CN222542652U - Compressor and air conditioner - Google Patents

Abstract

The utility model discloses a compressor and an air conditioner, wherein the compressor comprises a shell, the shell comprises a circumferential shell, an upper shell is arranged on the top of the circumferential shell, the upper shell comprises a circumferential wall and an arc-shaped top wall, the arc-shaped top wall is arranged on the top of the circumferential wall, the circumferential wall is connected to the circumferential shell, the arc-shaped top wall is formed by sequentially connecting a plurality of first arc-shaped top walls and a plurality of second arc-shaped top walls, the plurality of first arc-shaped top walls and a plurality of second arc-shaped top walls are arranged alternately along the circumference of the arc-shaped top wall, the radius of the circumference of the first arc-shaped top wall is greater than the radius of the circumference of the second arc-shaped top wall, and a platform part for mounting a device is arranged on the first arc-shaped top wall. The utility model can achieve the effects of reducing vibration and noise, reducing oil discharge rate, increasing oil supply, and improving fatigue strength.

Description

Compressor and air conditioner

Technical Field

The present disclosure relates to the field of air conditioning technologies, and in particular, to a compressor and an air conditioner.

Background

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 compressor comprises a shell, a motor and a compression mechanism are arranged in an inner cavity surrounded by the shell, the compression mechanism is used for compressing refrigerant, and an exhaust pipe is arranged at the top of the shell. The gaseous refrigerant compressed and discharged by the compression mechanism flows into the space between the motor and the upper shell and is discharged through the exhaust pipe. In the prior art, the design of the upper shell of the compressor has the following disadvantages:

(1) The space between the motor and the upper shell is smaller, which is not beneficial to the design of the oil discharge rate;

(2) When the gaseous refrigerant flows to the upper space through the motor, a certain impact is formed on the upper shell, so that the resonance between the airflow and the upper shell is easily caused, and the noise of the compressor is increased;

(3) The upper shell is generally required to be provided with a junction box, a temperature sensor and other components, so that a mounting platform is required to be arranged on the upper shell, and the space between the motor and the upper shell can be further reduced due to the arrangement of the mounting platform.

The above information disclosed in this background section is only for enhancement of understanding of the background section of the application and therefore it may not form the prior art that is already known to those of ordinary skill in the art.

Disclosure of utility model

Aiming at the problems pointed out in the background art, the utility model provides a compressor and an air conditioner, which are used for improving the structure of an upper shell of the compressor, so as to achieve the effects of reducing vibration and noise, reducing oil discharge rate, improving oil supply and improving fatigue strength.

In one aspect, a compressor is provided, the compressor includes the casing, the casing includes circumference casing, the top of circumference casing sets up the casing, it includes circumference wall and arc roof to go up the casing, the arc roof sets up in the top of circumference wall, circumference wall and circumference casing are connected, the arc roof is formed by a plurality of first arc roof and a plurality of second arc roof tandem in proper order, a plurality of first arc roof and a plurality of second arc roof are along the circumference staggered arrangement of arc roof, the radius of the circumference that first arc roof was located is greater than the radius of the circumference that second arc roof was located, set up the platform portion that is used for installing the device on the first arc roof.

The arrangement of the arc top wall enables the upper shell to be of a hemispherical structure, is beneficial to improving resonance frequency, avoiding resonance between the airflow frequency of the pump body and the upper shell, improving vibration reduction and noise reduction effects, and meanwhile, the volume of the cavity is increased, which is beneficial to the design of oil discharge rate, and in addition, is beneficial to improving fatigue strength of the upper shell.

The arc top wall is arranged by the staggered arrangement of the first arc top wall and the second arc top wall, the radiuses of the arc top wall and the second arc top wall are different, the cavity volume is increased as much as possible, a height difference is formed between the first arc top wall and the second arc top wall, and when a device is installed on the first arc top wall, the second arc top wall at a low position can avoid.

The platform part is designed to mount devices, such as junction boxes, temperature sensors, welding electrodes, hooks and the like, so that the devices are convenient to mount.

In another aspect, an air conditioner is provided. The air conditioner comprises a compressor, an evaporator, a condenser and a throttling device. The compressor is the compressor.

Drawings

FIG. 1 is a block diagram of a compressor according to some embodiments;

FIG. 2A is a side view of a compressor according to some embodiments;

FIG. 2B is a cross-sectional view of a compressor according to some embodiments;

FIG. 3 is a top view of a compressor according to some embodiments;

FIG. 4 is a block diagram of a bracket according to some embodiments;

FIG. 5 is another block diagram of a bracket according to some embodiments;

FIG. 6 is another top view of a compressor according to some embodiments;

FIG. 7 is yet another block diagram of a bracket according to some embodiments;

FIG. 8 is a block diagram of a bracket and a circumferential housing according to some embodiments;

FIG. 9 is a cross-sectional view of a gas-liquid separator according to some embodiments;

FIG. 10 is a block diagram of a floating portion after floating up according to some embodiments;

FIG. 11 is a block diagram of a floating member after it has fallen in accordance with some embodiments;

FIG. 12 is a block diagram of a floating portion according to some embodiments;

FIG. 13 is a block diagram of a compressor body according to some embodiments;

FIG. 14 is a block diagram of an upper housing according to some embodiments;

FIG. 15 is a cross-sectional view of a first housing according to some embodiments;

FIG. 16A is an enlarged view of a portion of 15 at circle A;

FIG. 16B is an enlarged view of a portion of 15 at circle B;

FIG. 17 is a cross-sectional view of an upper housing according to some embodiments;

FIG. 18 is a block diagram of a lower housing according to some embodiments;

FIG. 19 is a block diagram of the lower housing and the suction portion according to some embodiments;

FIG. 20 is a block diagram of an adsorbent section according to some embodiments;

FIG. 21 is a cross-sectional view of a compression mechanism according to some embodiments;

FIG. 22 is a block diagram of a third sub-muffler according to some embodiments;

FIG. 23 is another block diagram of a third sub-muffler according to some embodiments;

FIG. 24 is a block diagram of a fourth sub-muffler according to some embodiments;

FIG. 25 is an assembly view of an eccentric crankshaft, a second bearing, a second cylinder, a second piston according to some embodiments;

FIG. 26 is a block diagram of an exhaust valve plate and lift limiter according to some embodiments;

FIG. 27 is another block diagram of an exhaust valve plate and lift limiter according to some embodiments;

FIG. 28 is a block diagram of an exhaust valve sheet according to some embodiments;

FIG. 29 is a block diagram of a compressor body, an exhaust pipe, a muffler according to some embodiments;

FIG. 30 is a block diagram of a muffler according to some embodiments;

FIG. 31 is a block diagram of an eccentric crankshaft according to some embodiments.

Detailed Description

Some embodiments of the present disclosure will now be described more fully hereinafter with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the disclosure. All other embodiments obtained by one of ordinary skill in the art based on the embodiments provided by the present disclosure are within the scope of the present disclosure.

Throughout the specification and claims, unless the context requires otherwise, the word "comprise" and its other forms such as the third person referring to the singular form "comprise" and the present word "comprising" are to be construed as open, inclusive meaning, i.e. as "comprising, but not limited to. In the description of the specification, the terms "one embodiment", "some embodiments (some embodiments)", "exemplary embodiment (exemplary embodiments)", "example (example)", "specific example (some examples)", etc. are intended to indicate that a particular feature, structure, material, or characteristic associated with the embodiment or example is included in at least one embodiment or example of the present disclosure. The schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.

The terms "first" and "second" are used below for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the embodiments of the present disclosure, unless otherwise indicated, the meaning of "a plurality" is two or more.

In describing some embodiments, expressions of "coupled" and "connected" and their derivatives may be used. The term "coupled" is used in a broad sense, and may be either permanently coupled, detachably coupled, or integrally formed, or indirectly coupled via an intervening medium, for example. The term "coupled" means that two or more elements are in direct physical or electrical contact. The term "coupled" or "communicatively coupled (communicatively coupled)" may also mean that two or more elements are not in direct contact with each other, but yet still co-operate or interact with each other. The embodiments disclosed herein are not necessarily limited to the disclosure herein.

At least one of "A, B and C" has the same meaning as at least one of "A, B or C" and each includes a combination of A, B and C of a alone, B alone, C alone, a combination of a and B, a combination of a and C, a combination of B and C, and a combination of A, B and C.

"A and/or B" includes three combinations of A only, B only, and a combination of A and B.

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

As used herein, "about," "approximately" or "approximately" includes the stated values as well as average values within an acceptable deviation range of the particular values as determined by one of ordinary skill in the art in view of the measurement in question and the errors associated with the measurement of the particular quantity (i.e., limitations of the measurement system).

As used herein, "parallel", "perpendicular", "equal" includes the stated case as well as the case that approximates the stated case, the range of which is within an acceptable deviation range as determined by one of ordinary skill in the art taking into account the measurement in question and the errors associated with the measurement of the particular quantity (i.e., limitations of the measurement system). For example, "parallel" includes absolute parallel and approximately parallel, where the range of acceptable deviation of approximately parallel may be, for example, within 5 ° of deviation, and "perpendicular" includes absolute perpendicular and approximately perpendicular, where the range of acceptable deviation of approximately perpendicular may also be, for example, within 5 ° of deviation. "equal" includes absolute equal and approximately equal, where the difference between the two, which may be equal, for example, is less than or equal to 5% of either of them within an acceptable deviation of approximately equal.

