Compressor and air conditioner

Abstract

The compressor comprises a first shell, a compression mechanism is arranged in the first shell, the compression mechanism comprises an eccentric crankshaft, an air cylinder, a piston and a bearing, the piston is arranged on an eccentric shaft section of the eccentric crankshaft in a sleeving mode and located in a compression cavity of the air cylinder, the bearing is arranged on the eccentric crankshaft in a sleeving mode, and an exhaust port communicated with the compression cavity is formed in the bearing; the bearing is arranged on the compressor, the exhaust port is arranged on the bearing, the expansion type silencer is arranged on the bearing and covers the exhaust port, a first mounting cavity is formed in the expansion type silencer, the first mounting cavity communicates with an inner cavity of the expansion type silencer, and the at least one Helmholtz silencer is arranged in the first mounting cavity so as to improve the noise reduction effect of the compressor.

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] An expansion muffler is provided on the compression mechanism to reduce the exhaust noise of the compressor. The expansion muffler has a good noise reduction effect on medium-frequency noise (e.g., 800Hz-1600Hz), but has a poor noise reduction effect on high-frequency noise (e.g., above 2000Hz).

[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, and improves the silencer component of the compressor to enhance the noise reduction effect of the compressor.

[0006] On the one hand, a compressor is provided, which includes a first shell, a compression mechanism is arranged in the first shell, the compression mechanism includes an eccentric crankshaft, a cylinder, a piston and a bearing, the piston sleeve is arranged on the eccentric shaft section of the eccentric crankshaft and is located in the compression chamber of the cylinder, the bearing sleeve is arranged on the eccentric crankshaft, an exhaust port connected to the compression chamber is arranged on the bearing, an expansion muffler is arranged on the bearing and covers the exhaust port, a first installation cavity is arranged on the expansion muffler, the first installation cavity is connected to the inner cavity of the expansion muffler, and at least one Helmholtz muffler is arranged in the first installation cavity.

[0007] The silencer in the compressor disclosed in the present invention combines the advantages of the expansion silencer and the Helmholtz silencer resonance chamber, and merges the two into one structural component, which is convenient for installation and replacement. At the same time, it can also effectively increase the transmission sound loss inside the compressor without increasing the clearance volume, reduce the fluid noise of the compressor, and achieve effective suppression of the fluid noise inside the compressor from low frequency to high frequency.

[0008] 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.

[0009] 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

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

[0011] Figure 2 is a cross-sectional view of a compressor according to some embodiments;

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

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

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

[0015] Figure 6 is a structural diagram of a second connecting portion according to some embodiments;

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

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

[0018] Fig. 9 is a structural diagram of an expansion silencer and a Helmholtz silencer according to some embodiments;

[0019] Fig.10 is a graph of the amount of attenuation of a muffler according to some embodiments;

[0020] Fig.11 is a cross-sectional view of a gas-liquid separator according to some embodiments;

[0021] Fig.12A structural diagram of a first partition and a second partition according to some embodiments;

[0022] Fig.13 is another structural diagram of a gas-liquid separator according to some embodiments;

[0023] Fig.14 is a control logic diagram of a gas-liquid separator according to some embodiments;

[0024] Fig.15 is a structural diagram of an air outlet pipe according to some embodiments;

[0025] Fig.16 is a structural diagram of a compression mechanism according to some embodiments;

[0026] Fig.17 is a cross-sectional view of an eccentric crankshaft according to some embodiments;

[0027] Fig.18 is a structural diagram of a rotor according to some embodiments;

[0028] Fig.19 is a structural diagram of a stator according to some embodiments. DETAILED DESCRIPTION

[0029] 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.

[0030] 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.

[0031] 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.

[0032] 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.

[0033] 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.

[0034] 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.

[0035] [Air conditioner]

[0036] 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.

[0037] 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.

[0038] 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.

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

[0040] 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.

[0041] 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.

[0042] 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.

[0043] The heating working principle of the air conditioner is as follows: the gaseous refrigerant is pressurized by the compressor to become a high-temperature and high-pressure refrigerant gas. The refrigerant gas enters the indoor heat exchanger (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.

[0044] [Compressor body]

[0045] In some embodiments of the present disclosure, the compressor is a rolling rotor compressor. Figure 1 and Figure 2 as well as Fig.16The 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. Figure 2 As shown, the compressor body 100 further includes a motor 130, which is disposed in the accommodating 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. Fig.16 A cross-sectional view of the compression mechanism 120 .

[0046] In some embodiments, reference Figure 2 The motor 130 includes a rotor 132. The motor 130 also includes a stator 131, and the stator 131 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.

[0047] In some embodiments, reference Fig.16 The compression mechanism 120 further includes an eccentric crankshaft 121. The compression mechanism 120 further includes a muffler 704.

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

[0049] Reference Fig.16, the compression mechanism 120 further includes a cylinder 701. The compression mechanism 120 further includes a piston 702. The piston 702 is arranged in the compression chamber of the cylinder 701, and the piston 702 is sleeved on the eccentric shaft section. The compression mechanism 120 further includes a bearing 703. The bearing 703 is fixedly connected to the cylinder 701. The bearing 703 is provided with an exhaust hole, and the exhaust hole is communicated with the compression chamber. The compression mechanism 120 further includes a slide groove; the slide groove is arranged in the cylinder 701. The compression mechanism 120 further includes a slide. The slide is arranged in the slide groove. The eccentric crankshaft 121 drives the piston 702 to make circumferential motion in the compression chamber, and the slide reciprocates along the slide groove, and the slide always abuts against the piston. 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 702 separate the compression chamber into the first sub-compression chamber and the second sub-compression chamber. 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 121 to perform a rotational motion together, and the rotation of the eccentric crankshaft 121 drives the piston 702 mounted on the eccentric shaft segment to perform an eccentric circular motion in the compression chamber of the cylinder 701, and the vane performs a reciprocating motion in the vane groove, and the vane and the piston divide the compression chamber of the cylinder 701 into a first sub-compression chamber and a second sub-compression chamber, and the eccentric crankshaft 121 drives the piston 702 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.

