Compressor and air conditioner

Abstract

The compressor comprises a shell, the shell comprises a circumferential shell body and a lower shell body, the lower shell body is arranged at the bottom of the circumferential shell body, the lower shell body comprises a circumferential wall and an arc-shaped bottom wall, the arc-shaped bottom wall is arranged at the bottom of the circumferential wall, the circumferential wall is connected with the circumferential shell body, and a plane part is arranged at the bottom of the arc-shaped bottom wall; the adsorption part is arranged on the plane part, the adsorption part is configured to adsorb scrap iron, a through hole is formed in the adsorption part, and the through hole extends in the height direction of the adsorption part. The utility model can achieve the effects of improving the scrap iron adsorption rate, reducing vibration and noise and improving the oil supply amount, and is low in cost.

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] An air conditioner utilizes a compressor, condenser, expansion valve, and evaporator to perform its cooling and heating cycles. The compressor houses a motor and compression mechanism. During operation, each friction pair generates wear debris. If these debris are not effectively controlled, they can cause wear on all three friction pairs, reducing compressor performance and potentially damaging the compressor. Magnets are typically placed within the oil reservoir at the bottom of the compressor to attract these debris. However, this approach presents a significant disadvantage: larger magnet diameters increase costs, while smaller magnet diameters reduce magnet retention and lead to poorer scrap absorption.

[0003] The magnets are set on the bottom shell of the compressor. The space between the existing bottom shell and the compression mechanism is small, resulting in limited oil pool volume, which is not conducive to oil supply design. The lower shell is prone to resonate with the airflow, increasing the noise of the compressor.

[0004] The above information disclosed in this background technology is only used to increase the understanding of the background technology of this application. Therefore, it may contain information that does not constitute the prior art known to ordinary technicians in this field. Summary of the Invention

[0005] In response to the problems pointed out in the background technology, the utility model proposes a compressor and an air conditioner, which improve the magnets in the compressor bottom shell and the oil pool to achieve the effects of increasing the iron filings adsorption rate, low cost, vibration reduction and noise reduction, and increasing the oil supply.

[0006] On the one hand, a compressor is provided, including a shell, the shell including a circumferential shell and a lower shell, the lower shell is arranged at the bottom of the circumferential shell, the lower shell includes a circumferential wall and an arc-shaped bottom wall, the arc-shaped bottom wall is arranged at the bottom of the circumferential wall, the circumferential wall is connected to the circumferential shell, and a flat portion is provided at the bottom of the arc-shaped bottom wall; an adsorption portion is provided on the flat portion, the adsorption portion is configured to adsorb iron filings, a through hole is provided on the adsorption portion, and the through hole extends along the height direction of the adsorption portion.

[0007] The curved bottom wall creates a hemispherical lower housing, raising the resonant frequency and preventing resonance between the pump airflow frequency and the lower housing. This also increases the chamber volume and the bottom oil sump volume, facilitating oil supply design. The spherical lower housing design minimizes the planar surface area. The smaller the surface area, the higher the hydraulic reciprocating fatigue strength and water pressure resistance.

[0008] By providing a through hole on the adsorption part, it is helpful to reduce costs and improve the iron filings adsorption effect while ensuring that the outer diameter of the adsorption part is large enough.

[0009] On the other hand, an air conditioner is provided. The air conditioner includes a compressor, an evaporator, a condenser, and a throttling device. The compressor is the compressor described above. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0011] Figure 2A is a side view of a compressor according to some embodiments;

[0012] Figure 2B is a cross-sectional view of a compressor according to some embodiments;

[0013] Figure 3 is a top view of a compressor according to some embodiments;

[0014] Figure 4 is a structural diagram of a stent according to some embodiments;

[0015] Figure 5 is another structural diagram of a stent according to some embodiments;

[0016] Figure 6 is another top view of a compressor according to some embodiments;

[0017] Figure 7 is another structural diagram of a stent according to some embodiments;

[0018] Figure 8 is a structural diagram of a bracket and a circumferential shell according to some embodiments;

[0019] Figure 9 is a cross-sectional view of a gas-liquid separator according to some embodiments;

[0020] Figure 10 A structural diagram of a floating portion after floating according to some embodiments;

[0021] Figure 11 is a structural diagram after the floating portion descends according to some embodiments;

[0022] Figure 12 is a structural diagram of a floating portion according to some embodiments;

[0023] Figure 13 is a structural diagram of a compressor body according to some embodiments;

[0024] Figure 14 is a structural diagram of an upper housing according to some embodiments;

[0025] Figure 15is a cross-sectional view of a first housing according to some embodiments;

[0026] Figure 16A This is a partial enlarged view of the circle A in Figure 15;

[0027] Figure 16B This is a partial enlarged view of the circle B in Figure 15;

[0028] Figure 17 is a cross-sectional view of an upper housing according to some embodiments;

[0029] Figure 18 is a structural diagram of a lower housing according to some embodiments;

[0030] Figure 19 is a structural diagram of a lower shell and an adsorption portion according to some embodiments;

[0031] Figure 20 is a structural diagram of an adsorption portion according to some embodiments;

[0032] Figure 21 is a cross-sectional view of a compression mechanism according to some embodiments;

[0033] Figure 22 is a structural diagram of a third sub-muffler according to some embodiments;

[0034] Figure 23 is another structural diagram of a third sub-muffler according to some embodiments;

[0035] Figure 24 is a structural diagram of a fourth sub-muffler according to some embodiments;

[0036] Figure 25 is an assembly diagram of an eccentric crankshaft, a second bearing, a second cylinder, and a second piston according to some embodiments;

[0037] Figure 26 is a structural diagram of an exhaust valve plate and a lift limiter according to some embodiments;

[0038] Figure 27 is another structural diagram of an exhaust valve plate and a lift limiter according to some embodiments;

[0039] Figure 28 is a structural diagram of an exhaust valve plate according to some embodiments;

[0040] Figure 29 A structural diagram of a compressor body, an exhaust pipe, and a muffler according to some embodiments;

[0041] Figure 30 is a structural diagram of a muffler according to some embodiments;

[0042] Figure 31 1 is a structural diagram of an eccentric crankshaft according to some embodiments. DETAILED DESCRIPTION

[0043] The following will be combined with the accompanying drawings to clearly and completely describe some embodiments of the present disclosure. Obviously, the embodiments described are only some embodiments of the present disclosure, rather than all embodiments. Based on the embodiments provided by the present disclosure, all other embodiments obtained by ordinary technicians in this field are within the scope of protection of the present disclosure.

