Compressor and air conditioner

Abstract

The compressor comprises a shell, a containing cavity is formed in the shell, a compression mechanism is arranged in the containing cavity, the compression mechanism comprises an eccentric crankshaft and a bearing, the bearing comprises a first shaft hole, the eccentric crankshaft passes through the first shaft hole, an oil groove is formed in the hole wall of the first shaft hole, and the oil groove comprises a plurality of first oil sub-grooves and a plurality of second oil sub-grooves; the first sub-oil grooves and the second sub-oil grooves are arranged at intervals in the axial direction of the first shaft hole, the adjacent first sub-oil grooves and second sub-oil grooves are communicated, the first sub-oil grooves extend in the axial direction of the first shaft hole, and the second sub-oil grooves spirally extend in the circumferential direction of the first shaft hole. The number of the first sub-oil grooves is N1, the number of the second sub-oil grooves is N2, N1 / N2 is larger than 3.5 and smaller than 4.6, the friction noise and the oil discharge rate of the compressor are reduced, and the performance of the compressor is improved.

Description

Technical Field

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

[0002] An air conditioner includes an outdoor unit and an indoor unit, and the outdoor unit is connected to the indoor unit. The air conditioner performs a refrigeration and heating cycle by using a compressor, a condenser, an expansion valve, and an evaporator. The compressor is fixedly arranged in the outdoor unit. A compression mechanism is arranged in the inner cavity of a scroll compressor. The compression mechanism is configured to compress a refrigerant. Its working principle is as follows: After the motor stator is electrified, a magnetic pulling force is generated. The motor rotor makes a rotational motion under the action of the magnetic pulling force of the stator, and drives the eccentric crankshaft of the compression mechanism to make a rotational motion together. When the eccentric crankshaft rotates, it drives the piston sleeved on its eccentric shaft section to make an eccentric circular motion in the cylinder. The sliding vane is installed in the sliding vane groove of the cylinder, and always abuts against the piston under the action of the compression spring in the spring hole, so that it makes a reciprocating motion in the sliding vane groove. The sliding vane and the piston divide the cylinder into a high-pressure chamber and a low-pressure chamber. When the eccentric crankshaft drives the piston to rotate one week, it sucks air from the low-pressure chamber and discharges air from the high-pressure chamber to complete one exhaust, thus realizing the compression of gas by the compressor.

[0003] A bearing is sleeved on the eccentric crankshaft. An oil groove is arranged on the inner wall of the shaft hole of the bearing. The oil groove usually rises in the shape of an equal curve or a straight line. When the compressor operates at a low frequency, there is no oil in the oil groove, and the friction between the bearing and the eccentric crankshaft is large, thereby increasing the friction noise of the compressor. When the compressor operates at a high frequency, the excess oil supply is discharged through the oil groove, and the oil discharge rate of the compressor increases, thereby reducing the performance of the compressor.

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

[0005] In view of the problems pointed out in the background art, the present disclosure provides a compressor and an air conditioner, which reduce the friction noise and oil discharge rate of the compressor and improve the performance of the compressor.

[0006] On the one hand, a compressor is provided. The compressor includes a housing, an accommodation cavity is formed in the housing, a compression mechanism is arranged in the accommodation cavity. The compression mechanism includes an eccentric crankshaft and a bearing. The bearing includes a first shaft hole. The eccentric crankshaft passes through the first shaft hole. An oil groove is arranged on the hole wall of the first shaft hole. The oil groove includes a plurality of first sub-oil grooves and a plurality of second sub-oil grooves. The plurality of first sub-oil grooves and the plurality of second sub-oil grooves are arranged at intervals along the axial direction of the first shaft hole. Adjacent first sub-oil grooves and second sub-oil grooves are communicated. The first sub-oil grooves extend along the axial direction of the first shaft hole, and the second sub-oil grooves extend spirally along the circumferential direction of the first shaft hole. The number of the first sub-oil grooves is N1, and the number of the second sub-oil grooves is N2, and 3.5 < N1 / N2 < 4.6.

[0007] The oil sump is a composite oil sump composed of a linear first sub-oil sump and a spiral second sub-oil sump. First, when the compressor operates at low frequency, the oil sump can reliably transport oil to the friction pair, avoiding oil-free lubrication friction of the friction pair components (such as the eccentric crankshaft and the bearing); second, when the compressor operates at high frequency, excessive oil supply is avoided, reducing the oil discharge rate; third, reasonable oil supply can effectively reduce the friction noise of the compressor, thereby reducing the vibration and noise of the compressor.

[0008] On the other hand, an air conditioner is provided, including a compressor, an evaporator, a condenser, and a throttling device, and the compressor is the compressor as described above.

[0009] After reading the specific embodiments of the present invention in conjunction with the drawings, other features and advantages of the present invention will become clearer. Description of the Drawings

[0010] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0011] Figure 1 A structural diagram of a compressor according to some embodiments;

[0012] Figure 2 A sectional view of a compressor according to some embodiments;

[0013] Figure 3 A structural diagram of a bearing according to some embodiments;

[0014] Figure 4 An exploded view of a bearing according to some embodiments;

[0015] Figure 5 A sectional view of a bearing according to some embodiments;

[0016] Figure 6 A structural diagram of a first bearing portion according to some embodiments;

[0017] Figure 7 A structural diagram of a bearing bush according to some embodiments;

[0018] Figure 8 Another sectional view of a bearing according to some embodiments;

[0019] Figure 9Graph showing the relationship between θ1 / φ + θ2 / φ and the height of the compressor oil sump / height of the installation cavity, and the oil discharge rate according to some embodiments;

[0020] Figure 10 Graph showing the relationship between N1 / N2 and the height of the compressor oil sump / height of the installation cavity, and the oil discharge rate according to some embodiments;

[0021] Figure 11 Graph showing the relationship between T / D and the height of the compressor oil sump / height of the installation cavity, and the oil discharge rate according to some embodiments;

[0022] Figure 12 Graph showing the relationship between D1 / D2 and the contact surface pressure height according to some embodiments;

[0023] Figure 13 Graph showing the relationship between H1 / H2 and the contact surface pressure height according to some embodiments;

[0024] Figure 14 Graph showing the relationship between D2 / D3 and the contact surface pressure height according to some embodiments;

