Compressor and air conditioner

Abstract

A compressor (1000) and an air conditioner. The compressor (1000) comprises a compressor body (100) and a foot (300). The compressor body (100) comprises a first housing (110); the foot (300), which is provided on the first housing (110), is capable of mounting the compressor body (100) to a mounting base (500) on which the compressor (1000) is situated, and comprises a housing (310), supporting members (320), and a first driving portion (330). The housing (310) is connected to the first housing (110) and the mounting base (500), and the first driving portion (330) is capable of adjusting a rigidity of the supporting members (320) according to a vibration signal of the compressor (1000).

Description

Compressor and air conditioner

[0001] This application claims priority to Chinese Patent Application No. 202421841468.9, filed on July 31, 2024; Chinese Patent Application No. 202421841352.5, filed on July 31, 2024; Chinese Patent Application No. 202421841376.0, filed on July 31, 2024; Chinese Patent Application No. 202421841416.1, filed on July 31, 2024; Chinese Patent Application No. 202421841447.7, filed on July 31, 2024; Chinese Patent Application No. 202421841398.7, filed on July 31, 2024; Chinese Patent Application No. 202421841456.6, filed on July 31, 2024; Chinese Patent Application No. 202421841329.6, filed on July 31, 2024; Chinese Patent Application No. 202411045632.X, filed on July 31, 2024; Chinese Patent Application No. 202421841441.X, filed on July 31, 2024; and Chinese Patent Application No. 202411045637.2, filed on July 31, 2024; the contents of all of which are incorporated herein by reference in their entirety. TECHNICAL FIELD

[0002] The present disclosure relates to the field of air conditioning technology, and in particular, to a compressor and an air conditioner. BACKGROUND

[0003] 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 cycle or a heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve, and an evaporator.

[0004] SUMMARY

[0005] The present disclosure aims to solve one of the technical problems in the related art. To this end, the present disclosure provides a compressor that can solve the technical problem that the self mode of the foot and the compressor excitation are coupled with each other, reduce the vibration isolation effect of the foot, and thus increase the vibration and noise of the outdoor unit of the air conditioner.

[0006] In one aspect, a compressor is provided. The compressor includes a compressor body and a foot. The compressor body includes a first shell; the foot is arranged on the first shell, and the foot can mount the compressor body to a mounting carrier where the compressor is located, and the foot includes an outer shell, a support and a first driving part. The outer shell connects the first shell and the mounting carrier, and an installation cavity is formed in the outer shell. The support is arranged in the installation cavity; and the first driving part is arranged in the installation cavity, and the first driving part can adjust the rigidity of the support according to a vibration signal of the compressor.

[0007] The compressor in some embodiments of the present disclosure improves the foot, effectively suppresses the rigid body mode of the compressor in low-frequency operation, improves the vibration isolation effect of the compressor in high-frequency operation, and further reduces the vibration and noise of the outdoor unit.

[0008] In another aspect, an air conditioner is provided. The air conditioner includes the compressor, an evaporator, a condenser and a throttling device.

[0009] The air conditioner in some embodiments of the present disclosure improves the foot, effectively suppresses the rigid body mode of the compressor in low-frequency operation, improves the vibration isolation effect of the compressor in high-frequency operation, and further reduces the vibration and noise of the outdoor unit. BRIEF DESCRIPTION OF DRAWINGS

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

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

[0012] FIG. 3 is a structural diagram of a bearing according to some embodiments;

[0013] FIG. 4 is an exploded view of a bearing according to some embodiments;

[0014] FIG. 5 is a sectional view of a bearing according to some embodiments;

[0015] FIG. 6 is a structural diagram of a first bearing part according to some embodiments;

[0016] FIG. 7 is a structural diagram of a bearing bush according to some embodiments;

[0017] FIG. 8 is another sectional view of a bearing according to some embodiments;

[0018] FIG. 9 is a graph of the relationship between θ1 / φ+θ2 / φ and the first ratio and oil discharge rate according to some embodiments;

[0019] FIG. 10 is a graph of the relationship between N1 / N2 and the first ratio and oil discharge rate according to some embodiments;

[0020] FIG. 11 is a graph of T / D vs. first ratio, oil throw rate, according to some embodiments;

[0021] FIG. 12 is a graph of D1 / D2 vs. contact face pressure height, according to some embodiments;

[0022] FIG. 13 is a graph of H1 / H2 vs. contact face pressure height, according to some embodiments;

[0023] FIG. 14 is a graph of D2 / D3 vs. contact face pressure height, according to some embodiments;

[0024] FIG. 15 is a graph of (T1+T2) / D4 vs. contact face pressure height, according to some embodiments;

[0025] FIG. 16 is a diagram of an eccentric crankshaft, according to some embodiments;

[0026] FIG. 17 is an exploded view of an eccentric crankshaft, according to some embodiments;

[0027] FIG. 18 is a cross-sectional view of an eccentric crankshaft, according to some embodiments;

[0028] FIG. 19 is a diagram of an eccentric shaft segment, according to some embodiments;

[0029] FIG. 20 is an exploded view of an eccentric shaft segment, according to some embodiments;

[0030] FIG. 21 is a diagram of a multi-chip system, according to some embodiments;

[0031] FIG. 22 is a diagram of a compressor and gas-liquid separator, according to some embodiments;

[0032] FIG. 23 is another diagram of a compressor, according to some embodiments;

[0033] FIG. 24 is another cross-sectional view of a compressor body, according to some embodiments;

[0034] FIG. 25 is a diagram of a tee, according to some embodiments;

[0035] FIG. 26 is a diagram of a fixed portion, according to some embodiments.

[0036] FIG. 27 is a diagram of a compressor, according to some embodiments;

[0037] FIG. 28 is a cross-sectional view of a compressor, according to some embodiments;

[0038] FIG. 29 is another diagram of a compressor, according to some embodiments;

[0039] FIG. 30 is a diagram of a foot, according to some embodiments;

[0040] FIG. 31 is a flow chart of steps performed by a first controller, according to some embodiments;

[0041] FIG. 32 is a structural diagram of a second connection portion, according to some embodiments;

[0042] FIG. 33 is a flow chart of steps performed by a second controller, according to some embodiments;

[0043] FIG. 34 is a plot of a frequency response function of a gas-liquid separator, according to some embodiments;

[0044] FIG. 35 is a structural diagram of a first muffler and a second muffler, according to some embodiments;

[0045] FIG. 36 is a plot of a sound attenuation volume of a sound attenuation assembly, according to some embodiments;

[0046] FIG. 37 is a cross-sectional view of a gas-liquid separator, according to some embodiments;

[0047] FIG. 38 is a structural diagram of a first partition portion and a second partition portion, according to some embodiments;

[0048] FIG. 39 is a structural diagram of a gas-liquid separator, according to some embodiments;

[0049] FIG. 40 is another flow chart of steps performed by a second controller, according to some embodiments;

[0050] FIG. 41 is a structural diagram of an air outlet pipe, according to some embodiments;

[0051] FIG. 42 is a structural diagram of a compression mechanism, according to some embodiments;

[0052] FIG. 43 is a cross-sectional view of an eccentric crankshaft, according to some embodiments;

[0053] FIG. 44 is a structural diagram of a rotor, according to some embodiments;

[0054] FIG. 45 is a structural diagram of a stator, according to some embodiments. DETAILED DESCRIPTION

[0055] Some embodiments of the present disclosure will be described hereinafter in conjunction with the accompanying drawings. However, the described embodiments are only some embodiments of the present disclosure, but not all embodiments. Based on the embodiments provided in the present disclosure, all other embodiments obtained by those skilled in the art belong to the scope of protection of the present disclosure.

[0056] Unless the context clearly requires otherwise, throughout the description and the claims, the term "comprise," and variations thereof (e.g., "comprises" and "comprising"), will be construed both to cover the containing feature or features and additional feature or features. In describing some embodiments, the use of "connection" or "coupling" or variations thereof can be used. The term "connection" is to be construed broadly, for example, "connection" can be fixed connections, detachable connections, or integral; can be direct connections, or indirect connections through an intermediate medium. The embodiments disclosed herein are not necessarily limited by the content herein.

[0057] Hereinafter, the terms "first", "second", etc. are used only for the purpose of description, and should not be construed as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the embodiments of the present disclosure, the meaning of "a plurality of" is two or more, unless otherwise specified.

[0058] In describing some embodiments, the use of "connection" and its derivatives can be used. The term "connection" should be broadly understood, for example, "connection" can be fixed connection, detachable connection, or integral; can be direct connection, or indirect connection through an intermediate medium. The embodiments disclosed herein are not necessarily limited by the content herein.

[0059] "A, B, and C at least one of" has the same meaning as "at least one of A, B, or C", and includes the following combinations of A, B, and C: only A, only B, only C, a combination of A and B, a combination of A and C, a combination of B and C, and a combination of A, B, and C.

[0060] The use of "adapted for" or "configured for" herein means open and inclusive language that does not exclude devices adapted for or configured for performing additional tasks or steps.

[0061] As used herein, "about," "approximately," or "around" includes the recited value and the average value within an acceptable range of deviation from the particular value, as determined by one of ordinary skill in the art considering the measurement in question and the error in measuring the particular quantity (i.e., the limitations of the measurement system).

[0062] Generally, the compressor is fixedly provided in the outdoor unit. In the case of a rotor compressor, a compression structure is provided in an inner cavity of the compressor. An exhaust hole, which communicates with the inner cavity of the cylinder, and an exhaust valve, which can open or close the exhaust hole, are provided on a bearing of the compression mechanism. However, noise of striking the bearing can occur during movement of the exhaust valve, increasing the operating noise of the compressor and increasing the resistance to opening of the exhaust valve.

[0063] Some embodiments of the present disclosure provide a compressor, the foot is improved, the first driving part adjusts the stiffness of the support according to the vibration signal of the compressor to adjust the rigid body mode of the compressor, so that the rigid body mode of the compressor in low frequency operation can be effectively inhibited, the vibration isolation effect of the compressor in high frequency operation is improved, and then the vibration and noise of the outdoor unit are reduced.

[0064] [Air conditioner]

[0065] In some embodiments, the air conditioner performs a refrigeration cycle or a heating cycle of the air conditioner 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, and cools or heats an indoor space.

[0066] The low-temperature and low-pressure refrigerant enters the compressor, which compresses the low-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant gas and discharges the compressed refrigerant gas to the condenser. The condenser condenses the compressed gas refrigerant into a liquid-phase refrigerant, and releases the heat of the refrigerant to the surrounding environment through the condensation process.

[0067] The expansion valve expands the high-temperature and high-pressure liquid-phase refrigerant formed 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 exchanging heat with a material to be cooled using the latent heat of evaporation of the refrigerant. In the entire refrigeration cycle or heating cycle, the air conditioner can adjust the temperature of the indoor space.

[0068] The outdoor unit of the air conditioner includes the compressor and the outdoor heat exchanger, the indoor unit of the air conditioner includes the indoor heat exchanger, and the expansion valve can be provided in the indoor unit or the outdoor unit.

[0069] The indoor heat exchanger and the outdoor heat exchanger are used as a condenser or an evaporator. When the indoor heat exchanger is used as a condenser, the air conditioner performs a heating mode; when the indoor heat exchanger is used as an evaporator, the air conditioner performs a cooling mode.

[0070] The outdoor unit further comprises a four-way valve configured to switch the indoor heat exchanger and the outdoor heat exchanger as a condenser or an evaporator.

[0071] The working principle of the air conditioner in the cooling mode is that the compressor works to make the indoor heat exchanger (at this time, as an evaporator) in a low pressure state, the liquid refrigerant in the indoor heat exchanger evaporates rapidly and absorbs heat, the wind blown by the indoor fan becomes cold wind after being cooled by the coil of the indoor heat exchanger, and the cold wind is blown into the room, the evaporated refrigerant is pressurized by the compressor, and then condensed into liquid in the high pressure environment of the outdoor heat exchanger (at this time, as a condenser), and releases heat, which is dissipated to the atmosphere by the outdoor fan, so as to achieve the cooling effect.

[0072] The working principle of the air conditioner in the heating mode is that the gaseous refrigerant is pressurized by the compressor to become high-temperature and high-pressure refrigerant gas, the refrigerant gas enters the indoor heat exchanger (at this time, as a condenser), is condensed and liquefied to release heat, becomes liquid, and heats the indoor air, thereby achieving the purpose of increasing the indoor temperature. The liquid refrigerant is reduced in pressure by the throttling device and enters the outdoor heat exchanger (at this time, as an evaporator), the liquid refrigerant evaporates and absorbs heat to become gas, and absorbs the heat of the outdoor air to reduce the temperature of the outdoor air, and becomes gaseous refrigerant, which enters the compressor again to start the next cycle.