[0044] Unless the context requires otherwise, throughout the specification and claims, the term "comprise" and its other forms, such as the third person singular form "comprises" and the present participle form "comprising", are to be interpreted as open, inclusive, that is, "including, but not limited to". In the description of the specification, the terms "one embodiment", "some embodiments", "exemplary embodiments", "example", "specific example" or "some examples" are intended to indicate that the specific features, structures, materials or characteristics associated with the embodiment or example are included in at least one embodiment or example of the present disclosure. The schematic representation of the above terms does not necessarily refer to the same embodiment or example. In addition, the specific features, structures, materials or characteristics may be included in any one or more embodiments or examples in any appropriate manner.

[0045] In the following, the terms "first" and "second" are used for descriptive purposes only and should not be understood to indicate or imply relative importance or implicitly specify the number of the technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the embodiments of the present disclosure, unless otherwise specified, "plurality" means two or more.

[0046] When describing some embodiments, the expressions "coupled" and "connected" and their derivatives may be used. The term "connected" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; it can be directly connected or indirectly connected through an intermediate medium. The term "coupled" indicates that two or more components are in direct physical or electrical contact. The term "coupled" or "communicatively coupled" may also refer to two or more components that are not in direct contact with each other, but still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the contents of this document.

[0047] “At least one of A, B and C” has the same meaning as “at least one of A, B or C” and both include the following combinations of A, B and C: A only, B only, C only, the combination of A and B, the combination of A and C, the combination of B and C, and the combination of A, B and C.

[0048] “A and / or B” includes the following three combinations: A only, B only, and a combination of A and B.

[0049] The use of "adapted to" or "configured to" herein is intended to be open and inclusive language that does not exclude devices adapted or configured to perform additional tasks or steps.

[0050] As used herein, "about," "substantially," or "approximately" includes the stated value and an average value that is within an acceptable range of deviation from the particular value as determined by one of ordinary skill in the art taking into account the measurements in question and the errors associated with the measurement of the particular quantity (i.e., the limitations of the measurement system).

[0051] As used herein, "parallel", "perpendicular", and "equal" include the situations described and situations similar to the situations described, and the range of the similar situations is within an acceptable deviation range, wherein the acceptable deviation range is as determined by a person of ordinary skill in the art taking into account the measurement in question and the errors associated with the measurement of the specific quantity (i.e., the limitations of the measurement system). For example, "parallel" includes absolute parallelism and approximate parallelism, wherein the acceptable deviation range of approximate parallelism can be, for example, a deviation within 5°; "perpendicular" includes absolute perpendicularity and approximate perpendicularity, wherein the acceptable deviation range of approximate perpendicularity can also be, for example, a deviation within 5°. "Equal" includes absolute equality and approximate equality, wherein the acceptable deviation range of approximate equality can be, for example, that the difference between the two equals is less than or equal to 5% of either one.

[0052] [Air Conditioner]

[0053] In some embodiments, the air conditioner 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.

[0054] Low-temperature, low-pressure refrigerant enters the compressor, which compresses it into 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 refrigerant into a liquid phase, releasing heat into the surrounding environment through the condensation process.

[0055] The expansion valve expands the high-temperature, high-pressure liquid refrigerant condensed in the condenser to a lower-pressure liquid. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the low-temperature, low-pressure refrigerant gas to the compressor. The evaporator achieves cooling by utilizing the latent heat of evaporation to exchange heat with the material being cooled. Throughout this cycle, the air conditioner regulates the temperature of the indoor space.

[0056] 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.

[0057] 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 operates in a heating mode; when the indoor heat exchanger functions as an evaporator, the air conditioner operates in a cooling mode.

[0058] The outdoor assembly further includes a four-way valve configured to switch between the indoor heat exchanger and the outdoor heat exchanger as a condenser or an evaporator.

[0059] The refrigeration working principle of the air conditioner is: the operation of the compressor makes the indoor heat exchanger (in the indoor component, this is the evaporator) in an ultra-low pressure state, and the liquid refrigerant in the indoor heat exchanger evaporates rapidly to absorb heat. The air 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. The heat is dissipated into the atmosphere through the outdoor fan, and this cycle achieves the cooling effect.

[0060] The air conditioner's heating principle works as follows: The gaseous refrigerant is pressurized by the compressor, becoming a high-temperature, high-pressure gas. It then enters the indoor heat exchanger (the condenser), where it condenses and liquefies, releasing heat and becoming a liquid. This heats the indoor air, thereby raising the indoor temperature. The liquid refrigerant is then reduced in pressure by the throttling device and enters the outdoor heat exchanger (the evaporator). It evaporates, absorbs heat, and becomes a gas, absorbing heat from the outdoor air (making the outdoor air even cooler). It then becomes a gaseous refrigerant and enters the compressor again to begin the next cycle.

[0061] [Compressor body]

[0062] In some embodiments of the present disclosure, the compressor is a rolling rotor compressor. Figure 1 As shown in Figure 2 , the compressor includes a compressor body 1. The compressor body 1 includes a first housing 11, which defines a closed inner cavity within which a motor 13 and a compression mechanism 14 are disposed. Motor 13 provides power to the compressor mechanism. Compression mechanism 14 is configured to compress refrigerant. Motor 13 is positioned above compression mechanism 14. Figure 21 It is a cross-sectional view of the compression mechanism 14.