[0050] In some embodiments of the present disclosure, the compressor is a double-cylinder rolling rotor compressor. Fig.16 The compression mechanism 120 includes an eccentric crankshaft 121. 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.

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

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

[0053] The first eccentric shaft segment 1212 and the second eccentric shaft segment 1213 are arranged along both sides of the central axis of the eccentric crankshaft 121. For example, the first eccentric shaft segment 1212 and the second eccentric shaft segment 1213 are arranged at a relative angle of 180°, the first piston 1231 and the second piston 1232 rotate eccentrically at the same time, and the compressed gas in the compression chamber of the first cylinder 1221 is discharged through the exhaust hole on the first bearing 1241, and the compressed gas in the compression chamber of the second cylinder 1222 is discharged through the exhaust hole on the second bearing 1242.

[0054] Continue to refer to Fig.16 The first muffler 1261 is arranged on the first bearing 1241. The first muffler 1261 covers the exhaust hole of the first bearing 1241. The compressed gas in the first cylinder 1221 is first discharged through the exhaust hole of the first bearing 1241 to the space surrounded by the first muffler 1261 and the first bearing 1241, and then discharged into the inner cavity of the compressor through the first muffler 1261.

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

[0056] In some embodiments, different from the related art, Fig.16 The exhaust hole can be omitted on the second muffler 1262. A plurality of vertically penetrating airflow channels are provided on the first bearing 1241, the first cylinder 1221, the middle partition 125, the second cylinder 1222 and the wall of the second bearing 1242. The compressed air in the second bearing 1242 and the second muffler 1262 is discharged upward through the airflow channel to the space surrounded by the first bearing 1241 and the first muffler 1261, and then discharged through the exhaust hole of the first muffler 1261 to the inner cavity of the compressor.

[0057] [Gas-Liquid Separator]

[0058] In some embodiments, reference Figure 1 The compressor further includes a gas-liquid separator 200. The gas-liquid separator 200 is disposed outside the compressor body 100 and is configured to provide gaseous refrigerant to the compression chamber of the compression mechanism 120. The gas-liquid separator 200 separates the liquid refrigerant from the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 100 and causing the compressor to malfunction.

[0059] In some embodiments, reference Figure 1 and Fig.11 The gas-liquid separator 200 includes a second shell 210; the gas-liquid separator 200 also includes an air outlet pipe 240. The air outlet pipe 240 is arranged at the bottom of the second shell 210. The first end of the air outlet pipe 240 extends into the inner cavity of the second shell 210, and the second end of the air outlet pipe 240 is connected to the compression mechanism 120, for example, the second end of the air outlet pipe 240 is connected to the air intake port of the cylinder 701 to provide gaseous refrigerant to the compression mechanism 120.

[0060] [Bottom]

[0061] Typically, the compressor body 100 includes a rubber foot. The rubber foot is fixedly disposed at the bottom of the first shell 110. After the rubber foot is installed, the vibration isolation amount of the rubber foot and the overall mode of the compressor have been determined. As the operating frequency range of the compressor continues to expand, for example, 10Hz-160Hz, on the one hand, the sixth-order rigid body mode of the compressor is usually in the range of 5Hz-30Hz, which is easily excited, thereby causing violent shaking of the compressor. On the other hand, according to the stiffness vibration isolation principle, as the operating frequency range of the compressor increases, the rubber foot's own mode and the compressor excitation are easily coupled with each other, thereby reducing the vibration isolation effect of the rubber foot, and then increasing the vibration and noise of the outdoor unit.

[0062] In order to solve this technical problem, in some embodiments, referring to Figure 3The compressor includes at least one foot 300, and at least one foot 300 is disposed on the first housing 110. The foot 300 is configured to mount the compressor to a mounting carrier 500 where the compressor is located. For example, the compressor is fixedly mounted to a bottom plate of an outdoor unit through the foot 300, and in this case, the mounting carrier 500 is the bottom plate of the outdoor unit.

[0063] In some embodiments, the at least one foot 300 includes a plurality of feet 300. The plurality of feet 300 are respectively disposed at the bottom of the first housing 110, and the plurality of feet 300 are spaced apart along the circumference of the first housing 110 to improve the installation stability of the compressor.

[0064] In some embodiments, reference Figure 4 The foot 300 includes a housing 310. The housing 310 is configured to connect the first housing 110 and the bottom plate of the outdoor unit. The foot 300 also includes a second mounting cavity 311. The second mounting cavity 311 is formed in the housing 310. For example, a first end of the housing 310 is fixed to the first housing 110 by bolts, and a second end of the housing 310 is fixed to the bottom plate of the outdoor unit by bolts, and the first end is arranged opposite to the second end.

[0065] In some embodiments, Figure 4 As shown, the foot 300 includes a support member 320. The support member 320 is disposed in the second installation cavity 311. When the support member 320 is acted upon by an external force, it can extend or contract along the height direction of the second installation cavity 311 (ie, the height direction of the compressor).

[0066] In some embodiments, the foot 300 further includes a first driving portion 330. The first driving portion 330 is disposed in the second mounting cavity 311. The first driving portion 330 is configured to adjust the stiffness of the support member 320 according to the vibration signal of the compressor to adjust the rigid body mode of the compressor.

[0067] In some embodiments, the foot 300 and the support member 320 of some embodiments of the present disclosure actively adjust the stiffness according to the vibration signal of the compressor, thereby adjusting the rigid body mode of the compressor. On the one hand, the active deviation of the stiffness mode of the compressor is achieved to avoid the violent shaking of the compressor and reduce the impact on the pipeline; on the other hand, when the compressor is running at a high frequency, a high stiffness vibration isolation effect can be obtained, thereby reducing the vibration transmission amount and reducing the vibration and noise of the outdoor unit.

