Compressor and air conditioner

Abstract

The compressor comprises a shell, a compression mechanism is arranged in the shell, and the compression mechanism comprises a bearing, an air inlet, an air outlet, an air inlet and an air outlet, the exhaust valve plate is arranged on the bearing, and the exhaust valve plate is configured to open or close the exhaust hole; the lift limiter is arranged on the bearing, and the lift limiter is configured to limit the displacement amount of the exhaust valve plate; the electromagnetic attraction part is arranged on the lift limiter, and the electromagnetic attraction part is configured to be electrified to attract the exhaust valve plate when the compression mechanism exhausts air; and the reset piece is arranged between the exhaust valve plate and the lift limiter, and the reset piece is configured to apply acting force to the exhaust valve plate to enable the exhaust valve plate to move in the direction close to the exhaust hole. According to the utility model, the exhaust valve plate can be normally opened at low frequency without vibration; therefore, 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 performs the cooling and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve and an evaporator. A compression mechanism is provided in the compressor, and the refrigerant is compressed by the compression mechanism. An exhaust hole is provided on the bearing of the compression mechanism, and an exhaust valve plate and a lift limiter are provided on the bearing. The exhaust valve plate is used to close or open the exhaust hole, and the lift limiter is used to limit the displacement of the valve plate.

[0003] In the related art, the opening of the exhaust valve is affected by the coupling of back pressure, airflow thrust and elastic force, and when closed, it only relies on the elastic force of the valve itself. The opening and closing of the valve is greatly affected by the working conditions, and it is difficult to achieve accurate opening and closing. It is easy to fail to open normally at low frequencies and close with delay at high frequencies, thus affecting 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 utility model proposes a compressor and an air conditioner, and improves the exhaust mechanism of the compressor so that the exhaust valve plate can open normally at low frequency without vibration; and close in time at high frequency, thereby improving the performance of the compressor.

[0006] In order to achieve the above-mentioned utility model purpose, the utility model adopts the following technical solutions:

[0007] In one aspect, a compressor is provided, comprising:

[0008] case;

[0009] A compression mechanism is disposed in the shell, and is configured to compress the refrigerant. The compression mechanism includes:

[0010] Bearings are provided with exhaust holes;

[0011] An exhaust valve plate, disposed on the bearing, and configured to open or close the exhaust hole;

[0012] a lift limiter, disposed on the bearing, the lift limiter being configured to limit the displacement of the exhaust valve plate;

[0013] An electromagnetic suction part, arranged on the lift limiter, the electromagnetic suction part is configured to be energized to attract the exhaust valve plate when the compression mechanism is exhausted;

[0014] A reset member is disposed between the exhaust valve plate and the lift limiter, and the reset member is configured to apply a force to the exhaust valve plate to move the exhaust valve plate toward the exhaust hole.

[0015] When the compressor needs to start exhausting, the electromagnetic suction part is energized, and the exhaust valve plate 720 is attracted by the electromagnetic suction part to realize the rapid opening of the exhaust valve plate, and the vibration can be avoided by the attraction during the opening process, thereby avoiding the pressure loss caused by the vibration of the exhaust valve plate. At this time, the reset member is squeezed and compressed.

[0016] Before the exhaust is completed, the electromagnetic suction part is powered off, and the elastic potential energy of the exhaust valve plate itself and the reset member is used to achieve rapid closing of the exhaust valve plate, avoiding the problem of delayed closing of the exhaust valve plate.

[0017] By reducing exhaust resistance losses and reducing high-pressure gas backflow, the capacity of the compressor can be significantly improved, thereby improving energy efficiency.

[0018] On the other hand, an air conditioner is provided. The air conditioner comprises a compressor, an evaporator, a condenser and a throttling device. The compressor is the compressor described above. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 is a structural diagram of a compressor according to some embodiments;

[0020] Figure 2A is a side view of a compressor according to some embodiments;

[0021] Figure 2B is a cross-sectional view of a compressor according to some embodiments;

[0022] Figure 3 is a top view of a compressor according to some embodiments;

[0023] Figure 4 is a structural diagram of a bracket according to some embodiments;

[0024] Figure 5 is another structural diagram of a stent according to some embodiments;

[0025] Figure 6 is another top view of a compressor according to some embodiments;

[0026] Figure 7 is another structural diagram of a stent according to some embodiments;

[0027] Figure 8 is a structural diagram of a bracket and a circumferential shell according to some embodiments;

[0028] Fig. 9 is a cross-sectional view of a gas-liquid separator according to some embodiments;

[0029] Fig.10 A structural diagram of a floating part after floating according to some embodiments;

[0030] Fig.11 A structural diagram of a floating portion after descending according to some embodiments;

[0031] Fig.12 is a structural diagram of a floating portion according to some embodiments;

[0032] Fig.13 is a structural diagram of a compressor body according to some embodiments;

[0033] Fig.14 is a structural diagram of an upper housing according to some embodiments;

[0034] Fig.15 is a cross-sectional view of a first housing according to some embodiments;

[0035] Fig.16A This is a partial enlarged view of the circle A in 15;

[0036] Fig. 16B This is a partial enlarged view of the circle B in 15;

[0037] Fig.17 is a cross-sectional view of an upper housing according to some embodiments;

[0038] Fig.18 is a structural diagram of a lower housing according to some embodiments;

[0039] Fig.19 A structural diagram of a lower shell and an adsorption portion according to some embodiments;

[0040] Fig. 20 is a structural diagram of an adsorption portion according to some embodiments;

[0041] Fig.21 is a cross-sectional view of a compression mechanism according to some embodiments;

[0042] Fig. 22 is a structural diagram of a third sub-muffler according to some embodiments;

[0043] Fig.23 is another structural diagram of a third sub-muffler according to some embodiments;

[0044] Fig.24 is a structural diagram of a fourth sub-muffler according to some embodiments;

[0045] Fig.25 An assembly diagram of an eccentric crankshaft, a second bearing, a second cylinder, and a second piston according to some embodiments;

[0046] Fig.26 A structural diagram of an exhaust valve plate and a lift limiter according to some embodiments;

[0047] Fig. 27 is another structural diagram of an exhaust valve plate and a lift limiter according to some embodiments;

[0048] Fig.28 is a structural diagram of an exhaust valve sheet according to some embodiments;

[0049] Fig.29 A structural diagram of a compressor body, an exhaust pipe, and a muffler according to some embodiments;

[0050] Fig.30 is a structural diagram of a muffler according to some embodiments;

[0051] Fig.31 is a structural diagram of an eccentric crankshaft according to some embodiments. DETAILED DESCRIPTION

[0052] Some embodiments of the present disclosure will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present disclosure, rather than all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments provided by the present disclosure are within the scope of protection of the present disclosure.

[0053] [Air conditioner]

[0054] In some embodiments, the air conditioner in the present application performs a cooling and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve and an evaporator. The cooling and heating cycle includes a series of processes involving compression, condensation, expansion and evaporation to cool or heat the indoor space.

[0055] The low-temperature and low-pressure refrigerant enters the compressor, which compresses it into high-temperature and high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the surrounding environment through the condensation process.

[0056] 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. In the entire cycle, the air conditioner can adjust the temperature of the indoor space.

[0057] The outdoor component of the air conditioner refers to a portion of a refrigeration cycle including a compressor and an outdoor heat exchanger, the indoor component of the air conditioner includes an indoor heat exchanger, and the expansion valve may be provided in the indoor component or the outdoor component.

[0058] The outdoor assembly 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.

[0059] Among them, the indoor heat exchanger and the outdoor heat exchanger are converted to serve as a condenser or an evaporator, generally using a four-way valve. Please refer to the settings of conventional air conditioners for details, which will not be elaborated here.

[0060] The refrigeration working principle of the air conditioner is: the operation of the compressor makes the indoor heat exchanger (in the indoor component, it is the evaporator at this time) 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, it is the condenser at this time), releasing heat, and dissipating the heat into the atmosphere through the outdoor fan. This cycle achieves the cooling effect.

[0061] The heating working principle of the air conditioner is as follows: the gaseous refrigerant is pressurized by the compressor, becomes a high-temperature and high-pressure 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 at the same time, thereby achieving the purpose of raising 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 vaporizes to absorb heat, becomes a gas, and absorbs heat from the outdoor air (the outdoor air becomes colder), becomes a gaseous refrigerant, and enters the compressor again to start the next cycle.

[0062] [Compressor body]

[0063] In some embodiments of the present disclosure, the compressor is a rolling rotor compressor. Figure 1 2 , the compressor includes a compressor body 1. The compressor body 1 includes a first shell 11, and a closed inner cavity is formed in the first shell 11, and a motor 13 and a compression mechanism 14 are arranged in the inner cavity. The motor 13 provides power for the compressor mechanism. The compression mechanism 14 is configured to compress the refrigerant. The motor 13 is arranged above the compression mechanism 14. Fig.21 It is a cross-sectional view of the compression mechanism 14.

[0064] In some embodiments, reference Fig.13 The first housing 11 includes an upper housing 410, a circumferential housing 430 and a lower housing 420. The circumferential housing 430 is disposed between the upper housing 410 and the lower housing 420. The upper housing 410 is disposed at the top of the circumferential housing 430, and the lower housing 420 is disposed at the bottom of the circumferential housing 430. The upper housing 410, the circumferential housing 430 and the lower housing 420 surround the inner cavity of the compressor body 1.