[0063] In some embodiments, reference Figure 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 enclose the inner cavity of the compressor body 1.

[0064] 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.

[0065] In some embodiments, reference Figure 21 The compression mechanism 14 includes an eccentric crankshaft 110, a cylinder, a piston, a bearing, a muffler, etc.

[0066] In some embodiments, reference Figure 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 provided 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 provided on the bearing, and the bearing exhaust hole is connected to the compression chamber; a vane groove is provided on the cylinder, and a vane is provided in the vane groove. The eccentric crankshaft 110 drives the piston to perform circumferential motion in the compression chamber, and the vane reciprocates along the vane groove. 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.

[0067] 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 performs reciprocating motion 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, and then inhales air from the low-pressure chamber and exhausts 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.

[0068] In some disclosed embodiments, the compressor is a twin-cylinder rolling rotor compressor, referring to Figure 21 The 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)).

[0069] In some embodiments, reference Figure 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.

[0070] 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; the 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; the 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.

[0071] The first eccentric shaft segment 112 and the second eccentric shaft segment 114 are arranged at a relative angle of 180°, and 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.

[0072] Continue to refer to Figure 21 A first sub-muffler 142 is provided on the first bearing 152. 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 into the space enclosed by the first sub-muffler 142 and the first bearing 152, and then discharged into the inner cavity of the compressor through the exhaust hole of the first sub-muffler 142.

[0073] The second sub-muffler 141 is provided on the second bearing 151 . The second sub-muffler 141 covers the exhaust hole of the second bearing 151 . The compressed gas in the second cylinder 121 is first discharged through the exhaust hole on the second bearing 151 into the space enclosed by the second sub-muffler 141 and the second bearing 151 .

[0074] In some embodiments, unlike related art, Figure 21 The second sub-muffler 141 is not provided with an exhaust hole. Multiple vertically extending airflow channels 170 are provided through the walls 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 within the second bearing 151 and the second sub-muffler 141 is discharged upward through the airflow channels 170 into the space enclosed by the first bearing 152 and the first sub-muffler 142, and then discharged into the compressor's inner cavity through the exhaust hole of the first sub-muffler 142.

[0075] [Oil pool adsorption part of the compressor body]

[0076] In some embodiments, when a compressor is operating, each friction pair generates wear debris. If this debris is not effectively controlled, it can cause three-way wear of the friction pairs, reducing compressor performance and potentially damaging the compressor. Magnets are typically placed within the oil sump at the bottom of the compressor to attract the debris. However, larger magnet diameters increase costs, while smaller magnet diameters reduce magnet absorption efficiency and result in poor scrap absorption.

[0077] 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 prone to resonate with the airflow, increasing the noise of the compressor.

[0078] This embodiment improves the magnets in the compressor bottom shell and the oil pool to achieve the effects of increasing the iron chip adsorption rate, reducing costs, reducing vibration and noise, and increasing oil supply.

[0079] In some embodiments, reference Figure 15 、 Figures 18 to 20The 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 arcuate bottom wall 621, respectively designated as a lower circumferential wall 422 and a lower arcuate bottom wall 421. The lower arcuate bottom wall 421 is disposed at the bottom of the lower circumferential wall 422 and is connected to the circumferential housing 430. A flat surface 423 is provided at the bottom of the lower arcuate bottom wall 421.

[0080] The setting of the lower arc-shaped bottom wall 421 makes the lower shell 420 have a hemispherical structure, which increases the resonance frequency and avoids the resonance of the pump body airflow frequency with 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.

[0081] The spherical design of the lower shell 420 reduces the plane area. The smaller the area, the higher the oil pressure reciprocating fatigue strength and water pressure resistance.

[0082] The flat surface 423 is provided with an adsorption portion 500. The adsorption portion 500 is located in the oil pool and is configured to adsorb iron filings. The adsorption portion 500 is provided with a through hole 520 extending along the height direction of the adsorption portion 500. The adsorption portion 500 is, for example, a magnet.

[0083] 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.

[0084] In some embodiments, reference Figure 18 The outer diameter of the inner wall of the lower circumferential wall 422 is D4, refer to Figure 20 , the outer diameter of the adsorption part 500 is D5, D4 / D5=[3, 6].

[0085] The inner diameter of the through hole 520 is D6, where D5 / D6=[1.5, 3].

[0086] The thickness of the adsorption portion 500 is t, and D5 / t=[6, 15].

[0087] Through the above settings, the high-speed impurity adsorption requirements are met and the low-cost requirements are met.

[0088] In some embodiments, reference Figure 18 The height of the lower shell 420 is H7, the radius of the flat portion 423 is R6, the radius of the circle on which the lower arc-shaped bottom wall 421 is located is R7, H7 / (R6×R7)>0.013, and the resonance frequency is not significantly improved within this range.

[0089] In some embodiments, reference Figure 19A connecting portion 510 is provided on the plane portion 423, and the connecting portion 510 includes a base 511, which 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 achieve fixed installation of the adsorption portion 500 on the connecting portion 510.

[0090] The adsorption portion 500 is limited by folding the fold 512 to facilitate installation of the adsorption portion 500.

[0091] In some embodiments, an inclined extension portion 513 is provided on one of the side edges of the base 511 . 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 .

[0092] In some embodiments, reference Figure 15 and Figure 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 above the second lower circumferential wall section 42202. The thickness of the first lower circumferential wall section 42201 is less than that 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.

[0093] The first section 42201 of the lower circumferential wall is inserted into the bottom of the circumferential shell 430 , and the upper portion of the first section 42201 of the lower circumferential wall is an inclined wall, which facilitates the plug-in installation between the first section 42201 of the lower circumferential wall and the circumferential shell 430 .

[0094] 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.

