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 bearing part and a second bearing part, a sixth groove is formed in the first bearing part, and the second bearing part is connected with the first bearing part; the second bearing part extends towards one side of the first bearing, a first shaft hole is formed in the second bearing part, and the eccentric crankshaft surrounds the first shaft hole through the first shaft hole and the sixth groove. The height of the sixth groove in the axial direction of the first shaft hole is H1, the height of the bearing in the axial direction of the first shaft hole is H2, and H1 / H2 is larger than 0.12 and smaller than 0.25. The inner diameter of the sixth groove is D2, the extension size of the first bearing part in the direction perpendicular to the second bearing part is D3, and D2 / D3 is larger than 0.1 and smaller than 0.24. The contact surface pressure height between the bearing and the eccentric crankshaft can be increased, the friction noise of the compressor is 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 in particular to a compressor and an air conditioner. Background Art

[0002] The air conditioner includes an outdoor unit and an indoor unit, and the outdoor unit is connected to the indoor unit. The air conditioner performs the cooling and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve and an evaporator. The compressor is fixedly arranged in the outdoor unit. A compression mechanism is arranged in the inner cavity of the rolling rotor compressor, and the compression mechanism is configured to compress the refrigerant. Its working principle is as follows: the motor stator generates a magnetic pull after being energized, and the motor rotor rotates under the action of the magnetic pull of the stator, and drives the eccentric crankshaft of the compression mechanism to rotate together. The rotation of the eccentric crankshaft drives the piston sleeved on its eccentric shaft section to make an eccentric circular motion in the cylinder. The vane is installed in the vane groove of the cylinder. Under the action of the compression spring in the spring hole, the piston is always supported, so that it reciprocates in the vane groove. The vane and the piston divide the cylinder into a high-pressure chamber and a low-pressure chamber. The eccentric crankshaft drives the piston to rotate one circle, and then the low-pressure chamber is sucked in and the high-pressure chamber is exhausted, thereby completing one exhaust, thereby realizing the compression of the gas by the compressor.

[0003] The bearing sleeve is arranged on the eccentric crankshaft. The contact surface pressure height between the bearing and the eccentric crankshaft is small, which is not conducive to the formation of an oil film between the two. The friction between the two is large, which increases the friction noise of the compressor and reduces the performance of the compressor.

[0004] The above information disclosed in the background technology is only used to increase the understanding of the background technology of the present application, and therefore, it may include information that does not constitute the prior art known to ordinary technicians in the field. Summary of the invention

[0005] In view of the problems pointed out in the background technology, the present disclosure provides a compressor and an air conditioner, which increase the contact surface pressure height between the bearing and the eccentric crankshaft, reduce the friction noise of the compressor, and improve the performance of the compressor.

[0006] On the one hand, a compressor is provided, the compressor includes a shell, a receiving cavity is formed in the shell, a compression mechanism is arranged in the receiving cavity, the compression mechanism includes an eccentric crankshaft and a bearing, the bearing includes a first bearing part and a second bearing part, a sixth groove is arranged on the first bearing part, the second bearing part is connected to the first bearing part, the second bearing part extends to one side of the first bearing, a first shaft hole is formed in the second bearing part, the eccentric crankshaft passes through the first shaft hole, and the sixth groove surrounds the first shaft hole. The height of the sixth groove along the axial direction of the first shaft hole is H1, the height of the bearing along the axial direction of the first shaft hole is H2, 0.12<

[0007] H1 / H2<0.25. The inner diameter of the sixth groove is D2, the extension dimension of the first bearing portion perpendicular to the second bearing portion is D3, and 0.1<D2 / D3<0.24.

[0008] Within the above parameter range, the contact surface pressure height between the eccentric crankshaft and the bearing is large, which is conducive to the formation of an oil film between the two, and the friction between the two is small, thereby reducing the friction noise of the compressor and improving the performance of the compressor.

[0009] On the other hand, an air conditioner is provided, comprising a compressor, an evaporator, a condenser and a throttling device, wherein the compressor is the compressor as described above.

[0010] After reading the specific embodiments of the present invention in conjunction with the accompanying drawings, other features and advantages of the present invention will become more clear. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0012] Figure 1 is a structural diagram of a compressor according to some embodiments;

[0013] Figure 2 is a cross-sectional view of a compressor according to some embodiments;

[0014] Figure 3 is a structural diagram of a bearing according to some embodiments;

[0015] Figure 4 is an exploded view of a bearing according to some embodiments;

[0016] Figure 5 is a cross-sectional view of a bearing according to some embodiments;

[0017] Figure 6 is a structural diagram of a first bearing portion according to some embodiments;

[0018] Figure 7 is a structural diagram of a bearing bush according to some embodiments;

[0019] Figure 8 is another cross-sectional view of a bearing according to some embodiments;