[0073] [Compressor body]

[0074] In some embodiments of the present disclosure, the compressor 1000 is a rolling rotor type compressor, referring to FIGS. 1 and 2, the compressor 1000 comprises a compressor body 100. The compressor body 100 comprises a first shell 110. The compressor body 100 further comprises a containing cavity 111. The containing cavity 111 is formed in the first shell 110. The compressor body 100 further comprises a compression mechanism 120. The compression mechanism 120 is arranged in the containing cavity 111. The compression mechanism 120 is configured to compress refrigerant. The compressor body 100 further comprises a first motor 130 (such as a motor), which is arranged in the containing cavity 111. In the height direction of the compressor body 100, the first motor 130 is arranged on the side (such as the upper side) of the compression mechanism 120 close to the exhaust port of the compressor body 1000. The first motor 130 is configured to provide power for the compression mechanism 120.

[0075] In some embodiments, referring to FIG. 2, the first motor 130 comprises a rotor 132. The first motor 130 further comprises a stator 131, which is fixedly connected with the inner wall of the first shell 110 to achieve fixed installation of the first motor 130 in the containing cavity 111.

[0076] In some embodiments, referring to FIG. 2, the compression mechanism 120 further comprises an eccentric crankshaft 140. The eccentric crankshaft 140 comprises a main shaft section 141. The main shaft section 141 is fixedly connected with the rotor 132.

[0077] Referring to FIG. 2, the compression mechanism 120 further comprises a cylinder 122; the compression mechanism 120 further comprises a piston 123. The eccentric crankshaft 140 further comprises an eccentric shaft section 142. The piston 123 is arranged in a compression chamber of the cylinder 122, and the piston 123 is sleeved on the eccentric shaft section 142. The compression mechanism 120 further comprises at least one bearing 150, for example, the at least one bearing 150 comprises two bearings 150, which are a first bearing 1241 and a second bearing 1242. The bearing 150 is fixedly connected with the cylinder 122, and the first bearing 1241 is fixedly connected with the inner wall of the first housing 110. The bearing 150 is provided with an exhaust hole, and the exhaust hole is in communication with the compression chamber.

[0078] The compression mechanism 120 further comprises a sliding vane groove; the sliding vane groove is arranged in the cylinder 122. The compression mechanism 120 further comprises a sliding vane. The sliding vane is arranged in the sliding vane groove. The eccentric crankshaft 140 drives the piston 123 to make a circumferential motion in the compression chamber, and the sliding vane reciprocates along the sliding vane groove, and the sliding vane is always in abutment with the piston 123. The compression chamber comprises a first sub-compression chamber (for example, a high-pressure chamber); the compression chamber further comprises a second sub-compression chamber (for example, a 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 123 divide the compression chamber into the first sub-compression chamber and the second sub-compression chamber.

[0079] The compression mechanism 120 further comprises at least one sound attenuation assembly 704. For example, the at least one sound attenuation assembly 704 comprises two sound attenuation assemblies 704, which are a first sound attenuation assembly 1261 and a second sound attenuation assembly 1262. The first sound attenuation assembly 1261 is arranged on the first bearing 1241, and the second sound attenuation assembly 1262 is arranged on the second bearing 1242.

[0080] The working principle of the compressor 1000 is as follows: the stator 131 of the first motor 130 generates a magnetic pull after being energized, the rotor 132 of the first motor 130 rotates under the magnetic pull of the stator 131 and drives the eccentric crankshaft 140 to rotate, the eccentric crankshaft 140 drives the piston 123 sleeved on the eccentric shaft segment 142 to move in an eccentric circle in the compression chamber of the cylinder 122, the sliding vane moves in the sliding vane groove, the sliding vane and the piston 123 divide the compression chamber of the cylinder 122 into the first sub-compression chamber and the second sub-compression chamber, the eccentric crankshaft 140 drives the piston 123 to rotate one circle, to complete a compression cycle by inhaling from the second sub-compression chamber and discharging from the first sub-compression chamber, so that the compressor 1000 compresses the gas, and the compressed gas is discharged through the discharge hole on the bearing 150.

[0081] In an embodiment of the present disclosure, referring to FIG. 2, the compressor 1000 is a single-cylinder rolling rotor compressor.

[0082] In some embodiments of the present disclosure, referring to FIG. 24, the compressor 1000 is a double-cylinder rolling rotor compressor, and the compression mechanism 120 includes the eccentric crankshaft 140. The compression mechanism 120 further includes two cylinders 122, i.e., a first cylinder 1221 and a second cylinder 1222. The compression mechanism 120 further includes two bearings 150, i.e., a first bearing 1241 and a second bearing 1242. The compression mechanism 120 further includes two pistons 123, i.e., a first piston 1231 and a second piston 1232. The compression mechanism 120 further includes a partition plate 125. The compression mechanism 120 further includes two silencing assemblies 704, i.e., a first silencing assembly 1261 and a second silencing assembly 1262.

[0083] [First gas-liquid separator]

[0084] In some embodiments, referring to FIG. 1, the compressor 1000 further includes a first gas-liquid separator 510. The first gas-liquid separator 510 is arranged outside the compressor body 100 and is configured to provide gaseous refrigerant into the compression chamber of the compression mechanism 120. The first gas-liquid separator 510 can separate the liquid refrigerant from the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 100 and causing the compressor 1000 to be abnormal.

[0085] In some embodiments, referring to FIG. 1, the first gas-liquid separator 510 comprises a second housing 512; the first gas-liquid separator 510 further comprises at least one first gas outlet pipe 511, which is arranged at the bottom of the second housing 512. A first end of the first gas outlet pipe 511 extends into the inner cavity of the second housing 512, and a second end of the first gas outlet pipe 511 is connected with the compression mechanism 120, for example, the second end of the first gas outlet pipe 511 is connected with the suction port of the cylinder 122, so as to provide gaseous refrigerant to the compression mechanism 120.

[0086] [the bearing]

[0087] In some embodiments, referring to FIG. 3 and FIG. 6, the bearing 150 comprises an exhaust hole 1511, which is in communication with the inner cavity of the cylinder 122, and is configured to exhaust refrigerant in the cylinder 122.

[0088] Referring to FIG. 2, FIG. 4 and FIG. 6, the compression mechanism 120 comprises an exhaust valve plate 170. The exhaust valve plate 170 is configured to open or close the exhaust hole 1511. When the exhaust valve plate 170 moves towards the exhaust hole 1511, the exhaust valve plate 170 covers the exhaust hole 1511, and the exhaust hole 1511 is closed. When the exhaust valve plate 170 moves away from the exhaust hole 1511, the exhaust hole 1511 is opened.

[0089] Referring to FIG. 4, the exhaust valve plate 170 comprises a first end 171; the exhaust valve plate 170 further comprises a second end 172; the exhaust valve plate 170 further comprises a first connecting section 173. The first connecting section 173 is connected between the first end 171 and the second end 172.

[0090] Referring to FIG. 6, the bearing 150 further comprises a bearing body; the bearing 150 further comprises a first mounting hole 1516 (such as a mounting hole). The first mounting hole 1516 is provided on the bearing body, and the first end 171 of the exhaust valve plate 170 is fixedly arranged on the bearing 150, for example, referring to FIG. 4 and FIG. 6, the first end 171 of the exhaust valve plate 170 is fixedly mounted to the first mounting hole 1516 by a bolt 190. The second end 172 can close or open the exhaust hole 1511.

[0091] Referring to FIG. 4, the compression mechanism 120 further comprises a lift limiter 180, which is configured to limit the opening stroke of the exhaust valve plate 170.

[0092] It should be noted that the exhaust valve plate 170 generates noise during movement, which increases the working noise of the compressor 1000 and increases the opening resistance of the exhaust valve plate 170.

[0093] To solve the technical problem, in some embodiments, referring to FIG. 3 and FIG. 6, the bearing 150 further comprises a first groove 1512. The first groove 1512 is arranged around the exhaust hole 1511. The first groove 1512 is configured to store oil. The bearing 150 further comprises an abutting portion 1515. The abutting portion 1515 is formed between the first groove 1512 and the exhaust hole 1511.

[0094] Referring to FIG. 6, the bearing 150 further comprises at least one second groove 1513, which is configured to store oil. When the compressor 1000 is running, the oil in the oil pool at the bottom of the compressor 1000 is supplied to any friction pair by the eccentric crankshaft 140, and the first groove 1512 and the second groove 1513 are filled with oil.

[0095] When the exhaust valve sheet 170 closes the exhaust hole 1511, the second groove 1513 is located between the first end 171 and the second end 172 of the exhaust valve sheet 170, and the exhaust valve sheet 170 is further configured to cover the first groove 1512 and the second groove 1513 and abut against the abutting portion 1515 when the exhaust valve sheet 170 closes the exhaust hole 1511.

[0096] When the exhaust valve sheet 170 closes the exhaust hole 1511, the first groove 1512 stores oil, and the exhaust valve sheet 170 is in contact with the oil, forming an oil seal, thereby improving the sealing effect of the exhaust hole 1511.

[0097] The outer surface of the abutting portion 1515 is a plane, so that the abutting portion 1515 abuts against the exhaust valve sheet 170, improving the sealing effect.

[0098] In some embodiments, the abutting portion 1515 is narrow in width, so as to reduce the contact area of the exhaust valve sheet 170 and the abutting portion 1515, thereby reducing the opening resistance of the exhaust valve sheet 170.

[0099] When the exhaust valve sheet 170 closes the exhaust hole 1511, the exhaust valve sheet 170 covers the second groove 1513, the second groove 1513 is filled with oil, and the second groove 1513 plays a role of shock absorption, which can reduce the impact sound of the exhaust valve sheet 170 hitting the bearing 150 when the exhaust valve sheet 170 is closed, thereby reducing the working noise of the compressor 1000.

[0100] In some embodiments, referring to FIG. 4 and FIG. 6, the at least one second groove 1513 comprises a plurality of second grooves 1513, which are arranged at intervals along the length direction of the exhaust valve sheet 170, so as to improve the noise reduction effect of the impact sound of the exhaust valve sheet 170.

[0101] In some embodiments, when the exhaust valve sheet 170 closes the exhaust hole 1511, the first connecting section 173 covers the second groove 1513, the second end 172 covers the first groove 1512, and the second end 172 closes the exhaust hole 1511.

[0102] It should be noted that the most of the impact sound of the exhaust valve piece 170 is generated by the first connecting section 173 impacting the bearing 150. The compressor 1000 in some embodiments of the present disclosure is provided with the first connecting section 173 to cover the second groove 1513, and the second groove 1513 is used to reduce the impact sound of the first connecting section 173 impacting the bearing 150, thereby improving the noise reduction effect.

[0103] The compressor 1000 in some embodiments of the present disclosure, when the exhaust valve piece 170 closes the exhaust hole 1511, the second end 172 of the exhaust valve piece 170 covers the exhaust hole 1511 to close the exhaust hole 1511, and the second end 172 abuts against the abutting portion 1515, which can improve the sealing effect of the exhaust hole 1511.

[0104] In some embodiments, referring to FIGS. 4 and 6, the bearing 150 further comprises a first bearing portion 151. The exhaust hole 1511, the first groove 1512, the at least one second groove 1513, and the first mounting hole 1516 are arranged on the first bearing portion 151. The bearing 150 further comprises an assembly hole 1514. The assembly hole 1514 is arranged on the first bearing portion 151.

[0105] Referring to FIG. 4, the bearing 150 further comprises a second bearing portion 152. The second bearing portion 152 is fixedly arranged on the first bearing portion 151. The second bearing portion 152 is fixedly arranged on one side of the first bearing portion 151. The second bearing portion 152 comprises a first shaft hole 1522 (such as a mounting hole), and the first shaft hole 1522 is in communication with the assembly hole 1514. The eccentric crankshaft 140 is mounted with the bearing 150 via the first shaft hole 1522 and the assembly hole 1514.

[0106] The bearing 150 in some embodiments of the present disclosure comprises a two-part structure (such as the first bearing portion 151 and the second bearing portion 152), which facilitates processing and manufacturing.

[0107] The bearing 150 is usually a cast part, and has a low elastic modulus. The wear between the bearing 150 and the eccentric crankshaft 140 is large. The processing process of the bearing 150 includes casting, mechanical rough machining, mechanical finishing, phosphating, brushing, and the like. The processing process is complex and has a high cost. The processing processes such as casting and phosphating consume fossil fuels and pollute the environment.