[ Air conditioner ]

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 refrigerating and heating cycle includes a series of processes involving compression, condensation, expansion and evaporation, and refrigerating or heating an indoor space.

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

The expansion valve expands the liquid-phase refrigerant in a high-temperature and high-pressure state formed by condensation in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator may achieve a cooling effect by exchanging heat with a material to be cooled using latent heat of evaporation of a refrigerant. The air conditioner may adjust the temperature of the indoor space throughout the cycle.

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

The indoor heat exchanger and the outdoor heat exchanger function as a condenser or an evaporator. The air conditioner performs a heating mode when the indoor heat exchanger is used as a condenser, and performs a cooling mode when the indoor heat exchanger is used as an evaporator.

The outdoor assembly further includes a four-way valve configured to allow the indoor heat exchanger and the outdoor heat exchanger to be switched as a condenser or an evaporator.

The refrigerating principle of the air conditioner is that the compressor works to make the interior of the indoor heat exchanger (in the indoor component, the evaporator at this time) in ultra-low pressure state, the liquid refrigerant in the indoor heat exchanger is quickly evaporated to absorb heat, the air blown out by the indoor fan is cooled by the indoor heat exchanger coil pipe and then changed into cold air to blow into the indoor, the evaporated refrigerant is pressurized by the compressor and then condensed into liquid state in the high-pressure environment in the outdoor heat exchanger (in the outdoor component, the condenser at this time) to release heat, and the heat is dissipated into the atmosphere by the outdoor fan, so that the refrigerating effect is achieved.

The heating principle of the air conditioner is that the gaseous refrigerant is pressurized by the compressor to become high temperature and high pressure gas, which enters the indoor heat exchanger (the condenser at this time), and the gas is condensed, liquefied and released to become liquid, and the indoor air is heated at the same time, so as to achieve the purpose of increasing the indoor temperature. The liquid refrigerant is decompressed by the throttling device, enters the outdoor heat exchanger (an evaporator at the moment), evaporates, gasifies and absorbs heat to become gas, and simultaneously absorbs heat of outdoor air (the outdoor air becomes colder) to become gaseous refrigerant, and enters the compressor again to start the next cycle.

[ Compressor body ]

In some embodiments of the present disclosure, the compressor is a rolling rotor compressor, and referring to fig. 1 and 2, the compressor includes a compressor body 1. The compressor body 1 includes a first housing 11, a closed inner cavity is formed in the first housing 11, and a motor 13 and a compression mechanism 14 are disposed in the inner cavity. The motor 13 powers the compressor mechanism. The compression mechanism 14 is configured to compress a refrigerant. The motor 13 is disposed above the compression mechanism 14. Fig. 21 is a cross-sectional view of compression mechanism 14.

In some embodiments, referring to fig. 13, the first housing 11 includes an upper housing 410, a circumferential housing 430, and a lower housing 420. The circumferential housing 430 is disposed between the upper housing 410 and the lower housing 420. The upper case 410 is disposed at the top of the circumferential case 430, and the lower case 420 is disposed at the bottom of the circumferential case 430. The upper casing 410, the circumferential casing 430 and the lower casing 420 enclose an inner cavity of the compressor body 1.

In some embodiments, the motor 13 includes a stator and a rotor, the stator being fixedly coupled to the inner wall of the first housing 11 to achieve a fixed mounting of the motor 13 in the compressor cavity.

In some embodiments, referring to fig. 21, the compression mechanism 14 includes an eccentric crankshaft 110, a cylinder, a piston, bearings, a muffler, and the like.

In some embodiments, referring to fig. 31, the eccentric crankshaft 110 includes a first shaft section 111 (upper shaft section), an eccentric shaft section, and a second shaft section 115 (lower shaft section), the first shaft section 111 is fixedly connected with the rotor, a piston is disposed in a compression chamber of the cylinder, the piston is sleeved on the eccentric shaft section, a bearing is fixedly connected with the cylinder, a bearing exhaust hole is disposed on the bearing, the bearing exhaust hole is communicated with the compression chamber, a sliding vane groove is disposed on the cylinder, a sliding vane is disposed in the sliding vane groove, the eccentric crankshaft 110 drives the piston to do circumferential movement in the compression chamber, the sliding vane reciprocates along the sliding vane groove, the sliding vane always abuts against the piston, and the sliding vane and the piston divide the compression chamber into a high pressure chamber and a low pressure chamber.

The working principle of the compressor is that a stator of the motor 13 generates magnetic pulling force after being electrified, a rotor of the motor 13 rotates under the action of the magnetic pulling force of the stator and drives the eccentric crankshaft 110 to rotate together, the eccentric crankshaft 110 rotates to drive a piston sleeved on an eccentric shaft section of the eccentric crankshaft to do eccentric circular motion in a compression cavity of a cylinder, a sliding vane reciprocates in a sliding vane groove, the sliding vane and the piston divide the compression cavity of the cylinder into a high-pressure cavity and a low-pressure cavity, the eccentric crankshaft 110 drives the piston to rotate for one circle, air is sucked from the low-pressure cavity and exhausted from the high-pressure cavity to complete one-time exhaust, the compressor compresses air, and the compressed air is exhausted through a bearing exhaust hole.

In some disclosed embodiments, the compressor is a double-cylinder scroll rotor type compressor, and referring to fig. 21, the compression mechanism 14 specifically includes an eccentric crankshaft 110, two cylinders (a first cylinder 122 (upper cylinder) and a second cylinder 121 (lower cylinder), respectively), two bearings (a first bearing 152 (upper bearing) and a second bearing 151 (lower bearing), respectively), two pistons (a first piston 132 (upper piston) and a second piston 131 (lower piston), respectively), a middle partition 160, and two silencers (divided into a first sub-silencer 142 (upper silencer) and a second sub-silencer 141 (lower silencer)).

In some embodiments, referring to fig. 31, the eccentric crankshaft 110 includes, in order 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.

In some embodiments, a first piston 132 capable of eccentric movement is arranged in a compression cavity of the first cylinder 122, the first piston 132 is sleeved on the first eccentric shaft section 112, a second piston 131 capable of eccentric movement is arranged in a compression cavity of the second cylinder 121, the second piston 131 is sleeved on the second eccentric shaft section 114, a middle partition 160 is sleeved on the connecting shaft section 113, the middle partition 160 is positioned between the first cylinder 122 and the second cylinder 121, a first bearing 152 is sleeved on the first shaft section 111 and is simultaneously connected with the first cylinder 122, and a second bearing 151 is sleeved on the second shaft section 115 and is simultaneously connected with the second cylinder 121.

The first eccentric shaft section 112 and the second eccentric shaft section 114 are arranged at 180 ° relative angles, the first piston 132 and the second piston 131 simultaneously perform eccentric rotation, compressed air in the compression chamber of the first cylinder 122 is discharged through the exhaust hole on the first bearing 152, and compressed air in the compression chamber of the second cylinder 121 is discharged through the exhaust hole on the second bearing 151.

With continued reference to fig. 21, first sub-muffler 142 is disposed on first bearing 152, and first sub-muffler 142 covers the exhaust hole of first bearing 152, and compressed air in first cylinder 122 is discharged into the space surrounded by first sub-muffler 142 and first bearing 152 through the exhaust hole of first bearing 152, and then is discharged into the inner cavity of the compressor through the exhaust hole of first sub-muffler 142.

The second sub-muffler 141 is disposed on the second bearing 151, and the second sub-muffler 141 covers the exhaust hole of the second bearing 151, and the compressed air in the second cylinder 121 is discharged into the space surrounded by the second sub-muffler 141 and the second bearing 151 through the exhaust hole of the second bearing 151.

In some embodiments, unlike the related art, no exhaust hole is provided on the second sub-muffler 141 in fig. 21. The walls of the first bearing 152, the first cylinder 122, the middle partition 160, the second cylinder 121 and the second bearing 151 are provided with a plurality of air flow channels 170 which are penetrated up and down, and compressed air in the second bearing 151 and the second sub-muffler 141 is discharged upwards into a space surrounded by the first bearing 152 and the first sub-muffler 142 through the air flow channels 170 and then is discharged into the inner cavity of the compressor through the exhaust holes of the first sub-muffler 142.

[ Shell of compressor body ]

The gaseous refrigerant compressed and discharged by the compression mechanism 14 flows into the space between the motor 13 and the upper case, and is discharged through the discharge pipe 12.

In some embodiments, the upper housing 410 is modified to facilitate vibration damping, noise reduction, reduced oil discharge rate, increased oil supply, and increased fatigue strength.

In some embodiments, the oil discharge rate is not favored due to the small space between the motor 13 and the upper housing 410, and when the gaseous refrigerant flows to the upper space through the motor 13, a certain impact is formed to the upper housing 410, which easily causes the air flow to resonate with the upper housing 410, increasing the compressor noise.