[0065] In some embodiments, the motor 13 includes a stator and a rotor, and the stator is fixedly connected to the inner wall of the first housing 11 to achieve fixed installation of the motor 13 in the inner cavity of the compressor.

[0066] In some embodiments, reference Fig.21 The compression mechanism 14 includes an eccentric crankshaft 110, a cylinder, a piston, a bearing, a muffler, etc.

[0067] In some embodiments, reference Fig.31 The eccentric crankshaft 110 includes a first shaft section 111 (upper shaft section), an eccentric shaft section and a second shaft section 115 (lower shaft section), the first shaft section 111 is fixedly connected to the rotor; a piston is arranged in the compression chamber of the cylinder, and the piston is sleeved on the eccentric shaft section; the bearing is fixedly connected to the cylinder, and a bearing exhaust hole is arranged on the bearing, and the bearing exhaust hole is communicated with the compression chamber; a vane groove is arranged on the cylinder, and a vane is arranged in the vane groove, the eccentric crankshaft 110 drives the piston to make circumferential motion in the compression chamber, and the vane reciprocates along the vane groove, and the vane always abuts against the piston, and the vane and the piston separate the compression chamber into a high-pressure chamber and a low-pressure chamber.

[0068] The working principle of the compressor is as follows: the stator of the motor 13 generates a magnetic pull after being energized, and the rotor of the motor 13 rotates under the action of the magnetic pull of the stator, and drives the eccentric crankshaft 110 to rotate together. The rotation of the eccentric crankshaft 110 drives the piston sleeved on its eccentric shaft segment to perform eccentric circular motion in the compression chamber of the cylinder, and the vane reciprocates in the vane groove. The vane and the piston divide the compression chamber of the cylinder into a high-pressure chamber and a low-pressure chamber. The eccentric crankshaft 110 drives the piston to rotate one circle, sucking air from the low-pressure chamber and exhausting air from the high-pressure chamber to complete one exhaust, thereby realizing the compression of the gas by the compressor, and the compressed gas is discharged through the bearing exhaust hole.

[0069] In some disclosed embodiments, the compressor is a twin-cylinder rolling rotor compressor, referring to Fig.21The compression mechanism 14 specifically includes an eccentric crankshaft 110, two cylinders (respectively a first cylinder 122 (upper cylinder) and a second cylinder 121 (lower cylinder)), two bearings (respectively a first bearing 152 (upper bearing) and a second bearing 151 (lower bearing)), two pistons (respectively a first piston 132 (upper piston) and a second piston 131 (lower piston)), a middle partition 160, and two mufflers (divided into a first sub-muffler 142 (upper muffler) and a second sub-muffler 141 (lower muffler)).

[0070] In some embodiments, reference Fig.31 The eccentric crankshaft 110 includes, from top to bottom, a first shaft section 111, a first eccentric shaft section 112 (upper eccentric shaft section), a connecting shaft section 113, a second eccentric shaft section 114 (lower eccentric shaft section) and a second shaft section 115.

[0071] In some embodiments, a first piston 132 capable of eccentric movement is provided in the compression chamber of the first cylinder 122, and the first piston 132 is sleeved on the first eccentric shaft segment 112; a second piston 131 capable of eccentric movement is provided in the compression chamber of the second cylinder 121, and the second piston 131 is sleeved on the second eccentric shaft segment 114; a middle partition plate 160 is sleeved on the connecting shaft segment 113, and the middle partition plate 160 is located between the first cylinder 122 and the second cylinder 121; a first bearing 152 is sleeved on the first shaft segment 111 and is connected to the first cylinder 122 at the same time; the second bearing 151 is sleeved on the second shaft segment 115 and is connected to the second cylinder 121 at the same time.

[0072] The first eccentric shaft segment 112 and the second eccentric shaft segment 114 are arranged at a relative angle of 180°, the first piston 132 and the second piston 131 rotate eccentrically at the same time, the compressed gas in the compression chamber of the first cylinder 122 is discharged through the exhaust hole on the first bearing 152, and the compressed gas in the compression chamber of the second cylinder 121 is discharged through the exhaust hole on the second bearing 151.

[0073] Continue to refer to Fig.21 A first sub-muffler 142 is arranged on the first bearing 152, and the first sub-muffler 142 covers the exhaust hole of the first bearing 152. The compressed gas in the first cylinder 122 is first discharged through the exhaust hole of the first bearing 152 to the space surrounded by the first sub-muffler 142 and the first bearing 152, and then discharged through the exhaust hole of the first sub-muffler 142 to the inner cavity of the compressor.

[0074] The second sub-muffler 141 is disposed on the second bearing 151 , and covers the exhaust hole of the second bearing 151 . The compressed gas in the second cylinder 121 is first discharged into the space enclosed by the second sub-muffler 141 and the second bearing 151 through the exhaust hole on the second bearing 151 .

[0075] In some embodiments, different from the related art, Fig.21 There is no exhaust hole on the second sub-muffler 141. A plurality of airflow channels 170 are provided on the wall of the first bearing 152, the first cylinder 122, the middle partition 160, the second cylinder 121 and the second bearing 151. The compressed air in the second bearing 151 and the second sub-muffler 141 is discharged upward through the airflow channel 170 to the space surrounded by the first bearing 152 and the first sub-muffler 142, and then discharged through the exhaust hole of the first sub-muffler 142 to the inner cavity of the compressor.

[0076] [Exhaust valve]

[0077] In the related art, the opening of the exhaust valve is affected by the coupling of the back pressure, airflow thrust and elastic force, and when closed, it only relies on the elastic force of the valve itself. The opening and closing of the valve is greatly affected by the working conditions, and it is impossible to achieve accurate opening and closing. It is easy to have problems such as failure to open normally at low frequencies and delayed closing at high frequencies, thereby affecting the performance of the compressor. In some embodiments, the exhaust mechanism of the compressor is improved so that the exhaust valve can open normally at low frequencies without vibration, and close in time at high frequencies, thereby improving the performance of the compressor.

[0078] In some embodiments, an exhaust hole is provided on the bearing. An exhaust valve plate 720 is provided on the bearing, and the exhaust valve plate 720 is configured to open or close the exhaust hole. A lift limiter 710 is provided on the bearing, and the lift limiter 710 is configured to limit the displacement of the exhaust valve plate 720.

[0079] Reference Figure 26 to Figure 28 An electromagnetic suction portion 730 is provided on the lift limiter 710 , and the electromagnetic suction portion 730 is configured to be energized to attract the exhaust valve plate 720 when the compression mechanism 14 is exhausted.

[0080] A reset member 740 , such as a spring, is disposed between the exhaust valve plate 720 and the lift limiter 710 . The reset member 740 is configured to apply a force to the exhaust valve plate 720 to move the exhaust valve plate 720 toward the exhaust hole.

[0081] When the compressor needs to start exhausting, the electromagnetic suction part 730 is energized, and the exhaust valve plate 720 is attracted by the electromagnetic suction part 730 to realize the rapid opening of the exhaust valve plate 720, and the exhaust valve plate 720 can be prevented from vibrating due to the attraction during the opening process, thereby avoiding the pressure loss caused by the vibration of the exhaust valve plate 720. At this time, the reset member 740 is squeezed and compressed.

[0082] Before exhaustion is completed, the electromagnetic suction part 730 is powered off, and the exhaust valve plate 720 itself and the elastic potential energy of the reset member 740 are used to achieve rapid closing of the exhaust valve plate 720, thereby avoiding the problem of delayed closing of the exhaust valve plate 720.

[0083] By reducing exhaust resistance losses and reducing high-pressure gas backflow, the capacity of the compressor can be significantly improved, thereby improving energy efficiency.

[0084] In some embodiments, reference Fig.26 and Fig.28 The exhaust valve plate 720 includes a valve plate head 721, a valve plate tail 722, and a connecting section 723, wherein the connecting section 723 is connected between the valve plate head 721 and the valve plate tail 722. The valve plate tail 722 is connected to the bearing, and the valve plate head 721 is configured to open or close the exhaust hole. The electromagnetic suction part 730 is directly opposite to the valve plate head 721, so as to improve the attraction of the electromagnetic suction part 730 to the valve plate head 721.

[0085] In some embodiments, the reset member 740 is disposed between the valve plate head 721 and the lift limiter 710 , so that the reset member 740 can apply a more reliable reset force to the valve plate head 721 .

[0086] In some embodiments, reference Fig. 27 , the effective length of the exhaust valve plate 720 is L1, the lift height of the exhaust valve plate 720 is H9, the curvature radius of the exhaust valve plate 720 is R12, the thickness of the exhaust valve plate 720 is t1, L1, R12, t1 and H9 satisfy the relationship: 1.5<(L1 / R12)×t1+H9<3.0.

[0087] The starting point of the effective length of the exhaust valve plate 720 is the tangent point between the valve plate and the lift limiter 710 , and the ending point is the center of the valve plate head 721 .