[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 abnormalities.

[0097] In some embodiments, reference Figure 1 and Figure 9The gas-liquid separator 2 includes a second shell 21, and an outlet pipe 22 is provided at the bottom of the second shell 21. One end of the outlet pipe 22 extends into the inner cavity of the second shell 21, and the other end of the 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] Currently, the gas-liquid separator 2 is fixedly mounted on the outside of the compressor body 1 via a bracket 200. During compressor operation, the compressor body 1 and the gas-liquid separator 2 are prone to low-frequency resonance, generating low-frequency noise. Therefore, it is necessary to increase the natural frequency of the upper rotation of the gas-liquid separator 2 to avoid low-frequency resonance during operation of the compressor body 1 and the gas-liquid separator 2. In related art, the natural frequency of the gas-liquid separator 2 is relatively low, making it prone to low-frequency noise during compressor operation.

[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 during the operation of the compressor.

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

[0105] For each bracket 200, by welding the bracket part 1 210 and the bracket part 4 240 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 , thereby improving 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 . 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. 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 portion 220 is W3, the outer 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 of the second bracket part 220 is R3, and the outer contour radius of the second shell 21 is R2, R3-R2=[0.5mm, 2mm]. Within this range, it is convenient to achieve welding and 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 between the intersection of bracket part 1 210 and bracket part 220 and the plane of symmetry between the two brackets 200 is W1, the distance between bracket part 3 230 and the plane of symmetry between the two brackets 200 is W2, the outer radius of the second shell 21 is R2, the outer radius of the first shell 11 is R1, and (W1 / R2)×(W2 / R1)>0.3. Within this range, the double torsional frequency of the gas-liquid separator 2 tends to be stable, and the fixed frequency is increased to above 510Hz, making it suitable for a two-cylinder compressor with a maximum speed of 180 rps.

[0113] In some embodiments, reference Figure 3 and Figure 4 The first section 210 of the bracket 210 includes an integrated structure of the first section 211 of the bracket 1 and the second section 212 of the bracket 1. The first section 211 of the bracket 1 extends obliquely outward from the first end of the second section 212 of the bracket 1. The first section 211 of the bracket 1 is adapted and fixedly connected to the first shell 11. The second end of the second section 212 of the bracket 1 is intersected and connected with the second section 220 of the bracket.

[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, as well as 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 from the bottom of the lower casing 420 to 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 casing 420) is H2, where H2 / H1 = [0.49, 0.71]. This range helps reduce radial vibration of the gas-liquid separator 2 and compressor noise.

[0117] In some embodiments, reference Figure 3 The distance between the connection points of the two bracket portions 210 and the first housing 11 is D2, the outer diameter of the first housing 11 is D1, and D2 / D1=[0.06, 0.9]. Within this range, radial vibration of the gas-liquid separator 2 is reduced, which helps reduce compressor noise.

[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 body 260, with bracket extensions 270 symmetrically disposed at opposite ends of the bracket body 260. The bracket body 260 conforms to and is fixedly connected to the outer contour of the first housing 11, such as by welding. The bracket extension 270 is an integral structure comprising a first extension section 271 and a second extension section 272. The first extension section 271 is connected between the bracket body 260 and the second extension section 272. The second extension section 272 is fixedly connected to the outer contour of the second housing 21, such as by welding.

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

[0122] In some embodiments, reference Figure 7 The distance between the welding point 280 between the bracket body 260 and the first shell 11 and the symmetry plane of the bracket 200 is W5, and W5 / W4>0.75. The larger the W5 / W4, the better. When it is greater than 0.75, the vibration increase 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. 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, refer to Figure 8 The distance between the support body 260 and the gas outlet pipe 22 of the gas-liquid separator 2 is H5, where H4 / H5=[0.2, 0.35]. Within this range, the vibration of the gas-liquid separator 2 is reduced.

[0126] In some embodiments, reference Figure 6 The angle θ of the vertical line between the two second 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, where H15 / H1=[0.25-0.35].

[0129] There is a certain cavity volume between the upper portion of the motor 13 and the upper housing 410. A larger cavity improves oil separation and reduces the oil discharge rate. Cavity volume is also related to compressor noise levels. Setting the above range helps reduce compressor noise.

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

[0131] In some embodiments, 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 air of the compressor body 1 is overheated, the separated liquid is refrigeration oil. Therefore, the oil return hole 2201 needs to be as large as possible to allow the refrigeration oil to flow quickly back into the compressor body 1 through the oil return hole 2201. When the compressor body 1 is not overheated, the separated liquid is liquid refrigerant. In this case, a smaller oil return hole 2201 is required to reduce the rate at which liquid refrigerant enters the compressor body 1 through the oil return hole 2201.

[0132] In the related art, the size of the oil return hole 2201 is fixed and cannot be adjusted according to the working conditions of the compressor body 1. It is impossible to 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 gas 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 directions.

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

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

[0137] Reference Figure 10 When the compressor is sucking 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] For example, when the floating portion 300 descends to the first position, both oil return holes 2201 are open. When the floating portion 300 ascends to the second position, the floating portion 300 blocks the upper oil return hole 2201, leaving the lower oil return hole 2201 open.

[0139] In some embodiments, reference Figure 9 and Figure 12 The floating portion 300 includes a floating main body 310, which is sleeved onto the outlet pipe 22. A gap 350 is defined between the floating main body 310 and the outlet pipe 22 for liquid circulation. The floating main body 310 has an opening, a second opening 340, which communicates with the gap 350. 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 the liquid can flow out smoothly along the oil return hole 2201 when the floating portion 300 rotates along the air outlet pipe 22 .

[0141] A folded portion 320 is provided at the bottom of the floating main body 310. The folded portion 320 folds inwardly of the floating main body 310 and fits over the outlet pipe 22. A small gap exists between the folded portion 320 and the outlet pipe 22, providing a tight fit that does not affect the vertical movement of the floating portion 300 along the outlet pipe 22. Furthermore, when the folded portion 320 is aligned with the oil return hole 2201, it seals the oil return hole 2201.