[0025] Figure 15 Graph showing the relationship between (T1 + T2) / D4 and the contact surface pressure height according to some embodiments;

[0026] Figure 16 Structural diagram of an eccentric crankshaft according to some embodiments;

[0027] Figure 17 Exploded view of an eccentric crankshaft according to some embodiments;

[0028] Figure 18 Cross-sectional view of an eccentric crankshaft according to some embodiments;

[0029] Figure 19 Structural diagram of an eccentric shaft section according to some embodiments;

[0030] Figure 20 Exploded view of an eccentric shaft section according to some embodiments;

[0031] Figure 21 Schematic diagram of a multi-connected air conditioner according to some embodiments;

[0032] Figure 22 Structural diagram of a compressor and a gas-liquid separator according to some embodiments;

[0033] Figure 23 Another structural diagram of a compressor according to some embodiments;

[0034] Figure 24 Another cross-sectional view of a compressor according to some embodiments;

[0035] Figure 25 A structural diagram of a three-way joint according to some embodiments;

[0036] Figure 26 A structural diagram of a fixing part according to some embodiments. Detailed implementation manners

[0037] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present application without creative efforts shall fall within the protection scope of the present application.

[0038] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of the present application.

[0039] The terms "first" and "second" are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, unless otherwise specified, the meaning of "a plurality" is two or more.

[0040] In the description of the present application, it should be noted that unless otherwise clearly defined and limited, the terms "mounted", "connected" and "coupled" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the internal communication of two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0041] In the present utility model, unless otherwise clearly defined and limited, the first feature being "above" or "below" the second feature may include direct contact between the first and second features, or may include the first and second features not being in direct contact but in contact through additional features therebetween. Moreover, the first feature being "above", "over" and "on top of" the second feature includes the first feature being directly above and obliquely above the second feature, or merely indicating that the horizontal height of the first feature is higher than that of the second feature. The first feature being "below", "beneath" and "underneath" the second feature includes the first feature being directly below and obliquely below the second feature, or merely indicating that the horizontal height of the first feature is less than that of the second feature.

[0042] The following disclosure provides many different embodiments or examples for implementing different structures of the present utility model. To simplify the disclosure of the present utility model, components and settings of specific examples are described below. Of course, they are merely examples and are not intended to limit the present utility model. In addition, the present utility model may repeat reference numerals and / or reference letters in different examples. Such repetition is for the purpose of simplification and clarity, and does not itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the present utility model provides examples of various specific processes and materials, but those of ordinary skill in the art can be aware of the application of other processes and / or the use of other materials.

[0043] [Air conditioner]

[0044] 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 to cool or heat an indoor space.

[0045] The low-temperature and low-pressure refrigerant enters the compressor, and the compressor compresses the low-temperature and low-pressure refrigerant into a refrigerant gas in a high-temperature and high-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed gas refrigerant into a liquid-phase refrigerant and releases the heat of the refrigerant to the surrounding environment through the condensation process.

[0046] The expansion valve expands the high-temperature and high-pressure liquid-phase refrigerant formed by condensation in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a refrigeration effect by using the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. During the entire refrigeration cycle or heating cycle, the air conditioner can adjust the temperature of the indoor space.

[0047] The outdoor unit of the air conditioner includes a compressor and an outdoor heat exchanger, the indoor unit of the air conditioner includes an indoor heat exchanger, and an expansion valve can be arranged in the indoor unit or the outdoor unit.

[0048] The indoor heat exchanger and the outdoor heat exchanger are used as condensers or evaporators. When the indoor heat exchanger is used as a condenser, the air conditioner operates in the heating mode; when the indoor heat exchanger is used as an evaporator, the air conditioner operates in the cooling mode.

[0049] The outdoor unit further includes a four-way valve, and the four-way valve is configured to enable the conversion of the indoor heat exchanger and the outdoor heat exchanger as condensers or evaporators.

[0050] The refrigeration working principle of the air conditioner is as follows: When the compressor works, the indoor heat exchanger (in the indoor unit, which is an evaporator at this time) is in an ultra-low pressure state. The liquid refrigerant in the indoor heat exchanger quickly evaporates and absorbs heat. The air blown by the indoor fan cools down after passing through the indoor heat exchanger coil and then blows into the room as cold air. After the refrigerant evaporates and vaporizes, it is pressurized by the compressor and condenses into a liquid under the high-pressure environment in the outdoor heat exchanger (in the outdoor component, which is a condenser at this time), releasing heat. Through the outdoor fan, the heat is dissipated into the atmosphere, and such a cycle achieves the refrigeration effect.

[0051] The heating working principle of the air conditioner is as follows: The gaseous refrigerant is pressurized by the compressor to become a high-temperature and high-pressure refrigerant gas. The refrigerant gas enters the indoor heat exchanger (which is a condenser at this time), condenses and liquefies to release heat, becoming a liquid, and heats the indoor air, thereby achieving the purpose of raising the indoor temperature. The liquid refrigerant is decompressed by the throttling device and enters the outdoor heat exchanger (which is an evaporator at this time), evaporates and vaporizes to absorb heat, becoming a gas, and absorbs the heat of the outdoor air (the temperature of the outdoor air decreases), becoming a gaseous refrigerant. The gaseous refrigerant enters the compressor again to start the next cycle.

[0052] [Compressor body]

[0053] In some embodiments of the present disclosure, the compressor is a rolling piston compressor. Referring to Figure 1 and Figure 2 , the compressor includes a compressor body 100. The compressor body 100 includes a first housing 110. The compressor body 100 further includes a receiving cavity 111. A closed receiving cavity 111 is formed inside the first housing 110. The compressor body 100 further includes a compression mechanism 120. The compression mechanism 120 is arranged in the receiving cavity 111. The compression mechanism 120 is configured to compress the refrigerant. The compressor body 100 further includes a motor 130. The motor 130 is arranged inside the receiving cavity 111. The motor 130 is arranged above the compression mechanism 120. The motor 130 is configured to provide power for the compression mechanism 120.

[0054] In some embodiments, the motor 130 includes a rotor 132. The motor 130 further includes a stator 131, which is fixedly connected to the inner wall of the first housing 110 to fixedly mount the motor 130 in the accommodation cavity 11.

[0055] In some embodiments, referring to Figure 2 , the compression mechanism 120 further includes an eccentric crankshaft 140.