[0108] In order to solve this technical problem, in some embodiments, the first bearing portion 151 is configured as a sheet metal stamping part. The second bearing portion 152 is configured as a metal pipe, and the first shaft hole 1522 is formed in the metal pipe. The first bearing portion 151 and the second bearing portion 152 are fixedly welded.

[0109] The bearing 150 in some embodiments of the present disclosure has low cost and simplified processing, including stamping, finishing, and welding. The processing of the bearing 150 can reduce environmental pollution.

[0110] The bearing 150 in some embodiments of the present disclosure adopts sheet metal stamping and metal pipe materials, and the material is any one of steel, cast iron, and alloy, which has a large elastic modulus and can reduce the friction between the bearing 150 and the eccentric crankshaft 140.

[0111] In some embodiments, referring to FIGS. 3 and 4, the bearing 150 further includes a plurality of reinforcing portions 153, which are arranged along the circumference of the second bearing portion 152 and connected to the first bearing portion 151 to improve the structural reliability of the first bearing portion 151 and the second bearing portion 152.

[0112] In some embodiments, the reinforcing portion 153 is a rib structure, and the reinforcing portion 153 is welded to the first bearing portion 151 and the second bearing portion 152, respectively.

[0113] In the compressor 1000 provided in some embodiments of the present disclosure, referring to FIG. 8, the bearing 150 further includes an oil groove 154. The oil groove 154 is arranged on the inner wall of the shaft hole (such as the first shaft hole 1522) of the bearing 150. The oil groove 154 is generally an equal-shaped curve or a straight line. When the compressor 1000 operates at a low frequency, there is no oil in the oil groove 154, and the friction between the bearing 150 and the eccentric crankshaft 140 is large, thereby increasing the friction noise of the compressor 1000. When the compressor operates at a high frequency, the excess oil is discharged through the oil groove 154, the oil discharge rate of the compressor 1000 is increased, and the performance of the compressor 1000 is reduced.

[0114] To solve this technical problem, in some embodiments, referring to FIGS. 2 and 8, the eccentric crankshaft 140 passes through the first shaft hole 1522. The oil groove 154 includes a plurality of first sub-oil grooves 1541, and the oil groove 154 further includes a plurality of second sub-oil grooves 1542. For example, referring to FIG. 8, three first sub-oil grooves 1541 and two second sub-oil grooves 1542 are arranged on the hole wall of the first shaft hole 1522. The first sub-oil grooves 1541 and the second sub-oil grooves 1542 are alternately arranged along the axial direction of the first shaft hole 1522, and adjacent first sub-oil grooves 1541 and second sub-oil grooves 1542 are in communication. The first sub-oil grooves 1541 extend along the axial direction of the first shaft hole 1522, and the first sub-oil grooves 1541 are straight grooves. The second sub-oil grooves 1542 extend helically along the circumferential direction of the first shaft hole 1522, and the second sub-oil grooves 1542 are spiral grooves.

[0115] The oil groove 154 in some embodiments of the present disclosure is a composite oil groove composed of a first sub-oil groove 1541 in straight line and a second sub-oil groove 1542 in spiral. Firstly, when the compressor 1000 is running at low frequency, the oil groove 154 can reliably transport oil to the friction pair, avoiding the oil-free lubrication of the friction pair assembly (such as the eccentric crankshaft 140 and the bearing 150); secondly, when the compressor 1000 is running at high frequency, it avoids excessive oil supply, which can reduce the oil discharge rate of the compressor 1000; thirdly, reasonable oil supply can effectively reduce the friction noise of the compressor 1000, thereby reducing the vibration and noise of the compressor 1000.

[0116] The ratio of the oil pool height of the compressor 1000 to the installation cavity height is defined as the first ratio; the number of the first sub-oil groove 1541 to the number of the second sub-oil groove 1542 is the second ratio.

[0117] In some embodiments, the oil groove 154 includes N1 first sub-oil grooves 1541, and the oil groove 154 further includes N2 second sub-oil grooves 1542, and the second ratio is N1 / N2. FIG. 10 is a graph of the relationship between N1 / N2 and the first ratio and the oil discharge rate of the compressor 1000 according to some embodiments. As shown in FIG. 10, the curve M is the curve of the second ratio and the oil discharge rate of the compressor 1000, and the curve L is the curve of the second ratio and the first ratio. When the second ratio is greater than 3.5 and less than 4.6 (3.5

[0118] In some embodiments, the groove depth of the oil groove 154 is T, and with reference to FIG. 8, the groove depth T is the opening depth of the oil groove 154 along the height H2 direction perpendicular to the first shaft hole 1522, and the hole diameter of the first shaft hole 1522 is D. The ratio of the groove depth T to the hole diameter D of the first shaft hole 1522 is defined as the third ratio (T / D). FIG. 11 is a graph of the relationship between T / D and the first ratio and the oil discharge rate of the compressor 1000, and the curve M is the curve of the third ratio and the oil discharge rate of the compressor 1000, and the curve L is the curve of the third ratio and the first ratio. When the third ratio is greater than 0.15 and less than 0.21 (0.15

[0119] In some embodiments, the starting angle of the oil groove 154 is θ1, the ending angle of the oil groove 154 is θ2, and the pitch of the second sub-oil groove 1542 is The starting angle θ1 of the oil groove 154 to the pitch of the second sub-oil groove 1542 is defined as the fourth ratio (θ1 / P2). the ratio of the first ratio to the target sum, and the end angle of the oil groove 154 is θ2 and the pitch of the second sub-oil groove 1542 is θ1 the sum of the first ratio and the target sum is the target sum. FIG. 9 is a graph of the target sum versus the oil discharge rate of the compressor 1000 according to some embodiments. Curve M is a curve of the target sum versus the oil discharge rate of the compressor 1000, and curve L is a curve of the target sum versus the first ratio. When the target sum is greater than 1.6 and less than 2.8, the first ratio is reasonable and the oil discharge rate of the compressor 1000 is good. For example, the target sum is 1.8, 1.9, 2.2, 2.5, or 2.8.

[0120] The contact surface pressure between the bearing 150 and the eccentric crankshaft 140 is defined as the pressure generated by the interaction of the contact surface between the bearing 150 and the eccentric crankshaft 140 under the combined load of gas load, centrifugal force, electromagnetic force, etc. The axial height of the contact surface between the bearing 150 and the eccentric crankshaft 140 is defined as the contact surface pressure height. In the disclosed compressor 1000, the contact surface pressure height between the bearing 150 and the eccentric crankshaft 140 is small, it is difficult to form an oil film between the bearing 150 and the eccentric crankshaft 140, the friction between the bearing 150 and the eccentric crankshaft 140 is large, which further increases the friction noise of the compressor 1000 and reduces the performance of the compressor 1000.

[0121] To solve this technical problem, in some embodiments, referring to FIG. 8, the bearing 150 further includes a sixth groove 1517. The first bearing part 151 is provided with the sixth groove 1517. The second bearing part 152 extends to one side of the first bearing part 151. For example, the first bearing part 151 and the second bearing part 152 are one-piece. For another example, the first bearing part 151 and the second bearing part 152 are separate pieces, and the first bearing part 151 and the second bearing part 152 can be fixed by welding. The second bearing part 152 is formed with a first shaft hole 1522. The sixth groove 1517 surrounds the first shaft hole 1522.

[0122] ​​Referring to FIG. 8, a height of the sixth groove 1517 along an axial direction of the first shaft hole 1522 is defined as H1, a height of the bearing 150 along the axial direction of the first shaft hole 1522 is defined as H2, and a ratio of the height H1 of the first shaft hole 1522 along the axial direction to the height H2 of the bearing 150 along the axial direction of the first shaft hole 1522 is defined as a fourth ratio (H1 / H2). FIG. 13 is a graph of the fourth ratio versus the contact surface pressure height according to some embodiments. Referring to FIG. 13, when the fourth ratio is greater than 0.12 and less than 0.25 (0.12

[0123] In some embodiments, referring to FIG. 8, an inner diameter of the sixth groove 1517 is defined as D2, a length of the first bearing portion 151 along a direction perpendicular to the extension of the second bearing portion 152 is defined as D3, and a ratio of the inner diameter D2 of the sixth groove 1517 to the length D3 of the first bearing portion 151 along the direction perpendicular to the extension of the second bearing portion 152 is defined as a fifth ratio (D2 / D3). FIG. 14 is a graph of the fifth ratio versus the contact surface pressure height according to some embodiments. Referring to FIG. 14, when the fifth ratio is greater than 0.1 and less than 0.24 (0.1

[0124] In some embodiments, referring to FIG. 8, an outer diameter of the sixth groove 1517 is defined as D1, an inner diameter of the sixth groove 1517 is defined as D2, and a ratio of the outer diameter D1 of the sixth groove 1517 to the inner diameter D2 of the sixth groove 1517 is defined as a sixth ratio (D1 / D2). FIG. 12 is a graph of the sixth ratio versus the contact surface pressure height according to some embodiments. Referring to FIG. 12, when the sixth ratio is greater than 0.9 and less than 1.65 (0.9

[0125] In some embodiments, referring to FIG. 8, a target difference T1 is defined as a difference between an outer diameter D1 of the sixth groove and an inner diameter D2 of the sixth groove 1517 (T1 = D1 - D2). The second bearing portion 152 includes a journal portion 1521 having a dimension T2 in a direction perpendicular to the extension of the second bearing portion 152. Referring to FIG. 2, an outer diameter of the rotor 132 is D4. A ratio of a sum of the dimension T2 of the journal portion 1521 in the direction perpendicular to the extension of the second bearing portion 152 and the target difference T1 to the outer diameter D4 of the rotor 132 is a seventh ratio ((T1 + T2) / D4). FIG. 15 is a graph of the seventh ratio versus the contact face pressure height according to some embodiments. Referring to FIG. 15, when the seventh ratio is greater than 0.095 and less than 0.15 (0.095 < (T1 + T2) / D4 < 0.15), the contact face pressure height between the eccentric crankshaft 140 and the bearing 150 is large, which is conducive to forming an oil film between the eccentric crankshaft 140 and the bearing 150, reducing the friction between the eccentric crankshaft 140 and the bearing 150, and thus reducing the friction noise of the compressor 1000 and improving the performance of the compressor 1000. For example, the seventh ratio is 0.10, 0.11, 0.12, 0.13, or 0.14.

[0126] [the bearing shell]

[0127] In the compressor 1000 in some disclosed embodiments, the bearing 150 is generally sleeved on the outside of the eccentric crankshaft 140. The wear between the shaft sleeve 144 and the eccentric crankshaft 140 is large, which increases the friction noise of the compressor 1000 and reduces the performance of the compressor 1000.

[0128] To solve this technical problem, in some embodiments, referring to FIGS. 4, 5, and 7, the compressor mechanism 120 includes two bearing shells 160. The bearing shells 160 are arranged in the first shaft hole 1522, for example, the bearing shells 160 are interference-fitted into the first shaft hole 1522.

[0129] The two bearing shells 160 are arranged in the axial direction of the first shaft hole 1522. The bearing shells 160 include second shaft holes 1611 through which the eccentric crankshaft 140 passes. The two bearing shells 160 have a gap 1630 therebetween, which is an annular groove surrounding the second shaft hole 1611. The bearing shells 160 further include fifth grooves 165. The fifth grooves 165 are arranged on the inner circumferential wall of the bearing shells 160 and communicate with the gap 1630.

[0130] The gap 1630 and the fifth grooves 165 can function as the oil groove 154, improve the wear resistance between the eccentric crankshaft 140 and the bearing shells 160, reduce the friction noise of the compressor 1000, and improve the performance of the compressor 1000.

[0131] In some embodiments, referring to FIG. 7, the fifth groove 165 spirally extends along the circumference of the bearing bush 160. In this way, the extension length of the fifth groove 165 can be increased, and the oil storage capacity of the fifth groove 165 can be increased, which helps to improve the wear resistance between the eccentric crankshaft 140 and the bearing bush 160.

[0132] In some embodiments, referring to FIG. 5, the two fifth grooves 165 of the two bearing bushes 160 are respectively a first sub-groove 165A and a second sub-groove 165B. The first sub-groove 165A and the second sub-groove 165B are located on the same spiral track, and the first sub-groove 165A is farther away from the first bearing part 151 than the second sub-groove 165B. In this way, oiling is facilitated, and it is ensured that the parts of the eccentric crankshaft 140 in contact with the bearing 150 can be effectively lubricated to reduce friction. For example, oil flows from bottom to top through the second shaft hole 1611. The oil first passes through the lower first sub-groove 165A, and then enters the gap 1630 between the two bearing bushes 160, and then flows into the upper second sub-groove 165B.