[0088] The present disclosure determines the airflow thrust of the exhaust valve plate 720 under high frequency operation through theoretical calculation, and uses this as the design boundary. In the finite element simulation of CAE, the height H, effective length L, curvature radius R, and valve thickness T of the exhaust valve plate 720 are designed through multi-objective design. After multiple iterations, combined with the exhaust valve plate 720SN curve, it is determined that when 1.5<(L1 / R12)×t1+H9<3.0, the head stress of the exhaust valve plate 720 is within the permitted range. In theory, the exhaust valve plate 720 can be used unlimitedly. Although the stress of the exhaust valve plate 720 also meets the requirements when the value of the relationship (L1 / R12)×t1+H9 is below 1.5, when its value is lower, the effective flow area is lower, which will seriously affect the performance of the compressor. Therefore, in summary, when the relationship satisfies 1.5<(L1 / R12)×t1+H9<3.0, while ensuring the service life of the exhaust valve plate 720, it is also beneficial to realize the accurate opening and closing of the exhaust valve plate 720.

[0089] In some embodiments, reference Fig.28The diameter of the valve plate head 721 is D11, the diameter of the exhaust hole is D12, and D11 and D12 satisfy the relationship: 0.7<D11 / D12<0.8, which is conducive to meeting the reliability of the exhaust valve plate 720.

[0090] In some embodiments, the inner diameter of the cylinder is D13, and D12 and D13 satisfy the relationship: 0.2<D12 / D13<0.3.

[0091] It should be noted that the size of the cylinder, cylinder diameter and exhaust hole will significantly affect the airflow velocity. If the airflow velocity is too high, it will also cause a large impact on the exhaust valve plate 720. When the relationship satisfies 0.2<D12 / D13<0.3, the impact force on the exhaust valve plate 720 can be reduced as much as possible while satisfying the premise of low pressure loss.

[0092] In some embodiments, reference Fig.26 A copper wire is arranged on the side of the lift limiter 710 away from the exhaust valve plate 720, and the copper wire is connected to the controller. The copper wire is energized to form an electromagnetic suction part 730, which has a simple structure and is easy to implement.

[0093] In some embodiments, the electromagnetic suction part 730 is disposed on the lift limiter 710 , and is configured to be energized to attract the exhaust valve plate 720 when the compression mechanism 14 is exhausting, and is configured to be de-energized when the compression mechanism 14 is not exhausting.

[0094] The reset member 740 is disposed between the exhaust valve plate 720 and the lift limiter 710. The reset member 740 is configured to contract when the electromagnetic suction part 730 attracts the exhaust valve plate 720. The reset member 740 is configured to apply a force to the exhaust valve plate 720 to move the exhaust valve plate 720 toward the exhaust hole.

[0095] [Gas-Liquid Separator]

[0096] In some embodiments, reference Figure 1 The compressor further includes a gas-liquid separator 2. The gas-liquid separator 2 is disposed outside the compressor body 1 and is configured to provide gaseous refrigerant to the compression chamber of the compression mechanism 14. The gas-liquid separator 2 separates the liquid refrigerant from the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 1 and causing compressor abnormality.

[0097] In some embodiments, reference Figure 1 and Fig. 9 The gas-liquid separator 2 includes a second shell 21, and an air outlet pipe 22 is arranged at the bottom of the second shell 21. One end of the air outlet pipe 22 extends into the inner cavity of the second shell 21, and the other end of the air outlet pipe 22 is connected to the compression mechanism 14 to provide gaseous refrigerant to the compression mechanism 14.

[0098] [Connection structure between compressor body and gas-liquid separator]

[0099] At present, the gas-liquid separator 2 is fixedly installed on the outside of the compressor body 1 through a bracket 200. When the compressor is running, the compressor body 1 and the gas-liquid separator 2 are prone to low-frequency resonance and low-frequency noise. Therefore, it is necessary to increase the natural frequency of the upper part of the gas-liquid separator 2 to avoid low-frequency resonance when the compressor body 1 and the gas-liquid separator 2 are running. In the related art, the natural frequency of the gas-liquid separator 2 is low, which makes it easy to generate low-frequency noise when the compressor is running.

[0100] In order to solve the above problems, some embodiments of the present disclosure improve the connection structure between the gas-liquid separator 2 and the compressor body 1 to achieve the effect of increasing the natural frequency of the gas-liquid separator 2 and avoiding low-frequency noise generated when the compressor is running.

[0101] This embodiment provides two connection structures between the gas-liquid separator 2 and the compressor body 1, which are described below respectively.

[0102] [Connection structure between compressor body and gas-liquid separator]

[0103] In some embodiments, reference Figures 3 to 5 The compressor includes two symmetrically arranged brackets 200 , and the two brackets 200 are configured to connect the first shell 11 and the second shell 21 .

[0104] Any of the two brackets 200 includes a bracket part 210, a bracket part 220, a bracket part 3 230 and a bracket part 4 240 connected in sequence. The bracket part 1 210 and the bracket part 3 230 are located on the same side of the bracket part 220, and the bracket part 220 and the bracket part 4 240 are located on different sides of the bracket part 3 230. The bracket part 220 is adapted to the outer contour of the second shell 21 and is fixedly connected, such as by welding. The bracket part 1 210 and the bracket part 3 230 extend between the first shell 11 and the second shell 21, respectively. The bracket part 1 210 and the bracket part 4 240 are fixedly connected to the first shell 11, such as by welding. The length of the bracket part 210 is greater than the length of the bracket part 3 230, and the two bracket parts 4 240 are close to each other.

[0105] For each bracket 200, by welding the first bracket part 210 and the fourth bracket part 240 to the first shell 11, two fixations with the first shell 11 are achieved. Then, when two brackets 200 are used together, there are four fixations on the first shell 11, which improves the connection stability between the bracket 200 and the first shell 11.

[0106] For example, when two brackets 200 are used together, the two bracket second parts 220 together clamp the gas-liquid separator 2 to improve the connection stability between the bracket 200 and the second shell 21 .

[0107] In some embodiments, reference Figure 5 An opening is provided on the bracket portion 210, namely, the first opening 250, and the first opening 250 extends along the length direction of the bracket portion 210. The width of the first opening 250 is H, and the length of the first opening 250 is L, and H / L=(0, 0.82].

[0108] By changing the size of the first opening 250 , the connection stiffness of the gas-liquid separator 2 can be changed, which is beneficial for obtaining the required natural frequency.

[0109] In some embodiments, reference Figure 3 and Figure 4 The width of the second bracket part 220 is W3, the outer contour radius of the second shell 21 is R2, and the range of W3 / R2 is [1.4, 2.2]. Within this range, it is helpful to improve the natural frequency of the gas-liquid separator 2.

[0110] In some embodiments, reference Figure 3 The radius of the arc structure where the second bracket part 220 is located is R3, the outer contour radius of the second shell 21 is R2, and R3-R2=[0.5mm, 2mm]. Within this range, it is convenient to realize the welding installation positioning between the two.

[0111] In some embodiments, reference Figure 3 The arc angle α of the second part 220 of the bracket is greater than 39°, which helps to improve the clamping reliability of the bracket 200 on the gas-liquid separator 2.

[0112] In some embodiments, reference Figure 3 , the distance from the intersection of the first bracket 210 and the second bracket 220 to the symmetry plane of the two brackets 200 is W1, the distance from the third bracket 230 to the symmetry plane of the two brackets 200 is W2, the outer contour radius of the second shell 21 is R2, the outer contour radius of the first shell 11 is R1, (W1 / R2)×(W2 / R1)>0.3. Within the above range, the double torsional frequency of the gas-liquid separator 2 tends to be stable, and the fixed frequency is increased to above 510Hz, which is suitable for a two-cylinder compressor with a maximum speed of 180 rps.

[0113] In some embodiments, reference Figure 3 and Figure 4The bracket part 210 includes a bracket part one section 211 and a bracket part two section 212 of an integrated structure. The bracket part one section 211 extends obliquely outward from a first end of the bracket part two section 212. The bracket part one section 211 is adapted and fixedly connected to the first shell 11, and the second end of the bracket part two section 212 is intersected and connected to the bracket part two 220.

[0114] An angle β between the second end of the bracket first section 212 and the end of the bracket first section 211 and the bracket first section 212 is 2°.

[0115] In some embodiments, the number of welding points between the first part 210 of the bracket and the first shell 11 is greater than 2, for example 4, and the number of welding points between the fourth part 240 of the bracket and the first shell 11 is also greater than 2, for example 4. In this way, the connection reliability between the first part 210 and the first shell 11 and the connection reliability between the fourth part 240 of the bracket and the first shell 11 can be improved.

[0116] In some embodiments, reference Figure 2A , the height of the compressor body 1 is H1, specifically the distance between the bottom of the lower shell 420 and the top of the exhaust pipe 12. The height of the bracket 200 from the bottom of the compressor body 1 (referring to the bottom of the lower shell 420) is H2, H2 / H1=[0.49, 0.71]. Within this range, it is helpful to reduce the radial vibration of the gas-liquid separator 2 and reduce the noise of the compressor.

[0117] In some embodiments, reference Figure 3 The distance between the connection positions of the two bracket parts 210 and the first shell 11 is D2, the outer diameter of the first shell 11 is D1, and D2 / D1=[0.06, 0.9]. Within this range, it is helpful to reduce the radial vibration of the gas-liquid separator 2 and the noise of the compressor.

[0118] [Connection structure between compressor body and gas-liquid separator]

[0119] In some embodiments, reference Figure 6 and Figure 7 The compressor includes a bracket 200 configured to connect the first shell 11 and the second shell 21 .

