gas-liquid separator and reducing the compressor efficiency.

[0004] The above information disclosed in this background art is only used to increase the understanding of the background art of the present application. Therefore, it may include prior art that is not known to those of ordinary skill in the art. Summary of the Invention

[0005] In view of the problems pointed out in the background art, the present disclosure provides a compressor and an air conditioner, designs the liquid return hole of the gas-liquid separator, and improves the liquid return rate and the compressor efficiency.

[0006] On the one hand, a compressor is provided. The compressor includes a compressor body and a gas-liquid separator. The compressor body includes a compression mechanism. The gas-liquid separator includes an outlet pipe configured to input the gaseous refrigerant in the gas-liquid separator into the compression chamber of the compression mechanism. M liquid return holes are provided along the height direction of the outlet pipe, the aperture of the liquid return hole is D, the distance between two adjacent liquid return holes is Nn, n = (1,..., M - 1), D×M / (N1 +... + N M-1 ) ∈ (0.15, 0.20), so that the position and aperture of the liquid return hole are within a reasonable data range, thereby improving the oil return rate and the compressor efficiency.

[0007] On the other hand, an air conditioner is provided, including a compressor, an evaporator, a condenser, and a throttling device, and the compressor is the compressor as described above.

[0008] After reading the specific embodiments of the present utility model in conjunction with the accompanying drawings, other features and advantages of the present utility model will become clearer. Description of the Drawings

[0009] In order to more clearly illustrate the technical solutions in the embodiments of the present utility model or the prior art, the following will briefly introduce the accompanying drawings required for the description of the embodiments or the prior art. Obviously, the accompanying drawings in the following description are some embodiments of the present utility model. For those of ordinary skill in the art, without creative efforts, other accompanying drawings can also be obtained based on these drawings.

[0010] Figure 1 FIG. [ID] is a structural diagram of a compressor according to some embodiments;

[0011] Figure 2 FIG. [ID] is a sectional view of a compressor according to some embodiments;

[0012] Figure 3 FIG. [ID] is another structural diagram of a compressor according to some embodiments;

[0013] Figure 4 FIG. [ID] is a structural diagram of a foot according to some embodiments;

[0014] Figure 5 FIG. [ID] is a control logic diagram of a compressor according to some embodiments;

[0015] Figure 6 FIG. [ID] is a structural diagram of a second connection portion according to some embodiments;

[0016] Figure 7 FIG. [ID] is another control logic diagram of a compressor according to some embodiments;

[0017] Figure 8 FIG. [ID] is a frequency response function curve diagram of a gas-liquid separator according to some embodiments;

[0018] Figure 9 FIG. [ID] is a structural diagram of an expansion muffler and a Helmholtz muffler according to some embodiments;

[0019] Figure 10 FIG. [ID] is a noise reduction volume curve diagram of a muffler according to some embodiments;

[0020] Figure 11 FIG. [ID] is a sectional view of a gas-liquid separator according to some embodiments;

[0021] Figure 12 FIG. [ID] is a structural diagram of a first partition portion and a second partition portion according to some embodiments;

[0022] Figure 13Another structural diagram of the gas-liquid separator according to some embodiments;

[0023] Figure 14 A control logic diagram of the gas-liquid separator according to some embodiments;

[0024] Figure 15 A structural diagram of the outlet pipe according to some embodiments;

[0025] Figure 16 A structural diagram of the compression mechanism according to some embodiments;

[0026] Figure 17 A cross-sectional view of the eccentric crankshaft according to some embodiments;

[0027] Figure 18 A structural diagram of the rotor according to some embodiments;

[0028] Figure 19 A structural diagram of the stator according to some embodiments. Detailed implementation manners

[0029] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present application without creative efforts shall fall within the protection scope of the present application.

[0030] In the description of the present application, it should be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus cannot be understood as a limitation to the present application.

[0031] The terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, unless otherwise stated, the meaning of "a plurality" is two or more.

[0032] In the description of the present application, it should be noted that unless otherwise clearly specified or limited, the terms "installed", "connected", and "coupled" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0033] In the present utility model, unless otherwise clearly specified or limited, the first feature being "above" or "below" the second feature may include the direct contact between the first and second features, or may include the situation where the first and second features are not in direct contact but in contact through other features therebetween. Moreover, the first feature being "above", "over", and "on top of" the second feature includes that the first feature is directly above and obliquely above the second feature, or merely indicates that the horizontal height of the first feature is higher than that of the second feature. The first feature being "under", "beneath", and "underneath" the second feature includes that the first feature is directly below and obliquely below the second feature, or merely indicates that the horizontal height of the first feature is lower than that of the second feature.

[0034] The following disclosure provides many different embodiments or examples for implementing different structures of the present utility model. To simplify the disclosure of the present utility model, the components and settings of specific examples are described below. Of course, they are merely examples and are not intended to limit the present utility model. In addition, the present utility model may repeat reference numerals and / or reference letters in different examples. This repetition is for the purpose of simplification and clarity, and does not itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the present utility model provides examples of various specific processes and materials, but those of ordinary skill in the art may be aware of the application of other processes and / or the use of other materials.

[0035] [Air conditioner]

[0036] In some embodiments, the air conditioner performs a refrigeration cycle or a heating cycle by using a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration cycle or the heating cycle includes a series of processes involving compression, condensation, expansion, and evaporation to cool or heat the indoor space.

[0037] The low-temperature and low-pressure refrigerant enters the compressor, and the compressor compresses the low-temperature and low-pressure refrigerant into a refrigerant gas in a high-temperature and high-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed gaseous refrigerant into a liquid-phase refrigerant and releases the heat of the refrigerant to the surrounding environment through the condensation process.

[0038] The expansion valve expands the liquid-phase refrigerant in a high-temperature and high-pressure state formed by condensation in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a refrigeration effect by using the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. During the entire refrigeration cycle or heating cycle, the air conditioner can adjust the temperature of the indoor space.

[0039] The outdoor unit of the air conditioner includes a compressor and an outdoor heat exchanger, the indoor unit of the air conditioner includes an indoor heat exchanger, and the expansion valve can be arranged in the indoor unit or the outdoor unit.

[0040] The indoor heat exchanger and the outdoor heat exchanger serve as a condenser or an evaporator. When the indoor heat exchanger serves as a condenser, the air conditioner operates in the heating mode; when the indoor heat exchanger serves as an evaporator, the air conditioner operates in the refrigeration mode.

[0041] The outdoor unit also includes a four-way valve, and the four-way valve is configured to enable the conversion of the indoor heat exchanger and the outdoor heat exchanger as a condenser or an evaporator.

[0042] The refrigeration working principle of the air conditioner is as follows: When the compressor operates, the indoor heat exchanger (in the indoor unit, which is an evaporator at this time) is in an ultra-low pressure state. The liquid refrigerant in the indoor heat exchanger quickly evaporates and absorbs heat. The air blown by the indoor fan cools down after passing through the indoor heat exchanger coil and then blows into the room as cold air. After the refrigerant evaporates and vaporizes, it is pressurized by the compressor and condenses into a liquid state under the high-pressure environment in the outdoor heat exchanger (in the outdoor component, which is a condenser at this time), releasing heat. Through the outdoor fan, the heat is dissipated into the atmosphere, and such a cycle achieves the refrigeration effect.