[0056] The eccentric crankshaft 140 includes a main shaft section 141; the eccentric crankshaft 140 further includes an eccentric shaft section 142. The main shaft section 141 is fixedly connected to the rotor 132.

[0057] Referring to Figure 2 , the compression mechanism 120 further includes a cylinder 122; the compression mechanism 120 further includes a piston 123. The piston 123 is disposed in the compression cavity of the cylinder 122, and the piston 123 is sleeved on the eccentric shaft section 142. The compression mechanism 120 further includes at least one bearing 703. For example, the at least one bearing 703 includes two bearings 703, namely a first bearing 1241 and a second bearing 1242. The bearing 703 is fixedly connected to the cylinder 122, the first bearing 1241 is fixedly connected to the inner wall of the first housing 110, and an exhaust hole is provided on the bearing 703, and the exhaust hole communicates with the compression cavity; the compression mechanism 120 further includes a sliding vane groove; the sliding vane groove is disposed in the cylinder 122. The compression mechanism 120 further includes a sliding vane. The sliding vane is disposed in the sliding vane groove. The eccentric crankshaft 121 drives the piston 123 to perform a circumferential motion in the compression cavity, the sliding vane reciprocates along the sliding vane groove, and the sliding vane always abuts against the piston 123. The compression cavity includes a first sub-compression cavity (high-pressure cavity); the compression cavity further includes a second sub-compression cavity (low-pressure cavity). The pressure in the first sub-compression cavity is greater than the pressure in the second sub-compression cavity. The sliding vane and the piston 123 divide the compression cavity into the first sub-compression cavity and the second sub-compression cavity. The compression mechanism 120 further includes at least one silencer 704. For example, the at least one silencer 704 includes two silencers 704, namely a first silencer 1261 and a second silencer 1262. The first silencer 1261 is disposed on the first bearing 1241, and the second silencer 1262 is disposed on the second bearing 1242.

[0058] The working principle of the compressor is as follows: After the stator 131 of the motor 130 is energized, a magnetic pulling force is generated. The rotor 132 of the motor 130 makes a rotational motion under the action of the magnetic pulling force of the stator 131, and drives the eccentric crankshaft 140 to make a rotational motion together. The rotation of the eccentric crankshaft 140 drives the piston 123 sleeved on the eccentric shaft section to make an eccentric circular motion in the compression cavity of the cylinder 122. The sliding vane makes a reciprocating motion in the sliding vane groove. The sliding vane and the piston 123 divide the compression cavity of the cylinder 122 into a first sub-compression cavity and a second sub-compression cavity. When the eccentric crankshaft 140 drives the piston 123 to rotate one week, it sucks air from the second sub-compression cavity and discharges air from the first sub-compression cavity to complete one exhaust, realizing the compression of the gas by the compressor. The compressed gas is discharged through the exhaust hole.

[0059] In an embodiment of the present disclosure, referring to Figure 2 , the compressor is a single-cylinder rolling rotor compressor.

[0060] In some embodiments of the present disclosure, referring to Figure 24 , the compressor is a double-cylinder rolling rotor compressor, and the compression mechanism 120 includes an eccentric crankshaft 140. The compression mechanism 120 further includes two cylinders 701, namely a first cylinder 1221 and a second cylinder 1222. The compression mechanism 120 further includes two bearings 703, namely a first bearing 1241 and a second bearing 1242. The compression mechanism 120 further includes two pistons 702, namely a first piston 1231 and a second piston 1232. The compression mechanism 120 further includes a middle partition plate 125. The compression mechanism 120 further includes two mufflers 704, namely a first muffler 1261 and a second muffler 1262.

[0061] [First gas-liquid separator]

[0062] In some embodiments, referring to Figure 1 , the compressor further includes a first gas-liquid separator 510. The first gas-liquid separator 510 is disposed outside the compressor body 100 and is configured to supply gaseous refrigerant to the compression cavity of the compression mechanism 120. The first gas-liquid separator 510 completes the separation of the liquid refrigerant and the gaseous refrigerant to prevent the liquid refrigerant from entering the compression cavity of the compressor body 100 and causing abnormalities in the compressor.

[0063] In some embodiments, referring to Figure 1 , the first gas-liquid separator 510 includes a second housing 512; the first gas-liquid separator 510 further includes a first gas outlet pipe 511, and the first gas outlet pipe 511 is disposed at the bottom of the second housing 512. The first end of the first gas outlet pipe 511 extends into the inner cavity of the second housing 512, and the second end of the first gas outlet pipe 511 is connected to the compression mechanism 120. For example, the second end of the gas outlet pipe 240 is connected to the suction port of the cylinder to supply gaseous refrigerant to the compression mechanism 120.

[0064] [Bearing]

[0065] In some embodiments, referring to Figure 3 and Figure 6 , the bearing 150 includes an exhaust hole 1511, the exhaust hole 1511 communicates with the inner cavity of the cylinder 122, and the exhaust hole 1511 is configured to discharge the refrigerant in the cylinder 122.

[0066] Referring to Figure 2 , Figure 4 and Figure 6 , the compression mechanism 120 includes 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 in the direction close to 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 in the direction away from the exhaust hole 1511, the exhaust hole 1511 is opened.

[0067] Referring to Figure 4 , the exhaust valve plate 170 includes a first end 171; the exhaust valve plate 170 further includes a second end 172; the exhaust valve plate 170 further includes a first connecting section 173. The first connecting section 173 is connected between the first end 171 and the second end 172.

[0068] Referring to Figure 6 , the bearing 150 further includes a bearing body; the bearing 150 further includes a mounting hole 1516. The mounting hole 1516 is provided in 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 Figure 4 and Figure 6 , the first end 171 of the exhaust valve plate 170 is fixedly installed in the mounting hole 1516 through a bolt 190. The second end 172 of the exhaust valve plate 170 is configured to close or open the exhaust hole 1511.

[0069] The compression mechanism 120 further includes a lift limiter 180, and the lift limiter 180 is configured to limit the opening stroke of the exhaust valve plate 170.

[0070] In some disclosed compressors, during the movement of the exhaust valve plate 170, there is noise generated by hitting the bearing 150, which increases the working noise of the compressor, and the opening resistance of the exhaust valve plate 170 is large.