[0020] Fig. 9is a relationship diagram of θ1 / φ+θ2 / φ, compressor oil pool height / installation cavity height, and oil discharge rate according to some embodiments;

[0021] Fig.10 is a relationship diagram of N1 / N2, compressor oil pool height / installation cavity height, and oil discharge rate according to some embodiments;

[0022] Fig.11 is a relationship diagram of T / D, compressor oil pool height / installation cavity height, and oil discharge rate according to some embodiments;

[0023] Fig.12 is a graph showing the relationship between D1 / D2 and contact surface pressure height according to some embodiments;

[0024] Fig.13 is a graph showing the relationship between H1 / H2 and contact surface pressure height according to some embodiments;

[0025] Fig.14 is a graph showing the relationship between D2 / D3 and contact surface pressure height according to some embodiments;

[0026] Fig.15 is a graph showing the relationship between (T1+T2) / D4 and contact surface pressure height according to some embodiments;

[0027] Fig.16 is a structural diagram of an eccentric crankshaft according to some embodiments;

[0028] Fig.17 is an exploded view of an eccentric crankshaft according to some embodiments;

[0029] Fig.18 is a cross-sectional view of an eccentric crankshaft according to some embodiments;

[0030] Fig.19 is a structural diagram of an eccentric shaft segment according to some embodiments;

[0031] Fig. 20 is an exploded view of an eccentric shaft segment according to some embodiments;

[0032] Fig.21 is a schematic diagram of a multi-link according to some embodiments;

[0033] Fig. 22 is a structural diagram of a compressor and a gas-liquid separator according to some embodiments;

[0034] Fig.23 is another structural diagram of a compressor according to some embodiments;

[0035] Fig.24 is another cross-sectional view of a compressor according to some embodiments;

[0036] Fig.25 is a structural diagram of a tee according to some embodiments;

[0037] Fig.26 is a structural diagram of a fixing portion according to some embodiments. DETAILED DESCRIPTION

[0038] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0039] In the description of the present application, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0040] The terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of this application, unless otherwise specified, "plurality" means two or more.

[0041] In the description of this application, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0042] In the present utility model, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0043] The disclosure below provides many different embodiments or examples for realizing different structures of the utility model. In order to simplify the disclosure of the utility model, the components and settings of specific examples are described below. Of course, they are merely examples, and the purpose is not to limit the utility model. In addition, the utility model may repeat reference numbers and / or reference letters in different examples, and 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 utility model provides various specific examples of processes and materials, but those of ordinary skill in the art may be aware of the application of other processes and / or the use of other materials.

[0044] [Air conditioner]

[0045] 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 the indoor space.

[0046] The low-temperature, low-pressure refrigerant enters the compressor, which compresses the low-temperature, low-pressure refrigerant into a high-temperature, high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed gas refrigerant into a liquid refrigerant and releases the heat of the refrigerant to the surrounding environment through the condensation process.

[0047] The expansion valve expands the high-temperature and high-pressure liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the low-temperature and low-pressure refrigerant gas to the compressor. The evaporator can achieve a cooling effect by utilizing 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.

[0048] The outdoor unit of the air conditioner includes a compressor and an outdoor heat exchanger, the indoor unit of the air conditioner includes an indoor heat exchanger, and the expansion valve may be provided in the indoor unit or the outdoor unit.

[0049] The indoor heat exchanger and the outdoor heat exchanger function as a condenser or an evaporator. When the indoor heat exchanger functions as a condenser, the air conditioner performs a heating mode; when the indoor heat exchanger functions as an evaporator, the air conditioner performs a cooling mode.

[0050] The outdoor unit further includes a four-way valve configured to switch the indoor heat exchanger and the outdoor heat exchanger to function as a condenser or an evaporator.

[0051] The refrigeration working principle of the air conditioner is: the operation of the compressor makes the indoor heat exchanger (in the indoor unit, this is the evaporator) in an ultra-low pressure state, the liquid refrigerant in the indoor heat exchanger evaporates rapidly to absorb heat, and the wind blown out by the indoor fan is cooled by the indoor heat exchanger coil and becomes cold air blown into the room. The evaporated refrigerant is pressurized by the compressor and condensed into liquid under the high-pressure environment of the outdoor heat exchanger (in the outdoor component, this is the condenser), releasing heat, and dissipating the heat into the atmosphere through the outdoor fan. This cycle achieves a cooling effect.

[0052] 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 (the condenser at this time), condenses and liquefies to release heat, becomes a liquid, and heats the indoor air, thereby achieving the purpose of increasing the indoor temperature. The liquid refrigerant is decompressed by the throttling device and enters the outdoor heat exchanger (the evaporator at this time), evaporates and absorbs heat to become a gas, and absorbs the heat of the outdoor air (the outdoor air temperature decreases), becoming a gaseous refrigerant, and the gaseous refrigerant enters the compressor again to start the next cycle.