[0043] The heating working principle of the air conditioner is as follows: The gaseous refrigerant is pressurized by the compressor to become a high-temperature and high-pressure refrigerant gas. The refrigerant gas enters the indoor heat exchanger (which is a condenser at this time), condenses and liquefies to release heat, becoming a liquid, and heats the indoor air, thereby achieving the purpose of raising the indoor temperature. The liquid refrigerant is decompressed by the throttling device and enters the outdoor heat exchanger (which is an evaporator at this time), evaporates and vaporizes to absorb heat, becoming a gas, and absorbs the heat of the outdoor air (the outdoor air temperature decreases), becoming a gaseous refrigerant. The gaseous refrigerant enters the compressor again to start the next cycle.

[0044] [Compressor body]

[0045] In some embodiments of the present disclosure, the compressor is a rolling piston compressor, refer to Figure 1 and Figure 2 as well as Figure 16, the compressor includes a compressor body 100. The compressor body 100 includes a first housing 110. The compressor body 100 further includes a receiving cavity 111. A closed receiving cavity 111 is formed within the first housing 110. The compressor body 100 further includes a compression mechanism 120. The compression mechanism 120 is disposed within the receiving cavity 111. The compression mechanism 120 is configured to compress a refrigerant. As Figure 2 shown, the compressor body 100 further includes an electric motor 130. The electric motor 130 is disposed within the receiving cavity 111. The electric motor 130 is disposed above the compression mechanism 120. The electric motor 130 is configured to provide power to the compression mechanism 120. Figure 16 is a cross-sectional view of one type of compression mechanism 120.

[0046] In some embodiments, referring to Figure 2 , the electric motor 130 includes a rotor 132. The electric motor 130 further includes a stator 131. The stator 131 is fixedly connected to the inner wall of the first housing 110 to achieve fixed installation of the electric motor 130 within the receiving cavity 11.

[0047] In some embodiments, referring to Figure 16 , the compression mechanism 120 further includes an eccentric crankshaft 121. The compression mechanism 120 further includes a muffler 704.

[0048] In some embodiments, referring to Figure 17 , the eccentric crankshaft 121 includes a first shaft segment 1211. The first shaft segment 1211 is fixedly connected to the rotor 132. The eccentric crankshaft 121 further includes a third shaft segment 1217; the eccentric crankshaft 121 further includes a second shaft segment 1215. The first shaft segment 1211 is connected to one end of the third shaft segment, and the second shaft segment 1215 is connected to the other end of the third shaft segment.

[0049] Referring to Figure 16, the compression mechanism 120 further includes a cylinder 701. The compression mechanism 120 further includes a piston 702. The piston 702 is disposed in the compression chamber of the cylinder 701, and the piston 702 is sleeved on the eccentric shaft section. The compression mechanism 120 further includes a bearing 703. The bearing 703 is fixedly connected to the cylinder 701. An exhaust hole is provided on the bearing 703, and the exhaust hole communicates with the compression chamber. The compression mechanism 120 further includes a sliding vane groove; the sliding vane groove is provided in the cylinder 701. The compression mechanism 120 further includes a sliding vane. The sliding vane is disposed in the sliding vane groove. The eccentric crankshaft 121 drives the piston 702 to perform a circumferential motion in the compression chamber, and the sliding vane reciprocates along the sliding vane groove, and the sliding vane always abuts against the piston. The compression chamber includes a first sub-compression chamber (high-pressure chamber); the compression chamber further includes a second sub-compression chamber (low-pressure chamber). The pressure in the first sub-compression chamber is greater than the pressure in the second sub-compression chamber. The sliding vane and the piston 702 divide the compression chamber into the first sub-compression chamber and the second sub-compression chamber. The working principle of the compressor is as follows: After the stator 131 of the motor 130 is energized, a magnetic pulling force is generated. The rotor 132 of the motor 130 performs a rotational motion under the action of the magnetic pulling force of the stator 131 and drives the eccentric crankshaft 121 to perform a rotational motion together. The eccentric crankshaft 121 rotates to drive the piston 702 sleeved on the eccentric shaft section to perform an eccentric circular motion in the compression chamber of the cylinder 701. The sliding vane reciprocates in the sliding vane groove. The sliding vane and the piston divide the compression chamber of the cylinder 701 into a first sub-compression chamber and a second sub-compression chamber. When the eccentric crankshaft 121 drives the piston 702 to rotate one week, air is inhaled from the second sub-compression chamber and exhausted from the first sub-compression chamber to complete one exhaust, realizing the compression of the gas by the compressor. The compressed gas is discharged through the exhaust hole.

[0050] In some embodiments of the present disclosure, the compressor is a twin-cylinder rolling piston compressor. Refer to Figure 16 , the compression mechanism 120 includes an eccentric crankshaft 121. The compression mechanism 120 further includes two cylinders 701, namely a first cylinder 1221 and a second cylinder 1222. The compression mechanism 120 further includes two bearings 703, namely a first bearing 1241 and a second bearing 1242. The compression mechanism 120 further includes two pistons 702, namely a first piston 1231 and a second piston 1232. The compression mechanism 120 further includes a middle partition 125. The compression mechanism 120 further includes two mufflers 704, namely a first muffler 1261 and a second muffler 1262.

[0051] In some embodiments, refer to Figure 17, the eccentric crankshaft 121 includes a first shaft section 1211; the third shaft section 1217 includes a first eccentric shaft section 1212; the third shaft section 1217 further includes a connecting shaft section 1214; the third shaft section 1317 further includes a second eccentric shaft section 1213. Along the height direction of the eccentric crankshaft 121, the first shaft section 1211, the first eccentric shaft section 1212, the connecting shaft section 1214, the second eccentric shaft section 1213, and the second shaft section 1215 are connected in sequence from top to bottom.

[0052] In some embodiments, as Figure 16 and Figure 17 shown, the first piston 1231 is disposed in the compression chamber of the first cylinder 1221, and the first piston 1231 can perform eccentric motion. The first piston 1231 is sleeved on the first eccentric shaft section 1212. The second piston 1232 is disposed in the compression chamber of the second cylinder 1222, and the second piston 1232 can perform eccentric motion. The second piston 1232 is sleeved on the second eccentric shaft section 1213. The middle partition 125 is sleeved on the connecting shaft section 1214, and the middle partition 125 is located between the first cylinder 1221 and the second cylinder 1222. The first bearing 1241 is sleeved on the first shaft section 1211 and is connected to the first cylinder 1221; the second bearing 1242 is sleeved on the second shaft section 1215 and is connected to the second cylinder 1222.