In some embodiments, referring to fig. 13-17, the upper housing 410 is disposed on top of the circumferential housing 430. The upper housing 410 includes a circumferential wall and an arcuate top wall, denoted as upper circumferential wall 412 and upper arcuate top wall 411, respectively. The upper arc-shaped top wall 411 is disposed on top of the upper circumferential wall 412, and the upper circumferential wall 412 is connected with the circumferential housing 430.

In some embodiments, the upper arc-shaped top wall 411 is formed by sequentially joining a plurality of first arc-shaped top walls 41101 and a plurality of second arc-shaped top walls 41102, and the plurality of first arc-shaped top walls 41101 and the plurality of second arc-shaped top walls 41102 are staggered along the circumferential direction of the upper arc-shaped top wall 411.

It should be noted that, the radius of the circumference of the first arc-shaped top wall 41101 is larger than the radius of the circumference of the second arc-shaped top wall 41102, and the first arc-shaped top wall 41101 is provided with a platform portion for mounting the device.

In some embodiments, the upper arc top wall 411 is configured to make the upper housing 410 have a hemispherical structure, which is helpful for increasing the resonance frequency, avoiding the pump body air flow frequency from resonating with the upper housing 410, improving the vibration reduction and noise reduction effects, and simultaneously increasing the cavity volume, which is beneficial for the design of the oil discharge rate, and in addition, is helpful for improving the fatigue strength of the upper housing 410.

It should be noted that, the upper arc top wall 411 is formed by staggering the first arc top wall 41101 and the second arc top wall 41102, and the radii of the first arc top wall 41101 and the second arc top wall 41102 are different, so that the cavity volume can be increased, a height difference is formed between the first arc top wall 41101 and the second arc top wall 41102, and when a device is installed on the first arc top wall 41101, the second arc top wall 41102 at a low position can avoid.

The platform portion is designed to facilitate the mounting of devices such as junction box 18, temperature sensor 117, welding electrodes, hooks, etc.

In some embodiments, referring to fig. 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, and the height of the upper housing 410 is H6, H6/(r4×r5) >0.01, which is in the range that is beneficial for reducing resonance.

In some embodiments, the upper housing 410 generally needs to be provided with a junction box 18, a temperature sensor 117, and the like, so a mounting platform needs to be provided on the upper housing 410, and the provision of the mounting platform reduces the space between the motor 13 and the upper housing 410.

In some embodiments, referring to fig. 13 and 14, a first platform 413 is disposed on the first arc-shaped top wall 41101, the first platform 413 is configured to mount the junction box 18, a portion of the bottom surface of the junction box 18 is in contact with the first platform 413, another portion is not in contact with the adjacent second arc-shaped top wall 41102, and the second arc-shaped top wall 41102 at a low position is configured to avoid the junction box 18, so as to facilitate the mounting of the junction box 18.

In some embodiments, referring to fig. 17, a first mounting hole 417 is provided on the first platform 413, and the terminal 1801 of the terminal block 18 is disposed in the first mounting hole 417, and a fit clearance between the terminal 1801 and the first mounting hole 417 ranges from [0.1mm,0.8mm ], which helps to improve the mounting reliability of the terminal 1801.

In some embodiments, a second platform portion 414 is disposed on the first arcuate top wall 41101, the second platform portion 414 being configured to mount the lifting portion 20, the lifting portion 20 being configured to lift the compressor body 1 for use in an up-stream of the production line.

The matching area of the second platform part 414 and the lifting part 20 is larger than 766mm ², which is helpful to improve the strength of the mounting structure of the lifting part 20, thereby improving the lifting reliability of the compressor body 1.

In some embodiments, referring to fig. 13, a third platform portion 415 is provided on the first arcuate top wall 41101, and a connector 19 is provided on the third platform portion 415, with the connector 19 being disposed obliquely. An angled spacing cavity is formed between the connector 19 and the third platform portion 415, the spacing cavity being configured to mount the temperature sensor 117.

The temperature sensor 117 is mounted and limited by the connector 19. The connecting piece 19 is obliquely arranged, so that the temperature sensor 117 can be conveniently inserted from top to bottom in an inclined mode, and the temperature sensor 117 is prevented from falling out.

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

In some embodiments, referring to fig. 15 and 16A, the upper circumferential wall 412 includes an upper circumferential wall first section 41201 and an upper circumferential wall second section 41202, the upper circumferential wall first section 41201 being located at a lower portion of the upper circumferential wall second section 41202, the upper circumferential wall first section 41201 having a thickness less than a thickness of the upper circumferential wall second section 41202, a step being formed between the upper circumferential wall first section 41201 and the upper circumferential wall second section 41202.

The upper circumferential wall section 41201 is inserted at the top of the upper circumferential housing 430, and the height of the upper circumferential wall section 41201 is E1, for example, E1 may be 12±0.2mm, which helps to ensure the reliability of the insertion between the upper housing 410 and the circumferential housing 430. The lower portion of the upper circumferential wall 41201 is a sloped wall to facilitate insertion into the circumferential housing 430.

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 ranges from [5,20] mm. The position is a low pressure area, the oil baffle plate rotates along with the eccentric crankshaft 110, oil is thrown to the wall surface of the shell, and the exhaust pipe 12 extends to the position range, so that the design of preventing the oil discharge rate is facilitated.

[ Gas-liquid separator ]

In some embodiments, referring to fig. 1, the compressor further comprises a gas-liquid separator 2. The gas-liquid separator 2 is provided outside the compressor body 1 and is configured to supply gaseous refrigerant into the compression chamber of the compression mechanism 14. The gas-liquid separator 2 completes separation of the liquid refrigerant and the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 1 to cause compressor abnormality.

In some embodiments, referring to fig. 1 and 9, the gas-liquid separator 2 includes a second housing 21, and an outlet pipe 22 is provided at the bottom of the second housing 21. One end of the air outlet pipe 22 extends into the inner cavity of the second shell 21, and the other end of the air outlet pipe 22 is connected with the compression mechanism 14 to provide gaseous refrigerant for the compression mechanism 14.

[ Connection Structure of compressor body and gas-liquid separator ]

Currently, the gas-liquid separator 2 is fixedly installed outside the compressor body 1 by the bracket 200. When the compressor is operated, the compressor body 1 and the gas-liquid separator 2 are prone to generate low-frequency resonance and low-frequency noise. Therefore, it is necessary to increase the natural frequency of the upper revolution of the gas-liquid separator 2 to avoid low frequency resonance when the compressor body 1 and the gas-liquid separator 2 are operated. In the related art, the natural frequency of the gas-liquid separator 2 is low, so that low-frequency noise is easily generated when the compressor is operated.

In order to solve the above-mentioned 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 avoid low frequency noise generated when the compressor is operated.

The present embodiment gives a connection structure between the two gas-liquid separators 2 and the compressor body 1, which will be described separately below.

[ Connection Structure of compressor body and gas-liquid separator ]

In some embodiments, referring to fig. 3-5, the compressor includes two symmetrically arranged brackets 200, the two brackets 200 being configured to connect the first housing 11 and the second housing 21.

Either stent 200 of the two stents 200 comprises a stent one portion 210, a stent two portion 220, a stent three portion 230, and a stent four portion 240, which are connected in sequence. The first bracket part 210 and the third bracket part 230 are positioned on the same side of the second bracket part 220, the second bracket part 220 and the fourth bracket part 240 are positioned on different sides of the third bracket part 230, and the second bracket part 220 is adapted to and fixedly connected with the outer contour of the second housing 21, such as by welding. The first bracket 210 and the third bracket 230 extend between the first housing 11 and the second housing 21, respectively. The first bracket part 210 and the fourth bracket part 240 are fixedly connected, such as welded, with the first housing 11. The length of the first bracket portion 210 is greater than the length of the third bracket portion 230, and the two fourth bracket portions 240 are adjacent to each other.

For each bracket 200, two fixing parts of the first housing 11 are realized by welding the first bracket part 210 and the fourth bracket part 240 with the first housing 11, so that when the two brackets 200 are matched for use, the first housing 11 is fixed everywhere, and the connection stability of the bracket 200 and the first housing 11 is improved.

For example, when the two brackets 200 are used in combination, the two bracket two parts 220 together play a role in clamping the gas-liquid separator 2, so as to improve the connection stability of the brackets 200 and the second housing 21.

In some embodiments, referring to fig. 5, an opening is disposed on the first portion 210 of the bracket, that is, a first opening 250, where the first opening 250 extends along the length direction of the first portion 210 of the bracket, the width of the first opening 250 is H, and the length of the first opening 250 is L, H/l= (0,0.82).

By varying the size of the first opening 250, the connection stiffness of the gas-liquid separator 2 can be varied, which is advantageous in obtaining the desired natural frequency.

In some embodiments, referring to fig. 3 and 4, the width of the bracket two 220 is W3, the outer contour radius of the second housing 21 is R2, and the range of W3/R2 is [1.4,2.2]. Within this range, the natural frequency of the gas-liquid separator 2 is facilitated to be increased.