[0053] [Compressor body]

[0054] In some embodiments of the present disclosure, the compressor is a rolling rotor compressor. Figure 1 and Figure 2 The compressor includes a compressor body 100. The compressor body 100 includes a first shell 110. The compressor body 100 also includes a receiving chamber 111. A closed receiving chamber 111 is formed in the first shell 110. The compressor body 100 also includes a compression mechanism 120. The compression mechanism 120 is disposed in the receiving chamber 111. The compression mechanism 120 is configured to compress the refrigerant. The compressor body 100 also includes a motor 130, which is disposed in the receiving chamber 111. The motor 130 is disposed above the compression mechanism 120. The motor 130 is configured to provide power for the compression mechanism 120.

[0055] In some embodiments, the motor 130 includes a rotor 132. The motor 130 also includes a stator 131, which is fixedly connected to the inner wall of the first housing 110 to achieve fixed installation of the motor 130 in the accommodating cavity 11.

[0056] In some embodiments, reference Figure 2 The compression mechanism 120 further includes an eccentric crankshaft 140 .

[0057] The eccentric crankshaft 140 includes a main shaft section 141 ; the eccentric crankshaft 140 also includes an eccentric shaft section 142 . The main shaft section 141 is fixedly connected to the rotor 132 .

[0058] Reference Figure 2 , the compression mechanism 120 further includes a cylinder 122; the compression mechanism 120 further includes a piston 123. A piston 123 is provided in the compression chamber 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 is connected to the compression chamber; the compression mechanism 120 further includes a vane groove; the vane groove is provided in the cylinder 122. The compression mechanism 120 further includes a vane. The vane is provided in the vane groove. The eccentric crankshaft 121 drives the piston 123 to make circumferential motion in the compression chamber, and the vane reciprocates along the vane groove, and the vane always abuts against the piston 123. The compression chamber includes a first sub-compression chamber (high-pressure chamber); the compression chamber also includes a second sub-compression chamber (low-pressure chamber). The pressure in the first sub-compression chamber is greater than the pressure in the second sub-compression chamber. The slide and the piston 123 separate the compression chamber into the first sub-compression chamber and the second sub-compression chamber. The compression mechanism 120 also includes at least one muffler 704. For example, the at least one muffler 704 includes two mufflers 704, namely a first muffler 1261 and a second muffler 1262. The first muffler 1261 is arranged on the first bearing 1241, and the second muffler 1262 is arranged on the second bearing 1242.

[0059] The working principle of the compressor is as follows: the stator 131 of the motor 130 generates a magnetic pull after being energized, and the rotor 132 of the motor 130 performs a rotational motion under the action of the magnetic pull of the stator 131, and drives the eccentric crankshaft 140 to perform a rotational motion together, and the rotation of the eccentric crankshaft 140 drives the piston 123 mounted on the eccentric shaft segment to perform an eccentric circular motion in the compression chamber of the cylinder 122, and the vane performs a reciprocating motion in the vane groove, and the vane and the piston 123 divide the compression chamber of the cylinder 122 into a first sub-compression chamber and a second sub-compression chamber, and the eccentric crankshaft 140 drives the piston 123 to rotate one circle, and then air is sucked from the second sub-compression chamber and exhausted from the first sub-compression chamber to complete one exhaust, thereby realizing the compression of the gas by the compressor, and the compressed gas is discharged through the exhaust hole.

[0060] In one embodiment of the present disclosure, referring to Figure 2 The compressor is a single-cylinder rolling rotor compressor.

[0061] In some embodiments of the present disclosure, referring to Fig.24 The compressor is a double-cylinder rolling rotor compressor, and the compression mechanism 120 includes an eccentric crankshaft 140. The compression mechanism 120 also includes two cylinders 701, namely a first cylinder 1221 and a second cylinder 1222. The compression mechanism 120 also includes two bearings 703, namely a first bearing 1241 and a second bearing 1242. The compression mechanism 120 also includes two pistons 702, namely a first piston 1231 and a second piston 1232. The compression mechanism 120 also includes a middle partition 125. The compression mechanism 120 also includes two mufflers 704, namely a first muffler 1261 and a second muffler 1262.

[0062] [First gas-liquid separator]

[0063] In some embodiments, reference 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 provide gaseous refrigerant to the compression chamber of the compression mechanism 120. The first gas-liquid separator 510 separates the liquid refrigerant from the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 100 and causing the compressor to malfunction.

[0064] In some embodiments, reference Figure 1 The first gas-liquid separator 510 includes a second shell 512; the first gas-liquid separator 510 also includes a first gas outlet pipe 511, which is arranged at the bottom of the second shell 512. The first end of the first gas outlet pipe 511 extends into the inner cavity of the second shell 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 air intake port of the cylinder to provide gaseous refrigerant to the compression mechanism 120.