[0053] The first eccentric shaft section 1212 and the second eccentric shaft section 1213 are disposed on both sides of the central axis of the eccentric crankshaft 121. For example, the first eccentric shaft section 1212 and the second eccentric shaft section 1213 are configured at a relative angle of 180°, the first piston 1231 and the second piston 1232 perform eccentric rotation simultaneously, and the compressed gas in the compression chamber of the first cylinder 1221 is discharged through the exhaust hole on the first bearing 1241, and the compressed gas in the compression chamber of the second cylinder 1222 is discharged through the exhaust hole on the second bearing 1242.

[0054] Continuing to refer to Figure 16 , the first muffler 1261 is disposed on the first bearing 1241, the first muffler 1261 covers the exhaust hole of the first bearing 1241, and the compressed gas in the first cylinder 1221 is first discharged to the space enclosed by the first muffler 1261 and the first bearing 1241 through the exhaust hole of the first bearing 1241, and then discharged to the inner cavity of the compressor through the first muffler 1261.

[0055] The second muffler 1262 is disposed on the second bearing 1242, the second muffler 1262 covers the exhaust hole of the second bearing 1242, and the compressed gas in the second cylinder 1222 is first discharged to the space enclosed by the second muffler 1262 and the second bearing 1242 through the exhaust hole on the second bearing 1242.

[0056] In some embodiments, different from the related art,Figure 16 The exhaust holes can be omitted on the second silencer 1262. A plurality of air flow channels penetrating up and down are provided on the walls of the first bearing 1241, the first cylinder 1221, the middle partition 125, the second cylinder 1222, and the second bearing 1242. The compressed air in the second bearing 1242 and the second silencer 1262 is discharged upward through the air flow channels into the space surrounded by the first bearing 1241 and the first silencer 1261, and then discharged into the inner cavity of the compressor through the exhaust holes of the first silencer 1261.

[0057] In some embodiments, referring to Figure 1 , the compressor further includes a gas-liquid separator 200. The gas-liquid separator 200 is disposed outside the compressor body 100 and is configured to supply gaseous refrigerant to the compression chamber of the compression mechanism 120. The gas-liquid separator 200 separates the liquid refrigerant from the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 100 and causing abnormalities in the compressor.

[0058] In some embodiments, referring to Figure 1 and Figure 11 , the gas-liquid separator 200 includes a second housing 210; the gas-liquid separator 200 further includes an outlet pipe 240. The outlet pipe 240 is disposed at the bottom of the second housing 210. The first end of the outlet pipe 240 extends into the inner cavity of the second housing 210, and the second end of the outlet pipe 240 is connected to the compression mechanism 120. For example, the second end of the outlet pipe 240 is connected to the suction port of the cylinder 701 to supply gaseous refrigerant to the compression mechanism 120.

[0059] [Base feet]

[0060] Generally, the compressor body 100 includes rubber base feet. The rubber base feet are fixedly disposed at the bottom of the first housing 110. After the rubber base feet are installed, the vibration isolation amount of the rubber base feet and the overall machine mode of the compressor are determined. As the operating frequency range of the compressor continues to widen, for example, from 10 Hz to 160 Hz, on the one hand, the range of the sixth-order rigid body mode of the compressor is usually from 5 Hz to 30 Hz and is easily excited, thus causing severe shaking of the compressor. On the other hand, according to the stiffness vibration isolation principle, as the operating frequency range of the compressor increases, the self-mode of the rubber base feet is easily coupled with the compressor excitation, thereby reducing the vibration isolation effect of the rubber base feet, and further increasing the vibration and noise of the outdoor unit.

[0061] To solve this technical problem, in some embodiments, referring to Figure 3, the compressor includes at least one foot 300, and at least one foot 300 is disposed on the first housing 110. The foot 300 is configured to mount the compressor to the mounting carrier 500 where the compressor is located. For example, the compressor is fixedly mounted to the bottom plate of the outdoor unit through the foot 300. At this time, the mounting carrier 500 is the bottom plate of the outdoor unit.

[0062] In some embodiments, at least one foot 300 includes a plurality of feet 300. The plurality of feet 300 are respectively disposed at the bottom of the first housing 110, and the plurality of feet 300 are arranged at intervals along the circumferential direction of the first housing 110 to improve the mounting stability of the compressor.

[0063] In some embodiments, referring to Figure 4 , the foot 300 includes a housing 310. The housing 310 is configured to connect the first housing 110 and the bottom plate of the outdoor unit. The foot 300 further includes a second mounting cavity 311. The second mounting cavity 311 is formed in the housing 310. For example, the first end of the housing 310 is fixed to the first housing 110 by bolts, and the second end of the housing 310 is fixed to the bottom plate of the outdoor unit by bolts, and the first end and the second end are oppositely arranged.

[0064] In some embodiments, as Figure 4 shown, the foot 300 includes a support member 320. The support member 320 is disposed in the second mounting cavity 311. When the support member 320 is subjected to an external force, it can extend or contract along the height direction of the second mounting cavity 311 (i.e., the height direction of the compressor).

[0065] In some embodiments, the foot 300 further includes a first driving portion 330. The first driving portion 330 is disposed in the second mounting cavity 311. The first driving portion 330 is configured to adjust the stiffness of the support member 320 according to the vibration signal of the compressor to adjust the rigid body mode of the compressor.

[0066] In some embodiments, for the foot 300 of some embodiments of the present disclosure, the support member 320 actively adjusts the stiffness according to the vibration signal of the compressor, thereby adjusting the rigid body mode of the compressor. On the one hand, the active deviation of the stiffness mode of the compressor is realized, the violent shaking of the compressor is avoided, and the impact on the pipeline is reduced; on the other hand, when the compressor operates at high frequency, a high stiffness vibration isolation effect can be obtained, thereby reducing the vibration transmission amount and reducing the vibration and noise of the outdoor unit.

[0067] In some embodiments, referring to Figure 3 , the compressor further includes a first sensor 410. The first sensor 410 is disposed on the first housing 110, and the first sensor 410 is configured to detect the vibration signal of the first housing 110.

[0068] The compressor further includes a second sensor 420. The second sensor 420 is disposed on the bottom plate of the outdoor unit, and the second sensor 420 is configured to detect the vibration signal of the bottom plate.

[0069] The first driving part 330 is configured to adjust the stiffness of the support member 320 according to the vibration signal of the first housing 110 and the vibration signal of the bottom plate.

[0070] For the compressor according to some embodiments of the present disclosure, by using the first sensor 410 and the second sensor 420, the vibration isolation amount is determined, so as to actively adjust the stiffness of the support member 320, and further change the rigid body mode of the compressor.

[0071] In some embodiments, as Figure 5 shown, the compressor body 100 further includes a first controller 610. The first controller 610 is respectively coupled to the first sensor 410, the feet 300 and the mounting carrier 500.

[0072] In some embodiments, referring to Figure 5 , the adjustment process of the feet 300 includes S11 to S15.

[0073] S11, obtain the first vibration signal detected by the first sensor 410 and the second vibration signal detected by the second sensor 420.

[0074] For example, the first vibration signal refers to the vibration signal of the first housing 110; the second vibration signal refers to the vibration signal of the bottom plate.

[0075] S12, process and analyze the first vibration signal and the second vibration signal.

