阅读说明：本技术 一种气缸、压缩机和空调器 (Cylinder, compressor and air conditioner ) 是由 魏会军 张心爱 吴健 王珺 黄纯浚 于 2021-09-14 设计创作，主要内容包括：本公开提供一种气缸、压缩机和空调器,气缸包括：气缸本体和气缸腔,所述气缸腔位于所述气缸本体的内侧,所述气缸本体上还设置有连通通道和消音腔体,所述连通通道的一端连通至所述气缸本体的径向内侧壁、另一端延伸并连通至所述消音腔体,所述消音腔体沿着所述气缸本体的周向方向延伸,同时所述消音腔体还沿着所述气缸本体的轴向方向延伸。根据本公开使得从气缸腔中引入的气体通过连通通道而进入消音腔体,使得消音腔体内的气体具有一定的固有频率,压缩机在旋转压缩过程中,当压缩腔内的声波频率与密封腔体的气体固有频率接近或一致时产生共振,从而大大降低声能,达到消声效果。(The present disclosure provides a cylinder, a compressor and an air conditioner, the cylinder includes: the cylinder body is further provided with a communicating channel and a silencing cavity, one end of the communicating channel is communicated to the radial inner side wall of the cylinder body, the other end of the communicating channel extends and is communicated to the silencing cavity, the silencing cavity extends along the circumferential direction of the cylinder body, and meanwhile the silencing cavity also extends along the axial direction of the cylinder body. According to the compressor, the gas introduced from the cylinder cavity enters the silencing cavity through the communicating channel, so that the gas in the silencing cavity has certain natural frequency, and the compressor generates resonance when the sound wave frequency in the compression cavity is close to or consistent with the natural frequency of the gas in the sealing cavity in the rotary compression process, so that the sound energy is greatly reduced, and the silencing effect is achieved.)

1. A cylinder, characterized by: the method comprises the following steps:

the cylinder structure comprises a cylinder body (23) and a cylinder cavity (24), wherein the cylinder cavity (24) is located on the inner side of the cylinder body (23), a communicating channel (22) and a silencing cavity (21) are further arranged on the cylinder body (23), one end of the communicating channel (22) is communicated to the radial inner side wall of the cylinder body (23), the other end of the communicating channel extends and is communicated to the silencing cavity (21), the silencing cavity (21) extends along the circumferential direction of the cylinder body (23), and meanwhile the silencing cavity (21) also extends along the axial direction of the cylinder body (23).

2. The cylinder of claim 1, wherein:

the cylinder body (23) comprises a first axial end face (28) located at one axial end of the cylinder body and a second axial end face (29) located at the other axial end of the cylinder body, and the silencing cavity (21) comprises a first shaft end (211) and a second shaft end (212) along the axial direction of the cylinder body (23), wherein the first shaft end (211) is located on the first axial end face (28), and the second shaft end (212) is located on the second axial end face (29), so that the silencing cavity (21) penetrates from the first axial end face (28) to the second axial end face (29).

3. The cylinder of claim 1, wherein:

cylinder body (23) is including first axial terminal surface (28) that is located its axial one end and second axial terminal surface (29) that is located the axial other end, follows the axial direction of cylinder body (23), amortization cavity (21) are including first axle head (211) and second axle end (212), first axle head (211) with first axial terminal surface (28) interval first predetermines the distance, second axle end (212) with second axial terminal surface (29) interval second predetermines the distance, first predetermines distance more than or equal to 0, the second predetermines distance more than or equal to 0.

4. The cylinder of claim 1, wherein:

the cylinder body (23) comprises a first axial end face (28) at one axial end thereof and a second axial end face (29) at the other axial end thereof, the communication passage (22) extends in a radial direction of the cylinder body (23), the communication passage (22) is located between the first axial end face (28) and the second axial end face (29) in the axial direction of the cylinder body (23), an axial minimum distance between the communication passage (22) and the first axial end face (28) is greater than 0, and an axial minimum distance between the communication passage (22) and the second axial end face (29) is greater than 0.

5. The cylinder of claim 1, wherein:

the silencing cavity (21) is a columnar cavity which surrounds the center of the cylinder (2), and the silencing cavity (21) is in a fan-shaped ring shape, a circular shape or a kidney shape in the cross section of the cylinder.

6. The cylinder according to any one of claims 1 to 5, wherein:

the cylinder body (23) is provided with an air suction port (25) and an air exhaust port (20), the communication channel (22) is positioned at a position close to the air exhaust port (20) relative to the air suction port (25), and the silencing cavity (21) is positioned at a position close to the air exhaust port (20) relative to the air suction port (25).

7. The cylinder of claim 6, wherein:

in an axial projection plane of the cylinder body (23), the communication passage (22) intersects the exhaust port (20), the sound-deadening chamber (21) includes a first circumferential end (213) and a second circumferential end (214) in a circumferential direction of the cylinder, and the communication passage (22) communicates to a position between the first circumferential end (213) and the second circumferential end (214); a span central angle between the first circumferential end (213) and the second circumferential end (214) in the cylinder circumferential direction is θ, θ < 45 °.