[0065] [Bearings]

[0066] In some embodiments, reference Figure 3 and Figure 6 The bearing 150 includes an exhaust hole 1511 , which is communicated with the inner cavity of the cylinder 122 , and the exhaust hole 1511 is configured to exhaust the refrigerant in the cylinder 122 .

[0067] Reference Figure 2 , Figure 4 as well as 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 toward a 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 toward a direction away from the exhaust hole 1511, the exhaust hole 1511 is opened.

[0068] Reference Figure 4 The exhaust valve plate 170 includes a first end 171 ; the exhaust valve plate 170 also includes a second end 172 ; the exhaust valve plate 170 also includes a first connecting section 173 . The first connecting section 173 is connected between the first end 171 and the second end 172 .

[0069] Reference 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 provided in the bearing 150. For example, referring to Figure 4 and Figure 6 The first end 171 of the exhaust valve plate 170 is fixedly mounted to the mounting hole 1516 by a bolt 190. The second end 172 of the exhaust valve plate 170 is configured to close or open the exhaust hole 1511.

[0070] The compression mechanism 120 further includes a lift limiter 180 , which is configured to limit an opening stroke of the exhaust valve plate 170 .

[0071] In some disclosed compressors, the exhaust valve plate 170 generates noise of hitting the bearing 150 during movement, which increases the working noise of the compressor, and the exhaust valve plate 170 has a large opening resistance.

[0072] In order to solve this technical problem, in some embodiments, referring to Figure 3 and Figure 6The bearing 150 further includes a first groove 1512. The first groove 1512 is arranged around the exhaust hole 1511. The bearing 150 further includes an abutment portion 1515. The abutment portion 1515 is formed between the first groove 1512 and the exhaust hole 1511. The abutment portion 1515 is located between the first groove 1512 and the exhaust hole 1511, and the first groove 1512 is configured to store oil.

[0073] The bearing 150 further includes at least one second groove 1513 configured to store oil. When the compressor is running, the oil in the oil pool 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.

[0074] 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 abutment portion 1515 .

[0075] When the exhaust valve plate 170 is closed, the exhaust valve plate 170 covers the first groove 1512 and abuts against the abutment 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 .

[0076] 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.

[0077] The narrow width of the abutting portion 1515 reduces 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 .

[0078] When the exhaust valve plate 170 is closed, the exhaust valve plate 170 covers the second groove 1513, and the second groove 1513 is filled with oil. The second groove 1513 plays a shock-absorbing role, which can reduce the impact sound of the exhaust valve plate 170 hitting the bearing 150 when the exhaust valve plate 170 is closed, thereby reducing the working noise of the compressor.

[0079] In some embodiments, reference Figure 6 The 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 exhaust valve plate 170 on the impact sound.

[0080] 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 .

[0081] Most of the impact sound of the exhaust valve plate 170 is generated by the first connecting section 173 hitting the bearing 150. The compressor in some embodiments of the present disclosure 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.

[0082] 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 compressor disclosed herein, 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 abutment portion 1515, thereby improving the sealing effect of the exhaust hole 1511.

[0083] In some embodiments, reference Figure 4 and Figure 6 The bearing 150 further includes a first bearing portion 151. The first bearing portion 151 is provided with an exhaust hole 1511, a first groove 1512, at least one second groove 1513 and a mounting hole 1516. The bearing 150 further includes a first opening 1514. The first bearing portion 151 is provided with a first opening 1514.

[0084] Reference Figure 4 The bearing 150 further includes a second bearing portion 152. The second bearing portion 152 is fixedly disposed on the first bearing portion 151. The second bearing portion 152 is fixedly disposed 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 is communicated with the first opening 1514. The main shaft section 141 of the eccentric crankshaft 140 is installed with the bearing 150 via the first shaft hole 1522 and the first opening 1514.

[0085] The bearing 150 in some embodiments of the present disclosure includes a two-part structure (a first bearing part 151 and a second bearing part 152 ) to facilitate processing and manufacturing.

[0086] The bearing 150 is usually a casting with a low elastic modulus, and the wear between the bearing 150 and the eccentric crankshaft 140 is large. The processing of the bearing 150 includes casting, rough machining, fine machining, phosphating, brushing, etc. The processing is complicated and costly. Casting, phosphating and other processing processes consume fossil fuels and pollute the environment.

[0087] In order to solve this technical problem, in some embodiments, the first bearing part 151 is configured as a sheet metal stamping part. The second bearing part 152 is configured as a metal tube, and a first shaft hole 1522 is formed in the metal tube. The first bearing part 151 and the second bearing part 152 are welded and fixed.