[0076] For example, the first controller 610 can process and analyze the first vibration signal and the second vibration signal.

[0077] S13, according to the analysis data of the first controller 610, judge whether the compressor is in the fixed-frequency (natural frequency) operation state at this time, and whether the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is greater than the set value X; if "yes", execute step S15; if "no", execute step S14.

[0078] S14, the first driving part 330 drives the support member 320 to extend to reduce the stiffness.

[0079] For example, when it is determined that the compressor is in a non-fixed-frequency operation state or the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is less than or equal to the set value X, control the first driving part 330 to drive the support member 320 to extend to reduce the stiffness.

[0080] S15, drive the support member 320 to contract to increase the stiffness.

[0081] For example, when it is determined that the compressor is operating at a fixed frequency or the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is greater than the set value X, the first driving part 330 is controlled to drive the support member 320 to extend to reduce the stiffness.

[0082] In some embodiments, referring to Figure 4 , the first driving part 330 includes a first driving motor 331. The power shaft end of the first driving motor 331 is connected to a first threaded column 332. A moving part 333 is arranged on the first threaded column 332. The moving part 333 is configured to move along the telescopic direction of the support member 320 to adjust the stiffness of the support member 320.

[0083] When the power shaft of the first driving motor 331 rotates in a first direction (e.g., clockwise), the first threaded column 332 drives the moving part 333 to move upward, and the moving part 333 presses the support member 320, and the support member 320 contracts under force.

[0084] When the power shaft of the first driving motor 331 rotates in a second direction (e.g., counterclockwise), the first threaded column 332 drives the moving part 333 to move downward, and the support member 320 rebounds and extends.

[0085] In some embodiments, the moving part 333 has a flat plate-like structure, and there is a gap between the outer peripheral end side of the moving part 333 and the inner cavity wall of the housing 310 to avoid increasing the friction force due to the contact between the moving part 333 and the housing 310.

[0086] In some embodiments, the support member 320 is a spring. The spring is sleeved on the outer periphery of the first threaded column 332. The first end of the spring abuts against the moving part 333, and the second end of the spring abuts against the top wall of the second installation cavity 311.

[0087] The first threaded column 332 is located inside the spring, and the structural layout is compact. The spring is limited between the moving part 333 and the top wall of the second installation cavity 311, and the structure is reliable.

[0088] In some embodiments, referring to Figure 4 , the housing 310 includes a first sub-housing 312. The first sub-housing 312 is configured to be connected to the bottom plate of the outdoor unit, and the first sub-housing 312 constitutes the bottom wall of the second installation cavity 311. For example, the first sub-housing 312 is fixed to the bottom plate by bolts. The first driving motor 331 is arranged on the first sub-housing 312.

[0089] In some embodiments, referring to Figure 4 , the housing 310 further includes a second sub-housing 313. A second installation cavity 311 is formed inside the second sub-housing 313. The second sub-housing 313 is connected to the first sub-housing 312. For example, the second sub-housing 313 is welded to the first sub-housing.

[0090] In some embodiments, referring to Figure 4 , the housing 310 further includes a third sub-housing 314. The third sub-housing 314 is connected to the second sub-housing 313. For example, the third sub-housing 314 is welded to the second sub-housing 313. The third sub-housing 314 and the first sub-housing 312 are disposed at opposite ends of the second sub-housing 313, and the third sub-housing 314 is configured to be connected to the first housing 110 of the compressor. For example, the third sub-housing 314 is fixedly connected to the outside of the first housing 110 by bolts.

[0091] In some embodiments, the housing 310 is made of rubber to enhance the vibration isolation effect of the feet 300.

[0092] [The second connection portion of the gas-liquid separator]

[0093] When the second harmonic noise of the rotary compressor is relatively large, it makes a relatively large contribution to the noise, vibration, and harshness (NVH) of the outdoor unit. Through modal analysis, it is found that the reason for the relatively large second harmonic noise of the compressor is the first-order rigid body torsional mode of the gas-liquid separator 200. The rigid body mode is only affected by the constraint boundary, that is, the greater the boundary stiffness, the higher the rigid body mode of the gas-liquid separator 200. Compressors usually improve the welding stiffness and increase the number of solder joints to increase the natural frequency of the gas-liquid separator 200. However, as the operating range of the compressor expands, the effect of increasing the natural frequency of the gas-liquid separator 200 by improving the welding stiffness and increasing the number of solder joints is limited.

[0094] To solve this technical problem, in some embodiments, referring to Figure 1 and Figure 6 , the compressor further includes a first connection portion 220. The first connection portion 220 is configured to fixedly connect the first housing 110 and the second housing 210.

[0095] For example, one side of the first connection portion 220 is welded to the first housing 110, and the other side of the first connection portion 220 surrounds the second housing 210 to fix the second housing 210.

[0096] The compressor further includes a second connection portion 230. As Figure 6 shown, the second connection portion 230 includes a fixing portion 231; the second connection portion 230 further includes two moving portions 232. The fixing portion 231 is fixedly connected to the first housing 110, and the two moving portions 232 are disposed on opposite sides of the fixing portion 231 along the length direction. The two moving portions 232 are configured to move toward the second housing 210 to surround the second housing 210 or move away from the second housing 210 to separate from the second housing 210 according to the vibration signal of the gas-liquid separator 200.

[0097] In some embodiments of the present disclosure, the second connecting portion 230 adjusts the rigid body mode of the gas-liquid separator 200 by the movement of the two moving portions 232, so as to achieve the offset of the natural frequency of the gas-liquid separator 200 and reduce the compressor double-frequency abnormal noise.

[0098] Refer to the frequency response function curve graph of the gas-liquid separator 200 Figure 8 , Curve A is the frequency response function curve graph of the gas-liquid separator 200 when the two moving portions 232 surround the second housing 210, and curve B is the frequency response function curve graph of the gas-liquid separator 200 when the two moving portions 232 are separated from the second housing 210.

[0099] In some embodiments, refer to Figure 1 , the compressor includes a third sensor 430, the third sensor 430 is disposed on the second housing 210, and the third sensor 430 is configured to detect the vibration signal of the second housing 210, that is, the vibration signal of the gas-liquid separator 200.

[0100] In some embodiments, when the operating frequency of the compressor is lower than the first set frequency, for example, lower than 60 rps (revolutions per second), the rigid body mode of the gas-liquid separator 200 is triggered, and the two moving portions 232 move towards the direction close to the second housing 210 to surround the second housing 210, so as to achieve the offset of the natural frequency of the gas-liquid separator 200.

[0101] In some embodiments, when the operating frequency of the compressor is higher than the second set frequency, for example, higher than 60 rps, the rigid body mode of the gas-liquid separator 200 is triggered, and the two moving portions 232 move towards the direction away from the second housing 210 to separate from the second housing 210, so as to achieve the offset of the natural frequency of the gas-liquid separator 200.

[0102] In some embodiments, as Figure 7 shown, the control process of the second connecting portion 230 includes S21 to S25.

[0103] S21, obtain the third vibration signal of the gas-liquid separator 200 detected by the third sensor 430.