[0120] The bracket 200 includes a bracket main body 260, and bracket extensions 270 are symmetrically arranged at opposite ends of the bracket main body 260. The bracket main body 260 is adapted to and fixedly connected to the outer contour of the first shell 11, such as by welding. The bracket extension 270 is an integral structure including an extension section 1 271 and an extension section 272. The extension section 1 271 is connected between the bracket main body 260 and the extension section 272. The extension section 272 is fixedly connected to the outer contour of the second shell 21, such as by welding.

[0121] For example, refer to Figure 6 The outer contour radius of the first shell 11 is R1, the outer contour radius of the second shell 21 is R2, the distance between the extension section 271 and the symmetry plane of the bracket 200 is W4, 2W4 / (R1+R2)=[0.35, 0.55]. Within this range, it is helpful to reduce the vibration of the gas-liquid separator 2.

[0122] In some embodiments, reference Figure 7 The distance between the welding point 280 between the bracket main body 260 and the first shell 11 and the symmetry plane of the bracket 200 is W5, W5 / W4>0.75. The larger the W5 / W4, the better. When it is greater than 0.75, the vibration enhancement amplitude of the gas-liquid separator 2 is not obvious.

[0123] In some embodiments, reference Figure 7 The second extension section 272 is welded to the second shell 21 , and the distance between two adjacent welding points 280 along the height direction of the second extension section 272 is H3 , and the height of the second extension section 272 is H4 , H3 / H4 = [0.75, 0.85].

[0124] Two welding holes 290 are set on each extension section 272, and the distance between two adjacent welding holes 290 is equal to the distance between two welding points 280, which is also H3. It should be noted that the distance between two adjacent welding holes 290 also meets the above range setting, which helps to reduce the vibration of the gas-liquid separator 2.

[0125] In some embodiments, reference Figure 7 The height of the bracket body 260 is H4, referring to Figure 8 The distance between the support body 260 and the gas outlet pipe 22 of the gas-liquid separator 2 is H5, H4 / H5=[0.2, 0.35]. Within this range, it is helpful to reduce the vibration of the gas-liquid separator 2.

[0126] In some embodiments, reference Figure 6 The angle θ of the vertical line between the two extension sections 272 and the axis of the second shell 21 is in the range of [90°, 140°]. This range helps to reduce the vibration of the gas-liquid separator 2 and increase the torsional frequency of the gas-liquid separator 2.

[0127] In some embodiments, reference Figure 2A A foot 15 is provided on the side of the first shell 11, the radius of the foot 15 is R8, the outer contour radius of the first shell 11 is R9, R8 / R9>0.15, within this range, the compressor body 1 has better stability and lower vibration.

[0128] In some embodiments, reference Figure 2A, the height of the first housing 11 is H1. The distance between the motor 13 and the top of the first housing 11 is H15, H15 / H1=[0.25-0.35].

[0129] There is a certain cavity volume between the upper part of the motor 13 and the upper shell 410. The larger the cavity, the more conducive it is to improving the oil separation effect and reducing the oil discharge rate. Since the cavity volume is also related to the noise level of the compressor, setting the above range helps to reduce the noise of the compressor.

[0130] [Gas outlet pipe of gas-liquid separator]

[0131] In some embodiments, the liquid is stored at the bottom of the gas-liquid separator 2, and an oil return hole 2201 is provided on the gas outlet pipe 22 of the gas-liquid separator 2. When the suction of the compressor body 1 is overheated, the separated liquid is refrigeration oil, and the oil return hole 2201 needs to be as large as possible so that the refrigeration oil can quickly flow back to the compressor body 1 through the oil return hole 2201. When the compressor body 1 is not overheated, the separated liquid is liquid refrigerant. At this time, in order to reduce the rate at which the liquid refrigerant enters the compressor body 1 through the oil return hole 2201, a smaller oil return hole 2201 is required.

[0132] In the related art, the size of the oil return hole 2201 is fixed and cannot be adjusted according to the working condition of the compressor body 1, and cannot balance the acceleration of the refrigeration oil return when overheating and the reduction of the liquid refrigerant return when there is no overheating.

[0133] In some embodiments, the outlet pipe 22 is improved to accelerate the return of the refrigeration oil and reduce the rate at which the liquid refrigerant enters the compressor body 1, thereby improving the efficiency of the compressor.

[0134] For example, refer to Figures 9 to 12 The outlet pipe 22 is provided with a plurality of oil return holes 2201 on the pipe section in the cavity, and the plurality of oil return holes 2201 are arranged at intervals along the height direction of the outlet pipe 22. For example, the outlet pipe 22 is provided with two oil return holes 2201 arranged at intervals in the upper and lower parts.

[0135] The gas-liquid separator 2 includes a floating part 300 , which is sleeved on the gas outlet pipe 22 . The floating part 300 is located in the cavity, and the floating part 300 is configured to move along the height direction of the gas outlet pipe 22 .

[0136] In some embodiments, reference Fig.11 When the compressor suction air is overheated, the floating part 300 drops to the first position, at which time the multiple oil return holes 2201 are in an open state, thereby increasing the oil return rate.

[0137] Reference Fig.10When the compressor inhales air without overheating, the liquid level inside the gas-liquid separator 2 will rise rapidly, and the floating part 300 will float to the second position under the buoyancy of the liquid in the cavity, and part of the oil return hole 2201 will be blocked, reducing the rate at which the liquid refrigerant flows into the compressor body 1 to prevent liquid hammer.

[0138] Taking two oil return holes 2201 as an example, when the floating part 300 descends to the first position, the two oil return holes 2201 are both in an open state. When the floating part 300 floats to the second position, the floating part 300 blocks the oil return hole 2201 located above, and the oil return hole 2201 located below is open.

[0139] In some embodiments, reference Fig. 9 and Fig.12 The floating part 300 includes a floating main body 310, which is sleeved on the outlet pipe 22, and a gap 350 for liquid to flow is provided between the floating main body 310 and the outlet pipe 22. An opening is provided on the floating main body 310, which is a second opening 340, and the second opening 340 is connected to the gap 350. The liquid enters the gap 350 through the second opening 340 and then flows out through the oil return hole 2201.

[0140] The cooperation between the second opening 340 and the gap 350 ensures that when the floating part 300 rotates along the air outlet pipe 22 , the liquid can still flow out smoothly along the oil return hole 2201 .

[0141] The bottom of the floating main body 310 is provided with a folding portion 320, which is folded toward the inside of the floating main body 310 and sleeved on the air outlet pipe 22. The gap between the folding portion 320 and the air outlet pipe 22 is small, and the gap between the two is matched, which does not affect the up and down movement of the floating part 300 along the air outlet pipe 22, and when the folding portion 320 is directly opposite to the oil return hole 2201, the folding portion 320 plays a role in blocking the oil return hole 2201.

[0142] The folding portion 320 is configured to block part of the oil return hole 2201 when the floating portion 300 is in the second position. In other words, taking two oil return holes 2201 as an example, when the floating portion 300 floats up to the second position, the folding portion 320 is directly opposite to the oil return hole 2201 located above, and the folding portion 320 blocks the oil return hole 2201 above.

[0143] The folding portion 320 is also configured to move away from the oil return hole 2201 when the floating portion 300 is in the first position so that the oil return hole 2201 is open. In other words, taking two oil return holes 2201 as an example, when the floating portion 300 descends to the first position, the folding portion 320 is staggered from the oil return hole 2201 so that all the oil return holes 2201 are in an open state.

[0144] In some embodiments, the floating body 310 and the folding portion 320 are integrally formed, and the floating body 310 and the folding portion 320 are connected in an arc transition. A step portion 2202 is provided on the air outlet pipe 22, and the step portion 2202 is configured to limit the descending position of the floating portion 300.

[0145] The step portion 2202 on the gas outlet pipe 22 limits the downward displacement of the floating portion 300 , thereby preventing the floating portion 300 from hitting the bottom wall of the gas-liquid separator 2 .

[0146] In some embodiments, the second opening 340 extends along the height direction of the floating body 310 to improve the smoothness of liquid flow and reduce liquid flow resistance.

[0147] In some embodiments, a plurality of second openings 340 are disposed on the floating main body 310 , and the plurality of second openings 340 are arranged at intervals to further increase the total area of ​​the second openings 340 , thereby facilitating liquid circulation.

[0148] In a specific embodiment, two second openings 340 are disposed on the floating body 310 .

[0149] In some embodiments, reference Fig. 9 A fixing part 23 is arranged in the cavity of the gas-liquid separator, and the gas outlet pipe 22 passes through the fixing part 23. A mounting hole for mounting the gas outlet pipe 22 is arranged on the fixing part 23. The fixing part 23 is also provided with a plurality of through holes for gas and liquid to flow.

[0150] The floating part 300 is located below the fixed part 23, and the fixed part 23 is configured to limit the floating position of the floating part 300. In other words, when the floating part 300 moves upward to abut against the fixed part 23, the upward movement stops.

[0151] The floating part 300 is limited by the existing fixing part 23 inside the gas-liquid separator 2, and no additional limiting structure is required.

[0152] In some embodiments, reference Fig.12 The top of the floating part 300 is provided with a flange part 330, and the flange part 330 extends toward the outer peripheral side of the floating part 300. The flange part 330 is configured to abut against the fixing part 23 to limit the floating position of the floating part 300.

[0153] The provision of the flange portion 330 increases the contact area with the fixing portion 23 and reduces the stress on the fixing portion 23 .