[0142] The folded portion 320 is configured to partially block 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 to the second position, the folded portion 320 faces the upper oil return hole 2201, thereby blocking the upper oil return hole 2201.

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

[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-shaped transition. A step portion 2202 is provided on the air outlet pipe 22 to limit the downward 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 colliding with 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 main 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 provided on the floating main body 310 , and the plurality of second openings 340 are arranged at intervals, further increasing the total area of ​​the second openings 340 and facilitating liquid circulation.

[0148] In one embodiment, two second openings 340 are defined on the floating main body 310 .

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

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

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

[0152] In some embodiments, reference Figure 12 The top of the floating part 300 is provided with a flange portion 330, which extends toward the outer peripheral side of the floating part 300. The flange portion 330 is configured to abut against the fixing portion 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 spaced apart 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 dual-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 to correspond 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 is then discharged through the exhaust pipe 12.

[0160] In some embodiments, improvements to the upper shell 410 are beneficial to reducing vibration and noise, reducing the oil discharge rate, increasing the oil supply, and improving 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 conducive. 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, thereby increasing the compressor noise.

[0162] In some embodiments, reference Figures 13 to 17 The upper shell 410 is disposed on top of the circumferential shell 430. The upper shell 410 includes a circumferential wall and an arcuate top wall, which are respectively referred to as the upper circumferential wall 412 and the upper arcuate top wall 411. The upper arcuate top wall 411 is disposed on 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 multiple first arc-shaped top walls 41101 and multiple second arc-shaped top walls 41102 , and the multiple first arc-shaped top walls 41101 and the multiple second arc-shaped top walls 41102 are staggered 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 curved top wall 41101 is located is greater than the radius of the circle on which the second curved top wall 41102 is located, and a platform portion for mounting components is provided on the first curved 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 pump body airflow frequency 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 curved top wall 411 is composed of the staggered arrangement of the first curved top wall 41101 and the second curved 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 curved top wall 41101 and the second curved top wall 41102. When installing devices on the first curved top wall 41101, the second curved top wall 41102 in a lower position can avoid it.

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

[0168] In some embodiments, reference Figure 17 The radius of the upper circumferential wall 412 is R4, the radius of the circumference of the second arc-shaped top wall 41102 is R5, the height of the upper shell 410 is H6, 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 Figure 13 and Figure 14 A first platform portion 413 is provided on the first curved top wall 41101. The first platform portion 413 is configured to install the 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 curved top wall 41102. The low-positioned second curved top wall 41102 avoids the junction box 18, thereby facilitating the installation of the junction box 18.

[0171] In some embodiments, reference Figure 17A 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 fitting clearance range between the wiring terminal 1801 and the first mounting hole 417 is [0.1 mm, 0.8 mm]. This helps to improve the installation reliability of the wiring terminal 1801.

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

[0173] The matching area between the second platform portion 414 and the hanging portion 20 is greater than 766mm 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 Figure 13 A third platform portion 415 is provided on the first curved top wall 41101, and a connecting member 19 is provided on the third platform portion 415. 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 defined at the top of the upper curved top wall 411, through which the exhaust pipe 12 passes. A fourth platform 416 is defined on the upper curved top wall 411, surrounding the second mounting hole 418. The fourth platform 416 is configured to mate with a welding electrode used when installing the exhaust pipe 12, facilitating welding operations on the exhaust pipe 12.

[0177] In some embodiments, reference Figure 15 and Figure 16A The upper lateral wall 412 includes the upper lateral wall section 1 41201 and the upper lateral wall section 2 41202. The upper lateral wall section 1 41201 is located at the lower part of the upper lateral wall section 2 41202. The thickness of the upper lateral wall section 1 41201 is less than the thickness of the upper lateral wall section 2 41202. A step is formed between the upper lateral wall section 1 41201 and the upper lateral wall section 2 41202.

[0178] Upper circumferential wall section 41201 is inserted into the top of circumferential housing 430. The height of upper circumferential wall section 41201 is E1. For example, E1 can be 12 ± 0.2 mm. This helps ensure reliable insertion between upper housing 410 and circumferential housing 430. The lower portion of upper circumferential wall section 41201 is inclined to facilitate insertion into circumferential housing 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, and the oil baffle rotates with the eccentric crankshaft 110, throwing oil onto the housing wall. Extending the exhaust pipe 12 to this position range helps prevent oil discharge rate design.

[0180] [The second sub-muffler of the compressor body]

[0181] In the related art, the second sub-muffler is a single-layer structure with 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 Figure 21 、 Figure 22 and Figure 24 The second sub-muffler 141 has a double-layer structure, including a third sub-muffler 610 (inner muffler) and a fourth sub-muffler 620 (outer muffler). An oil passage is provided within the eccentric crankshaft 110. The second bearing 151 includes an integral vertical portion 1511 and a transverse portion 1512. The eccentric crankshaft 110 is inserted through the vertical portion 1511. The lower shaft end is inserted through the vertical portion 1511.

[0182] 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.

[0183] The gas discharged from the second bearing 151 first enters the first silencer chamber 631 for the first silencer operation. The gas in the first silencer chamber 631 then flows into the second silencer chamber 632 for the second silencer operation. The gas then returns to the first silencer chamber 631 and is discharged to the top side of the compression mechanism 14 through the air flow channel 170 inside the compression mechanism 14.

[0184] The double-layer design of the second sub-muffler 141 extends the gas flow path, which helps to improve the sound-absorbing and noise-reducing effect.

[0185] In some embodiments, Figure 22 and Figure 23The following diagrams illustrate two different configurations of the third sub-muffler 610. The third sub-muffler 610 is provided with a first through-hole 611. The vertical portion 1511 extends through the first through-hole 611, forming a vent between the inner wall of the first through-hole 611 and the surrounding wall of the vertical portion 1511. The vent connects the first muffler chamber 631 with the second muffler chamber 632, allowing for gas flow.