[0104] For example, the third vibration signal may refer to the vibration signal of the gas-liquid separator 200.

[0105] S22, determine whether the amplitude value of the third vibration signal is greater than the set value N. If "yes", execute step S23; if "no", return to execute step S21.

[0106] S23, determine whether the operating frequency of the compressor is greater than the set value M. If "yes", execute step S25; if "no", return to execute step S24.

[0107] S24. Control the two moving parts 232 to move towards the second housing 210 to surround the second housing 210.

[0108] S25. Control the two moving parts 232 to move away from the second housing 210 to separate from the second housing 210.

[0109] In some embodiments, referring to Figure 6 , the fixing part 231 includes a first sub-fixing part 2311; the fixing part 231 further includes two second sub-fixing parts 2312, and the two second sub-fixing parts 2312 are arranged on opposite sides of the first sub-fixing part 2311 along the length direction of the first sub-fixing part 2311. The fixing part 231 has a U-shaped structure.

[0110] The first sub-fixing part 2311 is fixedly connected to the first housing 110. For example, the first sub-fixing part 2311 is welded to the first housing 110. The first sub-fixing part 2311 is arc-shaped to fit the outer contour of the first housing 110.

[0111] The second sub-fixing part 2312 extends from the first sub-fixing part 2311 towards the second housing 210, and the second sub-fixing part 2312 is rotatably connected to the moving part 232.

[0112] In some embodiments, the second connecting part 230 further includes a third driving motor. Referring to Figure 6 , the second connecting part 230 further includes a driving shaft 233. The power shaft end of the third driving motor is connected to the driving shaft 233, and the second sub-fixing part 2312 and the moving part 232 are rotatably connected through the driving shaft 233.

[0113] For example, the third driving motor is fixedly installed on the fixing part 231 or, the third driving motor is fixedly installed on the second housing 210.

[0114] In some embodiments, the moving part 232 is arc-shaped to fit the outer contour of the second housing 210, thereby improving the surrounding effect on the second housing 210.

[0115] [Inner cavity separation structure of gas-liquid separator]

[0116] Generally, a partition is provided inside the gas-liquid separator 200 to separate its internal space, thereby changing the acoustic cavity mode to increase or decrease the modal frequency. After the partition is fixed, the natural frequency of the acoustic cavity inside the gas-liquid separator 200 is determined. However, as the operating frequency range and pressure range of the compressor increase, and the physical parameters such as the physical properties of the refrigerant and the speed of sound change beyond the threshold range, the fixed acoustic cavity mode of the gas-liquid separator 200 is difficult to adapt to different operating scenarios of the compressor, resulting in large vibration and noise of the gas-liquid separator 200.

[0117] To solve this technical problem, in some embodiments, referring to Figures 11 to 13 , the gas-liquid separator 200 includes a first partition portion 250. The first partition portion 250 is fixedly disposed in the inner cavity of the gas-liquid separator 200. The gas-liquid separator 200 further includes a first chamber 291; the gas-liquid separator 200 further includes a second chamber 292. The first partition portion 250 divides the inner cavity of the gas-liquid separator 200 into a first chamber 291 and a second chamber 292. The first chamber 291 and the second chamber 292 are arranged in sequence along the height direction of the second housing 210, and the first chamber 291 is located above the second chamber 292. The gas outlet pipe 240 passes through the first partition portion 250, and one end of the gas outlet pipe 240 is located in the first chamber 291.

[0118] Referring to Figure 11 and Figure 12 , the first partition portion 250 is a plate-like structure, and the outer peripheral end side of the first partition portion 250 is welded to the inner peripheral wall of the second housing 210. The first partition portion 250 includes a first partition portion body; the first partition portion 250 further includes a plurality of first openings 251. The plurality of first openings 251 are provided in the first partition portion body and are for the refrigerant to flow through.

[0119] Referring to Figures 11 to 13 , the gas-liquid separator 200 includes a second partition portion 260, and the second partition portion 260 is disposed in the second chamber 292. The second chamber 292 includes a first sub-chamber 293; the second chamber 292 further includes a second sub-chamber 294. The second partition portion 260 divides the second chamber 292 into a first sub-chamber 293 and a second sub-chamber 294. The first sub-chamber 293 and the second sub-chamber 294 are arranged in sequence along the height direction of the second housing 210, and the first sub-chamber 293 is located on the side of the second sub-chamber 294 close to the first chamber 291.

[0120] The first partition portion 250 and the second partition portion 260 divide the inner cavity of the second housing 210 into three chambers, namely a first chamber 291, a first sub-chamber 293, and a second sub-chamber 294. These three chambers are arranged in sequence along the height direction of the second housing 210.

[0121] Referring to Figures 11 to 13 , the gas-liquid separator 200 further includes a second driving portion 270, and the second driving portion 270 is configured to drive the second partition portion 260 to move along the height direction of the second housing 210 to adjust the acoustic cavity mode of the gas-liquid separator 200.

[0122] In the gas-liquid separator 200 of some embodiments of the present disclosure, the second driving portion 270 drives the second partition portion 260 to move along the height direction of the second housing 210, adjusts the volumes of the first sub-chamber 293 and the second sub-chamber 294, and further adjusts the acoustic cavity mode of the gas-liquid separator 200, thereby achieving the effect of reducing the vibration and noise of the gas-liquid separator 200.

[0123] In some embodiments, the second driving part 270 drives the second partitioning part 260 to move towards or away from the first partitioning part 250 according to the vibration signal of the second housing 210.

[0124] When the second partitioning part 260 moves towards the first partitioning part 250, the volume of the first sub-chamber 293 decreases, and the volume of the second sub-chamber 294 increases.

[0125] When the second partitioning part 260 moves away from the first partitioning part 250, the volume of the first sub-chamber 293 increases, and the volume of the second sub-chamber 294 decreases.

[0126] In some embodiments, the initial position of the second partitioning part 260 is close to the first partitioning part 250. Thus, initially, the volume of the first sub-chamber 293 is small, and the volume of the second sub-chamber 294 is large.

[0127] When the gas-liquid separator 200 is in a non-resonant operating state, the second driving part 270 drives the second partitioning part 260 to move away from the first partitioning part 250, so that the volume of the first sub-chamber 293 increases and the volume of the second sub-chamber 294 decreases. When the vibration signal detected by the third sensor 430 is less than or equal to the second set value P, the second partitioning part 260 stops moving.

[0128] Here, the magnitude of the second set value P is related to the displacement of the compressor.

[0129] In some embodiments, referring to Figure 14 , the control process of the gas-liquid separator 200 includes S31 to S37.

[0130] S31, obtain the third vibration signal of the second housing 210 detected by the third sensor 430.

[0131] S32, the second controller 620 analyzes and processes the third vibration signal.

[0132] S33, determine whether the gas-liquid separator 200 is in a non-structural fixed-frequency operating state and whether the amplitude value of the third vibration signal is greater than the second set value P. If "yes", execute step S34; if "no", execute step S37.