[0068] In some embodiments, reference Figure 3 The compressor further includes a first sensor 410 . The first sensor 410 is disposed on the first housing 110 , and the first sensor 410 is configured to detect a vibration signal of the first housing 110 .

[0069] The compressor further includes a second sensor 420. The second sensor 420 is disposed on a bottom plate of the outdoor unit, and the second sensor 420 is configured to detect a vibration signal of the bottom plate.

[0070] The first driving part 330 is configured to adjust the rigidity of the support member 320 according to the vibration signal of the first housing 110 and the vibration signal of the bottom plate.

[0071] The compressor of some embodiments of the present disclosure uses the first sensor 410 and the second sensor 420 to determine the vibration isolation amount, thereby actively adjusting the stiffness of the support member 320, thereby changing the rigid body mode of the compressor.

[0072] In some embodiments, Figure 5 As shown, the compressor body 100 further includes a first controller 610. The first controller 610 is coupled to the first sensor 410, the foot 300 and the mounting carrier 500 respectively.

[0073] In some embodiments, reference Figure 5 , the adjustment process of the base 300 includes S11 to S15.

[0074] S11 , acquiring a first vibration signal detected by the first sensor 410 and a second vibration signal detected by the second sensor 420 .

[0075] For example, the first vibration signal refers to a vibration signal of the first housing 110 ; the second vibration signal refers to a vibration signal of the bottom plate.

[0076] S12, processing and analyzing the first vibration signal and the second vibration signal.

[0077] For example, the first controller 610 may process and analyze the first vibration signal and the second vibration signal.

[0078] S13, based on the analysis data of the first controller 610, determine whether the compressor is in a fixed frequency (natural frequency) operating state at this time, and whether the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is greater than the set value X; if "yes", execute step S15; if "no", execute step S14.

[0079] S14, the first driving part 330 drives the supporting member 320 to extend to reduce rigidity.

[0080] For example, when it is determined that the compressor is in a non-fixed frequency operation state or the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is less than or equal to the set value X, the first driving part 330 is controlled to drive the support member 320 to extend to reduce the stiffness.

[0081] S15, driving the support member 320 to contract to increase rigidity.

[0082] For example, when it is determined that the compressor is in a fixed frequency operation state or the difference A between the vibration amplitudes of the first vibration signal and the second vibration signal is greater than the set value X, the first driving part 330 is controlled to drive the support member 320 to extend to reduce the rigidity.

[0083] In some embodiments, reference Figure 4 The first driving part 330 includes a first driving motor 331, a power shaft end of the first driving motor 331 is connected to a first threaded column 332, and a moving part 333 is provided on the first threaded column 332. The moving part 333 is configured to move along the telescopic direction of the support member 320 to adjust the stiffness of the support member 320.

[0084] When the power shaft of the first driving motor 331 rotates in a first direction (eg, clockwise), the first threaded column 332 drives the moving portion 333 to move upward, and the moving portion 333 presses the supporting member 320 , so that the supporting member 320 contracts under the force.

[0085] When the power shaft of the first driving motor 331 rotates in the second direction (eg, counterclockwise), the first threaded column 332 drives the moving portion 333 to move downward, and the supporting member 320 rebounds and extends.

[0086] In some embodiments, the moving portion 333 is a flat plate structure, and an outer peripheral end side of the moving portion 333 is spaced apart from an inner cavity wall of the housing 310 to avoid increasing friction due to contact between the moving portion 333 and the housing 310 .

[0087] In some embodiments, the support member 320 is a spring, which is sleeved on the outer circumference of the first threaded column 332 , with the first end of the spring abutting against the moving portion 333 , and the second end of the spring abutting against the top wall of the second installation cavity 311 .

[0088] The first threaded column 332 is located in the spring, and the structure is compact. The spring is limited between the moving portion 333 and the top wall of the second installation cavity 311, and the structure is reliable.

[0089] In some embodiments, reference Figure 4 The housing 310 includes a first sub-housing 312, which is configured to be connected to the bottom plate of the outdoor unit, and the first sub-housing 312 constitutes the bottom wall of the second installation cavity 311. For example, the first sub-housing 312 is fixed to the bottom plate by bolts. The first drive motor 331 is disposed in the first sub-housing 312.

[0090] In some embodiments, reference Figure 4 The housing 310 further includes a second sub-housing 313, a second installation cavity 311 is formed in the second sub-housing 313, and the second sub-housing 313 is connected to the first sub-housing 312, for example, the second sub-housing 313 and the first sub-housing are welded.

[0091] In some embodiments, reference Figure 4 The housing 310 further includes a third sub-housing 314. The third sub-housing 314 is connected to the second sub-housing 313, for example, the third sub-housing 314 is welded to the second sub-housing 313. The third sub-housing 314 and the first sub-housing 312 are disposed at opposite ends of the second sub-housing 313, and the third sub-housing 314 is configured to be connected to the first housing 110 of the compressor. For example, the third sub-housing 314 is fixedly connected to the outside of the first housing 110 by bolts.

[0092] In some embodiments, the shell 310 is made of rubber to enhance the vibration isolation effect of the base 300 .

[0093] [Second connection portion of gas-liquid separator]

[0094] When the double frequency abnormal sound of the rotary compressor is large, it contributes greatly to the noise, vibration and acoustic roughness (NVH) of the outdoor unit. Modal analysis found that the cause of the large double frequency abnormal sound of the compressor is the first-order rigid body torsion mode of the gas-liquid separator 200. The rigid body mode is only affected by the constraint boundary, that is, the greater the boundary stiffness, the higher the rigid body mode of the gas-liquid separator 200. The compressor usually adopts the method of increasing the welding stiffness and increasing the welding points to increase the fixed frequency of the gas-liquid separator 200. However, with the expansion of the operating range of the compressor, the effect of increasing the welding stiffness and increasing the welding points on improving the fixed frequency of the gas-liquid separator 200 is limited.