In some embodiments, referring to fig. 3, the radius of the arc-shaped structure where the bracket two portion 220 is located is R3, and the outer contour radius of the second housing 21 is R2, R3-r2= [0.5mm,2mm ]. In the range, the welding installation positioning between the two is facilitated.

In some embodiments, referring to fig. 3, the arc α of the bracket two 220 is greater than 39 °, which helps to improve the reliability of the clamping of the bracket 200 to the gas-liquid separator 2.

In some embodiments, referring to fig. 3, the distance from the intersection of the first bracket portion 210 and the second bracket portion 220 to the symmetry plane of the two brackets 200 is W1, the distance from the third bracket portion 230 to the symmetry plane of the two brackets 200 is W2, the outer contour radius of the second housing 21 is R2, the outer contour radius of the first housing 11 is R1, (W1/R2) × (W2/R1) >0.3. In the range, the double torsion frequency of the gas-liquid separator 2 tends to be stable, the solid frequency is increased to be more than 510Hz, and the double-cylinder compressor is suitable for double-cylinder compressors with the maximum rotation speed of 180 rps.

In some embodiments, referring to fig. 3 and 4, the first bracket section 210 includes a first bracket section 211 and a second bracket section 212 that are integrally formed, the first bracket section 211 extends obliquely outward from a first end of the second bracket section 212, the first bracket section 211 is adapted and fixedly connected to the first housing 11, and a second end of the second bracket section 212 is connected to the second bracket section 220.

The angle beta between the second end of the first bracket section 212 and the end of the first bracket section 211 and the second bracket section 212 is 2 deg..

In some embodiments, the number of welding points between the bracket one portion 210 and the first housing 11 is greater than 2, such as 4, and the number of welding points between the bracket four portion 240 and the first housing 11 is also greater than 2, such as 4, so that the reliability of the connection between the bracket one portion 210 and the first housing 11 and the reliability of the connection between the bracket four portion 240 and the first housing 11 can be improved.

In some embodiments, referring to fig. 2A, the height of the compressor body 1 is H1, specifically the distance between the bottom of the lower housing 420 to the top of the discharge pipe 12. The bracket 200 has a height H2 from the bottom of the compressor body 1 (referred to as the bottom of the lower housing 420), H2/h1= [0.49,0.71]. Within this range, radial vibration of the gas-liquid separator 2 is reduced, and compressor noise is reduced.

In some embodiments, referring to fig. 3, the distance between the two bracket portions 210 and the connection location of the first housing 11 is D2, and the outer diameter of the first housing 11 is D1, D2/d1= [0.06,0.9]. Within this range, radial vibration of the gas-liquid separator 2 is reduced, and compressor noise is reduced.

[ Connection Structure of compressor body and gas-liquid separator ]

In some embodiments, referring to fig. 6 and 7, the compressor includes a bracket 200, the bracket 200 being configured to connect the first housing 11 and the second housing 21.

The stand 200 includes a stand body portion 260, and stand extension portions 270 are symmetrically provided at opposite ends of the stand body portion 260. The holder main body 260 is adapted to and fixedly coupled with the outer contour of the first housing 11, such as by welding. The bracket extension 270 is of unitary construction including an extension first segment 271 and an extension second segment 272. The extension portion one section 271 is connected between the bracket body portion 260 and the extension portion two section 272. The extension segment 272 is fixedly connected, for example welded, to the outer contour of the second housing 21.

For example, referring to fig. 6, the outer contour radius of the first housing 11 is R1, the outer contour radius of the second housing 21 is R2, and the distance between the extension portion segment 271 and the symmetry plane of the bracket 200 is W4,2W 4/(r1+r2) = [0.35,0.55]. Within this range, the vibration of the gas-liquid separator 2 is facilitated to be reduced.

In some embodiments, referring to fig. 7, the distance between the location of the weld 280 between the bracket body 260 and the first housing 11 and the plane of symmetry of the bracket 200 is W5, W5/W4> 0.75. The larger W5/W4 is, the better, and when the W5/W4 is larger than 0.75, the vibration lifting amplitude of the gas-liquid separator 2 is not obvious.

In some embodiments, referring to fig. 7, the extension portion two-section 272 is welded to the second housing 21, a distance between two adjacent welding points 280 along a height direction of the extension portion two-section 272 is H3, and a height of the extension portion two-section 272 is H4, H3/h4= [0.75,0.85].

Two welding holes 290 are formed in each second extending section 272, the distance between two adjacent welding holes 290 is equal to the distance between two welding points 280, and H3 is also used, and it is noted that the distance between two adjacent welding holes 290 also meets the above range, so that the vibration of the gas-liquid separator 2 can be reduced.

In some embodiments, referring to fig. 7, the height of the stand body 260 is H4, and referring to fig. 8, the distance between the stand body 260 and the outlet duct 22 of the gas-liquid separator 2 is H5, H4/h5= [0.2,0.35]. Within this range, the vibration of the gas-liquid separator 2 is facilitated to be reduced.

In some embodiments, referring to fig. 6, the angle θ of the perpendicular line between the two extension sections 272 and the axis of the second housing 21 ranges from [90 °,140 ° ], which helps to reduce the vibration of the gas-liquid separator 2 and increase the torsional frequency of the gas-liquid separator 2.

In some embodiments, referring to fig. 2A, the side of the first housing 11 is provided with a foot 15, the radius of the foot 15 is R8, the radius of the outer contour of the first housing 11 is R9, and R8/R9>0.15, which makes the compressor body 1 more stable and less vibrating.

In some embodiments, referring to fig. 2A, the height of the first housing 11 is H1. The distance between the motor 13 and the top of the first housing 11 is H15, H15/h1= [0.25-0.35].

A certain cavity volume exists between the upper part of the motor 13 and the upper shell 410, and the larger the cavity is, the more favorable the oil separation effect is improved, so that the oil discharge rate is reduced. As cavity volume is also related to compressor noise level. By setting the above range, the compressor noise can be reduced.

[ Gas outlet pipe of gas-liquid separator ]

In some embodiments, the liquid is stored at the bottom of the gas-liquid separator 2, and an oil return hole 2201 is provided on the gas outlet pipe 22 of the gas-liquid separator 2. When the compressor body 1 is overheated in suction, the separated liquid is the refrigerator oil, and the oil return hole 2201 needs to be as large as possible so that the refrigerator oil quickly flows back to the compressor body 1 through the oil return hole 2201. When the compressor body 1 is not overheated, the separated liquid is a liquid refrigerant, and in order to reduce the rate of the liquid refrigerant entering the compressor body 1 through the oil return hole 2201, a smaller oil return hole 2201 is required.

In the related art, the size of the oil return hole 2201 is fixed, cannot be adjusted according to the working condition of the compressor body 1, and cannot be used for both accelerating the return of the refrigerating machine oil when the balance is overheated and reducing the return of the liquid refrigerant when the balance is not overheated.

In some embodiments, the outlet tube 22 is modified to accelerate the return of the refrigerator oil and reduce the rate of liquid refrigerant entering the compressor body 1, thereby improving compressor efficiency.

For example, referring to fig. 9 to 12, the air outlet pipe 22 is provided with a plurality of oil return holes 2201 on a pipe section located in the cavity, and the plurality of oil return holes 2201 are arranged at intervals in the height direction of the air outlet pipe 22. For example, the air outlet pipe 22 is provided with two oil return holes 2201 which are arranged at intervals up and down.

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, and the floating portion 300 is configured to move along the height direction of the gas outlet pipe 22.

In some embodiments, referring to fig. 11, when the compressor suction is overheated, the float 300 is lowered to the first position, at which the plurality of oil return holes 2201 are in an open state, increasing the oil return rate.

Referring to fig. 10, when the suction gas of the compressor is not overheated, the liquid level in the gas-liquid separator 2 is rapidly increased, the floating part 300 floats up to the second position under the buoyancy of the liquid in the cavity, part of the oil return holes 2201 are blocked, the rate of flowing the liquid refrigerant into the compressor body 1 is reduced, and the liquid impact is prevented.

Taking the example of providing two oil return holes 2201, when the floating portion 300 is lowered to the first position, both the oil return holes 2201 are in an open state. When the floating portion 300 floats up to the second position, the floating portion 300 seals the oil return hole 2201 located above and the oil return hole 2201 located below is opened.

In some embodiments, referring to fig. 9 and 12, the floating portion 300 includes a floating body portion 310, the floating body portion 310 is sleeved on the air outlet pipe 22, and a gap 350 for liquid to circulate is provided between the floating body portion 310 and the air outlet pipe 22. The floating body 310 is provided with an opening, which is a second opening 340, and the second opening 340 communicates with the gap 350. The liquid enters the gap 350 through the second opening 340 and then flows out through the oil return hole 2201.

The cooperation of the second opening 340 and the gap 350 can ensure that the liquid can smoothly flow out along the oil return hole 2201 when the floating portion 300 rotates along the air outlet pipe 22.