[0088] The bearing 150 in some embodiments of the present disclosure has low cost and a simplified processing process, including stamping, finishing, and welding, which can reduce pollution to the environment.

[0089] The bearing 150 in some embodiments of the present disclosure is made of sheet metal stampings and metal pipes. 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.

[0090] In some embodiments, reference Figure 3 and Figure 4 The bearing 150 further includes a plurality of reinforcing portions 153 , which are arranged at intervals along the circumference of the second bearing portion 152 , and are connected to the first bearing portion 151 , thereby improving the structural reliability of the first bearing portion 151 and the second bearing portion 152 .

[0091] The reinforcement portion 153 is a rib structure, and the reinforcement portion 153 is welded to the first bearing portion 151 and the second bearing portion 152 respectively.

[0092] In the compressor disclosed in some embodiments, reference is made to Figure 8 , the bearing 150 also includes an oil groove 154. The inner wall of the shaft hole (first shaft hole 1522) of the bearing 150 is provided with an oil groove 154. The oil groove 154 is usually an isotropic curve rise or a straight line rise. When the compressor is running 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 is running at a high frequency, the excess oil supply is discharged through the oil groove 154, the oil discharge rate of the compressor is increased, and the performance of the compressor is reduced.

[0093] 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.

[0094] The oil groove 154 includes a plurality of first sub-oil grooves 1541; the oil groove 154 also 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 adjacent first sub-oil grooves 1541 and second sub-oil grooves 1542 are connected. The first sub-oil groove 1541 extends along the axial direction of the first shaft hole 1522, and the first sub-oil groove 1541 is a linear groove. The second sub-oil groove 1542 extends spirally along the circumference of the first shaft hole 1522, and the second sub-oil groove 1542 is a spiral groove.

[0095] For example, refer to Figure 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 .

[0096] The oil groove 154 in some embodiments of the present disclosure is a composite oil groove composed of a linear first sub-oil groove 1541 and a spiral second sub-oil groove 1542. On the one hand, when the compressor is running at a low frequency, the oil groove 154 can reliably transport oil to the friction pair to avoid oil-free lubrication friction of the friction pair components (such as the eccentric crankshaft 140 and the bearing 150); on the other hand, when the compressor is running at a high frequency, excessive oil supply is avoided to reduce the oil discharge rate; on the third hand, reasonable oil supply can effectively reduce the friction noise of the compressor, thereby reducing the vibration and noise of the compressor.

[0097] In some embodiments, the oil tank 154 includes N1 first sub-oil tanks 1541, and the oil tank 154 includes N2 second sub-oil tanks 1542, 3.5<N1 / N2<4.6, within this range, the ratio of the compressor oil pool height / installation cavity height is reasonable and the oil discharge rate of the compressor is good. Fig.10 It is a relationship diagram of N1 / N2, compressor oil pool height / installation cavity height, and 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 compressor oil pool height / installation cavity height.

[0098] In some embodiments, the depth of the oil groove 154 is T. Figure 8 The groove depth T is the opening depth of the oil groove 154 along the height H2 direction perpendicular to the first axial hole 1522. The aperture of the first axial hole 1522 is D, 0.15<T / D<0.21. Within this range, the ratio of the compressor oil pool height / installation cavity height is reasonable and the oil discharge rate of the compressor is good. Fig.11 It is a relationship diagram between T / D, compressor oil pool height / installation cavity height, and 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 compressor oil pool height / installation cavity height.

[0099] In some embodiments, the starting angle of the oil groove 154 is θ1, the ending angle of the oil groove 154 is θ2, the pitch of the second sub-oil groove 1542 is φ, 1.6<θ1 / φ+θ2 / φ<2.9, and within this range, the ratio of the compressor oil pool height / installation cavity height is reasonable and the oil discharge rate of the compressor is better. Fig. 9 It is a relationship diagram of θ1 / φ+θ2 / φ, compressor oil pool height / installation cavity height, and 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 compressor oil pool height / installation cavity height.

[0100] In the compressor 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 the formation of an oil film between the two, and the friction between the two is large, thereby increasing the friction noise of the compressor and reducing the performance of the compressor. Among them, under the combined load of gas load, centrifugal force, electromagnetic force, etc., 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.

[0101] In order 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 first bearing portion 151 is provided with the sixth groove 1517 .

[0102] 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 to one side of the first bearing portion 151. For example, the first bearing portion 151 and the second bearing portion 152 are an integral structure. For another example, the first bearing portion 151 and the second bearing portion 152 are split structures, and the two are welded and fixed.

[0103] A first shaft hole 1522 is formed in the second bearing portion 152 . The eccentric crankshaft 140 passes through the first shaft hole 1522 . The sixth groove 1517 surrounds the first shaft hole 1522 .