[0071] To solve this technical problem, in some embodiments, referring to Figure 3 and Figure 6, the bearing 150 further includes a first groove 1512. The first groove 1512 is disposed around the exhaust hole 1511. The bearing 150 further includes an abutting portion 1515. An abutting portion 1515 is formed between the first groove 1512 and the exhaust hole 1511. The abutting portion 1515 is located between the first groove 1512 and the exhaust hole 1511, and the first groove 1512 is configured to store oil.

[0072] The bearing 150 further includes at least one second groove 1513, and the second groove 1513 is configured to store oil. When the compressor operates, the oil in the oil sump at the bottom of the compressor is supplied to each friction pair through the eccentric crankshaft 140, and the first groove 1512 and the second groove 1513 are filled with oil.

[0073] The second groove 1513 is located between the first end 171 and the second end 172 of the exhaust valve plate 170. The exhaust valve plate 170 is further configured such that when the exhaust valve plate 170 is closed, the exhaust valve plate 170 covers the first groove 1512 and the second groove 1513 and abuts against the abutting portion 1515.

[0074] When the exhaust valve plate 170 is closed, the exhaust valve plate 170 covers the first groove 1512 and abuts against the abutting portion 1515. Oil is stored in the first groove 1512, and the exhaust valve plate 170 contacts the oil to form an oil seal, thereby improving the sealing effect of the exhaust hole 1511.

[0075] The outer surface of the abutting portion 1515 is a plane so that the abutting portion 1515 abuts against the exhaust valve plate 170 to improve the sealing effect.

[0076] The width of the abutting portion 1515 is narrow, reducing the contact area between the exhaust valve plate 170 and the abutting portion 1515, thereby reducing the opening resistance of the exhaust valve plate 170.

[0077] When the exhaust valve plate 170 is closed, the exhaust valve plate 170 covers the second groove 1513. The second groove 1513 is filled with oil, and the second groove 1513 functions as a shock absorber, which can reduce the impact sound when the exhaust valve plate 170 hits the bearing 150 when the exhaust valve plate 170 is closed, thereby reducing the operating noise of the compressor.

[0078] In some embodiments, referring to Figure 6 , at least one second groove 1513 includes a plurality of second grooves 1513, and the plurality of second grooves 1513 are arranged at intervals along the length direction of the exhaust valve plate 170 to improve the noise reduction effect of the impact sound of the exhaust valve plate 170.

[0079] In some embodiments, when the exhaust valve plate 170 is closed, 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.

[0080] Most of the impact sound of the exhaust valve plate 170 is generated by the first connecting section 173 hitting the bearing 150. In some embodiments of the present disclosure, the compressor is provided with the first connecting section 173 covering the second groove 1513, and the second groove 1513 is used to reduce the impact sound of the first connecting section 173 hitting the bearing 150, thereby improving the noise reduction effect.

[0081] When the exhaust valve plate 170 is closed, the second end 172 of the exhaust valve plate 170 is configured to cover the exhaust hole 1511 to close the exhaust hole 1511. In some embodiments of the present disclosure, when the exhaust valve plate 170 is closed, the second end 172 covers the first groove 1512, and the second end 172 abuts against the abutting portion 1515, improving the sealing effect of the exhaust hole 1511.

[0082] In some embodiments, referring to Figure 4 and Figure 6 the bearing 150 further includes a first bearing portion 151. The exhaust hole 1511, the first groove 1512, at least one second groove 1513 and the mounting hole 1516 are provided on the first bearing portion 151. The bearing 150 further includes a first opening 1514. The first opening 1514 is provided on the first bearing portion 151.

[0083] Referring to Figure 4 the bearing 150 further includes a second bearing portion 152. The second bearing portion 152 is fixedly provided on the first bearing portion 151. The second bearing portion 152 is fixedly provided on one side of the first bearing portion 151. The second bearing portion 152 includes a first shaft hole 1522, and the first shaft hole 1522 communicates with the first opening 1514. The main shaft section 141 of the eccentric crankshaft 140 passes through the first shaft hole 1522 and the first opening 1514 to realize the installation of the eccentric crankshaft 140 and the bearing 150.

[0084] The bearing 150 in some embodiments of the present disclosure includes two structural parts (the first bearing portion 151 and the second bearing portion 152), which is convenient for processing and manufacturing.

[0085] The bearing 150 is usually a casting, with a low elastic modulus, and there is a large amount of wear between the bearing 150 and the eccentric crankshaft 140. The processing process of the bearing 150 includes casting, mechanical rough machining, mechanical finish machining, phosphating, brushing, etc. The processing process is complex and the cost is high. Processing processes such as casting and phosphating consume fossil fuels and pollute the environment.

[0086] 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 tube, and a first shaft hole 1522 is formed inside the metal tube. The first bearing portion 151 and the second bearing portion 152 are welded and fixed.

[0087] In some embodiments of the present disclosure, the bearing 150 has a low cost and a simplified manufacturing process, including stamping, finishing, and welding. The manufacturing process can reduce environmental pollution.

[0088] In some embodiments of the present disclosure, the bearing 150 uses sheet metal stampings and metal pipes, and the material is any one of steel, cast iron, and alloy. It has a large elastic modulus and can reduce the friction between the bearing 150 and the eccentric crankshaft 140.

[0089] In some embodiments, referring to Figure 3 and Figure 4 , the bearing 150 further includes a plurality of reinforcing portions 153. The plurality of reinforcing portions 153 are arranged at intervals along the circumferential direction of the second bearing portion 152, and the plurality of reinforcing portions 153 are connected to the first bearing portion 151, improving the structural reliability of the first bearing portion 151 and the second bearing portion 152.

[0090] 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.

[0091] In some embodiments of the compressor of the present disclosure, referring to Figure 8 , the bearing 150 further includes an oil groove 154. An oil groove 154 is provided on the inner wall of the shaft hole (first shaft hole 1522) of the bearing 150. The oil groove 154 is usually an isometric curve or a straight line rising. When the compressor 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. When the compressor operates at a high frequency, the excess oil supply is discharged through the oil groove 154, and the oil discharge rate of the compressor increases, thereby reducing the performance of the compressor.