The bottom of the floating body 310 is provided with a turnover part 320, the turnover part 320 turns over inwards of the floating body 310, and the turnover part 320 is sleeved on the air outlet pipe 22. The gap between the turnover part 320 and the air outlet pipe 22 is smaller, the two are in clearance fit, the up-and-down movement of the floating part 300 along the air outlet pipe 22 is not influenced, and when the turnover part 320 is aligned with the oil return hole 2201, the turnover part 320 plays a role in blocking the oil return hole 2201.

The turnover portion 320 is configured to block a portion of the oil return hole 2201 when the floating portion 300 is in the second position. In other words, taking the example of providing two oil return holes 2201, when the floating portion 300 floats to the second position, the turnover portion 320 is opposite to the oil return hole 2201 located above, and the turnover portion 320 seals the oil return hole 2201 located above.

The turnover portion 320 is also configured to remove the oil return hole 2201 to open the oil return hole 2201 when the floating portion 300 is in the first position. In other words, taking the example of providing two oil return holes 2201, when the floating portion 300 is lowered to the first position, the turnover portion 320 is offset from the oil return holes 2201, so that all the oil return holes 2201 are in an open state.

In some embodiments, floating body portion 310 is integrally formed with flip portion 320, with an arcuate transition between floating body portion 310 and flip portion 320. The outlet pipe 22 is provided with a stepped portion 2202, and the stepped portion 2202 is configured to restrict the lowered position of the floating portion 300.

The descending displacement of the floating part 300 is restricted by the stepped part 2202 on the outlet pipe 22, and the floating part 300 is prevented from striking the bottom wall of the gas-liquid separator 2.

In some embodiments, the second opening 340 extends along the height direction of the floating body portion 310, improving the fluid flow smoothness and reducing the fluid flow resistance.

In some embodiments, the floating body 310 is provided with a plurality of second openings 340, and the plurality of second openings 340 are spaced apart, so as to further increase the total area of the second openings 340, and facilitate the circulation of the liquid.

In one embodiment, two second openings 340 are provided in the floating body portion 310.

In some embodiments, referring to fig. 9, a fixing portion 23 is disposed in the cavity of the gas-liquid separator, and the gas outlet pipe 22 passes through the fixing portion 23. The fixing portion 23 is provided with a mounting hole for mounting the air outlet pipe 22. The fixing portion 23 is further provided with a plurality of through holes through which gas and liquid circulate.

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, the floating portion 300 moves upward to the abutment with the fixed portion 23, and the stopper is moved upward.

The floating part 300 is limited by the existing fixed part 23 in the gas-liquid separator 2, and no additional limiting structure is needed.

In some embodiments, referring to fig. 12, the top of the floating portion 300 is provided with a burring portion 330, and the burring portion 330 extends toward the outer peripheral side of the floating portion 300. The burring 330 is configured to abut against the fixing portion 23 to limit the floating position of the floating portion 300.

The flanging part 330 increases the contact area with the fixing part 23 and reduces the stress of the fixing part 23.

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.

When the floating portion 300 is lowered to the first position, both oil return holes 2201 are in an open state.

When the floating portion 300 floats to the second position, the turnover portion 320 faces the oil return hole 2201 located above, and the oil return hole 2201 is blocked.

In some embodiments, the compressor body 1 is a double-cylinder rotary type, and the gas-liquid separator 2 includes two gas outlet pipes 22, and a floating portion 300 is disposed on each gas outlet pipe 22. The two air outlet pipes 22 are respectively arranged corresponding to the two air cylinders in the compression mechanism 14 so as to provide gaseous refrigerant for the inner cavities of the corresponding air cylinders.

[ Oil pool adsorption section of compressor body ]

In some embodiments, each friction pair may produce wear debris when the compressor is running, and if the debris is not effectively controlled, it may cause wear of the friction pair, degrading compressor performance and causing compressor damage. Generally, a mode of arranging a magnet in an oil pool at the bottom of the compressor is adopted to adsorb scrap iron on the magnet. However, the larger the magnet outer diameter is, the higher the cost is, and the smaller the magnet outer diameter is, the lower the magnet adsorption rate is, and the iron scrap adsorption effect is poor.

In addition, the magnets are disposed on the bottom shell of the compressor, and the volume of the space between the bottom shell and the compression mechanism 14 is generally small, which results in limited oil pool volume, which is disadvantageous to the oil supply design, and the lower shell easily resonates with the air flow, increasing compressor noise.

The embodiment improves the magnets in the bottom shell and the oil pool of the compressor, and achieves the effects of improving the iron filings adsorption rate, reducing the cost, vibration and noise and improving the oil supply.

In some embodiments, referring to fig. 15, 18-20, the housing includes a circumferential housing 430 and a lower housing 420. The lower case 420 is disposed at the bottom of the circumferential case 430. The lower housing 420 includes a peripheral wall and an arcuate bottom wall 621, respectively designated as lower peripheral wall 422 and lower arcuate bottom wall 421. The lower arc bottom wall 421 is disposed at the bottom of the lower circumferential wall 422, the lower circumferential wall 422 is connected with the circumferential housing 430, and the bottom of the lower arc bottom wall 421 is provided with the plane portion 423.

The lower arc bottom wall 421 enables the lower shell 420 to be of a hemispherical structure, improves the resonance frequency, avoids the resonance between the pump body airflow frequency and the lower shell 420, increases the cavity volume, increases the bottom oil pool volume, and is beneficial to oil supply design.

The spherical design of the lower housing 420 reduces the planar area, the smaller the area, the higher the oil pressure reciprocating fatigue strength and the water pressure resistance.

The plane portion 423 is provided with an adsorption portion 500, the adsorption portion 500 is located in the oil sump, and the adsorption portion 500 is configured to adsorb scrap iron. The suction portion 500 is provided with a through hole 520, and the through hole 520 extends in the height direction of the suction portion 500. The suction portion 500 is, for example, a magnet.

Through the through holes 520 arranged on the adsorption part 500, the cost is reduced and the scrap iron adsorption effect is improved while the outer diameter of the adsorption part 500 is ensured to be large enough.

In some embodiments, referring to fig. 18, the inner wall of the lower circumferential wall 422 has an outer diameter D4, and referring to fig. 20, the adsorbent 500 has an outer diameter D5, d4/d5= [3,6].

The inner diameter of the through hole 520 is D6, D5/d6= [1.5,3].

The thickness of the adsorption part 500 is t, d5/t= [6,15].

Through above-mentioned setting, satisfy high rotational speed impurity adsorption demand, satisfy the low cost demand.

In some embodiments, referring to fig. 18, the height of the lower housing 420 is H7, the radius of the planar portion 423 is R6, the radius of the circumference of the lower arc bottom wall 421 is R7, and the resonance frequency is not significantly increased within this range, i.e., H7/(r6×r7) > 0.013.

In some embodiments, referring to fig. 19, a connection portion 510 is provided on a planar portion 423, the connection portion 510 includes a base 511, the base 511 is fixedly provided on the planar portion 423, a turndown 512 is provided on a side edge of the base 511, and the turndown 512 is configured to press the adsorption portion 500 against a limit in a direction approaching the base 511, so as to achieve a fixed installation of the adsorption portion 500 on the connection portion 510.

The suction unit 500 is limited by the turndown 512, so that the suction unit 500 is convenient to install.

In some embodiments, an inclined extension 513 is provided on one of the side edges of the base 511, and the inclined extension 513 extends obliquely upward in a direction away from the suction part 500, so as to guide the detachment of the suction part 500.

In some embodiments, referring to fig. 15 and 16B, the lower circumferential wall 422 includes a lower circumferential wall first segment 42201 and a lower circumferential wall second segment 42202, the lower circumferential wall first segment 42201 being located above the lower circumferential wall second segment 42202, the thickness of the lower circumferential wall first segment 42201 being less than the thickness of the lower circumferential wall second segment 42202, a step being formed between the lower circumferential wall first segment 42201 and the lower circumferential wall second segment 42202.

The lower circumferential wall 42201 is inserted into the bottom of the circumferential housing 430, and the upper portion of the lower circumferential wall 42201 is an inclined wall, so that the insertion and installation between the lower circumferential wall 42201 and the circumferential housing 430 are facilitated.

The height of the lower circumferential wall 42201 is E2, E2 is 12±0.2mm, which helps to ensure the reliability of the insertion between the lower housing 420 and the circumferential housing 430.

[ Second sub-muffler of compressor body ]

In the related art, the second sub-muffler has a single-layer structure, and has limited noise reduction effect and poor oil discharge prevention effect. The embodiment improves the second sub-muffler, improves the noise reduction effect and reduces the oil discharge rate. In some embodiments, referring to fig. 21, 22 and 24, the second sub-muffler 141 has an inner and outer double structure, including a third sub-muffler 610 (inner muffler) and a fourth sub-muffler 620 (outer muffler). The eccentric crankshaft 110 is provided with an oil delivery passage inside. The second bearing 151 includes a vertical portion 1511 and a lateral portion 1512 of an integral structure, and the eccentric crankshaft 110 is provided through the vertical portion 1511. The lower shaft end is arranged on the vertical part 1511 in a penetrating way.