[0095] In order to solve this technical problem, in some embodiments, referring to Figure 1 and Figure 6 The compressor further includes a first connection portion 220. The first connection portion 220 is configured to fixedly connect the first shell 110 and the second shell 210.

[0096] For example, one side of the first connection portion 220 is welded to the first shell 110 , and the other side of the first connection portion 220 surrounds the second shell 210 to fix the second shell 210 .

[0097] The compressor further includes a second connection portion 230. Figure 6 As shown, the second connection part 230 includes a fixed part 231; the second connection part 230 also includes two moving parts 232. The fixed part 231 is fixedly connected to the first shell 110, and the two moving parts 232 are arranged on opposite sides of the fixed part 231 along the length direction. The two moving parts 232 are configured to move toward a direction close to the second shell 210 to surround the second shell 210 according to the vibration signal of the gas-liquid separator 200, or move toward a direction away from the second shell 210 to separate from the second shell 210.

[0098] The second connecting portion 230 in some embodiments of the present disclosure adjusts the rigid body mode of the gas-liquid separator 200 through the movement of the two moving portions 232, thereby achieving the shift of the fixed frequency of the gas-liquid separator 200 and reducing the second harmonic noise of the compressor.

[0099] The frequency response function curve of the gas-liquid separator 200 is shown in FIG. Figure 8 Curve A is a frequency response function curve diagram of the gas-liquid separator 200 when the two moving parts 232 surround the second shell 210 , and curve B is a frequency response function curve diagram of the gas-liquid separator 200 when the two moving parts 232 are separated from the second shell 210 .

[0100] In some embodiments, reference Figure 1 The compressor includes a third sensor 430 , which is disposed in the second shell 210 . The third sensor 430 is configured to detect a vibration signal of the second shell 210 , that is, a vibration signal of the gas-liquid separator 200 .

[0101] In some embodiments, when the operating frequency of the compressor is lower than the first set frequency, for example, lower than 60 rps (revolutions per second), the rigid body mode of the gas-liquid separator 200 is triggered, and the two moving parts 232 move toward the direction close to the second shell 210 to surround the second shell 210, thereby achieving a fixed frequency offset of the gas-liquid separator 200.

[0102] In some embodiments, when the operating frequency of the compressor is higher than the second set frequency, for example, higher than 60 rps, the rigid body mode of the gas-liquid separator 200 is triggered, and the two moving parts 232 move in a direction away from the second shell 210 to separate from the second shell 210, thereby achieving a fixed frequency offset of the gas-liquid separator 200.

[0103] In some embodiments, Figure 7 As shown, the control process of the second connection part 230 includes S21 to S25.

[0104] S21 , obtaining a third vibration signal of the gas-liquid separator 200 detected by the third sensor 430 .

[0105] For example, the third vibration signal may refer to a vibration signal of the gas-liquid separator 200 .

[0106] S22, determining whether the amplitude of the third vibration signal is greater than a set value N. If "yes", executing step S23; if "no", returning to executing step S21.

[0107] S23, judging whether the operating frequency of the compressor is greater than the set value M. If "yes", executing step S25; if "no", returning to executing step S24.

[0108] S24 , controlling the two moving parts 232 to move toward the direction approaching the second housing 210 to surround the second housing 210 .

[0109] S25 , controlling the two moving parts 232 to move in a direction away from the second housing 210 to separate from the second housing 210 .

[0110] In some embodiments, reference Figure 6 The fixing portion 231 includes a first sub-fixing portion 2311; the fixing portion 231 also includes two second sub-fixing portions 2312, and the two second sub-fixing portions 2312 are arranged on opposite sides of the first sub-fixing portion 2311 along the length direction of the first sub-fixing portion 2311. The fixing portion 231 has a U-shaped structure.

[0111] The first sub-fixing portion 2311 is fixedly connected to the first housing 110 , for example, the first sub-fixing portion 2311 is welded to the first housing 110 . The first sub-fixing portion 2311 is arc-shaped to match the outer contour of the first housing 110 .

[0112] The second sub-fixing portion 2312 extends from the first sub-fixing portion 2311 toward a direction close to the second housing 210 , and the second sub-fixing portion 2312 is rotatably connected to the moving portion 232 .

[0113] In some embodiments, the second connection portion 230 further includes a third driving motor. Figure 6 The second connecting portion 230 also includes a driving shaft 233 , a power shaft end of the third driving motor is connected to the driving shaft 233 , and the second sub-fixing portion 2312 and the moving portion 232 are rotationally connected through the driving shaft 233 .

[0114] For example, the third driving motor is fixedly mounted on the fixing portion 231 or the third driving motor is fixedly mounted on the second housing 210 .

[0115] In some embodiments, the moving portion 232 is arc-shaped to match the outer contour of the second shell 210 , thereby improving the surrounding effect on the second shell 210 .

[0116] [Inner cavity partition structure of gas-liquid separator]

[0117] A partition is usually provided inside the gas-liquid separator 200 to divide its internal space, thereby changing the acoustic cavity mode to increase or decrease the modal frequency. The partition is fixed so that after the partition is fixedly installed, the fixed frequency of the acoustic cavity inside the gas-liquid separator 200 is also determined. However, as the operating frequency range and pressure range of the compressor increase, and the physical parameters such as the physical properties and sound velocity of the refrigerant change beyond the threshold range, the fixed acoustic cavity mode of the gas-liquid separator 200 is difficult to adapt to different operating scenarios of the compressor, causing the gas-liquid separator 200 to vibrate and make a lot of noise.

[0118] In order to solve this technical problem, in some embodiments, referring to Figures 11 to 13 The gas-liquid separator 200 includes a first partition 250. The first partition 250 is fixedly disposed in the internal cavity of the gas-liquid separator 200. The gas-liquid separator 200 also includes a first cavity 291; the gas-liquid separator 200 also includes a second cavity 292. The first partition 250 divides the internal cavity of the gas-liquid separator 200 into a first cavity 291 and a second cavity 292. The first cavity 291 and the second cavity 292 are arranged in sequence along the height direction of the second shell 210, and the first cavity 291 is located above the second cavity 292. The gas outlet pipe 240 passes through the first partition 250, and one end of the gas outlet pipe 240 is located in the first cavity 291.