[0092] To solve this technical problem, in some embodiments, referring to Figure 8 , the bearing 150 includes a first shaft hole 1522, and the eccentric crankshaft 140 passes through the first shaft hole 1522. An oil groove 154 is provided on the hole wall of the first shaft hole 1522.

[0093] The oil groove 154 includes a plurality of first sub-oil grooves 1541; the oil groove 154 further includes a plurality of second sub-oil grooves 1542. 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 the adjacent first sub-oil grooves 1541 and second sub-oil grooves 1542 are communicated. 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 spirally along the circumferential direction of the first shaft hole 1522, and the second sub-oil grooves 1542 are spiral grooves.

[0094] For example, referring to Figure 8 , three first sub-oil grooves 1541 and two second sub-oil grooves 1542 are provided on the hole wall of the first shaft hole 1522.

[0095] In some embodiments of the present disclosure, the oil sump 154 is a composite oil sump composed of a linear first sub-oil sump 1541 and a spiral second sub-oil sump 1542. First, when the compressor operates at low frequency, the oil sump 154 can reliably transport oil to the friction pairs, avoiding oil-free lubrication friction of the friction pair components (such as the eccentric crankshaft 140 and the bearing 150). Second, when the compressor operates at high frequency, excessive oil supply is avoided, and the oil discharge rate is reduced. Third, reasonable oil supply can effectively reduce the friction noise of the compressor, thereby reducing the vibration and noise of the compressor.

[0096] In some embodiments, the oil sump 154 includes N1 first sub-oil sumps 1541, and the oil sump 154 includes N2 second sub-oil sumps 1542, where 3.5 < N1 / N2 < 4.6. Within this range, the ratio of the height of the compressor oil sump to the height of the installation cavity is reasonable, and the oil discharge rate of the compressor is better. Figure 10 FIG. is a relationship diagram of N1 / N2 with the height ratio of the compressor oil sump to the installation cavity and the oil discharge rate. Curve M is the curve of the compressor oil discharge rate, and curve L is the curve of the ratio of the height of the compressor oil sump to the installation cavity.

[0097] In some embodiments, the depth of the oil sump 154 is T. Referring to Figure 8 , the depth T is the opening depth of the oil sump 154 along the height H2 direction perpendicular to the first shaft hole 1522. The diameter of the first shaft hole 1522 is D, and 0.15 < T / D < 0.21. Within this range, the ratio of the height of the compressor oil sump to the height of the installation cavity is reasonable, and the oil discharge rate of the compressor is better. Figure 11 FIG. is a relationship diagram of T / D with the height ratio of the compressor oil sump to the installation cavity and the oil discharge rate. Curve M is the curve of the compressor oil discharge rate, and curve L is the curve of the ratio of the height of the compressor oil sump to the installation cavity.

[0098] In some embodiments, the starting angle of the oil sump 154 is θ1, the ending angle of the oil sump 154 is θ2, and the pitch of the second sub-oil sump 1542 is φ, where 1.6 < θ1 / φ + θ2 / φ < 2.9. Within this range, the ratio of the height of the compressor oil sump to the height of the installation cavity is reasonable, and the oil discharge rate of the compressor is better. Figure 9 FIG. is a relationship diagram of θ1 / φ + θ2 / φ with the height ratio of the compressor oil sump to the installation cavity and the oil discharge rate. Curve M is the curve of the compressor oil discharge rate, and curve L is the curve of the ratio of the height of the compressor oil sump to the installation cavity.

[0099] In the compressors of some disclosed embodiments, the contact surface pressure height between the bearing 150 and the eccentric crankshaft 140 is small, which is not conducive to forming an oil film between the two, resulting in large friction between the two, further increasing the frictional noise of the compressor and reducing the performance of the compressor. Among them, under the combined loads such as gas load, centrifugal force, and electromagnetic force, the pressure generated by the interaction force of the contact surface between the bearing 150 and the eccentric crankshaft 140 is the contact surface pressure, and the axial height of the contact surface between the bearing 150 and the eccentric crankshaft 140 is the contact surface pressure height.

[0100] To solve this technical problem, in some embodiments, referring to Figure 8 , the bearing 150 further includes a first bearing portion 151; the bearing 150 further includes a sixth groove 1517. The sixth groove 1517 is provided on the first bearing portion 151.

[0101] The bearing 150 includes a second bearing portion 152, and the second bearing portion 152 is connected to the first bearing portion 151. The second bearing portion 152 extends toward one side of the first bearing portion 151. For example, the first bearing portion 151 and the second bearing portion 152 are of an integral structure. Or, for example, the first bearing portion 151 and the second bearing portion 152 are of a split structure and are fixed by welding.

[0102] A first shaft hole 1522 is formed in the second bearing portion 152, and the eccentric crankshaft 140 passes through the first shaft hole 1522, and the sixth groove 1517 surrounds the first shaft hole 1522.

[0103] The height of the sixth groove 1517 along the axial direction of the first shaft hole 1522 is H1, the height of the bearing 150 along the axial direction of the first shaft hole 1522 is H2, and 0.12 < H1 / H2 < 0.25. In this range, the contact surface pressure height between the eccentric crankshaft 140 and the bearing 150 is large, which is conducive to forming an oil film between the two, resulting in small friction between the two, further reducing the frictional noise of the compressor and improving the performance of the compressor. Figure 13 The figure shows the relationship diagram between H1 / H2 and the contact surface pressure height.

[0104] In some embodiments, referring to Figure 8 , the inner diameter of the sixth groove 1517 is D2, and the extension dimension of the first bearing portion 151 perpendicular to the second bearing portion 152 is D3, and 0.1 < D2 / D3 < 0.24. In this range, the contact surface pressure height between the eccentric crankshaft 140 and the bearing 150 is large, which is conducive to forming an oil film between the two, resulting in small friction between the two, further reducing the frictional noise of the compressor and improving the performance of the compressor. Figure 14 The figure shows the relationship diagram between D2 / D3 and the contact surface pressure height.

[0105] In some embodiments, referring to Figure 8, the outer diameter of the sixth groove 1517 is D1, the inner diameter of the sixth groove 1517 is D2, 0.9 < D1 / D2 < 1.65. Within this range, the contact surface pressure height between the eccentric crankshaft 140 and the bearing 150 is large, which is conducive to forming an oil film between the two, the friction between the two is small, thereby reducing the friction noise of the compressor and improving the performance of the compressor. Figure 12 The figure shows the relationship between D1 / D2 and the contact surface pressure height.