[0154] In some embodiments, two oil return holes 2201 are provided on the air outlet pipe 22 , and the two oil return holes 2201 are arranged at intervals along the height direction of the air outlet pipe 22 .

[0155] When the floating portion 300 descends to the first position, the two oil return holes 2201 are both in an open state.

[0156] When the floating portion 300 floats up to the second position, the folding portion 320 faces the oil return hole 2201 located above, thereby blocking the oil return hole 2201 .

[0157] In some embodiments, the compressor body 1 is a double-cylinder rotary type, and the gas-liquid separator 2 includes two outlet pipes 22, each of which is provided with a floating portion 300. The two outlet pipes 22 are respectively provided corresponding to the two cylinders in the compression mechanism 14 to provide gaseous refrigerant to the corresponding cylinder cavities.

[0158] [Compressor housing]

[0159] The gaseous refrigerant compressed and discharged by the compression mechanism 14 flows into the space between the motor 13 and the upper shell, and then is discharged through the exhaust pipe 12.

[0160] In some embodiments, the upper shell 410 is improved to reduce vibration and noise, reduce oil discharge rate, increase oil supply, and improve fatigue strength.

[0161] In some embodiments, due to the small space between the motor 13 and the upper shell 410, the oil discharge rate is not favorable. In addition, when the gaseous refrigerant flows to the upper space through the motor 13, it forms a certain impact on the upper shell 410, which easily causes the airflow to resonate with the upper shell 410 and increase the compressor noise.

[0162] In some embodiments, reference Figures 13 to 17 The upper shell 410 is disposed on the top of the circumferential shell 430. The upper shell 410 includes a circumferential wall and an arc-shaped top wall, which are respectively denoted as an upper circumferential wall 412 and an upper arc-shaped top wall 411. The upper arc-shaped top wall 411 is disposed on the top of the upper circumferential wall 412, and the upper circumferential wall 412 is connected to the circumferential shell 430.

[0163] In some embodiments, the upper arc-shaped top wall 411 is formed by sequentially connecting a plurality of first arc-shaped top walls 41101 and a plurality of second arc-shaped top walls 41102 , and the plurality of first arc-shaped top walls 41101 and the plurality of second arc-shaped top walls 41102 are alternately arranged along the circumference of the upper arc-shaped top wall 411 .

[0164] It should be noted that the radius of the circle on which the first arc-shaped top wall 41101 is located is greater than the radius of the circle on which the second arc-shaped top wall 41102 is located, and a platform portion for mounting components is provided on the first arc-shaped top wall 41101 .

[0165] In some embodiments, the setting of the upper arc-shaped top wall 411 makes the upper shell 410 have a hemispherical structure, which helps to increase the resonance frequency, avoid resonance between the airflow frequency of the pump body and the upper shell 410, and improve the vibration reduction and noise reduction effect; at the same time, the cavity volume is increased, which is beneficial to the oil discharge rate design; in addition, it also helps to improve the fatigue strength of the upper shell 410.

[0166] It should be noted that the upper arc-shaped top wall 411 is composed of the staggered arrangement of the first arc-shaped top wall 41101 and the second arc-shaped top wall 41102, and the radii of the two are different. In this way, the volume of the cavity can be increased, and a height difference is formed between the first arc-shaped top wall 41101 and the second arc-shaped top wall 41102. When installing devices on the first arc-shaped top wall 41101, the second arc-shaped top wall 41102 in a lower position can avoid it.

[0167] The design platform part is used to install components, such as a junction box 18, a temperature sensor 117, welding electrodes, a hook, etc., to facilitate the installation of the components.

[0168] In some embodiments, reference Fig.17 The radius of the upper circumferential wall 412 is R4, the radius of the circle on which the second arc-shaped top wall 41102 is located is R5, the height of the upper shell 410 is H6, and H6 / (R4×R5)>0.01. Within this range, it is beneficial to reduce the resonance phenomenon.

[0169] In some embodiments, the upper shell 410 generally needs to be provided with components such as a junction box 18 and a temperature sensor 117 , so a mounting platform needs to be provided on the upper shell 410 . The provision of the mounting platform will reduce the space between the motor 13 and the upper shell 410 .

[0170] In some embodiments, reference Fig.13 and Fig.14 A first platform portion 413 is provided on the first arc-shaped top wall 41101, and the first platform portion 413 is configured to install a junction box 18. A portion of the bottom surface of the junction box 18 contacts the first platform portion 413, and the other portion has no contact with the adjacent second arc-shaped top wall 41102. The low-positioned second arc-shaped top wall 41102 avoids the junction box 18, thereby facilitating the installation of the junction box 18.

[0171] In some embodiments, reference Fig.17 A first mounting hole 417 is provided on the first platform portion 413, and the wiring terminal 1801 of the junction box 18 is provided in the first mounting hole 417. The matching clearance range between the wiring terminal 1801 and the first mounting hole 417 is [0.1mm, 0.8mm]. This helps to improve the installation reliability of the wiring terminal 1801.

[0172] In some embodiments, a second platform portion 414 is disposed on the first arc-shaped top wall 41101 , and the second platform portion 414 is configured to install a hoisting portion 20 , and the hoisting portion 20 is configured to be used for hoisting when the compressor body 1 is circulated on a production line.

[0173] The matching area between the second platform portion 414 and the hanging portion 20 is greater than 766 mm 2 This range helps to improve the installation structural strength of the hoisting part 20, thereby improving the hoisting reliability of the compressor body 1.

[0174] In some embodiments, reference Fig.13 The first arc-shaped top wall 41101 is provided with a third platform portion 415, and a connecting member 19 is provided on the third platform portion 415, and the connecting member 19 is provided at an angle. An inclined limiting cavity is formed between the connecting member 19 and the third platform portion 415, and the limiting cavity is configured to install the temperature sensor 117.

[0175] The temperature sensor 117 is installed and limited by the connecting piece 19. The connecting piece 19 is arranged obliquely to facilitate the inclined insertion of the temperature sensor 117 from top to bottom and prevent the temperature sensor 117 from falling out.

[0176] In some embodiments, a second mounting hole 418 is disposed at the top of the upper arc-shaped top wall 411, and the exhaust pipe 12 passes through the second mounting hole 418. A fourth platform portion 416 is disposed on the upper arc-shaped top wall 411, and the fourth platform portion 416 is disposed around the second mounting hole 418. The fourth platform portion 416 is configured to cooperate with a welding electrode used when installing the exhaust pipe 12, so as to facilitate the welding operation of the exhaust pipe 12.

[0177] In some embodiments, reference Fig.15 and Fig.16A The upper peripheral wall 412 includes a first upper peripheral wall section 41201 and a second upper peripheral wall section 41202. The first upper peripheral wall section 41201 is located at the lower part of the second upper peripheral wall section 41202. The thickness of the first upper peripheral wall section 41201 is less than the thickness of the second upper peripheral wall section 41202. A step is formed between the first upper peripheral wall section 41201 and the second upper peripheral wall section 41202.

[0178] The upper circumferential wall section 41201 is inserted into the top of the circumferential shell 430, and the height of the upper circumferential wall section 41201 is E1, for example, E1 can be 12±0.2 mm, which helps to ensure the plug-in reliability between the upper shell 410 and the circumferential shell 430. The lower part of the upper circumferential wall section 41201 is an inclined wall, which is easy to insert into the circumferential shell 430.

[0179] In some embodiments, the upper end of the eccentric crankshaft 110 passes through the motor 13, and the distance between the bottom end of the exhaust pipe 12 and the top end of the crankshaft is in the range of [5, 20] mm. This position is a low-pressure area, the oil baffle rotates with the eccentric crankshaft 110, and the oil is thrown onto the shell wall. The exhaust pipe 12 extends to this position range to prevent the oil discharge rate design.

[0180] [Oil pool adsorption part of the compressor body]

[0181] In some embodiments, when the compressor is running, each friction pair will produce wear iron chips. If the iron chips are not effectively controlled, it will cause three-body wear of the friction pair, reduce the performance of the compressor, and cause damage to the compressor. Generally, a magnet is set in the oil pool at the bottom of the compressor to adsorb the iron chips to the magnet. However, the larger the outer diameter of the magnet, the higher the cost; and the smaller the outer diameter of the magnet, the lower the magnet adsorption rate and the poorer the iron chip adsorption effect.

[0182] In addition, the magnets are arranged on the bottom shell of the compressor. Usually, the space volume between the bottom shell and the compression mechanism 14 is small, resulting in limited oil pool volume, which is not conducive to oil supply design. The lower shell is easy to resonate with the airflow, increasing the noise of the compressor.

[0183] This embodiment improves the magnets in the compressor bottom shell and the oil pool to achieve the effects of increasing the iron filings adsorption rate, reducing costs, reducing vibration and noise, and increasing oil supply.

[0184] In some embodiments, reference Fig.15 , Figures 18 to 20 The housing includes a circumferential housing 430 and a lower housing 420. The lower housing 420 is disposed at the bottom of the circumferential housing 430. The lower housing 420 includes a circumferential wall and an arc-shaped bottom wall 621, which are respectively referred to as a lower circumferential wall 422 and a lower arc-shaped bottom wall 421. The lower arc-shaped bottom wall 421 is disposed at the bottom of the lower circumferential wall 422, the lower circumferential wall 422 is connected to the circumferential housing 430, and a flat surface 423 is disposed at the bottom of the lower arc-shaped bottom wall 421.