[0119] Reference Fig.11 and Fig.12 The first partition 250 is a plate-shaped structure, and the outer peripheral end side of the first partition 250 is welded to the inner peripheral wall of the second shell 210. The first partition 250 includes a first partition body; the first partition 250 also includes a plurality of first openings 251. The plurality of first openings 251 are provided in the first partition body and are used for the refrigerant to flow.

[0120] Reference Figures 11 to 13 The gas-liquid separator 200 includes a second partition 260, which is disposed in the second cavity 292. The second cavity 292 includes a first sub-cavity 293; the second cavity 292 also includes a second sub-cavity 294. The second partition 260 divides the second cavity 292 into a first sub-cavity 293 and a second sub-cavity 294, which are arranged in sequence along the height direction of the second housing 210, and the first sub-cavity 293 is located on a side of the second sub-cavity 294 close to the first cavity 291.

[0121] The first partition 250 and the second partition 260 divide the inner cavity of the second shell 210 into three chambers, namely a first chamber 291 , a first sub-chamber 293 and a second sub-chamber 294 . The three chambers are arranged in sequence along the height direction of the second shell 210 .

[0122] Reference Figures 11 to 13 The gas-liquid separator 200 further includes a second driving unit 270 , which is configured to drive the second partition 260 to move along a height direction of the second shell 210 to adjust the acoustic cavity mode of the gas-liquid separator 200 .

[0123] In some embodiments of the gas-liquid separator 200 disclosed herein, the second driving portion 270 drives the second partition portion 260 to move along the height direction of the second shell 210, thereby adjusting the volumes of the first sub-cavity 293 and the second sub-cavity 294, and further adjusting the acoustic cavity mode of the gas-liquid separator 200, thereby achieving the effect of reducing the vibration and noise of the gas-liquid separator 200.

[0124] In some embodiments, the second driving unit 270 drives the second partition 260 to move toward or away from the first partition 250 according to the vibration signal of the second housing 210 .

[0125] When the second partition 260 moves toward the direction approaching the first partition 250 , the volume of the first sub-cavity 293 decreases, and the volume of the second sub-cavity 294 increases.

[0126] When the second partition 260 moves in a direction away from the first partition 250 , the volume of the first sub-cavity 293 increases, and the volume of the second sub-cavity 294 decreases.

[0127] In some embodiments, the initial position of the second partition 260 is close to the first partition 250, so that initially, the first sub-cavity 293 has a small volume and the second sub-cavity 294 has a large volume.

[0128] When the gas-liquid separator 200 is in a non-resonant operating state, the second driving part 270 drives the second partition part 260 to move in a direction away from the first partition part 250, so that the volume of the first sub-cavity 293 increases and the volume of the second sub-cavity 294 decreases. When the vibration signal detected by the third sensor 430 is less than or equal to the second set value P, the second partition part 260 stops moving.

[0129] Here, the size of the second set value P is related to the displacement of the compressor.

[0130] In some embodiments, reference Fig.14 , the control process of the gas-liquid separator 200 includes S31 to S37.

[0131] S31 , obtaining a third vibration signal of the second housing 210 detected by the third sensor 430 .

[0132] S32: the second controller 620 analyzes and processes the third vibration signal.

[0133] S33, judging whether the gas-liquid separator 200 is in a non-structural fixed frequency operation state and whether the amplitude of the third vibration signal is greater than the second set value P. If "yes", execute step S34; if "no", execute step S37.

[0134] S34 , controlling the second driving part 270 to drive the second partition part 260 to move in a direction away from the first partition part 250 .

[0135] S35, determining whether the vibration signal detected by the third sensor 430 is less than or equal to the second set value P, if "yes", executing step S36; if "no", returning to executing step S34.

[0136] S36, controlling the second partition 260 to stop moving. S37, controlling the second driving unit 270 to remain stationary, and the second partition 260 to remain stationary.

[0137] In some embodiments, reference Fig.12 The second driving part 270 includes a second driving motor 271, and the second driving part 270 also includes at least one second threaded column 272. The second threaded column 272 is disposed at the end of the power shaft of the second driving motor 271, the first end of the second threaded column 272 is fixedly connected to the first partition 250, the second end of the second threaded column 272 is threadedly connected to the second partition 260, and the second driving motor 271 is fixedly disposed on the second partition 260.

[0138] When the power shaft of the second driving motor 271 rotates in a first direction (eg, clockwise), the second partition 260 moves in a direction away from the first partition 250 .

[0139] When the power shaft of the second driving motor 271 rotates in the second direction (eg, counterclockwise), the second partition 260 moves toward a direction approaching the first partition 250 .

[0140] In some embodiments, the at least one second threaded column 272 includes a plurality of second threaded columns 272, the plurality of second threaded columns 272 are arranged at intervals along the circumference of the second partition 260, and at least one second threaded column 272 of the plurality of second threaded columns 272 is connected to the power shaft end of the second drive motor 271. In this way, the movement reliability of the second partition 260 is improved.

[0141] For example, refer to Fig.12 The at least one second threaded column 272 includes two second threaded columns 272 , and the two second threaded columns 272 are symmetrically arranged relative to the central axis of the second partition 260 .

[0142] In some embodiments, reference Fig.12 The second partition 260 further includes a second partition body; the second partition 260 further includes a second opening 261. The second opening 261 is provided in the second partition body, and the outlet pipe 240 passes through the second opening 261 to avoid interference between the movement of the second partition 260 and the outlet pipe 240. The diameter of the second opening 261 is larger than the diameter of the outlet pipe 240, so that the gap between the second opening 261 and the outlet pipe 240 facilitates the circulation of the refrigerant.