[0106] In some embodiments, referring to Figure 8 , the outer diameter of the sixth groove is D1, the inner diameter of the sixth groove 1517 is D2, T1 = D1 - D2, and the second bearing portion 152 includes a shaft neck portion 1521. The extension dimension of the shaft neck portion 1521 perpendicular to the second bearing portion 152 is T2. Referring to Figure 2 , the outer diameter of the rotor 132 is D4. 0.095 < (T1 + T2) / D4 < 0.15. Within this range, the contact surface pressure height between the eccentric crankshaft 140 and the bearing 150 is large, which is conducive to forming an oil film between the two, the friction between the two is small, thereby reducing the friction noise of the compressor and improving the performance of the compressor. Figure 15 The figure shows the relationship between (T1 + T2) / D4 and the contact surface pressure height.

[0107] [Bearing shell]

[0108] In some disclosed compressors, the bearing 150 is usually sleeved on the outside of the eccentric crankshaft 140. The wear between the shaft sleeve 144 and the eccentric crankshaft 140 is large, increasing the friction noise of the compressor and reducing the performance of the compressor.

[0109] To solve this technical problem, in some embodiments, referring to Figure 4 , Figure 5 and Figure 7 , the compression 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 press-fitted into the first shaft hole 1522.

[0110] The two bearing shells 160 are arranged at intervals along the axial direction of the first shaft hole 1522. The bearing shell 160 includes a second shaft hole 161, and the eccentric crankshaft 140 passes through the second shaft hole 161. There is a gap 163 between the two bearing shells 160. The gap 163 is an annular groove surrounding the second shaft hole 161. The bearing shell 160 further includes a fifth groove 162. The fifth groove 162 is arranged on the inner peripheral wall of the bearing shell 160, and the fifth groove 162 communicates with the gap 163.

[0111] The gap 163 and the fifth groove 162 between the two bearing shells 160 serve as oil grooves, improving the wear resistance between the eccentric crankshaft 140 and the bearing shells 160, reducing the friction noise of the compressor, and improving the performance of the compressor.

[0112] In some embodiments, referring to Figure 7 , the fifth groove 162 spirally extends circumferentially along the bearing shell 160, increasing the extension length of the fifth groove 162 and the oil storage capacity of the fifth groove 162, which helps to improve the wear resistance between the eccentric crankshaft 140 and the bearing shell 160.

[0113] In some embodiments, referring to Figure 5 , the two fifth grooves 162 of the two bearing shells 160 are the fifth groove 162A and the fifth groove 162B respectively, and are located on the same spiral track. For example, oil flows through the second shaft hole 161 from bottom to top. The oil first passes through the lower fifth groove 162A, then enters the gap 163 between the two bearing shells 160, and then flows into the upper fifth groove 162B. The fifth groove 162A and the fifth groove 162B are on the same thread track, which is convenient for oil supply, ensures that the parts of the eccentric crankshaft 140 in contact with the bearing 150 can be effectively lubricated, and reduces friction.

[0114] [Eccentric crankshaft]

[0115] In some disclosed compressors, the eccentric crankshaft 140 is usually a casting, with a low elastic modulus, and there is significant wear between the bearing 150 and the eccentric crankshaft 140. The processing process of the bearing 150 includes casting, mechanical rough machining, mechanical finish machining, phosphating, brushing, etc. The processing process is complex and costly. Processing processes such as casting and phosphating consume fossil fuels and pollute the environment.

[0116] To solve this technical problem, in some embodiments, referring to Figures 16 to 18 , the eccentric crankshaft 140 includes a main shaft section 141, and the eccentric crankshaft 140 further includes a third shaft hole 1411. The third shaft hole 1411 is formed inside the main shaft section 141. The eccentric crankshaft 140 further includes a blade 143. The blade 143 is arranged in the third shaft hole 1411. The eccentric crankshaft 140 further includes a shaft plug 145; the eccentric crankshaft 140 further includes a shaft sleeve 144. A shaft plug 145 is arranged at one end of the third shaft hole 1411, and a shaft sleeve 144 is arranged at the opposite end of the third shaft hole 1411.

[0117] The main shaft section 141 is made of a metal tube, such as a steel tube, and the third shaft hole 1411 is formed inside the metal tube.

[0118] The eccentric crankshaft 140 further includes a plurality of oil holes 1412. A plurality of oil holes 1412 are arranged on the main shaft section 141 to supply oil for lubricating each friction pair installed on the eccentric crankshaft 140.

[0119] The eccentric crankshaft 140 includes an eccentric shaft section 142, and the eccentric shaft section 142 is fixedly sleeved on the main shaft section 141. The eccentric crankshaft 140 is made of a sheet metal stamping part. The eccentric crankshaft 140 is fixedly welded to the main shaft section 141.

[0120] In some embodiments of the present disclosure, the eccentric crankshaft 140 has a low cost, and the processing process is simplified, including stamping, finishing, and welding. The processing process can reduce environmental pollution.

[0121] In some embodiments of the present disclosure, the eccentric crankshaft 140 uses sheet metal stampings and metal pipes. The material is steel, which has a large elastic modulus and reduces the friction between the bearing 150 and the eccentric crankshaft 140.

[0122] In some embodiments, referring to Figure 16 , the eccentric crankshaft 140 further includes a third groove 1426. The third groove 1426 is provided on the outer peripheral wall of the eccentric shaft section 142. The third groove 1426 surrounds the eccentric shaft section 142. The eccentric crankshaft 140 further includes a first channel 1428. The first channel 1428 is provided in the eccentric shaft section 142 and is configured to supply oil to the third groove 1426.

[0123] The third groove 1426 serves as an oil groove, adding a channel for the flow of lubricating oil, making the oil film state between the eccentric crankshaft 140 and the piston good, and avoiding the "seizing" phenomenon of the compressor caused by insufficient oil supply.

[0124] In some embodiments, referring to Figure 19 and Figure 20 , the eccentric shaft section 142 includes two sub-eccentric shaft sections 1421. The two sub-eccentric shaft sections 1421 are connected and symmetrically arranged on both sides in the height direction of the third groove 1426.