[0186] Figure 24 : This 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 to ensure normal oiling of the oil suction port.

[0187] The bottom of the fourth sub-muffler 620 contacts and seals the bottom end of the vertical portion 1511 to prevent gas from leaking therefrom.

[0188] In some embodiments, reference Figure 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. This gap should be understood as the vent mentioned above.

[0189] 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 circulation.

[0190] In some embodiments, reference Figure 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 communicates with the second sub-through-hole 613, and the second sub-through-hole 613 extends toward the outer periphery of the first sub-through-hole 612. The vertical portion 1511 penetrates 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. In other words, the second sub-through-hole 613 allows gas to circulate, and can be understood as the vent mentioned above.

[0191] 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.

[0192] It should be noted that the difference between the sound power level incident on the muffler inlet and the sound power level transmitted out of the muffler outlet is called sound transmission loss, or simply sound loss.

[0193] In some embodiments, reference Figure 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 .

[0194] 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 along the circumference of 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 .

[0195] In some embodiments, the area of ​​the vent is S1, the area of ​​the exhaust port on the transverse portion 1512 is S2, and S1 / S2>0.9.

[0196] 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 is greater than 0.9, the pressure loss and sound loss are relatively stable.

[0197] 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.

[0198] In some embodiments, reference Figures 21 to 23 The bottom wall of the third sub-muffler 610 is an arc-shaped wall 614. 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. 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. The flange 616 is connected to the transverse portion 1512.

[0199] The radius of the outer contour of the flange 616 is R10, and the radius of the arc wall 614 is R11. R10 and R11 satisfy the relationship: R10 / R11>0.3. The third sub-muffler 610 is designed to be hemispherical, which helps to increase the resonance frequency and reduce noise.

[0200] In some embodiments, reference Figure 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 .

[0201] 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, are passed through the outer mounting hole 624 and the inner mounting hole 617 to connect to the transverse portion 1512. In other words, the third sub-muffler 610 and the fourth sub-muffler 620 are fixedly mounted using the same connector, facilitating installation and improving installation efficiency.

[0202] [Matching structure of the second bearing, second piston, and second cylinder in the compression mechanism]

[0203] 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.

[0204] 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.

[0205] In some embodiments, reference Figure 25 A first annular groove 1513 is provided at the top of the transverse portion 1512 . 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 . The top of the first annular groove inner wall 1514 is lower than the top of the transverse portion 1512 .

[0206] The second cylinder 121 is disposed at the top of the transverse portion 1512. The second piston 131 is disposed within the compression chamber of the second cylinder 121 and is sleeved onto the second eccentric shaft segment 114. When the second piston 131 performs eccentric circular motion along 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.

[0207] By setting the top of the first annular groove inner wall 1514 lower than the top of the transverse portion 1512 , friction between the second piston 131 and the transverse portion 1512 is reduced, thereby helping to reduce compressor wear and improve performance.

[0208] In some embodiments, reference Figure 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. Figure 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.

[0209] In some embodiments, reference Figure 25 The distance between the bottom end of the first annular groove 1513 and the top 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 inner wall 1514 of the first annular groove is H13. H12 and H13 satisfy the relationship: 0.2mm≤H12-H13≤2mm, which is conducive to preventing radial deformation of the annular groove.

[0210] In some embodiments, reference Figure 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 segment 115 is D14, (D16-D17) / D14=0.08-0.22, which is beneficial to reducing the friction loss of the second bearing 151.

[0211] In some embodiments, reference Figure 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, and 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. 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 conducive to reducing wear and improving the reliability of the second bearing 151.

[0212] In some embodiments, a second annular groove is provided 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 provided in the second annular groove.

[0213] During compressor operation, the lower thrust surface of the eccentric crankshaft 110 and the surface of the second bearing 151 contact and move relative to each other, forming a friction pair. During compressor startup, the refrigeration oil has not yet circulated through this friction pair. The provision of a second annular groove and a lubrication area within it helps reduce wear between the thrust surface of the eccentric crankshaft 110 and the second bearing 151, improving reliability.

[0214] In some embodiments, the lubricating portion is a steel ring, and the upper surface of the steel ring is coated with a Teflon coating to achieve self-lubrication.

[0215] In some embodiments, reference Figure 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.

[0216] [Exhaust valve]

[0217] In related technologies, the opening of the exhaust valve is affected by the coupling of back pressure, airflow thrust, and elastic force. When closed, it relies solely on the valve's own elastic force. The opening and closing of the valve is significantly affected by operating conditions, making it difficult to accurately open and close. This can lead to problems such as failure to open properly at low frequencies and delayed closing at high frequencies, thus affecting compressor performance. In some embodiments, the compressor's exhaust mechanism is improved so that the exhaust valve opens normally and without vibration at low frequencies, and closes promptly at high frequencies, improving compressor performance.

[0218] In some embodiments, the bearing is provided with an exhaust hole. An exhaust valve plate 720 is provided on the bearing and is configured to open or close the exhaust hole. A lift limiter 710 is provided on the bearing and is configured to limit the displacement of the exhaust valve plate 720.

[0219] Reference Figures 26 to 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.

[0220] A reset member 740 , such as a spring, is provided between the exhaust valve disc 720 and the lift limiter 710 . The reset member 740 is configured to apply a force to the exhaust valve disc 720 to move the exhaust valve disc 720 toward the exhaust hole.

[0221] When the compressor needs to begin exhausting, the electromagnetic suction unit 730 is energized, and the electromagnetic suction unit 730 attracts the exhaust valve disc 720, thereby quickly opening the exhaust valve disc 720. During the opening process, the suction force prevents vibration, thereby preventing pressure loss caused by vibration of the exhaust valve disc 720. At this time, the reset member 740 is squeezed and compressed.