[0104] The axial height of the sixth groove 1517 along the first shaft hole 1522 is H1, and the axial height of the bearing 150 along the first shaft hole 1522 is H2, 0.12 Fig.13 Shown is a graph showing the relationship between H1 / H2 and contact surface pressure height.

[0105] In some embodiments, reference Figure 8 The inner diameter of the sixth groove 1517 is D2, the extension dimension of the first bearing portion 151 perpendicular to the second bearing portion 152 is D3, 0.1<D2 / D3<0.24, within this range, the contact surface pressure height between the eccentric crankshaft 140 and the bearing 150 is large, which is conducive to the formation of an oil film between the two, and the friction between the two is small, thereby reducing the friction noise of the compressor and improving the performance of the compressor. Fig.14 The figure shows the relationship between D2 / D3 and the contact surface pressure height.

[0106] In some embodiments, reference 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, and the friction between the two is small, thereby reducing the friction noise of the compressor and improving the performance of the compressor. Fig.12 The figure shows the relationship between D1 / D2 and the contact surface pressure height.

[0107] In some embodiments, reference Figure 8 The outer diameter of the sixth groove is D1, the inner diameter of the sixth groove 1517 is D2, T1=D1-D2, the second bearing portion 152 includes a journal 1521, and the extension dimension of the journal 1521 perpendicular to the second bearing portion 152 is T2. 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 the formation of an oil film between the two, and the friction between the two is small, thereby reducing the friction noise of the compressor and improving the performance of the compressor. Fig.15 The figure shows the relationship between (T1+T2) / D4 and the contact surface pressure height.

[0108] [bush]

[0109] In some disclosed compressors, the bearing 150 is usually sleeved on the outside of the eccentric crankshaft 140. The sleeve 144 and the eccentric crankshaft 140 are greatly worn, which increases the friction noise of the compressor and reduces the performance of the compressor.

[0110] In order to solve this technical problem, in some embodiments, referring to Figure 4 , Figure 5 as well as Figure 7 The compression mechanism 120 includes two bearing bushes 160 . The bearing bushes 160 are disposed in the first shaft hole 1522 , for example, the bearing bushes 160 are interference fitted into the first shaft hole 1522 .

[0111] Two bearing bushes 160 are arranged at intervals along the axial direction of the first shaft hole 1522. The bearing bush 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 bushes 160, and the gap 163 is an annular groove surrounding the second shaft hole 161. The bearing bush 160 also includes a fifth groove 162. The fifth groove 162 is arranged on the inner peripheral wall of the bearing bush 160, and the fifth groove 162 is connected to the gap 163.

[0112] The gap 163 between the two bearing shells 160 and the fifth groove 162 function as an oil groove, thereby improving the wear resistance between the eccentric crankshaft 140 and the bearing shell 160, reducing the friction noise of the compressor, and improving the performance of the compressor.

[0113] In some embodiments, reference Figure 7 The fifth groove 162 extends in a circumferential spiral 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 .

[0114] In some embodiments, reference Figure 5 , the two fifth grooves 162 of the two bearing shells 160, namely the fifth groove 162A and the fifth groove 162B, are located on the same spiral track. For example, when oil flows from bottom to top through the second shaft hole 161, 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 located on the same spiral track, which is convenient for oiling, ensuring that the contact parts of the eccentric crankshaft 140 and the bearing 150 can be effectively lubricated to reduce friction.

[0115] [Eccentric crankshaft]

[0116] In some disclosed compressors, the eccentric crankshaft 140 is usually a casting, with a low elastic modulus, and the wear between the bearing 150 and the eccentric crankshaft 140 is large. The processing of the bearing 150 includes casting, rough machining, fine machining, phosphating, brushing, etc. The processing is complicated and costly. Casting, phosphating and other processing processes consume fossil fuels and pollute the environment.

[0117] In order 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 also includes a third shaft hole 1411. The third shaft hole 1411 is formed inside the main shaft section 141. The eccentric crankshaft 140 also includes a blade 143. The blade 143 is arranged in the third shaft hole 1411. The eccentric crankshaft 140 also includes a shaft plug 145; the eccentric crankshaft 140 also includes a shaft sleeve 144. The shaft plug 145 is arranged at one end of the third shaft hole 1411, and the shaft sleeve 144 is arranged at the other end opposite to the third shaft hole 1411.

[0118] The main shaft section 141 is made of a metal tube, such as a steel tube, and a third shaft hole 1411 is formed in the metal tube.

[0119] The eccentric crankshaft 140 further includes a plurality of oil holes 1412. The main shaft section 141 is provided with a plurality of oil holes 1412 so as to provide oil lubrication for each friction pair on which the eccentric crankshaft 140 is installed.

[0120] 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 and the main shaft section 141 are welded and fixed.