[0125] Referring to Figure 20 , the sub-eccentric shaft section 1421 includes a first wall 1422; the sub-eccentric shaft section 1421 further includes a second wall 1423. The second wall 1423 extends from the circumferential edge of the first wall 1422 in a direction away from the first wall 1422. The two first walls 1422 on the two sub-eccentric shaft sections 1421 are connected, for example, by welding, to achieve the fixed connection of the two sub-eccentric shaft sections 1421.

[0126] The sub-eccentric shaft section 1421 is composed of the first wall 1422 and the second wall 1423, which is a non-solid structure, with less material used and lower cost.

[0127] The sub-eccentric shaft section 1421 further includes a weight-reducing hole 1429. The sub-eccentric shaft section 1421 further includes a second opening 1424. The second opening 1424 is provided on the first wall 1422, and the second openings 1424 on the two sub-eccentric shaft sections 1421 communicate with each other to form the weight-reducing hole 1429.

[0128] The sub-eccentric shaft section 1421 further includes a fourth groove 1427. The fourth groove 1427 is provided on the first wall 1422, and the two fourth grooves 1427 on the two sub-eccentric shaft sections 1421 are butt-connected and communicated to form the first channel 1428.

[0129] The sub-eccentric shaft segment 1421 further includes a transition surface 1430. The transition surface 1430 is located at the position where the first wall 1422 meets the second wall 1423. For example, the transition surface 1430 is arc-shaped or the like. When the two sub-eccentric shaft segments 1421 are fixedly connected, the two transition surfaces 1430 enclose a third groove 1426 surrounding the eccentric shaft segment 142.

[0130] The sub-eccentric shaft segment 1421 further includes a third opening 1425. The third opening 1425 is provided on the first wall 1422, and the two third openings 1425 on the two sub-eccentric shaft segments 1421 are oppositely communicated, and the main shaft segment 141 passes through the two third openings 1425.

[0131] [Multi-connected air conditioner]

[0132] In some embodiments, referring to Figure 21 , the multi-connected air conditioner includes an outdoor unit 610 and a plurality of indoor units 620, and the outdoor unit 610 is connected to the plurality of indoor units 620. A compressor and a second gas-liquid separator 520 are provided in the indoor unit 620. The compressor is independent of the second gas-liquid separator 520. At this time, the compressor does not need to be configured with a first gas-liquid separator 510, the size of the compressor is reduced, and the cost is reduced on the premise of ensuring the refrigerant gas-liquid separation effect.

[0133] In some embodiments, referring to Figures 22 to 24 , the compressor is a twin-cylinder rotary compressor, and the compression mechanism 120 includes two cylinders, namely a first cylinder 1221 and a second cylinder 1222.

[0134] The compressor includes a suction pipeline 200, and the suction pipeline 200 is configured to supply the gaseous refrigerant of the second gas-liquid separator 520 into the compression chamber of the compression mechanism 120.

[0135] The second gas-liquid separator 520 includes a second outlet pipe 521. The suction pipeline 200 includes a first suction pipe 210, and the first suction pipe 210 is configured to communicate with the second outlet pipe 521 of the second gas-liquid separator 520.

[0136] The suction pipeline 200 includes two second suction pipes 220, and the two second suction pipes 220 are configured to communicate with the two cylinders respectively.

[0137] The suction pipeline 200 includes a tee 230, referring to Figure 25, the three-way joint 230 includes three connection ports, namely a first connection port 231 and two second connection ports 232. The first connection port 231 is in communication with the second connection ports 232, and the two second connection ports 232 are arranged side by side. When installing the three-way joint 230, the opening of the first connection port 231 faces upward to be connected to the first suction pipe 210, and the openings of the second connection ports 232 face downward to be connected to the second suction pipes 220. The two second connection ports 232 are respectively in communication with the two second suction pipes 220.

[0138] The first connection port 231 of the three-way joint 230 faces upward, and the second connection ports 232 face downward. 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 from top to bottom, and is distributed into the two cylinders through the two second suction pipes 220, improving the distribution uniformity of the refrigerant.

[0139] In some embodiments, the three-way joint 230 extends along the height direction of the first housing 110, and the range of the angle difference between the center line of the three-way joint 230 and the center line of the first housing 110 is [0°, 10°], which helps to improve the distribution uniformity of the refrigerant.

[0140] In some embodiments, the two second connection ports 232 are symmetrically arranged with respect to the axis of the first connection port 231, which helps to improve the distribution uniformity of the refrigerant.

[0141] In some embodiments, the inner diameter of the second suction pipe 220 is D5, and the range of the difference between the inner diameters of the two second suction pipes 220 is [0, 0.5D5], which helps to improve the distribution uniformity of the refrigerant.

[0142] In some embodiments, the inner diameter of the second suction pipe 220 is D5, and the inner diameter of the suction port of the cylinder is D6, 0.5 ≤ D5 / D6 ≤ 2, which helps to improve the distribution uniformity of the refrigerant.

[0143] In some embodiments, the inner diameter of the second suction pipe 220 is D5, and the inner diameter of the first suction pipe 210 is D7, 1 ≤ D7 / D5 ≤ 5, which helps to improve the distribution uniformity of the refrigerant.

[0144] In some embodiments, the three-way joint 230, the first suction pipe 210, and the second suction pipes 220 are fixed by welding. The depth of insertion of the first suction pipe 210 into the first connection port 231 and the depth of insertion of the second suction pipes 220 into the second connection ports 232 are d, 50 mm ≥ d ≥ 10 mm, which helps to improve the structural reliability.

[0145] In some embodiments, referring to Figure 23 , the compressor includes a vibration isolation part 400. An installation hole is provided on the vibration isolation part 400, and the first suction pipe 210 passes through the installation hole. The vibration isolation part 400 is, for example, a rubber pad.

[0146] Reference Figure 23 and Figure 26 The compressor includes a fixing portion 300 , which is fixedly connected to the first shell 110 , for example, by welding. The fixing portion 300 forms an accommodating space 330 , and the vibration isolation portion 400 is located in the accommodating space 330 .

[0147] On the one hand, the vibration isolation part 400 plays a role in vibration isolation and noise reduction; on the other hand, the fixing part 300 improves the stability of the first intake pipe 210.

[0148] In some embodiments, reference Figure 26 The fixing portion 300 includes a first sub-fixing portion 310 ; the fixing portion 300 also includes a second sub-fixing portion 320 .