[0185] The setting of the lower arc bottom wall 421 makes the lower shell 420 have a hemispherical structure, which increases the resonance frequency and avoids the resonance between the pump body airflow frequency and the lower shell 420; at the same time, the cavity volume increases, and the bottom oil pool volume increases, which is beneficial to the oil supply design.

[0186] The lower shell 420 is spherical in design to reduce the plane area. The smaller the area, the higher the oil pressure reciprocating fatigue strength and water pressure resistance.

[0187] The plane portion 423 is provided with an adsorption portion 500, the adsorption portion 500 is located in the oil pool, and the adsorption portion 500 is configured to adsorb iron filings. The adsorption portion 500 is provided with a through hole 520, and the through hole 520 extends along the height direction of the adsorption portion 500. The adsorption portion 500 is, for example, a magnet.

[0188] By providing the through hole 520 on the adsorption part 500, it is helpful to reduce the cost and improve the iron filing adsorption effect while ensuring that the outer diameter of the adsorption part 500 is large enough.

[0189] In some embodiments, reference Fig.18 The inner wall outer diameter of the lower circumferential wall 422 is D4, referring to Fig. 20 , the outer diameter of the adsorption part 500 is D5, D4 / D5=[3, 6].

[0190] The inner diameter of the through hole 520 is D6, and D5 / D6=[1.5, 3].

[0191] The thickness of the adsorption portion 500 is t, and D5 / t=[6, 15].

[0192] Through the above settings, the high-speed impurity adsorption requirements are met and the low-cost requirements are met.

[0193] In some embodiments, reference Fig.18 , the height of the lower shell 420 is H7, the radius of the plane portion 423 is R6, the radius of the circle where the lower arc bottom wall 421 is located is R7, H7 / (R6×R7)>0.013, and the resonance frequency is not significantly improved within this range.

[0194] In some embodiments, reference Fig.19 A connecting portion 510 is provided on the plane portion 423, and the connecting portion 510 includes a base 511, and the base 511 is fixedly provided on the plane portion 423. A folded portion 512 is provided on the side edge of the base 511, and the folded portion 512 is configured to press the adsorption portion 500 toward a direction close to the base 511 to limit the position, thereby achieving fixed installation of the adsorption portion 500 on the connecting portion 510.

[0195] The adsorption part 500 is limited by folding the fold 512 to facilitate installation of the adsorption part 500.

[0196] In some embodiments, an inclined extension portion 513 is provided on one of the side edges of the base 511 , and the inclined extension portion 513 extends obliquely upward in a direction away from the adsorption portion 500 , thereby guiding the assembly and disassembly of the adsorption portion 500 .

[0197] In some embodiments, reference Fig.15 and Fig. 16B The lower circumferential wall 422 includes a first lower circumferential wall section 42201 and a second lower circumferential wall section 42202. The first lower circumferential wall section 42201 is located at the upper part of the second lower circumferential wall section 42202. The thickness of the first lower circumferential wall section 42201 is less than the thickness of the second lower circumferential wall section 42202. A step is formed between the first lower circumferential wall section 42201 and the second lower circumferential wall section 42202.

[0198] The first section 42201 of the lower circumferential wall is inserted into the bottom of the circumferential shell 430 , and the upper part of the first section 42201 of the lower circumferential wall is an inclined wall, which is convenient for plug-in installation between the first section 42201 of the lower circumferential wall and the circumferential shell 430 .

[0199] The height of the lower circumferential wall section 42201 is E2, and E2 is 12±0.2 mm. This range helps to ensure the plug-in reliability between the lower shell 420 and the circumferential shell 430.

[0200] [The second sub-muffler of the compressor body]

[0201] In the related art, the second sub-muffler is a single-layer structure, which has limited noise reduction effect and poor anti-oil spitting effect. This embodiment improves the second sub-muffler to improve the noise reduction effect and reduce the oil spitting rate. In some embodiments, refer to Fig.21 , Fig. 22 and Fig.24 The second sub-muffler 141 is an inner and outer double-layer structure, including a third sub-muffler 610 (inner muffler) and a fourth sub-muffler 620 (outer muffler). An oil delivery channel is arranged inside the eccentric crankshaft 110. The second bearing 151 includes a vertical portion 1511 and a transverse portion 1512 of an integral structure, and the eccentric crankshaft 110 is inserted through the vertical portion 1511. The lower shaft end is inserted through the vertical portion 1511.

[0202] The third sub-muffler 610 is disposed at the bottom of the second bearing 151, and a first muffler cavity 631 is formed between the third sub-muffler 610 and the second bearing 151. The fourth sub-muffler 620 is disposed at the bottom of the third sub-muffler 610, and a second muffler cavity 632 is formed between the fourth sub-muffler 620 and the third sub-muffler 610.

[0203] The gas discharged from the second bearing 151 first enters the first silencer chamber 631 for the first silencer, and then flows into the second silencer chamber 632 for the second silencer, and then returns to the first silencer chamber 631, and is then discharged to the top side of the compression mechanism 14 through the air flow channel 170 inside the compression mechanism 14.

[0204] The double-layer design of the second sub-muffler 141 prolongs the gas flow path, which helps to improve the sound-absorbing and noise-reducing effect.

[0205] In some embodiments, Fig. 22 and Fig.23 The third sub-muffler 610 is provided with a first through hole 611, and the vertical portion 1511 passes through the first through hole 611. A vent is formed between the inner wall of the first through hole 611 and the peripheral wall of the vertical portion 1511. The vent connects the first muffler cavity 631 with the second muffler cavity 632 for gas circulation.

[0206] Fig.24 6 is a structural diagram of the fourth sub-muffler 620. The fourth sub-muffler 620 is provided with a second through hole 623, and the bottom oil suction port of the oil delivery channel is directly opposite to the second through hole 623, so as to ensure the normal oiling of the oil suction port.

[0207] The bottom of the fourth sub-muffler 620 is in contact and sealed with the bottom end of the vertical portion 1511 to prevent gas leakage therefrom.

[0208] In some embodiments, reference Fig. 22 The inner diameter of the first through hole 611 is larger than the outer diameter of the vertical portion 1511. The vertical portion 1511 passes through the first through hole 611, and a gap for gas flow is formed between the outer peripheral wall of the vertical portion 1511 and the inner peripheral wall of the first through hole 611, and the gap should be understood as the vent mentioned above.

[0209] The difference between the inner diameter of the first through hole 611 and the outer diameter of the vertical portion 1511 is greater than 3 mm, which helps to ensure smooth gas flow.

[0210] In some embodiments, reference Fig.23 The first through hole 611 includes a first sub-through hole 612 (main through hole) and a second sub-through hole 613 (secondary through hole), the first sub-through hole 612 is connected to the second sub-through hole 613, and the second sub-through hole 613 extends to the outer peripheral side of the first sub-through hole 612. The vertical portion 1511 is penetrated through the first sub-through hole 612, and the second sub-through hole 613 connects the first muffler cavity 631 and the second muffler cavity 632, that is, the second sub-through hole 613 is for gas circulation, which can be understood as the vent mentioned above.

[0211] For example, the second sub-through hole 613 is designed as a semicircular hole, and the opening position is determined according to the sound loss design.

[0212] It should be noted that the difference between the sound power level incident on the muffler inlet and the sound power level transmitted through the muffler outlet is called sound transmission loss, or sound loss for short.

[0213] In some embodiments, reference Fig.23 Two second sub-through holes 613 are provided, and the two second sub-through holes 613 are symmetrically arranged relative to the first sub-through hole 612 .

[0214] In some embodiments, a protrusion is provided on the inner side of the bottom wall 621 of the fourth sub-muffler 620 , and the protrusion extends circumferentially along the second through hole 623 . The protrusion abuts against the bottom end surface of the vertical portion 1511 , and an interference fit design is adopted to achieve sealing with the second bearing 151 .

[0215] In some embodiments, the area of ​​the vent is S1, the area of ​​the exhaust port on the lateral portion 1512 is S2, and S1 / S2>0.9.

[0216] The larger S1 / S2 is, the better. That is, the larger S1 is, the smaller the pressure loss is, and the corresponding sound loss is also smaller. When S1 / S2>0.9, the pressure loss and sound loss are relatively stable.

[0217] It should be noted that pressure loss, referred to as pressure loss, refers to the phenomenon that pressure decreases due to friction, bending, expansion, contraction, etc. during the flow of fluid or gas.

[0218] In some embodiments, reference Figure 21 to Figure 23 The bottom wall of the third sub-muffler 610 is an arc-shaped wall 614, and the circumferential edge of the arc-shaped wall 614 is connected to the circumferential wall, which is recorded as the first circumferential wall 615. The first circumferential wall 615 extends upward, and the top of the first circumferential wall 615 is connected to the flange 616. The flange 616 extends toward the outer peripheral side of the first circumferential wall 615, and the flange 616 is connected to the transverse portion 1512.

[0219] The radius of the circle where the outer contour of the flange 616 is located is R10, and the radius of the circle where the arc wall 614 is located is R11, and R10 and R11 satisfy the relationship: R10 / R11>0.3. The third sub-muffler 610 is designed similar to a hemispherical shape, which helps to increase the resonance frequency and reduce noise.