[0143] In some embodiments, the second partition 260 is a plate-like structure, and a gap is provided between the outer peripheral side of the second partition 260 and the inner peripheral wall of the second shell 210 to avoid contact between the two and increase friction, and also to facilitate the circulation of the refrigerant.

[0144] [Gas outlet pipe of gas-liquid separator]

[0145] Reference Fig.15 , the air outlet pipe 240 includes an air outlet pipe body; the air outlet pipe 240 also includes a liquid return hole 241. The liquid return hole 241 is arranged in the air outlet pipe body, and the refrigerant in the system enters the air intake port of the compression mechanism 120 through the gas-liquid separator 200. The oil droplets carried by the refrigerant will accumulate in the gas-liquid separator 200 and return to the compressor through the liquid return hole 241. If the position of the liquid return hole 241 is too high or the aperture is too small, it will cause too much oil to accumulate in the gas-liquid separator 200 when the system reaches a dynamic balance, resulting in an increase in cost. If the position of the liquid return hole 241 is too low or the aperture is too large, it will easily cause liquid hammer, which will exceed the bearing range of the cylinder 701, damage the mechanical parts of the compressor, and be detrimental to the reliability of the compressor.

[0146] In order to solve this technical problem, in some embodiments, referring to Fig.15 The outlet pipe 240 includes M liquid return holes 241. The M liquid return holes 241 are arranged along the height direction of the outlet pipe 240. The diameter of the liquid return hole 241 is D, and the distance between two adjacent liquid return holes 241 is N. n , n=(1,...,M-1), then the diameter D of the liquid return hole 241 and the distance Nn between two adjacent liquid return holes 241 satisfy:

[0147] D×M / (N 1 +...+N M-1 )∈(0.15, 0.20)

[0148] By designing the liquid return hole 241 as above, the position and the aperture of the liquid return hole 241 are within a reasonable data range, thereby improving the oil return rate and the efficiency of the compressor.

[0149] In some embodiments, the distance between two adjacent liquid return holes 241 is the same and is N, then the diameter D of the liquid return hole 241 and the distance N between the two adjacent liquid return holes 241 satisfy:

[0150] D×M / ((M-1)×N)∈(0.15, 0.20)

[0151] In some embodiments, reference Fig.15 Two liquid return holes 241 are provided on the air outlet pipe 240 .

[0152] In some embodiments, reference body 11 and Fig.15 The gas-liquid separator 200 includes two gas outlet pipes 240 , namely a first gas outlet pipe 242 and a second gas outlet pipe 243 . M liquid return holes 241 are provided on each gas outlet pipe 240 .

[0153] Reference Fig.11 and Fig.16The compression mechanism 120 includes two cylinders 701, namely a first cylinder 1221 and a second cylinder 1222, and two air outlet pipes 240 are respectively connected to the compression chambers of the two cylinders 701. For example, the first air outlet pipe 242 is connected to the air intake port of the first cylinder 1221, and the second air outlet pipe 243 is connected to the air intake port of the second cylinder 1222.

[0154] [Silencer]

[0155] In some embodiments, reference Fig. 9 and Fig.16 The muffler 704 (the first muffler 1261 and the second muffler 1262) includes an expansion muffler 141. The expansion muffler 141 is disposed on the bearing 703 and covers the exhaust port on the bearing 703. The expansion muffler 141 is provided with at least one first installation cavity, which is communicated with the inner cavity of the expansion muffler 141.

[0156] The silencer 704 further includes at least one Helmholtz silencer 142. The Helmholtz silencer 142 is disposed in the first mounting cavity.

[0157] The first silencer 1261 includes an expansion silencer 141 and at least one Helmholtz silencer 142. The second silencer 1262 includes an expansion silencer 141 and at least one Helmholtz silencer 142.

[0158] The silencer 704 in the compressor of some embodiments of the present disclosure combines the advantages of the expansion silencer 141 and the resonance chamber of the Helmholtz silencer 142, and merges the two into one structural component, which is convenient for installation and replacement. It can also effectively increase the transmission sound loss inside the compressor without increasing the clearance volume, reduce the fluid noise of the compressor, and achieve effective suppression of the fluid noise inside the compressor from low frequency to high frequency.

[0159] Fig.10 is the muffler attenuation curve. Curve c is the muffler using Fig. 9 The expansion silencer 141 is shown as a silencer volume curve after the expansion silencer 141 is combined with the Helmholtz silencer 142. Curve d is a silencer volume curve when only the expansion silencer 141 is used.

[0160] In some embodiments, reference Fig. 9 The expansion muffler 141 includes a first wall 1411 ; the expansion muffler 141 also includes a second wall 1412 , the second wall 1412 is arranged along the circumference of the first wall 1411 and extends in a direction close to the cylinder 701 , and the first installation cavity is arranged in the first wall 1411 .

[0161] The first wall 1411 facilitates the arrangement of the first installation cavity and the installation of the Helmholtz silencer 142 .

[0162] In some embodiments, at least one first installation cavity includes a plurality of first installation cavities, and the plurality of first installation cavities are arranged at intervals on the first wall 1411. In this way, at least one Helmholtz silencer 142 includes a plurality of Helmholtz silencers 142, and the plurality of Helmholtz silencers 142 are arranged on the expansion silencer 141, which is conducive to improving the silencing effect.

[0163] In some embodiments, the first wall 1411 has a portion protruding in a direction away from the cylinder 701 to form a first installation cavity. In this way, the first installation cavity and the first wall 1411 are an integral piece, for example, the first wall 1411 is formed into the first installation cavity by stamping.

[0164] In some embodiments, an opening is provided on the first wall 1411, a connecting piece is provided on the side of the first wall 1411 away from the cylinder 701, the connecting piece is arranged opposite to (eg, directly opposite to) the opening 3, a first installation cavity is formed in the connecting piece, and the first installation cavity is connected to the opening.