[0222] Before the exhaust is completed, the electromagnetic suction part 730 is powered off, and the elastic potential energy of the exhaust valve plate 720 itself and the reset member 740 is used to achieve rapid closing of the exhaust valve plate 720, thereby avoiding the problem of delayed closing of the exhaust valve plate 720.

[0223] By reducing exhaust resistance loss and reducing high-pressure gas backflow, the capacity of the compressor can be significantly improved, thereby improving energy efficiency.

[0224] In some embodiments, reference Figure 26 and Figure 28 The exhaust valve plate 720 includes a valve head 721, a valve tail 722, and a connecting section 723. The connecting section 723 connects the valve head 721 and the valve tail 722. The valve tail 722 is connected to a bearing, and the valve head 721 is configured to open or close the exhaust hole. The electromagnetic suction unit 730 is directly opposite the valve head 721, improving the electromagnetic suction unit 730's attraction to the valve head 721.

[0225] 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 relatively reliable reset force to the valve plate head 721 .

[0226] In some embodiments, reference Figure 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, and 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.

[0227] The effective length of the exhaust valve plate 720 starts at the tangent point between the valve plate and the lift limiter 710 , and ends at the center of the valve plate head 721 .

[0228] 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 (Computer Aided Design Engineering), the height H, effective length L, curvature radius R, and valve thickness T of the exhaust valve plate 720 were designed through multi-objective design. After multiple iterations, combined with the exhaust valve plate 720SN curve, it was determined that when 1.5<(L1 / R12)×t1+H9<3.0, the stress on the head of the exhaust valve plate 720 is within the allowable range. In theory, the exhaust valve plate 720 can be used indefinitely. 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 low, the effective flow area is low, 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 achieve accurate opening and closing of the exhaust valve plate 720.

[0229] In some embodiments, reference Figure 28 The 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.

[0230] In some embodiments, the inner diameter of the cylinder is D13, and D12 and D13 satisfy the relationship: 0.2<D12 / D13<0.3.

[0231] It should be noted that the size of the cylinder, bore, and exhaust port significantly affect the airflow velocity. Excessive airflow velocity can also cause significant impact on exhaust valve plate 720. When the relationship 0.2 < D12 / D13 < 0.3 is satisfied, the impact force on exhaust valve plate 720 can be minimized while maintaining low pressure loss.

[0232] In some embodiments, reference Figure 26 A copper wire is provided on the side of the lift limiter 710 away from the exhaust valve plate 720, and the copper wire is connected to the controller. When the copper wire is energized, an electromagnetic suction part 730 is formed, which has a simple structure and is easy to implement.

[0233] In some embodiments, the electromagnetic suction part 730 is provided 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.

[0234] The reset member 740 is arranged 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.

[0235] [Muffler on the exhaust pipe]

[0236] The noise inside the air conditioner room usually comes from wind noise, refrigerant pulsation sound, etc. Wind noise is generally broadband white noise, which often does not cause discomfort to customers.

[0237] It should be noted that white noise refers to noise whose power spectral density is constant throughout the frequency domain. Random noise with the same energy density at all frequencies is called white noise.

[0238] However, refrigerant pulsation noise is mostly pure sound, and it varies with the compressor's operating frequency, the difference in indoor and outdoor temperature, and other factors. Since refrigerant pulsation noise primarily originates from the compressor, a muffler is typically placed at the compressor's exhaust port to reduce abnormal noise. However, traditional expansion mufflers can achieve a certain noise suppression effect in a small high-frequency or low-frequency band. However, when the compressor operates at a high frequency or the refrigerant pressure fluctuates significantly, they are unable to achieve a good noise reduction effect, resulting in the appearance of pure sound components in the room, leading to customer complaints.

[0239] In some embodiments, the silencer structure at the compressor exhaust port is improved to effectively reduce the refrigerant pulsation sound and avoid the appearance of pure sound components inside the air conditioner room.

[0240] For example, refer to Figure 29 and Figure 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 .

[0241] 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 .

[0242] The muffler 800 includes a connecting pipe section, the inner diameter of which is larger than the inner diameter of the exhaust pipe 12 .

[0243] The muffler 800 further includes a flexible pipe section 830. The inner diameter of the flexible pipe section 830 is larger than the inner diameter of the exhaust pipe 12.

[0244] 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 .

[0245] For example, the muffler 800 is an automatically variable volume muffler to suppress the transmission of refrigerant pulsation sound.

[0246] 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.

[0247] In some embodiments, reference Figure 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 .

[0248] 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 for easy expansion and contraction.

[0249] In some embodiments, the driving portion 860 is configured to drive the first connecting pipe segment 810 and the second connecting pipe segment 820 to move closer to each other so that the flexible pipe segment 830 contracts.

[0250] The driving portion 860 is further configured to drive the first connecting pipe segment 810 and the second connecting pipe segment 820 away from each other to extend the flexible pipe segment 830 .

[0251] It should be noted that the flexible pipe section 830 is located between the first connecting pipe section 810 and the second connecting pipe section 820 , and the driving unit 860 drives the movement of the first connecting pipe section 810 and the second connecting pipe section 820 to achieve the contraction or extension of the flexible pipe section 830 .

[0252] 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.

[0253] In some embodiments, a first connecting portion 840 is provided on one of the first connecting pipe segment 810 and the second connecting pipe segment 820 , and a second connecting portion 850 is provided on the other one.

[0254] A driving motor 861 is provided on one of the first connecting portion 840 and the second connecting portion 850 , and a threaded hole is provided on the other one. A screw rod 862 is provided at the power output end of the driving motor 861 , and the screw rod 862 is connected to the threaded hole.

[0255] 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.

[0256] In some embodiments, the sensor 17 detects the vibration frequency of the exhaust pipe 12 in the range of 1000 to 3000 Hz.