[0121] The eccentric crankshaft 140 in some embodiments of the present disclosure has low cost and a simplified processing process, including stamping, finishing, and welding, which can reduce pollution to the environment.

[0122] The eccentric crankshaft 140 in some embodiments of the present disclosure is made of sheet metal stampings and metal pipes. The material is steel with a large elastic modulus, which reduces the friction between the bearing 150 and the eccentric crankshaft 140.

[0123] In some embodiments, reference Fig.16 The eccentric crankshaft 140 further includes a third groove 1426. The third groove 1426 is disposed on the outer peripheral wall of the eccentric shaft segment 142, and the third groove 1426 surrounds the eccentric shaft segment 142. The eccentric crankshaft 140 further includes a first channel 1428. The first channel 1428 is disposed in the eccentric shaft segment 142, and the first channel 1428 is configured to supply oil to the third groove 1426.

[0124] The third groove 1426 serves as an oil groove, which adds a channel for the flow of lubricating oil, so that the oil film between the eccentric crankshaft 140 and the piston is in a good state, thereby avoiding the compressor "seizing" phenomenon caused by insufficient oil supply.

[0125] In some embodiments, reference Fig.19 and Fig. 20 The eccentric shaft segment 142 includes two sub-eccentric shaft segments 1421, and the two sub-eccentric shaft segments 1421 are connected and symmetrically arranged on both sides of the third groove 1426 in the height direction.

[0126] Reference Fig. 20 The sub-eccentric shaft segment 1421 includes a first wall 1422; the sub-eccentric shaft segment 1421 also 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, and the two first walls 1422 on the two sub-eccentric shaft segments 1421 are connected, for example, by welding, to achieve a fixed connection between the two sub-eccentric shaft segments 1421.

[0127] The sub-eccentric shaft segment 1421 is composed of a first wall 1422 and a second wall 1423, and has a non-solid structure, requires less material, and has low cost.

[0128] The sub-eccentric shaft segment 1421 further includes a weight-reducing hole 1429. The sub-eccentric shaft segment 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 segments 1421 are connected to form a weight-reducing hole 1429.

[0129] The sub-eccentric shaft segment 1421 further includes a fourth groove 1427. The first wall 1422 is provided with the fourth groove 1427, and the two fourth grooves 1427 on the two sub-eccentric shaft segments 1421 are connected to form a first channel 1428.

[0130] The sub-eccentric shaft segment 1421 further includes a transition surface 1430. The position where the first wall 1422 and the second wall 1423 meet is the transition surface 1430, for example, the transition surface 1430 is arc-shaped, etc. When the two sub-eccentric shaft segments 1421 are fixedly connected, the two transition surfaces 1430 form a third groove 1426 surrounding the eccentric shaft segment 142.

[0131] The sub-eccentric shaft segment 1421 further includes a third opening 1425. The first wall 1422 is provided with the third opening 1425, and the two third openings 1425 on the two sub-eccentric shaft segments 1421 are oppositely connected, and the main shaft segment 141 is connected via the two third openings 1425.

[0132] [Multi-link]

[0133] In some embodiments, reference Fig.21 The multi-split system 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. In this case, the compressor does not need to be equipped with the first gas-liquid separator 510, which reduces the size of the compressor and reduces the cost while ensuring the gas-liquid separation effect of the refrigerant.

[0134] In some embodiments, reference Figure 22 to Figure 24 The compressor is a twin-cylinder rotor compressor, and the compression mechanism 120 includes two cylinders, namely a first cylinder 1221 and a second cylinder 1222.

[0135] The compressor includes a suction line 200 configured to supply the gaseous refrigerant of the second gas-liquid separator 520 into the compression chamber of the compression mechanism 120 .

[0136] The second gas-liquid separator 520 includes a second gas outlet pipe 521 . The air intake line 200 includes a first air intake pipe 210 , and the first air intake pipe 210 is configured to communicate with the second gas outlet pipe 521 of the second gas-liquid separator 520 .

[0137] The intake line 200 includes two second intake pipes 220 , and the two second intake pipes 220 are configured to communicate with two cylinders respectively.

[0138] The air intake line 200 includes a tee 230, see Fig.25The tee 230 includes three connection ports, namely a first connection port 231 and two second connection ports 232. The first connection port 231 is connected to the second connection port 232, and the two second connection ports 232 are arranged side by side. When the tee 230 is installed, the opening of the first connection port 231 faces upward to connect with the first air intake pipe 210, and the opening of the second connection port 232 faces downward to connect with the second air intake pipe 220, and the two second connection ports 232 are connected to the two second air intake pipes 220 respectively.

[0139] The first connection port 231 of the tee 230 faces upward, and the second connection port 232 faces downward. The gaseous refrigerant flowing out of the second gas-liquid separator 520 flows from top to bottom through the first intake pipe 210 and the two second intake pipes 220, and is distributed into the two cylinders through the two second intake pipes 220, thereby improving the uniformity of the refrigerant distribution.