[0133] S34, control the second driving part 270 to drive the second partitioning part 260 to move away from the first partitioning part 250.

[0134] S35, determine whether the vibration signal detected by the third sensor 430 is less than or equal to the second set value P. If "yes", execute step S36; if "no", return to execute step S34.

[0135] S36, control the second partition portion 260 to stop moving. S37, control the second driving portion 270 to remain stationary, and the second partition portion 260 to remain stationary.

[0136] In some embodiments, referring to Figure 12 , the second driving portion 270 includes a second driving motor 271, and the second driving portion 270 further includes at least one second threaded post 272. The second threaded post 272 is disposed at the power shaft end of the second driving motor 271. The first end of the second threaded post 272 is fixedly connected to the first partition portion 250, and the second end of the second threaded post 272 is threadedly connected to the second partition portion 260. The second driving motor 271 is fixedly disposed on the second partition portion 260.

[0137] When the power shaft of the second driving motor 271 rotates in a first direction (e.g., clockwise), the second partition portion 260 moves away from the first partition portion 250.

[0138] When the power shaft of the second driving motor 271 rotates in a second direction (e.g., counterclockwise), the second partition portion 260 moves closer to the first partition portion 250.

[0139] In some embodiments, at least one second threaded post 272 includes a plurality of second threaded posts 272. The plurality of second threaded posts 272 are arranged at intervals along the circumferential direction of the second partition portion 260. At least one of the plurality of second threaded posts 272 is connected to the power shaft end of the second driving motor 271. In this way, it helps to improve the movement reliability of the second partition portion 260.

[0140] For example, referring to Figure 12 , at least one second threaded post 272 includes two second threaded posts 272, and the two second threaded posts 272 are symmetrically arranged with respect to the central axis of the second partition portion 260.

[0141] In some embodiments, referring to Figure 12 , the second partition portion 260 further includes a second partition portion body; the second partition portion 260 further includes a second opening 261. The second opening 261 is provided in the second partition portion body, and the air outlet pipe 240 passes through the second opening 261 to avoid interference between the movement of the second partition portion 260 and the air outlet pipe 240. The diameter of the second opening 261 is larger than the diameter of the air outlet pipe 240. In this way, the gap between the second opening 261 and the air outlet pipe 240 facilitates the circulation of the refrigerant.

[0142] In some embodiments, the second partition portion 260 is a plate-like structure, and there is a gap between the outer peripheral side of the second partition portion 260 and the inner peripheral wall of the second housing 210, which avoids contact between the two and increases the frictional force, and also facilitates the circulation of the refrigerant.

[0143] [Outlet pipe of the gas-liquid separator]

[0144] Referring to Figure 15 , the outlet pipe 240 includes an outlet pipe body; the outlet pipe 240 further includes a liquid return hole 241. The liquid return hole 241 is provided in the outlet pipe body. The refrigerant in the system enters the suction port of the compression mechanism 120 through the gas-liquid separator 200, and the oil droplets carried by the refrigerant will accumulate in the gas-liquid separator 200 and return to the compressor through the liquid return hole 241. If the position of the liquid return hole 241 is too high or the aperture is too small, when the system operation reaches dynamic balance, too much oil will accumulate in the gas-liquid separator 200, resulting in an increase in cost. If the position of the liquid return hole 241 is too low or the aperture is too large, it is likely to cause liquid hammer, exceeding the bearing range of the cylinder 701 and damaging the mechanical components of the compressor, which is not conducive to the reliability of the compressor.

[0145] To solve this technical problem, in some embodiments, referring to Figure 15 , the outlet pipe 240 includes M liquid return holes 241. The M liquid return holes 241 are arranged along the height direction of the outlet pipe 240, the aperture of the liquid return hole 241 is D, and the distance between two adjacent liquid return holes 241 is N n , n=(1,... M - 1), then the aperture D of the liquid return hole 241 and the distance Nn between two adjacent liquid return holes 241 satisfy:

[0146] D×M / (N1+...+N M-1 )∈(0.15, 0.20)

[0147] By designing the liquid return hole 241 as described above, the position and aperture of the liquid return hole 241 are within a reasonable data range, thereby improving the oil return rate and the efficiency of the compressor.

[0148] In some embodiments, if the distance between two adjacent liquid return holes 241 is the same and is N, then the aperture D of the liquid return hole 241 and the distance N between two adjacent liquid return holes 241 satisfy:

[0149] D×M / ((M - 1)×N)∈(0.15, 0.20)

[0150] In some embodiments, referring to Figure 15 , two liquid return holes 241 are provided on the outlet pipe 240.

[0151] In some embodiments, referring to the reference body 11 and Figure 15 , the gas-liquid separator 200 includes two outlet pipes 240, namely a first outlet pipe 242 and a second outlet pipe 243, and M liquid return holes 241 are provided on any one of the outlet pipes 240.

[0152] Referring to Figure 11 and Figure 16, the compression mechanism 120 includes two cylinders 701, namely a first cylinder 1221 and a second cylinder 1222 respectively. Two air outlet pipes 240 are respectively and correspondingly communicated with the compression chambers of the two cylinders 701. For example, the first air outlet pipe 242 is communicated with the air suction port of the first cylinder 1221, and the second air outlet pipe 243 is communicated with the air suction port of the second cylinder 1222.

[0153] [Silencer]

[0154] In some embodiments, referring to Figure 9 and Figure 16 , the silencer 704 (the first silencer 1261, the second silencer 1262) includes an expansion silencer 141. The expansion silencer 141 is arranged on the bearing 703 and covers the air exhaust port on the bearing 703. At least one first installation cavity is arranged on the expansion silencer 141, and the first installation cavity is communicated with the inner cavity of the expansion silencer 141.

[0155] The silencer 704 further includes at least one Helmholtz silencer 142. The Helmholtz silencer 142 is arranged in the first installation cavity.

[0156] The first silencer 1261 includes an expansion silencer 141 and at least one Helmholtz silencer 142. The second silencer 1262 includes an expansion silencer 141 and at least one Helmholtz silencer 142.

[0157] The silencer 704 in the compressor of some embodiments of the present disclosure combines the advantages of the resonance chambers of the expansion silencer 141 and the Helmholtz silencer 142, combines the two into one structural member, facilitates installation and replacement, and can effectively increase the transmission sound loss inside the compressor and reduce the fluid noise of the compressor without increasing the clearance volume, realizing the effective suppression of the fluid noise inside the compressor from low frequency to high frequency.

[0158] Figure 10 is the sound attenuation curve graph of the silencer. Curve c is the sound attenuation curve of the silencer after adopting the combination of the expansion silencer 141 and the Helmholtz silencer 142 as shown in Figure 9 . Curve d is the sound attenuation curve of only adopting the expansion silencer 141.

[0159] In some embodiments, referring to Figure 9 , the expansion silencer 141 includes a first wall 1411; the expansion silencer 141 further includes a second wall 1412, the second wall 1412 is arranged along the circumferential direction of the first wall 1411 and extends towards the direction close to the cylinder 701, and the first installation cavity is arranged on the first wall 1411.