[0165] In this way, the connecting piece is a hollow cylindrical structure with one side open. The connecting piece is fixed to the first wall 1411 by welding or the like. The connecting piece is located outside the first wall 1411. The opening of the connecting piece is opposite to the opening 3 (such as directly opposite). The first installation cavity formed in the connecting piece is connected to the inner cavity of the expansion muffler 141 through the opening.

[0166] When installing the silencer 704 , the Helmholtz silencer 142 is first fixedly installed in the inner cavity of the connecting member, and then the connecting member is fixedly installed to the outside of the expansion silencer 141 .

[0167] [Suction channel of compression mechanism]

[0168] In a dual-cylinder rolling rotor compressor, the phase difference between the two pistons in the two cylinders is 180°, which makes the compression process differ by 180° and the suction rate of the suction chamber also differ by 180°. Studies have found that suction pressure loss has a great impact on the cooling and heating capacity of the air conditioner. For example, when the pressure loss increases, the suction density decreases, and the compression mass of the refrigerant under the same volume decreases, which in turn leads to a decrease in the refrigerant circulation volume in the air conditioner, affecting the cooling and heating capacity of the air conditioner.

[0169] In order to solve this technical problem, in some embodiments, referring to Fig.16 Any cylinder 701 (the first cylinder 1221, the second cylinder 1222) includes at least one air intake channel 161; and any cylinder 701 also includes a ventilation channel 164. The ventilation channel 164 includes at least one first sub-ventilation channel 162, the air intake channel 161 is connected to the first sub-ventilation channel 162, and the air intake channel 161 is connected to the air outlet pipe 240.

[0170] The ventilation channel 164 also includes at least one second sub-ventilation channel 163. The second sub-ventilation channel 163 is provided on the middle partition 125. In the case where the at least one intake channel 161 includes two intake channels 161, one of the two intake channels 161 is located in the first cylinder 1221, and the other of the two intake channels 161 is located in the second cylinder 1222. The first sub-ventilation channel 162 and the second sub-ventilation channel 163 are connected to connect the two intake channels 161 of the two cylinders 703. The second sub-ventilation channel 163 and the two first sub-ventilation channels 162 are connected to form the ventilation channel 164.

[0171] When the first cylinder 1221 rapidly inhales air, a portion of the refrigerant in the intake passage 161 of the second cylinder 1222 flows into the first cylinder 1221 through the ventilation passage 164 .

[0172] When the second cylinder 1222 rapidly inhales air, a portion of the refrigerant in the intake passage 161 of the first cylinder 1221 flows into the second cylinder 1222 through the ventilation passage 164 .

[0173] In this way, by providing the ventilation channel 164, the refrigerant circulation amount in the air conditioner can be effectively increased, thereby improving the cooling and heating capabilities of the air conditioner.

[0174] In some embodiments, any cylinder 703 is provided with at least one first sub-vent channel 162, and the middle partition 125 is provided with at least one second sub-vent channel 163, and the at least one first sub-vent channel 162 is connected to the at least one second sub-vent channel 163 respectively.

[0175] For example, refer to Fig.16 A first sub-ventilation channel 162 is respectively provided on the first cylinder 1221 and the second cylinder 1222 , and a second sub-ventilation channel 163 is provided on the middle partition plate 125 , thereby forming a ventilation channel 164 .

[0176] For another example, two second sub-ventilation channels 163 are respectively disposed on the first cylinder 1221 and the second cylinder 1222 , and two second sub-ventilation channels 163 are disposed on the middle partition plate 125 , thereby forming two ventilation channels 164 .

[0177] [Other structures]

[0178] In some embodiments, reference Figure 1 , the inner diameter of the second shell 210 is D6. Fig.16 The inner diameter of the air intake passage 161 is D7, (D6 4 -D7 4 ) / D6 2 ×D7 2>4.6, this range can reduce the noise of the compressor.

[0179] In some embodiments, reference Fig.17 The outer diameter of the first shaft segment 1211 is D2, and an axial hole 1216 is formed in the first shaft segment 1211, and the inner diameter of the axial hole 1216 is D3.

[0180] The rotor 132 is disposed on the first shaft section 1211. Fig.18 , the inner diameter of the rotor 132 is D1. The inner diameter D1 of the rotor 132, the outer diameter D2 of the first shaft section 1211 and the inner diameter D3 of the shaft hole 1216 satisfy:

[0181] (D1-D2) / D3=[0.002, 0.01].

[0182] If (D1-D2) / D<0.002, the holding force of the rotor 132 is small, and there is a risk that the rotor 132 will fall off.

[0183] If (D1-D2) / D3>0.01, the compressive stress and electromagnetic loss of the rotor 132 will increase, resulting in a decrease in the efficiency of the motor 130; and a higher shrink-fit temperature is required to make the inner diameter of the rotor 132 expand outward so that the eccentric crankshaft 121 can be inserted. If the temperature exceeds the Curie temperature of the magnet of the rotor 132, irreversible damage will be caused to the magnet; the outer diameter of the rotor 132 will deform outward seriously, resulting in an increased risk of the stator 131 and the rotor 132 being swept outward.

[0184] In some embodiments of the present disclosure, by setting (D1-D2) / D3=[0.002, 0.01], the efficiency of the motor 130, the clamping force of the rotor 132, the shrink fitting process and the reduction of the risk of stator and rotor bore scraping can be taken into consideration. Within this range, the efficiency of the motor 130 is high and there is no risk of the rotor 132 falling off.

[0185] In some embodiments, reference Figure 1 , the inner diameter of the first shell 110 is D4, and the circumferential wall thickness of the first shell 110 is t. Fig.19 , the stator 131 is fixedly connected to the circumferential inner wall of the first housing 110, and the outer diameter of the stator 131 is D5. The inner diameter D4 of the first housing 110, the outer diameter D5 of the stator 131, and the circumferential wall thickness t of the first housing 110 satisfy:

[0186] (D5-D4) / t=[0.02, 0.08]. This range takes into account the efficiency of the motor 130, the clamping force of the stator 131, the shrink fitting process and the reduction of the risk of the stator and rotor bore scraping. The motor 130 has high efficiency and there is no risk of the stator 131 falling off.