[0140] In some embodiments, the tee 230 is extended along the height direction of the first shell 110, and the angle difference between the center line of the tee 230 and the center line of the first shell 110 is in the range of [0°, 10°], which helps to improve the uniformity of refrigerant distribution.

[0141] 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 uniformity of refrigerant distribution.

[0142] In some embodiments, the inner diameter of the second air intake pipe 220 is D5, and the difference between the inner diameters of the two second air intake pipes 220 is in the range of [0, 0.5D5], which helps to improve the uniformity of refrigerant distribution.

[0143] In some embodiments, the inner diameter of the second air intake pipe 220 is D5, the inner diameter of the air intake port of the cylinder is D6, and 0.5≤D5 / D6≤2, which helps to improve the uniformity of refrigerant distribution.

[0144] In some embodiments, the inner diameter of the second air intake pipe 220 is D5, the inner diameter of the first air intake pipe 210 is D7, and 1≤D7 / D5≤5, which helps to improve the uniformity of refrigerant distribution.

[0145] In some embodiments, the tee 230, the first air intake pipe 210, and the second air intake pipe 220 are welded and fixed, and the depth of the first air intake pipe 210 inserted into the first connecting port 231 and the depth of the second air intake pipe 220 inserted into the second connecting port 232 are d, 50mm≥d≥10mm, which helps to improve structural reliability.

[0146] In some embodiments, reference Fig.23 The compressor includes a vibration isolation part 400, and a mounting hole is provided on the vibration isolation part 400, and the first air intake pipe 210 passes through the mounting hole. The vibration isolation part 400 is, for example, a rubber pad.

[0147] Reference Fig.23 and Fig.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 .

[0148] 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.

[0149] In some embodiments, reference Fig.26 The fixing portion 300 includes a first sub-fixing portion 310 ; the fixing portion 300 also includes a second sub-fixing portion 320 .

[0150] 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.

[0151] 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.

[0152] 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 .

[0153] 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.

[0154] The second sub-fixing portion 320 includes a second connecting segment 322 . The second connecting segment 322 is arc-shaped. The second connecting segment 322 is adapted to the contour of the vibration isolation portion 400 , thereby improving the limiting effect on the vibration isolation portion 400 .

[0155] In the description of the above embodiments, specific features, structures, materials or characteristics may be combined in a suitable manner in any one or more embodiments or examples.

[0156] The above is only a specific implementation of the utility model, but the protection scope of the utility model is not limited to this. Any changes or substitutions that can be easily thought of by technicians familiar with the technical field within the technical scope disclosed by the utility model should be included in the protection scope of the utility model. Therefore, the protection scope of the utility model should be based on 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 bearing portion, wherein a sixth groove is provided on the first bearing portion; a second bearing portion connected to the first bearing portion, the second bearing portion extending toward one side of the first bearing, a first shaft hole formed in the second bearing portion, the eccentric crankshaft passing through the first shaft hole, and the sixth groove surrounding the first shaft hole; The height of the sixth groove along the axial direction of the first shaft hole is H1, the height of the bearing along the axial direction of the first shaft hole is H2, and 0.12<H1 / H2<0.25; The inner diameter of the sixth groove is D2, the extension dimension of the first bearing portion perpendicular to the second bearing portion is D3, and 0.1<D2 / D3<0.

24.

2. The compressor according to claim 1, characterized in that The outer diameter of the sixth groove is D1, 0.9<D1 / D2<1.

65.

3. The compressor according to claim 1, characterized in that The outer diameter of the sixth groove is D1, T1=D1-D2, the second bearing portion includes a journal portion, and the extension dimension of the journal portion perpendicular to the second bearing portion is T2; The compressor further includes a motor, the motor is configured to drive the eccentric crankshaft to rotate, the motor includes a rotor, and the outer diameter of the rotor is D4; 0.095<(T1+T2) / D4<0.

15.

4. The compressor according to any one of claims 1 to 3, characterized in that The bearing includes an oil groove, which is arranged on the hole wall of the first axial 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 axial hole, and the adjacent first sub-oil grooves are connected to the second sub-oil grooves. The first sub-oil groove extends along the axial direction of the first axial hole, and the second sub-oil groove extends along the circumferential spiral of the first axial hole.

5. The compressor according to claim 4, characterized in that 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.

6. The compressor according to claim 4, characterized in that The depth of the oil groove is T, the diameter of the first shaft hole is D, and 0.15<T / D<0.

21.

7. The compressor according to claim 4, 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.

8. The compressor according to any one of claims 1 to 3, 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.

9. The compressor according to any one of claims 1 to 3, 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.

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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