[0220] In some embodiments, reference Fig.24 The fourth sub-muffler 620 includes a bottom wall 621 and a second circumferential wall 622 , and the inner side wall of the second circumferential wall 622 is in contact with the outer circumferential wall of the transverse portion 1512 .

[0221] The third sub-muffler 610 is provided with an inner mounting hole 617, and the fourth sub-muffler 620 is provided with an outer mounting hole 624. Connectors, such as bolts, pass through the outer mounting hole 624 and the inner mounting hole 617 to be connected to the transverse portion 1512. That is, the third sub-muffler 610 and the fourth sub-muffler 620 are fixedly installed by the same connecting member, which facilitates installation and improves installation efficiency.

[0222] [Matching structure of lower bearing, lower piston and lower cylinder in compression mechanism]

[0223] In the related art, there is friction between the bottom end surface of the second piston 131 and the top end surface of the second bearing 151, which affects the efficiency of the compressor.

[0224] In some embodiments, the matching structure between the second bearing 151 and the second piston 131 and the second cylinder 121 is improved to achieve both low wear and high performance of the compressor.

[0225] In some embodiments, reference Fig.25A first annular groove 1513 is arranged at the top of the transverse portion 1512 , and the first annular groove 1513 surrounds the axial hole of the second bearing 151 . A first annular groove inner wall 1514 is formed between the first annular groove 1513 and the axial hole of the second bearing 151 , and the top of the first annular groove inner wall 1514 is lower than the top of the transverse portion 1512 .

[0226] The second cylinder 121 is disposed at the top of the transverse portion 1512. The second piston 131 is disposed in the compression chamber of the second cylinder 121, and the second piston 131 is sleeved on the second eccentric shaft segment 114. When the second piston 131 performs eccentric circular motion with the eccentric crankshaft 110, friction occurs between the bottom end surface of the second piston 131 and the top end surface of the transverse portion 1512.

[0227] By setting the top of the first annular groove inner wall 1514 lower than the top of the transverse portion 1512 , the friction between the second piston 131 and the transverse portion 1512 is reduced, thereby helping to reduce compressor wear and improve performance.

[0228] In some embodiments, reference Fig.25 The outer diameter of the second shaft section 115 is D14, the outer diameter of the vertical portion 1511 is D15, and the height of the vertical portion 1511 is H10. Fig.21 , the height of the second bearing 151 is H11, and D14, D15, H10 and H11 satisfy the relationship: (D14 / D15)×(H10 / H11)>0.38, which is beneficial to reducing the friction loss of the compressor.

[0229] In some embodiments, reference Fig.25 The distance between the bottom end of the first annular groove 1513 and the top end surface of the second bearing 151 is H12, and the distance between the bottom end of the first annular groove 1513 and the top of the first annular groove inner wall 1514 is H13. H12 and H13 satisfy the relationship: 0.2mm≤H12-H13≤2mm, which is helpful to prevent radial deformation of the annular groove.

[0230] In some embodiments, reference Fig.25 The outer wall diameter of the first annular groove 1513 is D16, the inner wall diameter of the first annular groove 1513 is D17, the outer diameter of the second shaft section 115 is D14, (D16-D17) / D14=0.08-0.22, which is helpful to reduce the friction loss of the second bearing 151.

[0231] In some embodiments, reference Fig.25The outer wall diameter of the first annular groove 1513 is D16, the inner wall diameter of the first annular groove 1513 is D17, the distance between the bottom end of the first annular groove 1513 and the top of the inner wall 1514 of the first annular groove is H13, and D16, D17 and H13 satisfy the relationship: 0.2≤(D16-D17) / H13≤0.5. In this way, the second bearing 151 is subjected to small radial force and small deformation, which is beneficial to reducing wear and improving the reliability of the second bearing 151.

[0232] In some embodiments, a second annular groove is disposed at the top of the transverse portion 1512 , the second annular groove surrounds the outer circumference of the first annular groove 1513 , and a lubrication portion is disposed in the second annular groove.

[0233] During the operation of the compressor, the lower thrust surface of the eccentric crankshaft 110 contacts and moves relative to the surface of the second bearing 151, forming a friction pair. When the compressor is just started, the refrigeration oil has not yet formed a circulation at this friction pair. By providing a second annular groove and arranging a lubricating part in the second annular groove, it is helpful to reduce the wear of the thrust surface of the eccentric crankshaft 110 and the second bearing 151, thereby improving reliability.

[0234] In some embodiments, the lubricating portion is a steel ring, and a Teflon coating is coated on the upper surface of the steel ring to achieve self-lubrication.

[0235] In some embodiments, reference Fig.25 The thickness of the middle partition 160 is t2, the height of the second cylinder 121 is H14, and t2 and H14 satisfy the relationship: 0.22≤t2 / H14≤0.35. This is beneficial to improving the energy conversion efficiency (Coefficient of Performance, COP) of the compressor.

[0236] [Muffler on exhaust pipe]

[0237] The noise inside the air conditioner room generally comes from wind noise, refrigerant pulsation sound, etc. Wind noise is generally broadband white noise, which often does not cause discomfort to customers.

[0238] It should be noted that white noise refers to noise whose power spectrum density is constant in the entire frequency domain. Random noise with the same energy density at all frequencies is called white noise.

[0239] However, the refrigerant pulsation sound is mostly pure sound components, and changes with the compressor operating frequency, indoor and outdoor temperature difference, etc. Since the refrigerant pulsation sound mainly comes from the compressor, the muffler is usually placed at the exhaust port of the compressor, and the muffler is configured to reduce abnormal noise. However, the traditional expansion muffler can have a certain noise suppression effect on a small frequency band of high or low frequencies, but when the compressor has a higher operating frequency and the refrigerant pressure has a large change, it cannot have a good noise reduction effect, which causes the appearance of indoor pure sound components and leads to customer complaints.

[0240] In some embodiments, the silencer structure at the compressor exhaust port is improved to effectively reduce the refrigerant pulsation sound and avoid the pure sound component appearing inside the air conditioner room.

[0241] For example, refer to Fig.29 and Fig.30 A sensor 17 is provided on the exhaust pipe 12 , and the sensor 17 is configured to detect the vibration frequency of the exhaust pipe 12 .

[0242] The exhaust pipe 12 is provided with a muffler 800. Along the gas flow direction in the exhaust pipe 12, the muffler 800 is provided downstream of the sensor 17.

[0243] The muffler 800 includes a connecting pipe section, the inner diameter of which is greater than the inner diameter of the exhaust pipe 12 .

[0244] The muffler 800 further includes a flexible pipe section 830. The inner diameter of the flexible pipe section 830 is greater than the inner diameter of the exhaust pipe 12.

[0245] The muffler 800 further includes a driving unit 860 , which is configured to drive the flexible pipe section 830 to expand and contract along the length direction of the exhaust pipe 12 according to the vibration frequency of the exhaust pipe 12 .

[0246] For example, the silencer 800 is an automatic variable volume silencer to suppress the transmission of the refrigerant pulsation sound.

[0247] It should be noted that based on the silencer principle, the silencer frequency is only related to the length of the silencer 800. Therefore, after obtaining the vibration frequency of the exhaust pipe 12 through the sensor 17, the driving unit 860 is used to drive the flexible pipe section 830 to extend or shorten, thereby realizing the length change of the silencer 800 to improve the silencer noise reduction effect.

[0248] In some embodiments, reference Fig.30 The connecting pipe section includes a first connecting pipe section 810 and a second connecting pipe section 820 , and the flexible pipe section 830 is connected between the first connecting pipe section 810 and the second connecting pipe section 820 .

[0249] The first connecting pipe section 810 and the second connecting pipe section 820 are metal pipes, such as copper pipes. The flexible pipe section 830 is a corrugated pipe, which is convenient for expansion and contraction.

[0250] In some embodiments, the driving unit 860 is configured to drive the first connecting pipe segment 810 and the second connecting pipe segment 820 to approach each other so that the flexible pipe segment 830 contracts.

[0251] The driving portion 860 is further configured to drive the first connecting pipe segment 810 and the second connecting pipe segment 820 to move away from each other so that the flexible pipe segment 830 extends.

[0252] It should be noted that the flexible pipe segment 830 is disposed between the first connecting pipe segment 810 and the second connecting pipe segment 820 , and the first connecting pipe segment 810 and the second connecting pipe segment 820 are driven to move by the driving unit 860 to achieve contraction or extension of the flexible pipe segment 830 .

[0253] The first connecting pipe section 810 and the second connecting pipe section 820 are metal pipes, which facilitate the installation of the driving part 860 .

[0254] In some embodiments, a first connecting portion 840 is disposed on one of the first connecting pipe segment 810 and the second connecting pipe segment 820 , and a second connecting portion 850 is disposed on the other one.

[0255] A driving motor 861 is disposed on one of the first connecting portion 840 and the second connecting portion 850 , and a threaded hole is disposed on the other one. A screw rod 862 is disposed at the power output end of the driving motor 861 , and the screw rod 862 is connected to the threaded hole.

[0256] The driving motor 861 drives the screw rod 862 to rotate, and through the threaded connection between the screw rod 862 and the threaded hole, the first connecting part 840 and the second connecting part 850 are moved closer to or farther away from each other, and then the first connecting pipe section 810 and the second connecting pipe section 820 are moved closer to or farther away from each other, thereby realizing the contraction or extension of the flexible pipe section 830.