[0133] [eccentric crankshaft]

[0134] In some disclosed compressors 1000, the eccentric crankshaft 140 is usually a cast part, and the elastic modulus is low. The wear between the bearing 150 and the eccentric crankshaft 140 is large. The processing of the bearing 150 includes casting, mechanical rough machining, mechanical finishing, phosphorization, brushing, etc. The processing is complex and the cost is high. The processing of casting, phosphorization, etc. consumes fossil fuels and pollutes the environment.

[0135] To solve this technical problem, in some embodiments, referring to FIGS. 16-18, the eccentric crankshaft 140 further comprises a third shaft hole 1411. The third shaft hole 1411 is formed inside the main shaft section 141. The eccentric crankshaft 140 further comprises a vane 143. The vane 143 is arranged in the third shaft hole 1411. The eccentric crankshaft 140 further comprises a shaft plug 145. The eccentric crankshaft 140 further comprises a shaft sleeve 144. One end of the third shaft hole 1411 is provided with the shaft plug 145, and the opposite end of the third shaft hole 1411 is provided with the shaft sleeve 144.

[0136] In some embodiments, the main shaft section 141 is made of a metal pipe, such as a steel pipe, and the third shaft hole 1411 is formed in the metal pipe.

[0137] In some embodiments, referring to FIG. 17, the eccentric crankshaft 140 further comprises a plurality of oil holes 1412. The plurality of oil holes 1412 are arranged on the main shaft section 141 to lubricate any friction pair mounted on the eccentric crankshaft 140. The eccentric shaft section 142 is fixedly sleeved on the main shaft section 141. The eccentric crankshaft 140 is configured as a sheet metal stamping part. The eccentric crankshaft 140 is welded to the main shaft section 141.

[0138] The eccentric crankshaft 140 in some embodiments of the present disclosure has low cost and simplified processing, including stamping, finishing, and welding. The processing can reduce environmental pollution.

[0139] The eccentric crankshaft 140 in some embodiments of the present disclosure adopts sheet metal stamping and metal pipe materials, and the material is steel, which has a large elastic modulus and can reduce the friction between the bearing 150 and the eccentric crankshaft 140.

[0140] In some embodiments, referring to FIG. 16, the eccentric crankshaft 140 further includes a third groove 1426. The third groove 1426 is arranged on the outer peripheral wall of the eccentric shaft segment 142 and surrounds the eccentric shaft segment 142. The eccentric crankshaft 140 further includes a first channel 1428 (e.g., a passage). The first channel 1428 is arranged in the eccentric shaft segment 142 and is configured to supply oil to the third groove 1426.

[0141] In some embodiments, the third groove 1426 can serve as an oil groove, providing a passage for the flow of lubricating oil and improving the oil film state between the eccentric crankshaft 140 and the piston, thereby avoiding the phenomenon of the compressor 1000 being stuck or dead during operation due to insufficient oil supply. For example, the rotor 132 and the stator 131 are stuck to each other and cannot operate.

[0142] In some embodiments, referring to FIGS. 19 and 20, the eccentric shaft segment 142 includes two sub- eccentric shaft segments 1421 that are connected to each other and symmetrically arranged on both sides in the height direction of the third groove 1426.

[0143] Referring to FIG. 20, the sub- eccentric shaft segment 1421 includes a first wall 1422. The sub- eccentric shaft segment 1421 further includes a second wall 1423 extending away from the first wall 1422 from the circumferential edge of the first wall 1422. The two first walls 1422 on the two sub- eccentric shaft segments 1421 are connected, for example, by welding, to achieve fixed connection of the two sub- eccentric shaft segments 1421.

[0144] It should be noted that the sub- eccentric shaft segment 1421 is composed of the first wall 1422 and the second wall 1423, and is not a solid structure, which saves materials and reduces cost.

[0145] Referring to FIGS. 19 and 20, the sub- eccentric shaft segment 1421 further includes a weight-reducing hole 1429. The sub- eccentric shaft segment 1421 further includes a sub- weight-reducing hole 1424. The sub- weight-reducing hole 1424 is arranged on the first wall 1422, and the sub- weight-reducing holes 1424 on the two sub- eccentric shaft segments 1421 are communicated to form the weight-reducing hole 1429.

[0146] The sub eccentric shaft section 1421 further comprises a fourth groove 1427. The fourth groove 1427 is arranged on the first wall 1422, and the two fourth grooves 1427 on the two sub eccentric shaft sections 1421 are in communication to form a first channel 1428.

[0147] The sub eccentric shaft section 1421 further comprises a transition surface 1430. The transition surface 1430 is located at the joint of the first wall 1422 and the second wall 1423, for example, the transition surface 1430 is arc-shaped, etc. When the two sub eccentric shaft sections 1421 are fixedly connected, the two transition surfaces 1430 enclose the third groove 1426.

[0148] The sub eccentric shaft section 1421 further comprises a communication hole 1425. The communication hole 1425 is arranged on the first wall 1422, and the two communication holes 1425 on the two sub eccentric shaft sections 1421 are in communication, and the main shaft section 141 passes through the two first communication holes 1425.

[0149] [Multi-split air conditioner]

[0150] In some embodiments, referring to FIG. 21, the multi-split air conditioner 2000 comprises an outdoor unit 6100 and a plurality of indoor units 6200, and the outdoor unit 6100 is connected with the plurality of indoor units 6200. The outdoor unit 6100 is provided with a compressor 1000 and a second gas-liquid separator 520. The compressor 1000 is independent of the second gas-liquid separator 520, and at this time, the compressor 1000 does not need to be provided with a first gas-liquid separator 510, thereby reducing the size of the compressor 1000 and reducing the cost under the premise of ensuring the gas-liquid separation effect of the refrigerant.

[0151] In some embodiments, referring to FIGS. 22-24, the compressor 1000 is a double-cylinder rotary compressor, and the compression mechanism 120 comprises two cylinders 122, which are a first cylinder 1221 and a second cylinder 1222.

[0152] Referring to FIGS. 22 and 23, the compressor 1000 further comprises a suction pipe 2100 configured to supply the gaseous refrigerant of the second gas-liquid separator 520 into the compression cavity of the compression mechanism 120.

[0153] The second gas-liquid separator 520 comprises a second gas outlet pipe 521. The suction pipe 2100 comprises a first suction pipe 210, and the first suction pipe 210 is in communication with the second gas outlet pipe 521.

[0154] Referring to FIGS. 22 and 23, the suction pipe 2100 comprises two second suction pipes 220, and the two second suction pipes 220 are in communication with the two cylinders 122, respectively.

[0155] Referring to FIGS. 22, 23 and 25, the suction pipe 2100 includes a tee joint 230, which includes three connecting ports, i.e., a first connecting port 231 and two second connecting ports 232. The first connecting port 231 is in communication with the second connecting port 232, and the two second connecting ports 232 are arranged side by side. When the tee joint 230 is installed, the opening of the first connecting port 231 faces upward to be connected with the first suction pipe 210, and the opening of the second connecting port 232 faces downward to be connected with the second suction pipe 220, and the two second connecting ports 232 are in communication with the two second suction pipes 220, respectively. In this way, the gaseous refrigerant flowing out of the second gas-liquid separator 520 flows through the first suction pipe 210 and the two second suction pipes 220 in sequence from top to bottom, and is distributed into the two cylinders through the two second suction pipes 220, thereby improving the uniformity of distribution of the refrigerant.

[0156] In some embodiments, the tee joint 230 is arranged along the height direction of the first housing 110, and the difference between the angle of the center line of the tee joint 230 and the center line of the first housing 110 is in the range of [0°, 10°], which helps to improve the uniformity of distribution of the refrigerant.

[0157] In some embodiments, the two second connecting ports 232 are arranged symmetrically relative to the axis of the first connecting port 231, which helps to improve the uniformity of distribution of the refrigerant.

[0158] In some embodiments, the inner diameter of the second suction pipe 220 is D5, and the difference between the inner diameters of the two second suction pipes 220 is in the range of [0, 0.5D5], which helps to improve the uniformity of distribution of the refrigerant.

[0159] In some embodiments, the inner diameter of the suction port of the cylinder 122 is D6, and 0.5≤D5 / D6≤2, which helps to improve the uniformity of distribution of the refrigerant.

[0160] In some embodiments, the inner diameter of the first suction pipe 210 is D7, and 1≤D7 / D5≤5, which helps to improve the uniformity of distribution of the refrigerant.

[0161] In some embodiments, the tee joint 230, the first suction pipe 210 and the second suction pipe 220 are fixed by welding, and the depth of the first suction pipe 210 inserted into the first connecting port 231 and the depth of the second suction pipe 220 inserted into the second connecting port 232 are d, respectively, and 50mm≥d≥10mm, which helps to improve the reliability of the structure.

[0162] In some embodiments, referring to FIG. 23, the compressor 1000 further includes a vibration isolation part 400, and the first suction pipe 210 passes through a second mounting hole arranged on the vibration isolation part 400. The vibration isolation part 400 is, for example, a rubber pad.

[0163] Referring to FIGS. 23 and 26, the compressor 1000 further includes a first fixing portion 3000 fixedly connected with the first shell 110, for example, the first fixing portion 3000 is fixedly connected with the first shell 110 by welding, the first fixing portion 3000 is formed with an accommodation space 330, and the vibration isolation portion 400 is located in the accommodation space 330. In a first aspect, the vibration isolation portion 400 plays a role in vibration isolation and noise reduction; in a second aspect, the first fixing portion 3000 can improve the stability of the first suction pipe 210.

[0164] In some embodiments, referring to FIG. 26, the first fixing portion 3000 includes a first sub-fixing portion 3100; and the first fixing portion 3000 further includes a second sub-fixing portion 3200.

[0165] The first sub-fixing portion 3100 includes a connecting portion 3110, the first sub-fixing portion 3100 further includes a first extending portion 3120, one end of the connecting portion 3110 is provided with the first extending portion 3120, the first sub-fixing portion 3100 further includes a second extending portion 3130, the other opposite end of the connecting portion 3110 is provided with the second extending portion 3130. The connecting portion 3110, the first extending portion 3120 and the second extending portion 3130 are one-piece. The connecting portion 3110 is fixedly connected with the first shell 110, for example, by welding.

[0166] The connecting portion 3110 is arc-shaped to adapt to the outer contour of the first shell 110 for fixed connection. The first extending portion 3120 extends towards the side of the connecting portion 3110 away from the first shell 110. The second extending portion 3130 includes two sub-extending portions, which are a first sub-extending portion 3131 and a second sub-extending portion 3132. The first sub-extending portion 3131 extends towards the side of the connecting portion 3110 away from the shell, and the second sub-extending portion 3132 extends from the first sub-extending portion 3131 towards the side away from the first extending portion 3120, for example, the second extending portion 3130 is L-shaped.

[0167] One end of the second sub-fixing portion 3200 is connected with the first extending portion 3120, and the other opposite end of the second sub-fixing portion 3200 is connected with the second extending portion 3130 to limit the vibration isolation portion 400 in the accommodation space 330.

[0168] In some embodiments, the first sub-fixing portion 3100 further includes a second clamping portion 3121, and the first extending portion 3120 is provided with the second clamping portion 3121, for example, the second clamping portion 3121 is an opening. The first fixing portion 3000 further includes a first clamping portion 3210, and one end of the second sub-fixing portion 3200 is provided with the first clamping portion 3210, for example, a clamping hook, and the first clamping portion 3210 is clamped with the second clamping portion 3121. The other end of the second sub-fixing portion 3200 is fixed with the second sub-extending portion 3132 by a bolt.

[0169] In some embodiments, referring to FIG. 26, the second sub-fixing part 3200 includes a second connecting section 3220, which is arc-shaped and matches the contour of the vibration isolation part 400, thereby improving the limiting effect on the vibration isolation part 400.

[0170] Some embodiments of the present disclosure also provide a compressor and an air conditioner.[Compressor body]

[0171] In some embodiments, referring to FIGS. 27, 28 and 43, the eccentric crankshaft 140 includes a first shaft section 1211. The first shaft section 1211 is fixedly connected with the rotor 132. The eccentric crankshaft 140 further includes a second shaft section 1215, and further includes a third shaft section 1217. The first shaft section 1211 is connected with one end of the third shaft section 1217, and the second shaft section 1215 is connected with the other end of the third shaft section 1217.

[0172] In some embodiments, referring to FIG. 43, the third shaft section 1217 includes a first sub- eccentric shaft section 1212, further includes a connecting shaft section 1214, and further includes a second sub- eccentric shaft section 1213. In the height direction of the eccentric crankshaft 140, the first shaft section 1211, the first sub- eccentric shaft section 1212, the connecting shaft section 1214, the second sub- eccentric shaft section 1213 and the second shaft section 1215 are sequentially connected from top to bottom.