[0149] The first sub-fixing portion 310 includes a connecting portion 311, and the first sub-fixing portion 310 also includes a first extending portion 312. One end of the connecting portion 311 is provided with the first extending portion 312. The first sub-fixing portion 310 also includes a second extending portion 313. The other opposite end of the connecting portion 311 is provided with the second extending portion 313. The connecting portion 311, the first extending portion 312 and the second extending portion 313 are an integral structure. The connecting portion 311 is fixedly connected to the first housing 110, for example, by welding.

[0150] The connecting portion 311 is arc-shaped to fit and be fixedly connected with the outer contour of the first housing 110. The first extension portion 312 extends toward the side of the connecting portion 311 away from the first housing 110. The second extension portion 313 includes two sub-extension portions, namely a first sub-extension portion 3131 and a second sub-extension portion 3132. The first sub-extension portion 3131 extends toward the side of the connecting portion 311 away from the housing, and the second sub-extension portion 3132 extends from the first sub-extension portion 3131 toward the side away from the first extension portion 312. For example, the second extension portion 313 is L-shaped.

[0151] One end of the second sub-fixing portion 320 is connected to the first extending portion 312 , and the other opposite end of the second sub-fixing portion 320 is connected to the second extending portion 313 , so as to limit the vibration isolation portion 400 in the accommodation space 330 .

[0152] For example, the first sub-fixing portion 310 further includes an opening 3121, the first extension portion 312 is provided with the opening 3121, the fixing portion 300 further includes a clamping portion 321, one end of the second sub-fixing portion 320 is provided with a clamping portion 321, such as a hook, and the clamping portion 321 is clamped with the opening 3121. The other end of the second sub-fixing portion 320 is fixed to the second sub-extension portion 3132 by a bolt.

[0153] The second sub-fixing portion 320 includes a second connecting section 322. The second connecting section 322 is arc-shaped and is adapted to the contour of the vibration isolation portion 400, improving the limiting effect on the vibration isolation portion 400.

[0154] In the description of the above embodiments, specific features, structures, materials, or characteristics may be combined in any one or more embodiments or examples in a suitable manner.

[0155] The above is only the specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed by the present invention should be covered within the protection scope of the present invention. Therefore, the protection scope of the present invention should be subject to the protection scope of the claims.

Claims

1. A compressor, characterized in that: include: A housing having a mounting cavity formed therein; A compression mechanism is disposed in the installation cavity, and the compression mechanism is configured to compress the refrigerant. The compression mechanism includes: Eccentric crankshaft; Bearings, including: a first shaft hole, through which the eccentric crankshaft passes; An oil groove, the oil groove is arranged on the hole wall of the first shaft hole, the oil groove includes a plurality of first sub-oil grooves and a plurality of second sub-oil grooves, the plurality of first sub-oil grooves and the plurality of second sub-oil grooves are alternately arranged along the axial direction of the first shaft hole, the adjacent first sub-oil grooves are connected to the second sub-oil grooves, the first sub-oil grooves extend along the axial direction of the first shaft hole, and the second sub-oil grooves extend in a circumferential spiral direction of the first shaft hole; The number of the first sub-oil tanks is N1, the number of the second sub-oil tanks is N2, and 3.5<N1 / N2<4.

6.

2. The compressor according to claim 1, characterized in that The groove depth of the oil groove is T, the hole diameter of the first shaft hole is D, and 0.15<T / D<0.

21.

3. The compressor according to claim 1, characterized in that The starting angle of the oil groove is θ1, the ending angle of the oil groove is θ2, the pitch of the second sub-oil groove is φ, and 1.6<θ1 / φ+θ2 / φ<2.

9.

4. The compressor according to claim 1, characterized in that The bearing comprises: an exhaust hole configured to exhaust the refrigerant in the compression mechanism; a first groove, arranged around the exhaust hole, an abutment portion being formed between the first groove and the exhaust hole, and the first groove being configured to store oil; The compression mechanism also includes an exhaust valve plate, a first end of which is fixedly disposed on the bearing, a second end of which is configured to close or open the exhaust hole, and the exhaust valve plate is configured to cover the first groove and abut against the abutment portion when closed.

5. The compressor according to claim 4, characterized in that The bearing further comprises at least one second groove configured to store oil; The exhaust valve sheet comprises a first connecting section connected between the first end and the second end. The exhaust valve sheet is configured such that when the exhaust valve sheet is closed, the first connecting section covers the second groove and the second end covers the first groove.

6. The compressor according to claim 5, characterized in that The bearing comprises: A first bearing portion is provided with the exhaust hole, the first groove and the second groove, and the first bearing portion is provided with a first opening; The second bearing part is fixedly arranged on the first bearing part. The first shaft hole is formed in the second bearing part. The first shaft hole is connected with the first opening. The eccentric crankshaft passes through the first shaft hole and the first opening.

7. The compressor according to claim 6, characterized in that The bearing includes a plurality of reinforcement parts, the plurality of reinforcement parts are arranged at intervals along the circumference of the second bearing part, and the plurality of reinforcement parts are connected to the first bearing part.

8. The compressor according to any one of claims 1 to 7, characterized in that The eccentric crankshaft comprises: A main shaft section, wherein a shaft hole is formed inside the main shaft section; An eccentric shaft segment is fixedly sleeved on the main shaft segment, a third groove is arranged on the outer peripheral wall of the eccentric shaft segment, the third groove surrounds the eccentric shaft segment, a first channel is arranged in the eccentric shaft segment, and the first channel is configured to supply oil to the third groove.

9. The compressor according to claim 8, characterized in that The eccentric shaft segment includes two sub-eccentric shaft segments, and the two sub-eccentric shaft segments are connected and symmetrically arranged on both sides of the height direction of the third slot; The sub-eccentric shaft segment comprises a first wall and a second wall, wherein the second wall extends from a circumferential edge of the first wall in a direction away from the first wall, and the two first walls of the two sub-eccentric shaft segments are connected; A second opening is provided on the first wall, and the second openings of the two sub-eccentric shaft segments are connected; A fourth groove is arranged on the first wall, and the two fourth grooves on the two sub-eccentric shaft segments are butt-jointed and connected to form the first channel.

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

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