[0160] The first wall 1411 facilitates the setting of the first installation cavity and the installation of the Helmholtz silencer 142.

[0161] In some embodiments, at least one first installation cavity includes a plurality of first installation cavities, and the plurality of first installation cavities are arranged at intervals on the first wall 1411. In this way, at least one Helmholtz silencer 142 includes a plurality of Helmholtz silencers 142, and the plurality of Helmholtz silencers 142 are arranged on the expansion silencer 141, which is conducive to improving the silencing effect.

[0162] In some embodiments, the first wall 1411 has a portion protruding in a direction away from the cylinder 701 to form a first installation cavity. In this way, the first installation cavity and the first wall 1411 are an integral piece, for example, the first wall 1411 is formed into the first installation cavity by stamping.

[0163] In some embodiments, an opening is provided on the first wall 1411, a connecting piece is provided on the side of the first wall 1411 away from the cylinder 701, the connecting piece is arranged opposite to (eg, directly opposite to) the opening 3, a first installation cavity is formed in the connecting piece, and the first installation cavity is connected to the opening.

[0164] In this way, the connecting piece is a hollow cylindrical structure with one side open. The connecting piece is fixed to the first wall 1411 by welding or the like. The connecting piece is located outside the first wall 1411. The opening of the connecting piece is opposite to the opening 3 (such as directly opposite). The first installation cavity formed in the connecting piece is connected to the inner cavity of the expansion muffler 141 through the opening.

[0165] When installing the silencer 704 , the Helmholtz silencer 142 is first fixedly installed in the inner cavity of the connecting member, and then the connecting member is fixedly installed to the outside of the expansion silencer 141 .

[0166] [Suction channel of compression mechanism]

[0167] In a dual-cylinder rolling rotor compressor, the phase difference between the two pistons in the two cylinders is 180°, which makes the compression process differ by 180° and the suction rate of the suction chamber also differ by 180°. Studies have found that suction pressure loss has a great impact on the cooling and heating capacity of the air conditioner. For example, when the pressure loss increases, the suction density decreases, and the compression mass of the refrigerant under the same volume decreases, which in turn leads to a decrease in the refrigerant circulation volume in the air conditioner, affecting the cooling and heating capacity of the air conditioner.

[0168] In order to solve this technical problem, in some embodiments, referring to Figure 16 Any cylinder 701 (the first cylinder 1221, the second cylinder 1222) includes at least one air intake channel 161; and any cylinder 701 also includes a ventilation channel 164. The ventilation channel 164 includes at least one first sub-ventilation channel 162, the air intake channel 161 is connected to the first sub-ventilation channel 162, and the air intake channel 161 is connected to the air outlet pipe 240.

[0169] The ventilation passage 164 further includes at least one second sub-ventilation passage 163. The second sub-ventilation passage 163 is disposed on the middle partition plate 125. When at least one suction passage 161 includes two suction passages 161, one of the two suction passages 161 is located within the first cylinder 1221, and the other suction passage 161 of the two suction passages 161 is located within the second cylinder 1222. The first sub-ventilation passage 162 and the second sub-ventilation passage 163 are in communication to connect the two suction passages 161 of the two cylinders 703. The second sub-ventilation passage 163 and the two first sub-ventilation passages 162 are in communication to form the ventilation passage 164.

[0170] When the first cylinder 1221 rapidly inhales, a part of the refrigerant within the suction passage 161 of the second cylinder 1222 flows into the first cylinder 1221 through the ventilation passage 164.

[0171] When the second cylinder 1222 rapidly inhales, a part of the refrigerant within the suction passage 161 of the first cylinder 1221 flows into the second cylinder 1222 through the ventilation passage 164.

[0172] In this way, by providing the ventilation passage 164, the refrigerant circulation amount within the air conditioner can be effectively increased, thereby enhancing the refrigeration and heating capabilities of the air conditioner.

[0173] In some embodiments, each cylinder 703 is provided with at least one first sub-ventilation passage 162, the middle partition plate 125 is provided with at least one second sub-ventilation passage 163, and at least one first sub-ventilation passage 162 and at least one second sub-ventilation passage 163 are respectively in corresponding communication.

[0174] For example, referring to Figure 16 , one first sub-ventilation passage 162 is respectively provided on the first cylinder 1221 and the second cylinder 1222, and one second sub-ventilation passage 163 is provided on the middle partition plate 125, thereby forming one ventilation passage 164.

[0175] For another example, two second sub-ventilation passages 163 are respectively provided on the first cylinder 1221 and the second cylinder 1222, and two second sub-ventilation passages 163 are provided on the middle partition plate 125, thereby forming two ventilation passages 164.

[0176] [Other structures]

[0177] In some embodiments, referring to Figure 1 , the inner diameter of the second housing 210 is D6. Referring to Figure 16 , the inner diameter of the suction passage 161 is D7, (D6 4 - D7 4 ) / D6 2 × D7 2> 4.6, this range can reduce the noise of the compressor.

[0178] In some embodiments, referring to Figure 17 , the outer diameter of the first shaft section 1211 is D2, a shaft hole 1216 is formed in the first shaft section 1211, and the inner diameter of the shaft hole 1216 is D3.

[0179] The rotor 132 is disposed on the first shaft section 1211. Referring to Figure 18 , the inner diameter of the rotor 132 is D1. The inner diameter D1 of the rotor 132, the outer diameter D2 of the first shaft section 1211, and the inner diameter D3 of the shaft hole 1216 satisfy:

[0180] (D1 - D2) / D3 = [0.002, 0.01].

[0181] If (D1 - D2) / D < 0.002, the clamping force of the rotor 132 is small, and there is a risk of the rotor 132 falling off.

[0182] If (D1 - D2) / D3 > 0.01, the compressive stress and electromagnetic loss of the rotor 132 increase, resulting in a decrease in the efficiency of the motor 130; and a higher shrink-fitting temperature is required, so that the inner diameter of the rotor 132 expands outward to be able to fit the eccentric crankshaft 121. If the temperature exceeds the Curie temperature of the magnet of the rotor 132, irreversible damage will be caused to the magnet; the outer diameter of the rotor 132 deforms outward seriously, resulting in an increased risk of stator 131 and rotor 132 rubbing.

[0183] In some embodiments of the present disclosure, by setting (D1 - D2) / D3 = [0.002, 0.01], the efficiency of the motor 130, the clamping force of the rotor 132, the shrink-fitting process, and the risk of reducing stator-rotor rubbing can be taken into account. Within this range, the efficiency of the motor 130 is high and there is no risk of the rotor 132 falling off.

[0184] In some embodiments, referring to Figure 1 , the inner diameter of the first housing 110 is D4, and the circumferential wall thickness of the first housing 110 is t. Referring to Figure 19 , the stator 131 is fixedly connected to the circumferential inner wall of the first housing 110, and the outer diameter of the stator 131 is D5. The inner diameter D4 of the first housing 110, the outer diameter D5 of the stator 131, and the circumferential wall thickness t of the first housing 110 satisfy:

[0185] (D5 - D4) / t = [0.02, 0.08], this range takes into account the efficiency of the motor 130, the clamping force of the stator 131, the shrink-fitting process, and the risk of reducing stator-rotor rubbing. The efficiency of the motor 130 is high and there is no risk of the stator 131 falling off.