[0173] In some embodiments, as shown in FIGS. 42 and 43, the first piston 1231 is arranged in the compression chamber of the first cylinder 1221 and can perform eccentric motion. The first piston 1231 is sleeved on the first sub- eccentric shaft section 1212. The second piston 1232 is arranged in the compression chamber of the second cylinder 1222 and can perform eccentric motion. The second piston 1232 is sleeved on the second sub- eccentric shaft section 1213. The partition plate 125 is sleeved on the connecting shaft section 1214. The partition plate 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 connected with the first cylinder 1221. The second bearing 1242 is sleeved on the second shaft section 1215 and connected with the second cylinder 1222.

[0174] The first sub- eccentric shaft section 1212 and the second sub- eccentric shaft section 1213 are arranged on both sides of the central axis of the eccentric crankshaft 140. For example, the first sub- eccentric shaft section 1212 and the second sub- eccentric shaft section 1213 are arranged at an opposite angle of 180°. The first piston 1231 and the second piston 1232 simultaneously perform eccentric rotation. The compressed gas in the compression chamber of the first cylinder 1221 is discharged through the exhaust hole on the first bearing 1241. The compressed gas in the compression chamber of the second cylinder 1222 is discharged through the exhaust hole on the second bearing 1242.

[0175] Referring to FIG. 42, the first silencing assembly 1261 is arranged on the first bearing 1241, and the first silencing assembly 1261 covers the exhaust hole of the first bearing 1241. The compressed gas in the first cylinder 1221 is first exhausted to the space surrounded by the first silencing assembly 1261 and the first bearing 1241 through the exhaust hole of the first bearing 1241, and then exhausted to the inner cavity of the compressor 1000 through the first silencing assembly 1261.

[0176] The second silencing assembly 1262 is arranged on the second bearing 1242, and the second silencing assembly 1262 covers the exhaust hole of the second bearing 1242. The compressed gas in the second cylinder 1222 is first exhausted to the space surrounded by the second silencing assembly 1262 and the second bearing 1242 through the exhaust hole of the second bearing 1242.

[0177] In some embodiments, unlike the related art, the exhaust hole can be omitted on the second silencing assembly 1262 in FIG. 42. The walls of the first bearing 1241, the first cylinder 1221, the partition plate 125, the second cylinder 1222, and the second bearing 1242 are provided with a plurality of airflow passages penetrating upward and downward. The compressed gas in the second bearing 1242 and the second silencing assembly 1262 is exhausted upward to the space surrounded by the first bearing 1241 and the first silencing assembly 1261 through the airflow passages, and then exhausted to the inner cavity of the compressor 1000 through the exhaust hole of the first silencing assembly 1261.

[0178] [foot]

[0179] Generally, the compressor body 100 includes a rubber foot. The rubber foot is fixedly arranged at the bottom of the first shell 110. After the rubber foot is installed, the vibration isolation amount of the rubber foot and the overall modal of the compressor are determined. As the operating frequency range of the compressor is continuously widened, for example, the operating frequency range of the compressor is 10 Hz to 160 Hz, on the one hand, the sixth rigid body modal of the compressor is usually 5 Hz to 30 Hz, which is easy to be excited, thereby causing severe shaking of the compressor. The sixth rigid body modal of the compressor refers to the first six modes in the free modal analysis, which are usually considered as rigid body modes, and the natural frequency is zero. On the other hand, according to the stiffness isolation principle, as the operating frequency range of the compressor increases, the modal of the rubber foot and the excitation of the compressor are easy to be coupled with each other, thereby reducing the vibration isolation effect of the rubber foot, and further increasing the vibration and noise of the outdoor unit. The stiffness isolation principle can refer to reducing vibration transmission and improving vibration isolation effect by increasing the stiffness of the structural system.

[0180] Some embodiments of the present disclosure also provide a compressor. From the perspective of active control, the compressor provides a foot pad structure of a hydraulic spring, determines the vibration isolation amount by using a sensor arranged on the compressor shell and the sheet metal part, and thus actively adjusts the spring stiffness and changes at least one of the rigid body mode of the compressor or the spring stiffness. In this way, on the one hand, active deviation of the rigid body mode of the compressor can be achieved, violent shaking of the compressor can be avoided, and impact on the pipeline can be reduced; on the other hand, when the compressor is operated at a high frequency, good stiffness vibration isolation effect can be achieved, so that the vibration transmission amount is reduced, and the vibration and noise of the outdoor unit are reduced.

[0181] To solve the technical problem, in some embodiments, referring to FIG. 29, the compressor 100 further comprises at least one foot 300, and the at least one foot 300 is arranged on the first shell 110. The foot 300 is configured to mount the compressor 1000 to a mounting carrier 500 on which the compressor 1000 is located. For example, the compressor 1000 is fixedly mounted to the bottom plate of the outdoor unit through the foot 300, and at this time, the mounting carrier 500 is the bottom plate of the outdoor unit.

[0182] In some embodiments, the at least one foot 300 comprises a plurality of feet 300. The plurality of feet 300 are respectively arranged at the bottom of the first shell 110, and the plurality of feet 300 are arranged at intervals along the circumference of the first shell 110, so as to improve the mounting stability of the compressor 1000.

[0183] In some embodiments, referring to FIG. 30, the foot 300 comprises a shell 310. The shell 310 is configured to connect the first shell 110 and the mounting carrier 500 (such as the bottom plate of the outdoor unit). For example, a first end of the shell 310 is fixed to the first shell 110 by a bolt, a second end of the shell 310 is fixed to the bottom plate of the outdoor unit by a bolt, and the first end and the second end are arranged opposite to each other. The foot 300 further comprises a second mounting cavity 311. The second mounting cavity 311 is formed in the shell 310.

[0184] In some embodiments, referring to FIG. 30, the foot 300 further comprises a support 320. The support 320 is arranged in the second mounting cavity 311. When subjected to an external force, the support 320 can be elongated or contracted along the height direction of the second mounting cavity 311 (i.e., the height direction of the compressor 1000).

[0185] In some embodiments, referring to FIG. 30, the foot 300 further comprises a first driving part 330. The first driving part 330 is arranged in the second mounting cavity 311. The first driving part 330 is configured to adjust the stiffness of the support 320 according to the vibration signal of the compressor 1000, so as to adjust the rigid body mode of the compressor 1000.

[0186] In some embodiments, the foot 300 of some embodiments of the present disclosure, the support 320 actively adjusts the stiffness according to the vibration signal of the compressor 1000, thereby adjusting the rigid body mode of the compressor 1000. On the one hand, active deviation of the stiffness mode of the compressor 1000 can be achieved, avoiding violent shaking of the compressor 1000 and reducing the impact on the pipeline; on the other hand, when the compressor 1000 is running at high frequency, good stiffness vibration isolation effect can be obtained, thereby reducing the vibration transmission amount and reducing the vibration and noise of the outdoor unit.

[0187] In some embodiments, referring to FIG. 29, the compressor 1000 further comprises a first sensor 410. The first sensor 410 is arranged on the first shell 110, and the first sensor 410 is configured to detect a vibration signal of the first shell 110.

[0188] The compressor 1000 further comprises a second sensor 420. The second sensor 420 is arranged on the mounting carrier 500, and the second sensor 420 is configured to detect a vibration signal of the mounting carrier 500.

[0189] In some embodiments, the first driving part 330 is further configured to adjust the stiffness of the support 320 according to the vibration signal of the first shell 110 and the vibration signal of the mounting carrier 500.

[0190] The compressor 1000 of some embodiments of the present disclosure determines the vibration isolation amount by using the first sensor 410 and the second sensor 420, thereby actively adjusting the stiffness of the support 320 and changing the rigid body mode of the compressor 1000.

[0191] In some embodiments, as shown in FIG. 29, the compressor 1000 further comprises a first controller 610. The first controller 610 is coupled with the first sensor 410, the foot 300 and the mounting carrier 500 respectively.

[0192] The adjustment process of the foot 300 is introduced below.

[0193] In some embodiments, referring to FIG. 31, the first controller 610 is configured to perform S11 to S15.

[0194] S11, obtaining a first vibration signal detected by the first sensor 410 and a second vibration signal detected by the second sensor 420.

[0195] For example, the first vibration signal refers to the vibration signal of the first shell 110; and the second vibration signal refers to the vibration signal of the mounting carrier 500.

[0196] S12, processing and analyzing the first vibration signal and the second vibration signal.

[0197] For example, the first controller 610 processes and analyzes the first vibration signal and the second vibration signal.

[0198] S13. Based on the processed and analyzed data, determine whether the compressor 1000 is in a fixed frequency (natural frequency) operating state and whether the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is greater than the first set value X; if “yes”, then execute step S15; if “no”, then execute step S14.

[0199] S14, control the first drive unit 330 to drive the support member 320 to extend, so as to reduce the stiffness of the support member 320.

[0200] For example, if the first controller 610 determines that the compressor 1000 is in a non-fixed frequency operation state when at least one of the following conditions is met, or if the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is less than or equal to the first set value X, the first controller 610 controls the first drive unit 330 to drive the support member 320 to extend in order to reduce the stiffness of the support member 320.

[0201] S15, control the first drive unit 330 to drive the support member 320 to retract, so as to increase the rigidity of the support member 320.

[0202] For example, when the first controller 610 determines that the compressor 1000 is in a fixed-frequency operation state and 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 controller 610 controls the first drive unit 330 to drive the support member 320 to extend, so as to reduce the stiffness of the support member 320.

[0203] In some embodiments, referring to FIG30, the first drive unit 330 includes a second motor 331, and the first drive unit 330 further includes a first threaded post 332; the first drive unit 330 also includes a moving part 333. The power shaft end of the second motor 331 is connected to the first threaded post 332, and the moving part 333 is provided on the first threaded post 332. The moving part 333 is configured to move along the extension and retraction direction of the support member 320 to adjust the stiffness of the support member 320.

[0204] When the power shaft of the second 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 against the support member 320, causing the support member 320 to contract under force.

[0205] When the power shaft of the second motor 331 rotates in the second direction (e.g., counterclockwise), the first threaded post 332 drives the moving part 333 to move downward, and the support member 320 springs back and extends.

[0206] In some embodiments, the movable part 333 has a flat plate structure, and the outer peripheral end of the movable part 333 is spaced from the inner cavity wall of the housing 310 to avoid increasing friction due to contact between the movable part 333 and the housing 310.

[0207] In some embodiments, the support member 320 is a spring, which is sleeved on the outer periphery of the first threaded post 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 mounting cavity 311.

[0208] In some embodiments, the first threaded post 332 is located within the spring, resulting in a compact structural layout. The spring is confined between the top wall of the moving part 333 and the second mounting cavity 311, ensuring a reliable structure.

[0209] In some embodiments, referring to FIG30, the housing 310 includes a first sub-housing 312 configured to connect to the base plate of the outdoor unit, the first sub-housing 312 forming the bottom wall of the second mounting cavity 311. For example, the first sub-housing 312 is bolted to the base plate. A second motor 331 is disposed on the first sub-housing 312.

[0210] In some embodiments, referring to FIG30, the housing 310 further includes a second sub-housing housing 313, a second mounting cavity 311 is formed in the second sub-housing housing 313, and the second sub-housing housing 313 is connected to the first sub-housing housing 312, for example, the second sub-housing housing 313 and the first sub-housing housing 312 are welded together.

[0211] In some embodiments, referring to FIG30, 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, by welding the third sub-housing 314 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. For example, the third sub-housing 314 is fixedly connected to the outside of the first housing 110 by bolts.

[0212] In some embodiments, the housing 310 is made of rubber to increase the vibration isolation effect of the feet 300.

[0213] [Second connection part of the gas-liquid separator]

[0214] A significant amount of second-frequency abnormal noise from a rotary compressor contributes substantially to the noise, vibration, and harshness (NVH) of the outdoor unit. Second-frequency abnormal noise refers to the noise caused by vibrations occurring at twice the compressor's operating frequency. Modal analysis revealed that the cause of the significant second-frequency abnormal noise is the first-order rigid-body torsional mode of the gas-liquid separator 200. The first-order rigid-body torsional mode describes the vibration characteristics of the gas-liquid separator 200. In structural analysis, the first-order rigid-body torsional mode refers to the first natural mode of the structure in the torsional direction; that is, the torsional vibration mode of the structure under the first-order rigid-body torsional mode. Rigid-body modes are only affected by the constraint boundaries; that is, the greater the boundary stiffness, the higher the rigid-body mode of the gas-liquid separator 200. Compressors typically increase the natural frequency of the gas-liquid separator 200 by increasing welding stiffness and adding weld points. However, as the operating range of the compressor expands, relying on increasing welding rigidity and adding weld points has limited effect on improving the frequency of the gas-liquid separator 200.