The third sub-muffler 610 is disposed at the bottom of the second bearing 151, and a first muffling chamber 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 muffling chamber 632 is formed between the fourth sub-muffler 620 and the third sub-muffler 610.

The gas discharged from the second bearing 151 enters the first muffler chamber 631 for the first time, and the gas in the first muffler chamber 631 flows into the second muffler chamber 632 again for the second time, is returned to the first muffler chamber 631 again, and is discharged to the top side of the compression mechanism 14 through the gas flow path 170 in the compression mechanism 14.

The double-layer design of the second sub-muffler 141 lengthens the gas flow path, contributing to the improvement of the noise reduction effect.

In some embodiments, fig. 22 and 23 are block diagrams of two different forms of third sub-muffler 610. The third sub-muffler 610 is provided with a first through hole 611, the vertical portion 1511 penetrates through the first through hole 611, and a vent is formed between an inner wall of the first through hole 611 and a peripheral wall of the vertical portion 1511. The vent communicates the first sound deadening chamber 631 with the second sound deadening chamber 632, and the gas is supplied.

Fig. 24 is a structural view 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 opposite to the second through hole 623, so that the normal oiling of the oil suction port is ensured.

The bottom of the fourth sub-muffler 620 is sealed in contact with the bottom end of the vertical portion 1511, avoiding gas leakage therefrom.

In some embodiments, referring to fig. 22, the inner diameter of the first through hole 611 is greater than the outer diameter of the vertical portion 1511. The vertical portion 1511 passes through the first through hole 611, and a gap through which gas flows is formed between the outer circumferential wall of the vertical portion 1511 and the inner circumferential wall of the first through hole 611, which should be understood as the above-described vent.

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

In some embodiments, referring to fig. 23, the first through hole 611 includes a first sub through hole 612 (main through hole) and a second sub through hole 613 (sub through hole), the first sub through hole 612 communicates with the second sub through hole 613, and the second sub through hole 613 extends to an outer circumferential side of the first sub through hole 612. The vertical portion 1511 is disposed through the first sub-through hole 612, and the second sub-through hole 613 communicates the first sound deadening chamber 631 with the second sound deadening chamber 632, that is, the second sub-through hole 613 is configured to allow gas to flow therethrough, which may be understood as the above-described vent.

For example, the second sub-through hole 613 is a semicircular hole design, and the position of the opening is determined according to the sound loss design.

The difference between the level of the sound power incident on the inlet of the muffler and the level of the sound power transmitted out of the outlet of the muffler is called sound transmission loss, or simply sound loss.

In some embodiments, referring to fig. 23, two second sub-vias 613 are provided, and the two second sub-vias 613 are symmetrically arranged with respect to the first sub-via 612.

In some embodiments, a protruding portion is disposed inside the bottom wall 621 of the fourth sub-muffler 620, and extends along the circumference of the second through hole 623, and abuts against the bottom end surface of the vertical portion 1511, and is designed in an interference manner, so as to achieve sealing with the second bearing 151.

In some embodiments, the vent area is S1 and the vent area on the transverse portion 1512 is S2, S1/S2>0.9.

The larger S1/S2 is, the better S1 is, the smaller the pressure loss is, the smaller the corresponding sound loss is, and when S1/S2 is more than 0.9, the pressure loss and the sound loss are stable.

The pressure loss is simply referred to as a pressure loss, and refers to a phenomenon in which pressure is reduced due to friction, bending, expansion, contraction, or the like during the flow of a fluid or gas.

In some embodiments, referring to fig. 21-23, 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 a circumferential wall, denoted as a first circumferential wall 615, the first circumferential wall 615 extends upward, the top of the first circumferential wall 615 is connected to a flange 616, the flange 616 extends to the outer circumferential side of the first circumferential wall 615, and the flange 616 is connected to the transverse portion 1512.

The radius of the circumference of the flange 616 is R10, the radius of the circumference of the curved wall 614 is R11, and R10 and R11 satisfy the relationship R10/R11>0.3. The third sub-muffler 610 is of a semi-spherical design, thus helping to increase the resonant frequency and reduce noise.

In some embodiments, referring to fig. 24, fourth sub-muffler 620 includes a bottom wall 621 and a second circumferential wall 622, the inner side wall of second circumferential wall 622 abutting the outer circumferential wall of transverse portion 1512.

The third sub-muffler 610 is provided with an inner mounting hole 617, the fourth sub-muffler 620 is provided with an outer mounting hole 624, and a connector, such as a bolt, is inserted through the outer mounting hole 624 and the inner mounting hole 617 to be coupled with the transverse portion 1512. That is, the third sub-muffler 610 and the fourth sub-muffler 620 are fixedly installed through the same connection member, so that installation is facilitated and installation efficiency is improved.

[ Fitting Structure of second bearing and second piston and second cylinder in compression mechanism ]

In the related art, friction exists between the bottom end surface of the second piston 131 and the top end surface of the second bearing 151, affecting the compressor efficiency.

In some embodiments, the mating structure between the second bearing 151 and the second piston 131, the second cylinder 121 is modified to allow for both low wear and high performance of the compressor.

In some embodiments, referring to fig. 25, a first annular groove 1513 is provided at the top of the transverse portion 1512, the first annular groove 1513 surrounding the shaft hole of the second bearing 151, a first annular groove inner wall 1514 being formed between the first annular groove 1513 and the shaft hole of the second bearing 151, the top of the first annular groove inner wall 1514 being lower than the top of the transverse portion 1512.

The second cylinder 121 is disposed on top of the transverse portion 1512. The second piston 131 is disposed in the compression chamber of the second cylinder 121, and the second piston 131 is sleeved on the second eccentric shaft section 114. When the second piston 131 moves eccentrically and circularly with the eccentric crankshaft 110, friction occurs between the bottom end surface of the second piston 131 and the top end surface of the transverse portion 1512.

By providing 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 contributing to reduced compressor wear and improved performance.

In some embodiments, referring to FIG. 25, the second shaft section 115 has an outer diameter D14, the vertical portion 1511 has an outer diameter D15, the vertical portion 1511 has a height H10, and referring to FIG. 21, the second shaft 151 has a height H11, D14, D15, H10, and H11 satisfying the relationship (D14/D15) × (H10/H11) >0.38, which is advantageous for reducing the friction loss of the compressor.

In some embodiments, referring to FIG. 25, the distance from the bottom end of the first annular groove 1513 to the top end surface of the second bearing 151 is H12, the distance from the bottom end of the first annular groove 1513 to the top of the first annular groove inner wall 1514 is H13, and H12 and H13 satisfy the relationship 0.2 mm.ltoreq.H2-H13.ltoreq.2 mm, which is advantageous in preventing radial deformation of the annular groove.

In some embodiments, referring to fig. 25, the first annular groove 1513 has an outer peripheral wall diameter D16, the first annular groove 1513 has an inner peripheral wall diameter D17, and the second shaft segment 115 has an outer diameter D14, (D16-D17)/d14=0.08-0.22, which is advantageous in reducing friction loss of the second bearing 151.

In some embodiments, referring to FIG. 25, the diameter of the outer peripheral wall of the first annular groove 1513 is D16, the diameter of the inner peripheral wall of the first annular groove 1513 is D17, the distance from the bottom end of the first annular groove 1513 to the top of the inner wall 1514 of the first annular groove is H13, and D16, D17 and H13 satisfy the relation of 0.2.ltoreq.D 16-D17/H13.ltoreq.0.5, thus the radial stress of the second bearing 151 is small, the deformation is small, the abrasion is facilitated to be reduced, and the reliability of the second bearing 151 is improved.

In some embodiments, a second annular groove is provided at the top of the transverse portion 1512, the second annular groove surrounding the outer peripheral side of the first annular groove 1513, and a lubrication is provided in the second annular groove.

During operation of the compressor, the lower thrust surface of the eccentric crankshaft 110 contacts and moves relative to the surface of the second bearing 151, forming a friction pair. At the very beginning of the compressor, the refrigerating machine oil has not yet been circulated at this friction pair. By providing the second annular groove and providing the lubrication portion in the second annular groove, the wear of the thrust surface of the eccentric crankshaft 110 and the second bearing 151 can be reduced, and the reliability can be improved.

In some embodiments, the lubrication part is a steel ring, and the upper surface of the steel ring is coated with a Teflon coating to play a self-lubricating role.

In some embodiments, referring to FIG. 25, the thickness of the partition 160 is t2, the height of the second cylinder 121 is H14, and t2 and H14 satisfy the relationship 0.22.ltoreq.t2/H14.ltoreq.0.35, which is advantageous for improving the energy conversion efficiency (Coefficient of Performance, COP) of the compressor.