[0257] In some embodiments, the sensor 17 detects the vibration frequency of the exhaust pipe 12 in the range of 1000 to 3000 Hz.

[0258] In some embodiments, the exhaust pipe 12 is disposed on the upper housing 410. Figure 7 , the inner diameter of the upper shell 410 is D8, refer to Figure 2A , the inner diameter of the exhaust pipe 12 is D9.

[0259] Reference Figure 2B The distance between the air inlet end of the exhaust pipe 12 and the top of the crankshaft is H8, and D8, D9 and H8 satisfy the relationship: 3.81<D8 / (D9×H8)<4.62. Within this range, the oil discharge rate of the compressor is reduced.

[0260] In some embodiments, reference Figure 2A , the inner diameter of the shell is D10, the inner diameter of the exhaust pipe 12 is D9, D10 / D9=[8, 12].

[0261] It should be noted that the inner diameter of the compressor main shell is greatly affected by the displacement. Generally, the larger the displacement, the larger the inner diameter. Moreover, the larger the displacement, the larger the inner diameter of the exhaust pipe 12 needs to be in order to reduce the oil discharge rate and the refrigerant gas pressure loss. When D10 / D9=[8, 12], the displacement can also be increased while reducing the oil discharge rate.

[0262] In some embodiments, the sensor 17 is disposed at the exhaust pipe 12 , and the sensor 17 is configured to detect a vibration frequency of the exhaust pipe 12 .

[0263] The silencer 800 includes a pipe section portion, which is connected to the exhaust pipe 12, and the inner diameter of the pipe section portion is larger than the inner diameter of the exhaust pipe 12. The silencer 800 is an expansion type silencer.

[0264] The muffler 800 includes a driving unit 860 configured to drive the pipe section to move to change the volume of the pipe section according to the vibration frequency of the exhaust pipe 12. The muffler 800 is an automatic variable volume muffler to improve the effect of suppressing the transmission of refrigerant pulsation sound.

[0265] [Compressor foot]

[0266] In order to reduce the vibration of the compressor body, vibration isolation pads may be used to reduce the vibration of the compressor from the perspective of stiffness matching and damping matching. However, as the size and weight of the compressor increase, the stiffness of the pads must not be too low. If the stiffness of the pads is too low, it is easy to cause excessive shaking of the compressor during transportation, thereby impacting the pipeline, causing pipeline breakage and other problems.

[0267] In some embodiments, the base of the compressor is optimized to improve the vibration reduction effect.

[0268] In some embodiments, reference Figure 2A The circumferential shell 430 constitutes the circumferential wall of the compressor body 1, the height of the circumferential shell 430 is H10, and the inner diameter of the circumferential shell 430 is D10.

[0269] The mounting portion 16 is disposed outside the circumferential shell 430 . A mounting hole is disposed on the mounting portion 16 , and the inner diameter of the mounting hole is D18 .

[0270] The compressor further includes a foot 15 , and a connecting member (such as a bolt) passes through the mounting hole to mount the foot 15 to the mounting portion 16 . The foot 15 is configured to support the compressor, and the height of the foot 15 is H16 .

[0271] It should be noted that, from the perspective of controlling the compressor mass center position, 4.5<H10 / H16<6.5, 5.5<D10 / D18<8.5. From the perspective of controlling the compressor mass center position, it is beneficial to reduce the vibration of the compressor housing and meet the vibration reduction requirements of the rotor compressor housing.

[0272] In some embodiments, if there are too many feet 15, installation is inconvenient. If there are too few feet 15, the feet 15 are subjected to greater force, the feet 15 are easily deformed when falling, and the vibration is large. For example, the weight of the compressor is G (kg), the number of feet 15 is N (pieces), G and N satisfy the formula: 12.5>G / N>5, that is, 12.5kg / piece>designed compressor weight / number of feet 15>5kg / piece, within this range, the compressor has low vibration and noise, and good anti-fall ability.

[0273] In some embodiments, three feet 15 are provided on the side of the circumferential shell 430, and the angle between the foot 15 close to the gas-liquid separator 2 and the gas-liquid separator 2 is greater than or equal to 30 and less than or equal to 60 degrees. In this range, the compressor has low vibration and noise and good anti-drop ability.

[0274] In some embodiments, four feet 15 are provided on the side of the circumferential shell 430, and the angle between the feet 15 close to the gas-liquid separator 2 and the gas-liquid separator 2 is greater than or equal to 20 and less than or equal to 45 degrees. In this range, the compressor has low vibration and noise and good anti-drop capability.

[0275] In some embodiments, the height of the foot 15 / the height of the center of gravity of the compressor = [0.07, 0.15], so that the vibration and noise of the compressor are small within this range.

[0276] It should be noted that any one of the technical solutions disclosed in the present disclosure can solve one or more of the above-mentioned technical problems and achieve certain invention purposes to a certain extent; multiple technical disclosures can also be combined into an overall solution to solve one or more of the above-mentioned technical problems and achieve certain invention purposes; some technical disclosures can also be selected to be combined into an overall solution, while adopting related technologies and deteriorated solutions, but the deterioration trend can be compensated by the means disclosed in this technology, and one or more of the above-mentioned technical problems can be solved to a certain extent as a whole and certain invention purposes can be achieved; each technical disclosure combined into a complete technical solution constitutes an organic and inseparable overall solution, which solves technical problems as a whole and achieves certain invention purposes.

[0277] Those skilled in the art will appreciate that the disclosure scope of the present invention is not limited to the above specific embodiments, and certain elements of the embodiments may be modified and replaced without departing from the spirit of the present application. The scope of the present application is limited by the appended claims.

Claims

1. A compressor, comprising: case; a compression mechanism disposed in the shell, the compression mechanism being configured to compress a refrigerant; Characterized in that the compression mechanism comprises: Bearings, with vent holes; An exhaust valve plate, disposed on the bearing, and configured to open or close the exhaust hole; a lift limiter, disposed on the bearing, the lift limiter being configured to limit the displacement of the exhaust valve plate; An electromagnetic suction part, arranged on the lift limiter, the electromagnetic suction part is configured to be energized to attract the exhaust valve plate when the compression mechanism is exhausted; A reset member is disposed between the exhaust valve plate and the lift limiter, and the reset member is configured to apply a force to the exhaust valve plate to move the exhaust valve plate toward the exhaust hole.

2. The compressor according to claim 1, characterized in that The exhaust valve plate includes a valve plate head, a valve plate tail and a connecting section, the connecting section is connected between the valve plate head and the valve plate tail, the valve plate tail is connected to the bearing, the valve plate head is configured to open or close the exhaust hole, and the electromagnetic suction part is opposite to the valve plate head.

3. The compressor according to claim 2, characterized in that The reset member is arranged between the valve plate head and the lift limiter.

4. The compressor according to claim 2, characterized in that The effective length of the exhaust valve plate is L1, the lift height of the exhaust valve plate is H9, the curvature radius of the exhaust valve plate is R12, the thickness of the exhaust valve plate is t1, and 1.5<(L1 / R12)×t1+H9<3.

0.

5. The compressor according to claim 2, characterized in that The diameter of the valve plate head is D11, the diameter of the exhaust hole is D12, and 0.7<D11 / D12<0.

8.

6. The compressor according to claim 5, characterized in that The compression mechanism includes a cylinder, the bearing is arranged in the cylinder, the exhaust hole is communicated with the inner cavity of the cylinder, the inner diameter of the cylinder is D13, and 0.2<D12 / D13<0.

3.

7. The compressor according to any one of claims 1 to 6, characterized in that: The lift limiter is provided with a copper wire on a side away from the exhaust valve plate, and the copper wire is energized to form the electromagnetic suction part.

8. The compressor according to any one of claims 1 to 6, characterized in that: comprising an exhaust pipe disposed on the top of the shell; a sensor disposed in the exhaust pipe, the sensor being configured to detect a vibration frequency of the exhaust pipe; A muffler is arranged on the exhaust pipe, and the muffler comprises: A connecting pipe section connected to the exhaust pipe, wherein the inner diameter of the connecting pipe section is larger than the inner diameter of the exhaust pipe; a flexible pipe section connected to the connecting pipe section, wherein the inner diameter of the flexible pipe section is larger than the inner diameter of the exhaust pipe; The driving unit is configured to drive the flexible pipe section to expand and contract along the length direction of the exhaust pipe according to the vibration frequency of the exhaust pipe.

9. A compressor, comprising: case; a compression mechanism disposed in the shell, the compression mechanism being configured to compress a refrigerant; Characterized in that the compression mechanism comprises: Bearings, with vent holes; An exhaust valve plate, disposed on the bearing, and configured to open or close the exhaust hole; a lift limiter, disposed on the bearing, the lift limiter being configured to limit the displacement of the exhaust valve plate; an electromagnetic suction part, arranged on the lift limiter, the electromagnetic suction part being configured to be energized to attract the exhaust valve plate when the compression mechanism is exhausting, and the electromagnetic suction part being configured to be de-energized when the compression mechanism is not exhausting; A reset member is arranged between the exhaust valve plate and the lift limiter, and the reset member is configured to contract when the electromagnetic suction part attracts the exhaust valve plate. The reset member is configured to apply a force to the exhaust valve plate to move the exhaust valve plate in a direction close to the exhaust hole.

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

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