[0215] To address this technical problem, in some embodiments, referring to FIG27, the compressor 1000 further includes a first connecting portion 220. The first connecting portion 220 is configured to fixably connect the first housing 110 and the second housing 512.

[0216] For example, one side of the first connecting portion 220 is welded to the first housing 110, and the other side of the first connecting portion 220 surrounds the second housing 512 to fix the first housing 110 and the second housing 512.

[0217] In some embodiments, referring to FIGS. 27 and 32, the compressor 1000 further includes a second connecting portion 2301. As shown in FIG. 32, the second connecting portion 2301 includes a second fixing portion 2313; the second connecting portion 2301 also includes two moving portions 2322. The second fixing portion 2313 is fixedly connected to the first housing 110, and the two moving portions 2322 are disposed on opposite sides along the length direction of the second fixing portion 2313. The two moving portions 2322 are configured to move toward the second housing 512 to surround the second housing 512, or move away from the second housing 512 to separate from the second housing 512, according to the vibration signal of the gas-liquid separator 200.

[0218] In some embodiments of this disclosure, the second connecting part 2301 adjusts the rigid body mode of the gas-liquid separator 200 by the movement of the two moving parts 2322, thereby achieving a shift in the natural frequency of the gas-liquid separator 200 and reducing the second harmonic noise of the compressor 1000.

[0219] Referring to Figure 34, curve A is the frequency response function curve of the gas-liquid separator 200 when the two moving parts 2322 surround the second housing 512, and curve B is the frequency response function curve of the gas-liquid separator 200 when the two moving parts 2322 separate from the second housing 512.

[0220] It should be noted that in Figure 34, the horizontal axis represents the natural frequency of the gas-liquid separator 200, and the vertical axis represents the ratio of gravitational acceleration to torque (g / N). Torque can refer to the torque or rotational torque applied to the gas-liquid separator 200. Figure 34 can represent the dynamic response characteristics of the gas-liquid separator 200 at different natural frequencies, such as the degree of response to torsional torque at different natural frequencies.

[0221] In some embodiments, referring to FIG27, the compressor 1000 further includes a third sensor 430 disposed in the second housing 512 and configured to detect vibration signals of the second housing 512, i.e., vibration signals of the gas-liquid separator 200.

[0222] In some embodiments, when the operating frequency of the compressor 1000 is lower than the first set frequency, for example, lower than 60 rpm, the first rigid body mode of the gas-liquid separator 200 is triggered, and the two moving parts 2322 move toward the second housing 512 to surround the second housing 512, thereby shifting the inherent frequency of the gas-liquid separator 200.

[0223] In some embodiments, when the operating frequency of the compressor 1000 is higher than the second set frequency, for example, higher than 60 rpm, the second rigid body mode of the gas-liquid separator 200 is triggered, and the two moving parts 2322 move away from the second housing 512 to separate from the second housing 512, thereby achieving a shift in the inherent frequency of the gas-liquid separator 200.

[0224] In some embodiments, referring to FIG39, the compressor 1000 further includes a second controller 620. The second controller 620 is disposed in the gas-liquid separator 200. The second controller 620 is connected (e.g., coupled) to a third sensor 430.

[0225] The control process of the second connecting part 2301 is described below.

[0226] In some embodiments, as shown in FIG33, the second controller 620 is configured to execute S21 to S25.

[0227] S21, acquire the third vibration signal of the gas-liquid separator 200 detected by the third sensor 430.

[0228] For example, the third vibration signal can refer to the vibration signal of the gas-liquid separator 200.

[0229] S22, determine whether the amplitude value of the third vibration signal is greater than the second set value N. If "yes", proceed to step S23; if "no", return to step S21.

[0230] S23, determine whether the operating frequency of compressor 1000 is greater than the third set value M. If "yes", proceed to step S25; if "no", proceed to step S24.

[0231] S24, control the two moving parts 2322 to move in a direction close to the second housing 512, so as to surround the second housing 512.

[0232] S25, control the two moving parts 2322 to move away from the second housing 512 so as to separate from the second housing 512.

[0233] In some embodiments, referring to FIG32, the second fixing portion 2313 includes a third sub-fixing portion 2311; the fixing portion 2313 further includes two fourth sub-fixing portions 2132, which are connected to the third sub-fixing portion 2311 and are disposed on opposite sides along the length direction of the third sub-fixing portion 2311. The fixing portion 2313 has a U-shaped structure, so as to achieve either surrounding the second housing 512 or separating from the second housing 512.

[0234] The third sub-fixing part 2311 is fixedly connected to the first housing 110, for example, by welding the third sub-fixing part 2311 to the first housing 110. The third sub-fixing part 2311 is arc-shaped to fit the outer contour of the first housing 110.

[0235] The fourth sub-fixing part 2132 extends from the third sub-fixing part 2311 toward the direction close to the second housing 512, and the fourth sub-fixing part 2132 is rotatably connected to the moving part 2322.

[0236] In some embodiments, the second connecting portion 2301 further includes a third motor. Referring to FIG32, the second connecting portion 2301 further includes at least two drive shafts 233, the power shaft end of the third motor is connected to the drive shafts 233, and the fourth sub-fixed portion 2132 and the moving portion 2322 are rotatably connected through the drive shafts 233.

[0237] For example, the third motor is fixedly installed in the second fixing part 2313, or the third motor is fixedly installed in the second housing 512.

[0238] In some embodiments, the moving part 2322 is arc-shaped to fit the outer contour of the second housing 512, thereby improving the surrounding effect of the second housing 512.

[0239] [Internal cavity partitioning structure of the gas-liquid separator]

[0240] A baffle is typically installed inside the gas-liquid separator 200 to divide its internal space, thereby altering the acoustic cavity mode and increasing or decreasing the modal frequency. After the baffle is fixed and installed, the natural frequency of the acoustic cavity inside the gas-liquid separator 200 is determined. However, as the operating frequency and pressure range of the compressor 1000 increases, and as the physical properties of the refrigerant, sound velocity, and other physical parameters change beyond a threshold range, the fixed acoustic cavity mode of the gas-liquid separator 200 becomes difficult to adapt to the different operating scenarios of the compressor 1000, resulting in significant vibration and noise from the gas-liquid separator 200.

[0241] To address this technical problem, in some embodiments, referring to Figures 37 to 39, the gas-liquid separator 200 includes a first partition 250. The first partition 250 is fixedly disposed within the internal cavity of the gas-liquid separator 200. The gas-liquid separator 200 also includes a first chamber 291; the gas-liquid separator 200 further includes a second chamber 292. The first partition 250 divides the internal cavity of the gas-liquid separator 200 into the first chamber 291 and the second chamber 292. The first chamber 291 and the second chamber 292 are arranged sequentially along the height direction of the second housing 512, with the first chamber 291 located above the second chamber 292. A first vent pipe 511 passes through the first partition 250, with one end of the first vent pipe 511 located within the first chamber 291.

[0242] Referring to Figures 37 and 38, the first partition 250 has a plate-like structure, and its outer peripheral end is welded to the inner peripheral wall of the second housing 512. The first partition 250 includes a first partition body; the first partition 250 also includes a plurality of first flow portions 251. For example, the first flow portions are openings. The plurality of first flow portions 251 are provided on the first partition body and allow refrigerant to flow through them.

[0243] Referring to Figures 37 to 39, the gas-liquid separator 200 includes a second partition 260 disposed within a second cavity 292. The second cavity 292 includes a first sub-cavity 293 and a second sub-cavity 294. The second partition 260 divides the second cavity 292 into the first sub-cavity 293 and the second sub-cavity 294, which are arranged sequentially along the height direction of the second housing 512, with the first sub-cavity 293 located on the side of the second sub-cavity 294 closest to the first cavity 291.

[0244] The first partition 250 and the second partition 260 divide the inner cavity of the second housing 512 into three chambers, namely the first chamber 291, the first sub-chamber 293 and the second sub-chamber 294, which are arranged sequentially along the height direction of the second housing 512.

[0245] Referring to Figures 37 to 39, the gas-liquid separator 200 further includes a second drive unit 270, which is configured to drive the second partition 260 to move along the height direction of the second housing 512 to adjust the acoustic cavity mode of the gas-liquid separator 200.

[0246] The gas-liquid separator 200 of some embodiments of the present disclosure drives the second partition 260 to move along the height direction of the second housing 512 by the second drive unit 270, adjusts the volume of the first sub-cavity 293 and the second sub-cavity 294, and thereby 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.

[0247] In some embodiments, the second drive unit 270 drives the second partition 260 to move toward or away from the first partition 250 based on the vibration signal of the second housing 512.

[0248] When the second partition 260 moves toward the first partition 250, the volume of the first sub-cavity 293 decreases and the volume of the second sub-cavity 294 increases.

[0249] When the second partition 260 moves away from the first partition 250, the volume of the first sub-cavity 293 increases and the volume of the second sub-cavity 294 decreases.

[0250] In some embodiments, the initial position of the second partition 260 is close to the first partition 250, so that the first sub-cavity 293 is small in volume and the second sub-cavity 294 is large in volume initially.

[0251] When the gas-liquid separator 200 is in a non-resonance operating state, the second drive unit 270 drives the second partition unit 260 to move away from the first partition unit 250, causing the volume of the first sub-cavity 293 to increase and the volume of the second sub-cavity 294 to decrease. The second partition unit 260 stops moving when the vibration signal detected by the third sensor 430 is less than or equal to the fourth set value P. The non-resonance operating state refers to a state where the operating frequency of the gas-liquid separator 200 differs from its natural frequency.

[0252] Here, the value of the second setting P is related to the displacement of the compressor 1000.

[0253] The control process of the gas-liquid separator 200 is described below.

[0254] In some embodiments, referring to FIG40, the second controller 620 is further configured to perform S31 to S37.

[0255] S31, acquire the third vibration signal of the second housing 512 detected by the third sensor 430.

[0256] S32 analyzes and processes the third vibration signal.

[0257] For example, the second controller 620 analyzes and processes the third vibration signal.

[0258] S33, determine whether the gas-liquid separator 200 is in a non-resonance operating state and whether the amplitude value of the third vibration signal is greater than the fourth set value P. If "yes", proceed to step S34; if "no", proceed to step S37.

[0259] S34, control the second drive unit 270 to drive the second partition 260 to move away from the first partition 250.

[0260] S35, determine whether the third vibration signal detected by the third sensor 430 is less than or equal to the fourth set value P. If "yes", proceed to step S36; if "no", return to step S34.

[0261] S36, control the second partition 260 to stop moving.

[0262] S37, the second drive unit 270 is kept stationary, and the second partition unit 260 is kept stationary.

[0263] In some embodiments, referring to FIG38, the second drive unit 270 includes a third motor 271 and at least one second threaded post 272. The third motor 271 is fixedly disposed on the second partition 260. The second threaded post 272 is disposed on the power shaft end of the third motor 271, the first end of the second threaded post 272 is fixedly connected to the first partition 250, and the second end of the second threaded post 272 is threadedly connected to the second partition 260.

[0264] When the power shaft of the third motor 271 rotates in a first direction (e.g., clockwise), the second partition 260 moves away from the first partition 250.

[0265] When the power shaft of the third motor 271 rotates in a second direction (e.g., counterclockwise), the second partition 260 moves toward the first partition 250.

[0266] In some embodiments, referring to FIG38, at least one second threaded post 272 includes a plurality of second threaded posts 272, which are arranged at circumferential intervals along the second partition 260, and at least one of the plurality of second threaded posts 272 is connected to the power shaft end of the third motor 271. This helps to improve the motion reliability of the second partition 260.

[0267] For example, referring to FIG38, at least one second threaded post 272 includes two second threaded posts 272, which are symmetrically arranged with respect to the central axis Y of the second partition 260.

[0268] In some embodiments, referring to FIG38, the second partition 260 further includes a second partition body; the second partition 260 also includes a second flow portion 261. For example, the second flow portion is an opening. The second flow portion 261 is disposed on the second partition body, and the first vent pipe 511 passes through the second flow portion 261 to avoid interference between the movement of the second partition 260 and the first vent pipe 511. The diameter of the second flow portion 261 is larger than the diameter of the first vent pipe 511, so that the gap between the second flow portion 261 and the first vent pipe 511 facilitates the flow of refrigerant.