[ Exhaust valve sheet ]

In the related art, the opening of the exhaust valve plate is influenced by the coupling of the back pressure, the air flow thrust and the elastic force, and the valve plate only depends on the elastic force when the exhaust valve plate is closed. The valve plate is opened and closed, so that the valve plate is greatly influenced by working conditions, the valve plate cannot be accurately opened and closed, and the problems that the valve plate cannot be normally opened at low frequency and is closed at high frequency time delay easily occur are solved, so that the performance of the compressor is influenced. In some embodiments, the exhaust mechanism of the compressor is improved, so that the exhaust valve plate is normally opened at low frequency without trembling, and is closed at high frequency in time, thereby improving the performance of the compressor.

In some embodiments, a vent is provided on the bearing. The bearing is provided with a discharge valve plate 720, and the discharge valve plate 720 is configured to open or close the discharge hole. The lift limiter 710 is provided to the bearing, and the lift limiter 710 is configured to limit the displacement amount of the exhaust valve plate 720.

Referring to fig. 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 discharge valve plate 720 when the compression mechanism 14 discharges.

A return member 740, such as a spring, is disposed between the exhaust valve plate 720 and the lift limiter 710, the return member 740 being configured to apply a force to the exhaust valve plate 720 that moves the exhaust valve plate 720 in a direction toward the exhaust hole.

When the compressor needs to start exhausting, the electromagnetic suction part 730 is electrified, the electromagnetic suction part 730 is utilized to attract the exhaust valve plate 720, the exhaust valve plate 720 is rapidly opened, and vibration can be avoided due to the attractive force in the opening process, so that pressure loss caused by vibration of the exhaust valve plate 720 is avoided. The restoring member 740 is compressed by being pressed at this time.

Before the exhaust is finished, the electromagnetic suction part 730 is powered off, and the quick closing of the exhaust valve plate 720 is realized by utilizing the elastic potential energy of the exhaust valve plate 720 and the resetting piece 740, so that the problem that the exhaust valve plate 720 is delayed to be closed is avoided.

By reducing the loss of exhaust resistance and reducing the reverse flow of high pressure gas, the capacity of the compressor can be significantly improved, thereby improving the energy efficiency.

In some embodiments, referring to fig. 26 and 28, the discharge valve plate 720 includes a valve plate head 721, a valve plate tail 722, and a connection section 723, the connection section 723 being connected between the valve plate head 721 and the valve plate tail 722. The valve plate tail 722 is connected to the bearing and the valve plate head 721 is configured to open or close the vent hole. The electromagnetic suction portion 730 faces the valve sheet head 721, and the suction effect of the electromagnetic suction portion 730 on the valve sheet head 721 is improved.

In some embodiments, the return member 740 is disposed between the valve plate head 721 and the lift limiter 710 such that the return member 740 can apply a more reliable return force to the valve plate head 721.

In some embodiments, referring to FIG. 27, the effective length of the discharge valve plate 720 is L1, the lift height of the discharge valve plate 720 is H9, the radius of curvature of the discharge valve plate 720 is R12, the thickness of the discharge valve plate 720 is t1, L1, R12, t1 and H9 satisfy the relationship 1.5< (L1/R12) xt1+H2 <3.0.

The effective length of the exhaust valve plate 720 begins at the point of tangency of the valve plate with the lift limiter 710 and ends at the center of the valve plate head 721.

In the present disclosure, the air flow thrust of the air discharge valve 720 under high-frequency operation is determined through theoretical calculation, and this is taken as a design boundary, in the finite element simulation of the Computer aided engineering (Computer AIDED ENGINEERING, CAE), through multiple iterations, the height H, the effective length L, the radius of curvature R and the valve sheet thickness T of the air discharge valve 720 are designed, and after the multiple iterations, the head stress of the air discharge valve 720 is determined to be within the allowable range when 1.5< (L1/R12) ×t1+h9<3.0, and the air discharge valve 720 can be theoretically used infinitely, and although the value of the relational (L1/R12) ×t1+h9 is below 1.5, the stress of the air discharge valve 720 also meets the requirement, but when the value is lower, the effective flow area is lower, the performance of the compressor is seriously affected, so when the relational meets 1.5< (L1/R12) ×t1+h9<3.0, and under the condition that the service life of the air discharge valve 720 is ensured, the air discharge valve 720 is also beneficial to be opened and closed accurately.

In some embodiments, referring to FIG. 28, the valve plate head 721 has a diameter D11 and the vent holes have a diameter D12, D11 and D12 satisfy the relationship 0.7< D11/D12<0.8, which is advantageous for satisfying the reliability of the vent valve plate 720.

In some embodiments, the cylinder bore is D13, and D12 and D13 satisfy the relationship 0.2< D12/D13<0.3.

It should be noted that, due to the sizes of the cylinder, the cylinder diameter and the exhaust hole, the airflow velocity may be significantly affected, and too large airflow velocity may also cause the impact of the exhaust valve plate 720 to be larger. When the relation satisfies 0.2< D12/D13<0.3, the impact force to the exhaust valve plate 720 can be reduced as much as possible on the premise of satisfying lower pressure loss.

In some embodiments, referring to fig. 26, the lift limiter 710 is provided with a copper wire on a side facing away from the exhaust valve plate 720, the copper wire is connected with the controller, and the copper wire is electrified to form the electromagnetic suction part 730, so that the structure is simple and convenient to implement.

In some embodiments, a solenoid suction 730 is provided to the lift limiter 710, the solenoid suction 730 being configured to energize to attract the discharge valve plate 720 when the compression mechanism 14 is discharged, the solenoid suction being configured to de-energize when the compression mechanism 14 is not discharged.

The reset member 740 is disposed between the discharge valve plate 720 and the lift limiter 710, the reset member 740 is configured to contract when the electromagnetic suction portion 730 attracts the discharge valve plate 720, and the reset member 740 is configured to apply a force to the discharge valve plate 720 that moves the discharge valve plate 720 in a direction approaching the exhaust hole.

[ Muffler on exhaust pipe ]

The noise inside the air conditioner generally originates from wind noise, refrigerant pulsation sound, and the like. Wind noise is typically broadband white noise, and many times does not cause customer discomfort.

White noise means noise in which the power spectral density is constant over the entire frequency domain. Random noise, where all frequencies have the same energy density, is called white noise.

However, most of the refrigerant pulsation sound is pure sound component and changes with the compressor running frequency, indoor and outdoor temperature difference and the like. Since the refrigerant pulsation sound is mainly from the compressor, a muffler is generally placed at the discharge port of the compressor, and the muffler is configured to reduce abnormal sound. However, the traditional expansion silencer can play a certain noise suppression effect on a small frequency band of high frequency or low frequency, but when the compressor has larger change of the operation frequency and the refrigerant pressure, the traditional expansion silencer cannot play a good noise reduction effect, so that the indoor pure-tone component is caused, and customer complaints are caused.

In some embodiments, the silencing structure at the exhaust port of the compressor is improved to effectively reduce the pulsation sound of the refrigerant and avoid pure sound components on the indoor side of the air conditioner.

For example, referring to fig. 29 and 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.

The exhaust pipe 12 is provided with a muffler 800. The muffler 800 is disposed downstream of the sensor 17 in the direction of gas flow in the exhaust pipe 12.

Muffler 800 includes a connecting pipe segment. The inner diameter of the connecting tube section is larger than the inner diameter of the exhaust tube 12.

Muffler 800 also includes a flexible pipe segment 830. The inner diameter of the flexible tube section 830 is greater than the inner diameter of the exhaust tube 12.

The muffler 800 further includes a driving portion 860, the driving portion 860 being configured to drive the flexible pipe section 830 to expand and contract in a length direction of the exhaust pipe 12 according to a vibration frequency of the exhaust pipe 12.

For example, muffler 800 is an automatically variable capacity muffler to suppress transmission of refrigerant pulsation sound.

It should be noted that, based on the muffler noise elimination principle, the noise elimination frequency is only related to the length of the muffler 800, so that the sensor 17 obtains the vibration frequency of the exhaust pipe 12, and then the driving part 860 drives the flexible pipe section 830 to extend or shorten, so as to realize the length change of the muffler 800, so as to improve the noise elimination effect.

In some embodiments, referring to fig. 30, the connecting tube segments include a first connecting tube segment 810 and a second connecting tube segment 820, with a flexible tube segment 830 connected between the first connecting tube segment 810 and the second connecting tube segment 820.

The first connection pipe segment 810 and the second connection pipe segment 820 are metal pipes, such as copper pipes. The flexible tube section 830 is a bellows to facilitate telescoping.

In some embodiments, the drive 860 is configured to drive the first and second connection tube segments 810, 820 toward each other to collapse the flexible tube segment 830.

The drive 860 is also configured to drive the first and second connecting tube segments 810, 820 away from each other to extend the flexible tube segment 830.

It should be noted that, the flexible pipe section 830 is disposed between the first connecting pipe section 810 and the second connecting pipe section 820, and the driving portion 860 drives the first connecting pipe section 810 and the second connecting pipe section 820 to move, so as to implement contraction or extension of the flexible pipe section 830.

The first and second connection pipe sections 810 and 820 are metal pipes, facilitating the installation of the driving part 860.

In some embodiments, one of the first connection tube segment 810 and the second connection tube segment 820 is provided with a first connection 840 and the other is provided with a second connection 850.