[0186] If (D5 - D4) / t < 0.02, the clamping force of the stator 131 is small and there is a risk of falling off.

[0187] If (D5 - D4) / t > 0.08, the compressive stress on the stator 131 and the electromagnetic loss of the motor 130 increase, resulting in a decrease in the efficiency of the motor 130; and a higher shrink-fit temperature is required to expand the inner diameter of the housing outward so that the stator 131 can be sleeved in. The higher the temperature, the more serious the blueing of the housing; the inner diameter of the stator 131 deforms severely inward, resulting in an increased risk of stator-rotor rubbing.

[0188] In some embodiments, referring to Figure 2 , the compressor body 100 further includes an oil sump 150. The oil sump 150 is formed at the bottom of the accommodation cavity 111 of the first housing 110. After the compressor wears, the wear debris deposits in the oil sump 150. If too much wear debris deposits, it will be re-sucked into the compressor body 100, resulting in the compressor jamming.

[0189] To solve this technical problem, referring to Figure 2 , the compressor body 100 includes a fourth sensor 440. The fourth sensor 440 is disposed in the oil sump 150, and the fourth sensor 440 is configured to detect the chromaticity of the oil in the oil sump 150. For example, the fourth sensor 440 is a chromaticity sensor.

[0190] The chromaticity of the oil in the oil sump 150 is detected in real time by the fourth sensor 440 to evaluate whether the compressor is worn by the chromaticity of the oil.

[0191] If the chromaticity of the oil sump 150 detected by the fourth sensor 440 is greater than a third set value, the compressor alarms and shuts down automatically, thereby reducing the failure rate.

[0192] In some embodiments, the fourth sensor 440 is fixedly mounted to the bottom wall of the first housing 110 by means of a buckle or the like.

[0193] In some embodiments, referring to Figure 11 , the gas-liquid separator 200 further includes a filter screen 280. The filter screen 280 is located at the top of the inner cavity of the gas-liquid separator 200. The height of the second housing 210 is H1, and the height of the outlet pipe 240 located inside the cavity is H2. The height H1 of the second housing 210 and the height H2 of the outlet pipe 240 located inside the cavity satisfy:

[0194] 0.5 < H2 / H1 < 0.8. This range can improve the gas-liquid separation performance of the gas-liquid separator 200 and reduce vibration noise.

[0195] If H2 / H1 > 0.8, the length of the outlet pipe 240 located in the inner cavity of the gas-liquid separator 200 is long, which will cause interference between the outlet pipe 240 and the filter screen 280; the length of the outlet pipe 240 extending out of the first partition 250 is too long, and the top end of the outlet pipe 240 deforms greatly, easily exciting the outlet pipe 240 to generate a bending mode and generating vibration noise.

[0196] If H2 / H1 < 0.5, the effective volume in the gas-liquid separator 20 is insufficient, which affects the gas-liquid separation performance.

[0197] In the description of the above embodiments, the specific features, structures, materials or characteristics may be combined in any one or more embodiments or examples in a suitable manner.

[0198] The above are only the specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by those skilled in the art within the technical scope disclosed by the present invention should be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims

1. A compressor, characterized in that: include: a compressor body including a compression mechanism configured to compress a refrigerant; A gas-liquid separator is configured to separate gaseous refrigerant and liquid refrigerant, the gas-liquid separator comprising: an air outlet pipe, the air outlet pipe being configured to input the gaseous refrigerant in the gas-liquid separator into the compression chamber of the compression mechanism; Liquid return hole, the outlet pipe is provided with M liquid return holes along its height direction, the aperture of the liquid return hole is D, and the distance between two adjacent liquid return holes is Nn, n=(1,...,M-1), D×M / (N1+...+N M-1 )∈(0.15, 0.20).

2. The compressor according to claim 1, characterized in that The distance between two adjacent liquid return holes is the same and is N, D×M / ((M-1)×N)∈(0.15, 0.20).

3. The compressor according to claim 1, characterized in that Two liquid return holes are arranged on the air outlet pipe.

4. The compressor according to claim 1, characterized in that The gas-liquid separator comprises two gas outlet pipes, each of which is provided with M liquid return holes; The compression mechanism comprises two cylinders, and the two air outlet pipes are respectively connected with the compression chambers of the two cylinders.

5. The compressor according to claim 4, characterized in that The compression mechanism also includes: An eccentric crankshaft, comprising a connecting shaft section and two eccentric shaft sections, wherein the two eccentric shaft sections are arranged at intervals along the axial direction of the eccentric crankshaft, and the connecting shaft section is located between the two eccentric shaft sections; Two pistons, the pistons are sleeved on the eccentric shaft segments, and the two pistons are respectively arranged corresponding to the two eccentric shaft segments; A middle partition plate is sleeved on the connecting shaft section, and a second sub-ventilation channel is arranged on the middle partition plate; Wherein, the two cylinders are respectively arranged corresponding to the two pistons, the pistons are located in the compression chambers of the corresponding cylinders, and any one of the cylinders comprises an air intake channel and a first sub-ventilation channel, and the air intake channel is connected to the first sub-ventilation channel; The first sub-breathing passage is communicated with the second sub-breathing passage to connect the two intake passages of the two cylinders.

6. The compressor according to claim 5, characterized in that At least one of the first ventilation sub-channels is disposed on each of the cylinders, and at least one of the second ventilation sub-channels is disposed on the middle partition plate. The at least one first ventilation sub-channel is connected to the at least one second ventilation sub-channel in a one-to-one correspondence.

7. The compressor according to any one of claims 1 to 6, characterized in that The gas-liquid separator also includes: A first partition is fixedly disposed in the inner cavity of the gas-liquid separator and divides the inner cavity into a first cavity and a second cavity, wherein the first cavity and the second cavity are arranged at intervals along the height direction of the gas-liquid separator, the gas outlet pipe passes through the first partition, and one end of the gas outlet pipe is located in the first cavity; A second partition, disposed in the second cavity; The driving part is configured to drive the second partition part to move along the height direction of the gas-liquid separator to adjust the acoustic cavity mode of the gas-liquid separator.

8. The compressor according to claim 7, characterized in that The gas-liquid separator also includes a second shell and a third sensor, wherein the third sensor is disposed on the second shell and is configured to detect a vibration signal of the second shell, and the driving unit drives the second partition to move toward or away from the first partition according to the vibration signal.

9. The compressor according to claim 7, characterized in that The driving part includes a driving motor, a threaded column is arranged at the power shaft end of the driving motor, a first end of the threaded column is fixedly connected to the first partition, a second end of the threaded column is threadedly connected to the second partition, and the driving motor is fixedly arranged at the second partition.

10. An air conditioner, comprising a compressor, an evaporator, a condenser and a throttling device, characterized in that: The compressor is a compressor according to any one of claims 1 to 9.

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