[0257] 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.

[0258] 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.

[0259] 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].

[0260] It should be noted that the inner diameter of the compressor main casing 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 be increased while reducing the oil discharge rate.

[0261] 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 .

[0262] The muffler 800 includes a pipe section connected to the exhaust pipe 12. The inner diameter of the pipe section is larger than the inner diameter of the exhaust pipe 12. The muffler 800 is an expansion type muffler.

[0263] The muffler 800 includes a driving unit 860 configured to drive the pipe section to move and change the volume of the pipe section according to the vibration frequency of the exhaust pipe 12. The muffler 800 is an automatically variable volume muffler to improve the effect of suppressing the transmission of refrigerant pulsation sound.

[0264] [Compressor foot]

[0265] To reduce the vibration of the compressor body, vibration isolation pads can 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 pads are too low, it is easy for the compressor to shake excessively during transportation, which can impact the pipeline and cause pipeline breakage and other problems.

[0266] In some embodiments, the base of the compressor is optimized to improve the vibration reduction effect.

[0267] 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.

[0268] The mounting portion 16 is disposed outside the circumferential housing 430 . A mounting hole is provided on the mounting portion 16 , and the inner diameter of the mounting hole is D18 .

[0269] 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 .

[0270] It should be noted that, from the perspective of controlling the compressor's center of mass, 4.5 < H10 / H16 < 6.5, and 5.5 < D10 / D18 < 8.5 are beneficial for reducing compressor housing vibration and meeting the requirements for rotor compressor housing vibration reduction.

[0271] In some embodiments, if the number of feet 15 is too large, installation becomes inconvenient. If the number of feet 15 is too small, the feet 15 are subjected to greater force, are susceptible to deformation when falling, and experience significant vibration. For example, the weight of the compressor is G (kg), and the number of feet 15 is N (units). G and N satisfy the formula: 12.5 > G / N > 5. In other words, 12.5 kg / unit > designed compressor weight / number of feet 15 > 5 kg / unit. Within this range, the compressor exhibits low vibration and noise, and exhibits excellent fall resistance.

[0272] In some embodiments, three feet 15 are provided on the side of the circumferential housing 430. The angle between the foot 15 near 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. Within this range, the compressor has low vibration and noise and good drop resistance.

[0273] In some embodiments, four feet 15 are provided on the side of the circumferential housing 430. The angle between the feet 15 near 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. Within this range, the compressor has low vibration and noise and good drop resistance.

[0274] 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 noise of the compressor is small within this range.

[0275] 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 of the technical disclosures can also be selected to combine 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 achieve certain invention purposes; 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.

[0276] Any technical disclosure in this disclosure, as well as the recombination of multiple technical disclosures, can form a complete technical solution and can solve one or more of the above-mentioned technical problems and achieve the purpose of the invention. They all belong to the content of this disclosure and are the content that is directly and unambiguously determined based on the content of this disclosure.

[0277] Those skilled in the art will understand that the scope of the present invention is not limited to the above specific embodiments, and that 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: a shell, wherein a compression mechanism is disposed inside the shell, and the compression mechanism is configured to compress the refrigerant; Characterized in that the housing comprises: Circumferential housing; A lower shell is arranged at the bottom of the circumferential shell, the lower shell comprises a circumferential wall and an arc-shaped bottom wall, the arc-shaped bottom wall is arranged at the bottom of the circumferential wall, the circumferential wall is connected to the circumferential shell, and a flat surface is arranged at the bottom of the arc-shaped bottom wall; The adsorption part is arranged on the plane part, the adsorption part is configured to adsorb iron filings, and a through hole is arranged on the adsorption part, and the through hole extends along the height direction of the adsorption part.

2. The compressor according to claim 1, characterized in that The outer diameter of the inner wall of the circumferential wall is D4, the outer diameter of the adsorption portion is D5, and D4 / D5=[3,6].

3. The compressor according to claim 1, characterized in that The outer diameter of the adsorption portion is D5, the inner diameter of the through hole is D6, and D5 / D6=[1.5,3].

4. The compressor according to claim 1, characterized in that The outer diameter of the adsorption part is D5, the thickness of the adsorption part is t, and D5 / t=[6,15].

5. The compressor according to claim 1, characterized in that The height of the lower shell is H7, the radius of the planar portion is R6, the radius of the circle where the arc-shaped bottom wall is located is R7, and H7 / (R6×R7)>0.

013.

6. The compressor according to any one of claims 1 to 5, characterized in that: A connecting portion is arranged on the planar portion, and the connecting portion includes a base. The base is arranged on the planar portion, and a plurality of folded portions arranged at intervals are arranged on the side edge of the base. The folded portions are configured to press the adsorption portion toward a direction close to the base to limit the position so as to install the adsorption portion on the connecting portion.

7. The compressor according to claim 6, characterized in that An inclined extension portion is disposed on one of the side edges of the base, and the inclined extension portion extends obliquely upward in a direction away from the adsorption portion.

8. The compressor according to any one of claims 1 to 5, characterized in that: The circumferential wall comprises a first circumferential wall section and a second circumferential wall section of an integral structure, wherein the first circumferential wall section is located at the upper portion of the second circumferential wall section, the thickness of the first circumferential wall section is smaller than the thickness of the second circumferential wall section, and a step is formed between the first circumferential wall section and the second circumferential wall section; The first section of the circumferential wall is inserted into the bottom of the circumferential shell, the height of the first section of the circumferential wall is 12±0.2 mm, and the upper part of the first section of the circumferential wall is an inclined wall.

9. The compressor according to any one of claims 1 to 5, characterized in that: A foot is provided on the side of the circumferential shell, and a plurality of the foot are provided. The plurality of foot are arranged at intervals along the circumference of the circumferential shell, the radius of the foot is R8, the outer contour radius of the circumferential shell is R9, and R8 / R9>0.

15.

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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