One of the first connection part 840 and the second connection part 850 is provided with a driving motor 861, the other is provided with a threaded hole, the power output end of the driving motor 861 is provided with a screw rod 862, and the screw rod 862 is connected with the threaded hole.

The driving motor 861 drives the screw rod 862 to rotate, and the first connecting portion 840 and the second connecting portion 850 are moved close to or away from each other through threaded connection between the screw rod 862 and the threaded hole, so that the first connecting pipe section 810 and the second connecting pipe section 820 are moved close to or away from each other, and shrinkage or extension of the flexible pipe section 830 is achieved.

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

In some embodiments, the exhaust pipe 12 is disposed in the upper housing 410, and referring to fig. 7, the upper housing 410 has an inner diameter D8, and referring to fig. 2A, the exhaust pipe 12 has an inner diameter D9.

Referring to FIG. 2B, the distance between the intake end of the exhaust pipe 12 and the top of the crankshaft is H8, and D8, D9 and H8 satisfy the relation of 3.81< D8/(D9×H28) <4.62, within which the oil discharge rate of the compressor is reduced.

In some embodiments, referring to fig. 2A, the inner diameter of the housing is D10, the inner diameter of the exhaust pipe 12 is D9, d10/d9= [8,12].

The larger the displacement, the larger the inner diameter of the compressor main casing is, the larger the displacement is, and the larger the displacement is, the larger the inner diameter of the exhaust pipe 12 is required to be in order to reduce the oil discharge rate and the pressure loss of the refrigerant gas, and when d10/d9= [8,12], the displacement may be increased when the oil discharge rate is reduced.

In some embodiments, a sensor 17 is provided to the exhaust pipe 12, the sensor 17 being configured to detect a vibration frequency of the exhaust pipe 12.

Muffler 800 includes a pipe segment that is connected to exhaust pipe 12, the pipe segment having an inner diameter that is greater than the inner diameter of exhaust pipe 12. Muffler 800 is an expanding muffler.

Muffler 800 includes a drive portion 860 configured to drive movement of the pipe segment to change the volume of the pipe segment according to the frequency of vibration of exhaust pipe 12. Muffler 800 is an automatic variable capacity muffler to enhance the effect of suppressing the transmission of refrigerant pulsation sound.

[ Footing of compressor ]

In order to reduce the vibration of the press body, vibration isolation footpads may be required to reduce the vibration of the compressor from a stiffness matched, damping matched angle. However, as the volume and weight of the compressor are increased, the rigidity of the foot pad cannot be too low, and too low rigidity of the foot pad easily causes excessive shaking of the compressor in the transportation process, so that the compressor impacts a pipeline, and other problems such as pipeline breakage are caused.

In some embodiments, the feet of the compressor are optimized to enhance vibration damping.

In some embodiments, referring to fig. 2A, the circumferential casing 430 constitutes a circumferential wall of the compressor body 1, the height of the circumferential casing 430 is H10, and the inner diameter of the circumferential casing 430 is D10.

The mounting portion 16 is provided outside the circumferential housing 430, and the mounting portion 16 is provided with a mounting hole having an inner diameter D18.

The compressor further comprises a foot 15, a connecting member (such as a bolt) passing through the mounting hole to mount the foot 15 to the mounting portion 16, the foot 15 being configured to carry the compressor, the foot 15 having a height H16.

From the standpoint of controlling the centroid position of the compressor, 4.5< H10/H16<6.5,5.5< D10/D18<8.5. From the perspective of controlling the barycenter position of the compressor, the vibration of the compressor shell is reduced, and the vibration reduction requirement of the rotor compressor shell is met.

In some embodiments, if the number of feet 15 is excessive, the installation is inconvenient. If the number of the bottom feet 15 is too small, the bottom feet 15 are stressed greatly, the bottom feet 15 are easy to deform due to falling resistance, and the vibration is large. For example, the weight of the compressor is G (kg), the number of feet 15 is N (one), and G and N satisfy the formula 12.5> G/N >5, that is, 12.5 kg/one > the weight of the designed compressor/the number of feet 15 >5 kg/one, and the compressor has small vibration noise and good anti-falling ability in the interval.

In some embodiments, three feet 15 are provided on the side of the circumferential housing 430, and the angle between the feet 15 near the gas-liquid separator 2 and the gas-liquid separator 2 is 30 ° or more and 60 ° or less. The compressor has small vibration noise and good anti-falling capability in the interval.

In some embodiments, four feet 15 are provided on the side of the circumferential housing 430, and the angle between the feet 15 near the gas-liquid separator 2 and the gas-liquid separator 2 is 20 ° or more and 45 ° or less. The compressor has small vibration noise and good anti-falling capability in the interval.

In some embodiments, the height of foot 15/the height of the center of gravity of the compressor= [0.07,0.15] such that compressor vibration noise is small in this interval.

It should be noted that any technical scheme of the disclosure may solve one or more technical problems and achieve a certain purpose of the invention to a certain extent, or may be combined into an integral scheme to solve one or more technical problems and achieve a certain purpose of the invention, or may be combined into an integral scheme by selecting part of technical publications, and meanwhile, related technologies and degradation schemes are adopted, but the degradation trend can be made up by the technical disclosure means, so that the one or more technical problems are solved and the purpose of the invention is achieved to a certain extent on the whole, and each technical disclosure is combined into a complete technical scheme to form an organic integral scheme which is not separable on the whole to solve the technical problems and achieve the purpose of the invention.

Any technical disclosure of the present disclosure, and the recombination of a plurality of technical disclosures can form a complete technical solution, and one or more of the above technical problems can be solved, so as to achieve the object of the invention, which belongs to the present disclosure and belongs to the content directly and unambiguously determined according to the present disclosure.

It will be understood by those skilled in the art that the scope of the present disclosure is not limited to the specific embodiments described above, and that certain elements of the embodiments may be modified and substituted without departing from the spirit of the application. The scope of the application is limited by the appended claims.

Claims (10)

1. A compressor, comprising:

A housing in which a compression mechanism configured to compress a refrigerant is disposed;

Characterized in that the housing comprises:

a circumferential housing;

The upper shell is arranged at the top of the circumferential shell and comprises circumferential walls and arc top walls, the arc top walls are arranged at the top of the circumferential walls, the circumferential walls are connected with the circumferential shell, the arc top walls are formed by sequentially converging a plurality of first arc top walls and a plurality of second arc top walls, the first arc top walls and the second arc top walls are arranged in a staggered mode along the circumference of the arc top walls, the radius of the circumference of the first arc top wall is larger than the radius of the circumference of the second arc top wall, and a platform part for installing devices is arranged on the first arc top wall.

2. The compressor of claim 1, wherein,

The radius of the circumferential wall is R4, the radius of the circumference where the second arc-shaped top wall is located is R5, and the height of the upper shell is H6, and H6/(R4X R5) >0.01.

3. The compressor of claim 1, wherein,

The first arc-shaped top wall is provided with a first platform part, the first platform part is configured to be used for installing a junction box, one part of the bottom surface of the junction box is contacted with the first platform part, and the other part of the bottom surface of the junction box is not contacted with the arc-shaped top wall.

4. A compressor according to claim 3, wherein,

The first platform part is provided with a first mounting hole, the wiring terminal of the junction box is arranged in the first mounting hole, and the fit clearance range between the wiring terminal and the first mounting hole is [0.1mm,0.8mm ].

5. The compressor of claim 1, wherein,

The first arc-shaped top wall is provided with a second platform part, the second platform part is configured to be provided with a hoisting part, and the matching area of the second platform part and the hoisting part is larger than 766mm < 2 >.

6. The compressor of claim 1, wherein,

The first arc roof is provided with a third platform part, the third platform part is provided with a connecting piece, the connecting piece is obliquely arranged, an oblique limiting cavity is formed between the connecting piece and the third platform part, and the limiting cavity is configured to be provided with a temperature sensor.

7. The compressor of claim 1, wherein,

The top of arc roof sets up the second mounting hole, the compressor includes the blast pipe, the blast pipe passes the second mounting hole, set up fourth platform portion on the arc roof, fourth platform portion encircles the second mounting hole sets up, fourth platform portion is configured to with the installation welding electrode cooperation that uses when the blast pipe.

8. A compressor according to any one of claims 1 to 7, wherein,

The circumferential wall comprises a first circumferential wall section and a second circumferential wall section, the first circumferential wall section is positioned at the lower part of the second circumferential wall section, the thickness of the first circumferential wall section is smaller than that 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 top of the circumferential shell, the height of the first section of the circumferential wall is 12+/-0.2 mm, and the lower part of the first section of the circumferential wall is an inclined wall.

9. A compressor according to any one of claims 1 to 7, wherein,

The compressor comprises a motor and an exhaust pipe, the compression mechanism comprises a crankshaft, the upper end of the crankshaft penetrates through the motor, and the distance range between the bottom end of the exhaust pipe and the top end of the crankshaft is [5,20] mm.

10. An air conditioner comprising a compressor, an evaporator, a condenser and a throttle device, wherein the compressor is the compressor according to any one of claims 1 to 9.