[0187] If (D5-D4) / t<0.02, the clamping force of the stator 131 is small and there is a risk of falling off.

[0188] If (D5-D4) / t>0.08, the compressive stress of the stator 131 and the electromagnetic loss of the motor 130 will increase, resulting in a decrease in the efficiency of the motor 130; and a higher shrinkage temperature is required to allow the inner radial expansion of the shell to expand outward so that the stator 131 can be inserted. The higher the temperature, the more serious the blueing of the shell; the inner radial deformation of the stator 131 is serious, resulting in an increased risk of stator and rotor bore scraping.

[0189] In some embodiments, reference Figure 2 The compressor body 100 further includes an oil pool 150. The oil pool 150 is formed at the bottom of the accommodating cavity 111 of the first housing 110. After the compressor is worn, wear debris is deposited in the oil pool 150. If too much wear debris is deposited, it will be re-absorbed into the compressor body 100, causing the compressor to jam.

[0190] To solve this technical problem, refer to Figure 2 The compressor body 100 includes a fourth sensor 440. The fourth sensor 440 is disposed in the oil pool 150, and the fourth sensor 440 is configured to detect the color of the oil in the oil pool 150. For example, the fourth sensor 440 is a color sensor.

[0191] The color of the oil in the oil pool 150 is detected in real time by the fourth sensor 440 to evaluate whether the compressor is worn according to the color of the oil.

[0192] If the color of the oil pool 150 detected by the fourth sensor 440 is greater than the third set value, the compressor alarms and automatically shuts down, thereby reducing the failure rate.

[0193] In some embodiments, the fourth sensor 440 is fixedly mounted to the bottom wall of the first housing 110 by means of snaps or the like.

[0194] In some embodiments, reference Fig.11 The gas-liquid separator 200 further includes a filter screen 280. The filter screen 280 is located at the top of the inner cavity of the gas-liquid separator 200. The height of the second shell 210 is H1, and the height of the portion of the gas outlet pipe 240 located in the cavity is H2. The height H1 of the second shell 210 and the height H2 of the portion of the gas outlet pipe 240 located in the cavity satisfy:

[0195] 0.5<H2 / H1<0.8. This range can improve the gas-liquid separation performance of the gas-liquid separator 200 and reduce vibration noise.

[0196] If H2 / H1>0.8, the length of the outlet pipe 240 in the inner cavity of the gas-liquid separator 200 is long, which will cause interference between the outlet pipe 240 and the filter 280; the length of the outlet pipe 240 extending out of the first partition 250 is too long, and the top end of the outlet pipe 240 is greatly deformed, which can easily stimulate the outlet pipe 240 to produce a bending mode and generate vibration noise.

[0197] If H2 / H1<0.5, the effective volume in the gas-liquid separator 20 is insufficient, which affects the gas-liquid separation performance.

[0198] 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.

[0199] 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 first shell having a receiving cavity formed therein; A compression mechanism is disposed in the accommodating chamber and is configured to compress the refrigerant. The compression mechanism comprises: An eccentric crankshaft, a cylinder, a piston and a bearing, wherein the piston sleeve is disposed on the eccentric shaft section of the eccentric crankshaft and is located in the compression chamber of the cylinder, the bearing sleeve is disposed on the eccentric crankshaft, and an exhaust port communicating with the compression chamber is disposed on the bearing; an expansion muffler, the expansion muffler being arranged on the bearing and covering the exhaust port, the expansion muffler being provided with a first mounting cavity, the first mounting cavity being communicated with an inner cavity of the expansion muffler; At least one Helmholtz silencer is disposed in the first mounting cavity.

2. The compressor according to claim 1, characterized in that The expansion muffler includes a first wall and a second wall, wherein the second wall is arranged along the circumference of the first wall and extends toward the direction close to the cylinder, and the first installation cavity is arranged on the first wall.

3. The compressor according to claim 2, characterized in that A plurality of the first installation cavities are arranged at intervals on the first wall.

4. The compressor according to claim 2, characterized in that The first wall has a portion protruding in a direction away from the cylinder to form the first installation cavity.

5. The compressor according to claim 2, characterized in that An opening is arranged on the first wall, a connecting piece is arranged on a side of the first wall away from the cylinder, the connecting piece is opposite to the opening, the first installation cavity is formed in the connecting piece, and the first installation cavity is communicated with the opening.

6. The compressor according to any one of claims 1 to 5, characterized in that The compressor further includes a foot, which is disposed on the first housing and is configured to mount the compressor on a mounting carrier on which the compressor is located, and the foot includes: A housing configured to connect the first housing and the mounting carrier, wherein a second mounting cavity is formed in the housing; A support member, disposed in the second mounting cavity; A driving unit is disposed in the second installation cavity, and is configured to adjust the stiffness of the support member according to a vibration signal of the compressor so as to adjust the rigid body mode of the compressor.

7. The compressor according to claim 6, characterized in that The compressor comprises: A first sensor is disposed on the first housing, and the first sensor is configured to detect a vibration signal of the first housing; a second sensor, disposed on a mounting carrier of the compressor, wherein the second sensor is configured to detect a vibration signal of the mounting carrier; The driving portion is configured to adjust the stiffness of the support member according to a vibration signal of the first housing and a vibration signal of the mounting carrier.

8. The compressor according to claim 6, characterized in that The driving part comprises a driving motor, a power shaft end of the driving motor is connected to a threaded column, a moving part is arranged on the threaded column, and the moving part is configured to move along the telescopic direction of the supporting member to adjust the stiffness of the supporting member.

9. The compressor according to claim 8, characterized in that The supporting member is a spring, and the spring is sleeved on the outer circumference of the threaded column. The first end of the spring abuts against the moving part, and the second end of the spring abuts against the top wall of the second installation cavity.

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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