[0269] In some embodiments, the second partition 260 is a plate-like structure, and there is a gap between the outer peripheral side of the second partition 260 and the inner peripheral wall of the second housing 512 to avoid the second partition 260 from contacting the inner peripheral wall of the second housing 512 and increasing the friction, and also to facilitate the flow of refrigerant.

[0270] [Gas-liquid separator outlet pipe]

[0271] Referring to Figure 41, the first outlet pipe 511 includes an outlet pipe body; the first outlet pipe 511 also includes at least one liquid return hole 241. At least one liquid return hole 241 is located in the outlet pipe body. Refrigerant enters the suction port of the compressor mechanism 120 through the gas-liquid separator 200. Oil droplets carried by the refrigerant accumulate in the gas-liquid separator 200 and return to the compressor body 100 through the liquid return hole 241. If the liquid return hole 241 is positioned too high or has too small a diameter, excessive oil accumulation in the gas-liquid separator 200 will occur when the air conditioning system reaches dynamic equilibrium, leading to increased costs. If the liquid return hole 241 is positioned too low or has too large a diameter, liquid slugging (e.g., liquid refrigerant impacting the cylinder 122) may easily occur, exceeding the tolerance range of the cylinder 122, damaging the mechanical components of the compressor 1000, and reducing the reliability of the compressor 1000.

[0272] To address this technical problem, in some embodiments, referring to FIG41, the first vent pipe 511 includes M return holes 241 (M≥2). The M return holes 241 are arranged along the height direction of the first vent pipe 511, the diameter of each return hole 241 is D, and the distance between two adjacent return holes 241 is N. n If n = (1,...,M-1), then the diameter D of the return hole 241 and the distance Nn between two adjacent return holes 241 satisfy:

[0273] D×M / (N1+...+N M-1 )∈(0.15, 0.20)

[0274] For example, D×M / (N1+...+N) M-1 The values ​​are 0.16, 0.17, 0.18, or 0.19. By designing the return liquid hole 241 as described above, the position and diameter of the return liquid hole 241 are within a reasonable range, thereby improving the oil return rate and compressor efficiency. Furthermore, it avoids the liquid refrigerant impacting the cylinder 122 due to the return liquid hole 241 being too low or too large, and also avoids excessive oil accumulation in the gas-liquid separator 200 due to the return liquid hole 241 being too high or too small.

[0275] In some embodiments, the distance between two adjacent return holes 241 is the same and is N. Then, the aperture D of the return hole 241 and the distance N between two adjacent return holes 241 satisfy the following:

[0276] D×M / ((M-1)×N)∈(0.15, 0.20)

[0277] For example, D×M / ((M-1)×N) is 0.16, 0.17, 0.18 or 0.19.

[0278] In some embodiments, referring to FIG41, if the value of M is 2, then two return holes 241 are provided on the first vent pipe 511.

[0279] In some embodiments, referring to Figures 37 and 41, the gas-liquid separator 200 includes two first gas outlet pipes 511, namely a first sub-gas outlet pipe 242 and a second sub-gas outlet pipe 243, and each of the first gas outlet pipes 511 is provided with M return liquid holes 241.

[0280] Referring to Figures 37 and 42, the two first outlet pipes 511 are respectively connected to the compression chambers of the two cylinders 122. For example, the first sub-outlet pipe 242 is connected to the intake port of the first cylinder 1221, and the second sub-outlet pipe 243 is connected to the intake port of the second cylinder 1222. In this way, each of the two first outlet pipes 511 has at least two liquid return holes 241, which can be used to remove the liquid accumulated in the gas-liquid separator 200, preventing excessive liquid accumulation and reducing the separation effect of the gas-liquid separator 200 on gaseous and liquid refrigerants.

[0281] [Silencer]

[0282] In some embodiments, referring to Figures 35 and 42, the silencing assembly 704 (such as the first silencing assembly 1261 and the second silencing assembly 1262) includes a first silencer 1451. The first silencer 1451 is disposed on the bearing 150 and covers an exhaust port (e.g., exhaust port 1511) on the bearing 150. The first silencer 1451 has at least one third mounting cavity, which communicates with the inner cavity of the first silencer 1451. The first silencer 1451 can be a diffusion silencer. A diffusion silencer includes a gradually expanding conduit that gradually diffuses from a narrow inlet to a wide outlet, utilizing the principle of energy attenuation when sound waves propagate in the expanding conduit to reduce noise.

[0283] Referring to Figures 35 and 42, the silencing assembly 704 further includes at least one second silencer 1452. The second silencer 1452 is disposed within the third mounting cavity. The second silencer may be a Helmholtz silencer. A Helmholtz silencer is a silencer that reduces noise at a specific frequency by utilizing the principle of resonance. For example, a Helmholtz silencer includes a closed cavity and an opening connected to the cavity.

[0284] For example, the first muffler assembly 1261 includes a first muffler 1451 and at least one second muffler 1452. The second muffler assembly 1262 includes the first muffler 1451 and at least one second muffler 1452.

[0285] This disclosure discloses some embodiments of the noise reduction assembly 704, which combines the advantages of the resonant chambers of the first silencer 1451 and the second silencer 1452, merging the first silencer 1451 and the second silencer 1452 into a single structural component. This facilitates installation and replacement, and can also effectively increase the transmission sound loss inside the compressor 1000 without increasing the clearance volume, thereby reducing the fluid noise of the compressor 1000 and effectively suppressing the fluid noise inside the compressor 1000 from low frequency to high frequency.

[0286] In some embodiments, referring to FIG36, curve C is the noise reduction curve of the silencing assembly 704 after combining the first silencer 1451 and the second silencer 1452 shown in FIG35. Curve D is the noise reduction curve of the silencing assembly 704 using only the first silencer 1451. It can be seen that the silencing assembly 704 after combining the first silencer 1451 and the second silencer 1452 can effectively increase the transmission sound loss inside the compressor 1000 and reduce the fluid noise of the compressor 1000.

[0287] In some embodiments, referring to FIG35, the first muffler 1451 includes a third wall 1453; the first muffler 1451 also includes a fourth wall 1454, which is disposed circumferentially along the third wall 1453 and extends toward the cylinder 122, and a third mounting cavity is disposed in the third wall 1453.

[0288] By setting the third wall 1453, it is convenient to set up the third mounting cavity and to install the second silencer 1452.

[0289] In some embodiments, at least one third mounting cavity includes a plurality of third mounting cavities, which are spaced apart from each other on the third wall 1453. At least one second muffler 1452 includes a plurality of second mufflers 1452, which are disposed on the first muffler 1451, thereby improving the noise reduction effect.

[0290] In some embodiments, the portion of the third wall 1453 that protrudes away from the cylinder 122 can form a third mounting cavity. In this way, the third mounting cavity and the third wall 1453 are integral parts, for example, the third wall 1453 is formed by stamping to form the third mounting cavity.

[0291] In some embodiments, an opening is provided on the third wall 1453, and a connector is provided on the side of the third wall 1453 opposite to the cylinder 122. The connector is positioned opposite (e.g., facing directly) to the opening 3, and a third mounting cavity is formed inside the connector. The third mounting cavity communicates with the opening 3.

[0292] Thus, the connector is a hollow cylindrical structure with an open side. The connector is fixed to the third wall 1453 by welding or other means. The connector is located outside the third wall 1453. The open side of the connector is opposite to the opening 3 (e.g., facing each other). The third mounting cavity formed inside the connector is connected to the inner cavity of the first silencer 1451 through the opening 3.

[0293] When installing the muffler assembly 704, first fix the second muffler 1452 into the internal cavity of the connector, and then fix the connector to the outside of the first muffler 1451.

[0294] [Intake passage of the compression mechanism]

[0295] In a dual-cylinder rotary compressor, the two pistons in the two cylinders have a 180° phase difference, resulting in a 180° difference in the compression process and a 180° difference in the suction rate of the suction chamber. Studies have found that suction pressure loss has a significant impact on the cooling and heating capacity of air conditioners. For example, when the pressure loss increases, the suction density decreases, resulting in a smaller compressed mass of refrigerant for the same volume. This, in turn, leads to a smaller amount of refrigerant circulating in the air conditioner, affecting its cooling and heating capabilities.

[0296] To address this technical problem, in some embodiments, referring to FIG42, any cylinder 122 (first cylinder 1221, second cylinder 1222) includes at least one second channel (e.g., intake channel) 161; and any cylinder 122 further includes a third channel 164 (ventilation channel). The third channel 164 includes at least one first sub-ventilation channel 162, the second channel 161 communicates with at least one first sub-ventilation channel 162, and the second channel 161 is also communicated with a first exhaust pipe 511.

[0297] The third passage 164 also includes at least one second sub-ventilation passage 163. The second sub-ventilation passage 163 is disposed in the partition 125. In the case where at least one second passage 161 includes two second passages 161, one of the two second passages 161 is located within the first cylinder 1221, and the other of the two second passages 161 is located within the second cylinder 1222. The first sub-ventilation passage 162 and the second sub-ventilation passage 163 communicate to connect the two second passages 161 of the two cylinders 122. The second sub-ventilation passage 163 and the two first sub-ventilation passages 162 communicate to form the third passage 164.

[0298] When the first cylinder 1221 rapidly draws in air, a portion of the refrigerant in the second channel 161 of the second cylinder 1222 flows into the first cylinder 1221 through the third channel 164.

[0299] When the second cylinder 1222 rapidly draws in air, a portion of the refrigerant in the second channel 161 of the first cylinder 1221 flows into the second cylinder 1222 through the third channel 164.

[0300] In this way, by setting the third channel 164, the amount of refrigerant circulating in the air conditioner can be effectively increased, thereby improving the air conditioner's cooling and heating capabilities.

[0301] In some embodiments, each cylinder 122 is provided with at least one first sub-ventilation channel 162, and the partition plate 125 is provided with at least one second sub-ventilation channel 163, wherein the at least one first sub-ventilation channel 162 and the at least one second sub-ventilation channel 163 are respectively connected to each other.

[0302] For example, referring to Figure 42, a first sub-ventilation channel 162 is provided on the first cylinder 1221 and the second cylinder 1222 respectively, and a second sub-ventilation channel 163 is provided on the middle partition 125, thereby forming a third channel 164.

[0303] For example, the first cylinder 1221 and the second cylinder 1222 are respectively provided with two second sub-ventilation channels 163, and the middle partition 125 is provided with two second sub-ventilation channels 163, thereby forming two third channels 164.

[0304] [Other Structures]

[0305] In some embodiments, referring to FIG27, the inner diameter of the second housing 512 is D6. Referring to FIG42, the inner diameter of the intake channel 161 is D7. (D6) 4 -D7 4 ) / D6 2 ×D7 2 >4.6, this range can reduce compressor noise by 1000.

[0306] In some embodiments, referring to FIG43, the outer diameter of the first shaft segment 1211 is D2, and a fourth shaft hole 1216 is formed in the first shaft segment 1211, the inner diameter of the fourth shaft hole 1216 being D3.

[0307] Rotor 132 is disposed on the first shaft segment 1211. Referring to Figure 44, the inner diameter of rotor 132 is D1. The inner diameter D1 of rotor 132, the outer diameter D2 of the first shaft segment 1211, and the inner diameter D3 of the fourth shaft hole 1216 satisfy the following:

[0308] (D1-D2) / D3∈[0.002, 0.01]

[0309] If (D1-D2) / D < 0.002, then the clamping force of rotor 132 is small, and rotor 132 is at risk of falling off.

[0310] If (D1-D2) / D3 > 0.01, the compressive stress and electromagnetic loss on rotor 132 will increase, leading to a decrease in the efficiency of the first motor 130. Furthermore, a higher temperature is required for the inner radial expansion of rotor 132 to fit the eccentric crankshaft 140. If the temperature exceeds the Curie temperature of the rotor 132 magnet, it will cause irreversible damage to the magnet. The severe outer radial deformation of rotor 132 will increase the risk of stator 131 and rotor 132 rubbing against the stator.

[0311] In some embodiments disclosed herein, by setting (D1-D2) / D3 ∈ [0.002, 0.01], the efficiency of the first motor 130, the clamping force of the rotor 132, the heat-shrinking process, and the risk of stator and rotor rubbing can be balanced. Within this range, the first motor 130 has high efficiency, and the rotor 132 has no risk of falling off. For example, (D1-D2) / D3 is 0.003, 0.004, 0.005, 0.007, or 0.01.

[0312] In some embodiments, referring to FIG27, the inner diameter of the first housing 110 is D4, and the circumferential wall thickness of the first housing 110 is T. Referring to FIG45, 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:

[0313] (D5-D4) / t ∈ [0.02, 0.08], this range takes into account the efficiency of the first motor 130, the clamping force of the stator 131, the heat fitting process, and the reduction of the risk of stator and rotor rubbing. The first motor 130 has high efficiency and the stator 131 has no risk of falling off. For example, (D5-D4) / t is 0.02, 0.03, 0.05, 0.07 or 0.08.

[0314] If (D5-D4) / T < 0.02, then the clamping force of stator 131 is small, and there is a risk of it falling off.

[0315] If (D5-D4) / T > 0.08, the compressive stress on the stator 131 and the electromagnetic loss of the first motor 130 will increase, resulting in a decrease in the efficiency of the first motor 130. Furthermore, a higher temperature is required for the inner radial expansion of the first housing 110 to fit the stator 131. The higher the temperature, the more severe the blueing of the first housing 110. The severe inner radial deformation of the stator 131 will increase the risk of stator 131 and rotor 132 rubbing against each other.

[0316] In some embodiments, referring to FIG28, the compressor body 100 further includes an oil sump 1500. An oil sump 1500 is formed at the bottom of the receiving cavity 111. After wear occurs in the compressor 1000, wear debris is deposited in the oil sump 1500. If too much wear debris is deposited, it will be re-drawn into the compressor body 100, causing the compressor 1000 to seize up.

[0317] To address this technical problem, referring to Figure 28, the compressor body 100 also includes a fourth sensor 440. The fourth sensor 440 is located within the oil sump 1500 and is configured to detect the color of the oil within the oil sump 1500. For example, the fourth sensor 440 is a color sensor. By real-time detection of the color of the oil within the oil sump 1500 using the fourth sensor 440, the wear of the compressor 1000 can be determined based on the oil's color.

[0318] If the color of the oil sump 1500 detected by the fourth sensor 440 is greater than the fifth set value, the compressor 1000 will alarm and automatically stop, thereby reducing the failure rate.

[0319] In some embodiments, the fourth sensor 440 is fixedly installed to the bottom wall of the first housing 110 by means of snap-fit ​​or the like.

[0320] In some embodiments, referring to FIG37, 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 512 is H1, and the height of the portion of the first outlet pipe 511 located inside the cavity is H2. The height H1 of the second housing 512 and the height H2 of the portion of the first outlet pipe 511 located inside the cavity satisfy the following:

[0321] 0.5 < H2 / H1 < 0.8

[0322] This range can improve the gas-liquid separation performance of the gas-liquid separator 200 and reduce vibration and noise. For example, H2 / H1 can be 0.55, 0.60, 0.65, 0.70, or 0.75.

[0323] If H2 / H1 > 0.8, the length of the first vent pipe 511 within the gas-liquid separator 200 will be too long, which will cause interference between the first vent pipe 511 and the filter screen 280. If the length of the first vent pipe 511 extending out of the first partition 250 is too long, the top of the first vent pipe 511 will deform greatly, which will easily induce the first vent pipe 511 to generate a bending mode and generate vibration noise.

[0324] If H2 / H1 < 0.5, the effective volume inside the gas-liquid separator 200 is insufficient, affecting the performance of the gas-liquid separator 200.

[0325] It should be noted that any one of the technical solutions disclosed in this disclosure can solve one or more of the above-mentioned technical problems and achieve a certain disclosure purpose to a certain extent; multiple technical disclosures can also be combined into an overall solution to solve one or more of the above-mentioned technical problems and achieve a certain disclosure purpose; some technical disclosures can also be selected and combined into an overall solution, while adopting related technologies and deteriorating solutions, but the deterioration trend can be compensated by the means of this technical disclosure, and the overall solution can solve one or more of the above-mentioned technical problems and achieve a certain disclosure purpose to a certain extent; each technical disclosure combined into a complete technical solution constitutes an organic and indivisible overall solution, which solves the technical problems and achieves a certain disclosure purpose as a whole.

[0326] Any technical disclosure in this disclosure, as well as the recombination of multiple technical disclosures, can form a complete technical solution and solve one or more of the aforementioned technical problems, thereby achieving the purpose of disclosure. All of these are part of the content of this disclosure and are directly and unambiguously determined based on the content of this disclosure.

[0327] Those skilled in the art will understand that the scope of this disclosure is not limited to the specific embodiments described above, and that modifications and substitutions can be made to certain elements of the embodiments without departing from the spirit of this disclosure. The scope of this disclosure is limited by the appended claims.

Claims

1. A compressor, comprising: a compressor body comprising a first casing; and a foot disposed on the first casing, the foot being capable of mounting the compressor body to a mounting carrier on which the compressor is located, the foot comprising: an outer shell connecting the first casing and the mounting carrier, the outer shell having a mounting cavity formed therein; a support disposed in the mounting cavity; and a first driving portion disposed in the mounting cavity, the first driving portion being capable of adjusting a rigidity of the support according to a vibration signal of the compressor. 2.The compressor of claim 1, further comprising: a first sensor disposed on the first casing, the first sensor being capable of detecting a first vibration signal of the first casing; and a second sensor disposed on the mounting carrier, the second sensor being capable of detecting a second vibration signal of the mounting carrier; the first driving portion being further capable of adjusting the rigidity of the support according to the first vibration signal and the second vibration signal. 3.The compressor of claim 2, further comprising a first controller coupled to the first sensor, the foot, and the mounting carrier, respectively; the first controller being configured to: obtain the first vibration signal and the second vibration signal; if it is determined that the compressor is operating at a natural frequency and a difference between vibration amplitudes of the first vibration signal and the second vibration signal is greater than a first set value, control the first driving portion to drive the support to extend; if it is determined that the compressor satisfies at least one of the following: the compressor is not operating at the natural frequency, or the difference between vibration amplitudes of the first vibration signal and the second vibration signal is less than or equal to the first set value, control the first driving portion to drive the support to contract. the first driving portion comprises a motor, a threaded column, and a moving portion, a power shaft end of the motor is connected to the threaded column, the moving portion is disposed on the threaded column, and the moving portion is configured to move in an extension direction of the support. the support comprises a spring, the spring is sleeved on an outer periphery of the threaded column, a first end of the spring abuts against the moving portion, and a second end of the spring abuts against a top wall of the mounting cavity.

4. The compressor of any one of claims 1 to 3, wherein, the outer shell comprises:

5. The compressor of claim 4, wherein, a first sub-shell, the first sub-shell being connected to the mounting carrier, the first sub-shell constituting a bottom wall of the mounting cavity, and the motor being disposed on the first sub-shell; 6. The compressor of claim 4 or 5, wherein, a second sub-shell, the second sub-shell forming the mounting cavity, and the second sub-shell being connected to the first sub-shell; and a third sub-shell, the third sub-shell being connected to the second sub-shell, the third sub-shell and the first sub-shell being disposed on opposite ends of the second sub-shell, and the third sub-shell being connected to the first casing. a material of the outer shell is rubber. 8.The compressor of any one of claims 1 to 7, further comprising:

7. The compressor of any one of claims 1 to 6, wherein, a gas-liquid separator comprising a second casing, the second casing being disposed outside the first casing; a first connecting portion fixedly connecting the first casing and the second casing; and a second connecting portion fixedly connecting the second casing and the mounting carrier. ​ ​ The second connecting portion includes a fixed portion and a plurality of moving portions. The fixed portion is fixedly connected with the first shell. Opposite sides of the fixed portion are respectively provided with at least one moving portion of the plurality of moving portions. The plurality of moving portions are configured to move towards the second shell or away from the second shell according to a vibration signal of the gas-liquid separator.

9. The compressor of claim 8, further comprising: a third sensor disposed on the second shell and configured to detect a third vibration signal of the gas-liquid separator; a second controller disposed on the gas-liquid separator and coupled with the third sensor, the second controller being configured to: obtain the third vibration signal detected by the third sensor; if it is determined that an amplitude value of the third vibration signal is greater than a second set value and the compressor operating frequency is greater than a third set value, control the plurality of moving portions to move away from the second shell; if it is determined that the amplitude value of the third vibration signal is greater than the second set value and the compressor operating frequency is less than or equal to the third set value, control the plurality of moving portions to move towards the second shell. The gas-liquid separator further comprises: a first separation portion that separates an internal cavity of the gas-liquid separator into a first cavity and a second cavity, the first cavity and the second cavity being arranged in sequence along a height direction of the second shell; 10. The compressor of claim 9, wherein, a second separation portion that separates the second cavity into a first sub-cavity and a second sub-cavity, the first sub-cavity and the second sub-cavity being arranged in sequence along the height direction of the second shell; a second driving portion configured to drive the second separation portion to move along the height direction of the second shell; wherein the second controller is further configured to: obtain the third vibration signal detected by the third sensor; analyze and process the third vibration signal; if the gas-liquid separator is in a non-resonance operating state and an amplitude value of the third vibration signal is greater than a fourth set value, control the second driving portion to drive the second separation portion to move away from the first separation portion until the third vibration signal is less than or equal to the fourth set value, and control the second separation portion to stop moving; if the gas-liquid separator satisfies at least one of the following conditions: the gas-liquid separator is in a resonance operating state, or the amplitude value of the third vibration signal is less than or equal to the fourth set value, control the second driving portion to remain stationary and the second separation portion to remain stationary.

11. The compressor of any one of claims 1 to 10, further comprising a compression mechanism disposed in the mounting cavity, the compression mechanism comprising: an eccentric crankshaft; a bearing sleeved on an outer side of the eccentric crankshaft, the bearing comprising: an exhaust hole configured to exhaust refrigerant in the compression mechanism; a first groove arranged around the exhaust hole; an abutting portion formed between the first groove and the exhaust hole; and at least one second groove; and ​ ​ An exhaust valve plate, a first end of the exhaust valve plate is fixedly arranged on the bearing, a second end of the exhaust valve plate is capable of closing or opening the exhaust hole, the at least one second groove is located between the first end and the second end, and the exhaust valve plate is configured to cover the first groove and the second groove and abut against the abutting portion when the exhaust hole is closed.

12. The compressor of claim 11, wherein, The at least one second groove comprises a plurality of second grooves arranged along a length direction of the exhaust valve plate, and any two adjacent second grooves of the plurality of second grooves have a spacing therebetween.

13. The compressor of claim 11 or 12, wherein, The exhaust valve plate comprises a first connecting section connected between the first end and the second end, and the exhaust valve plate is further configured such that, when the exhaust hole is closed, the first connecting section covers the second groove and the second end covers the first groove.

14. The compressor of any one of claims 11-13, wherein, The bearing comprises: a first bearing portion provided with the exhaust hole, the first groove and the second groove, and the first bearing portion is provided with a fitting hole; and a second bearing portion fixedly arranged on the first bearing portion, the second bearing portion comprises a first shaft hole, the first shaft hole is in communication with the fitting hole, and the eccentric crankshaft passes through the first shaft hole and the fitting hole.

15. The compressor of claim 14, wherein, The first bearing portion is configured as a sheet metal stamping part.

16. The compressor of claim 14 or 15, wherein, The second bearing portion is configured as a metal tube, and the first shaft hole is formed in the metal tube.

17. The compressor of any one of claims 14-16, wherein, The bearing comprises a plurality of reinforcing portions arranged along a circumferential direction of the second bearing portion, any two adjacent reinforcing portions of the plurality of reinforcing portions have a spacing therebetween, and the plurality of reinforcing portions are connected with the first bearing portion.

18. The compressor of any one of claims 11 to 17, wherein, The eccentric crankshaft comprises: a main shaft section, an inner portion of the main shaft section is formed with a second shaft hole; and an eccentric shaft section fixedly sleeved on an outer side of the main shaft section, an outer peripheral wall of the eccentric shaft section is provided with a third groove, the third groove surrounds the eccentric shaft section, and a passage is arranged in the eccentric shaft section.

19. The compressor of claim 18, wherein the eccentric shaft section comprises two sub-eccentric shaft sections, the two sub-eccentric shaft sections are connected and symmetrically arranged on two sides in a height direction of the third groove; the sub-eccentric shaft section comprises a first wall and a second wall, the second wall extends away from the first wall in a direction away from the first wall from a circumferential edge of the first wall, two first walls of the two sub-eccentric shaft sections are connected; the first wall is provided with a sub-weight-reducing hole, the sub-weight-reducing holes of the two sub-eccentric shaft sections are in communication to form a weight-reducing hole; the first wall is provided with a fourth groove, and two fourth grooves on the two sub-eccentric shaft sections are in abutment communication to form the passage.

20. An air conditioner comprising a compressor, an evaporator, a condenser, and a throttling device, wherein, The compressor is the compressor according to any one of claims 1 to 19.

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