8. The cylinder according to any one of claims 1 to 7, wherein:

the inner side surface radius of the silencing cavity (21) close to the axis of the cylinder is R1, the outer side surface radius of the silencing cavity (21) far away from the axis of the cylinder is R2, the span central angle between the starting and stopping positions of the silencing cavity (21) along the circumferential direction of the cylinder is theta, the section diameter of the communication channel (22) is d, the length of the communication channel is L, the axial height of the cylinder body is H, the sound velocity under the condition of the refrigerant medium for the compressor application system is set to be c, and all parameters meet the following requirements:

9. a compressor, characterized by: comprising a cylinder according to any one of claims 1-8.

10. An air conditioner, characterized in that: comprising the compressor of claim 9.

Technical Field

The disclosure relates to the technical field of compressors, in particular to an air cylinder, a compressor and an air conditioner.

Background

The rolling rotor compressor pump body component is composed of a cylinder, a roller, a crankshaft, an upper flange component, a lower flange component (including an upper flange, a lower flange, an exhaust valve plate and a valve plate limit baffle) and a slip sheet, wherein all pump body parts are mutually matched to form a closed high-pressure cavity (an exhaust cavity) and a closed low-pressure cavity (a suction cavity), the slip sheet is in clearance fit with a slip sheet groove and reciprocates in the slip sheet groove, so that the volume of the high-pressure cavity and the low-pressure cavity is periodically changed, a crescent exhaust oblique notch of the cylinder is formed in the cylinder compression cavity close to the slip sheet groove, a circular hole-shaped exhaust port is formed in the upper flange and the corresponding position of the exhaust oblique notch of the cylinder, the exhaust valve plate and the valve plate limit baffle are connected to a valve seat through a rivet at the tail part on the exhaust port of the flange, the exhaust valve plate is tightly attached to the exhaust port of the flange in the gas compression process of the compression cavity, the sealing of the compression cavity is realized, when the volume of the compression cavity is reduced to a certain degree, and the gas pressure in the compression cavity reaches or exceeds the back pressure of the valve plate, the valve plate is opened, and the gas in the compression cavity is discharged out of the pump body through the cylinder exhaust inclined notch and the flange exhaust port, so that the periodic air suction, compression and exhaust processes of the compressor are realized.

The pneumatic noise generated by periodic air suction, compression and exhaust of the compressor is one of the main noise sources of the compressor, the pneumatic noise is reduced to meet the low-noise development requirement of the rotor compressor, and the method is one of the difficult problems to be mainly solved in the research and development process of the compressor product at present.

Because the rotor compressor among the prior art exists in the periodic operation in-process, the pump body compression chamber volume constantly reduces and arouses pressure variation and pressure pulsation and then produce technical problem such as compressed pneumatic noise, consequently this disclosure research designs a cylinder, compressor and air conditioner.

Disclosure of Invention

Therefore, the technical problem to be solved by the present disclosure is to overcome the defect that in the prior art, in the rotor compressor, the volume of the compression cavity of the pump body is continuously reduced during the periodic operation process, so as to cause pressure variation and pressure pulsation and further generate compressed pneumatic noise, thereby providing a cylinder, a compressor and an air conditioner.

In order to solve the above-mentioned problem, the present disclosure provides a cylinder, which includes:

the cylinder body is further provided with a communicating channel and a silencing cavity, one end of the communicating channel is communicated to the radial inner side wall of the cylinder body, the other end of the communicating channel extends and is communicated to the silencing cavity, the silencing cavity extends along the circumferential direction of the cylinder body, and meanwhile the silencing cavity also extends along the axial direction of the cylinder body.

In some embodiments, the cylinder body includes a first axial end surface at one axial end thereof and a second axial end surface at the other axial end thereof, and the muffling cavity includes a first axial end and a second axial end along the axial direction of the cylinder body, the first axial end being located on the first axial end surface, the second axial end being located on the second axial end surface, so that the muffling cavity penetrates from the first axial end surface to the second axial end surface.

In some embodiments, the cylinder body includes a first axial end surface located at one axial end thereof and a second axial end surface located at the other axial end thereof, and the muffling cavity includes a first shaft end and a second shaft end along the axial direction of the cylinder body, the first shaft end and the first axial end surface are separated by a first preset distance, the second shaft end and the second axial end surface are separated by a second preset distance, the first preset distance is greater than or equal to 0, and the second preset distance is greater than or equal to 0.

In some embodiments, the cylinder body includes a first axial end surface at one axial end thereof and a second axial end surface at the other axial end thereof, the communication passage extends in a radial direction of the cylinder body, the communication passage is located between the first axial end surface and the second axial end surface in the axial direction of the cylinder body, an axial minimum distance between the communication passage and the first axial end surface is greater than 0, and an axial minimum distance between the communication passage and the second axial end surface is greater than 0.

In some embodiments, the sound-deadening chamber is a cylindrical chamber that surrounds the center of the cylinder, and the sound-deadening chamber has a fan-ring shape, a circular shape, or a kidney shape in a cross section of the cylinder.

In some embodiments, the cylinder body is provided with an intake port and an exhaust port, the communication passage is located near the exhaust port with respect to the intake port, and the sound-deadening chamber is located near the exhaust port with respect to the intake port.

In some embodiments, the communication passage intersects the exhaust port in an axial projection plane of the cylinder body, the sound-deadening chamber includes a first circumferential end and a second circumferential end in a circumferential direction of the cylinder, and the communication passage communicates to a position between the first circumferential end and the second circumferential end; a span central angle between the first circumferential end and the second circumferential end in the cylinder circumferential direction is θ, θ < 45 °.

In some embodiments, an inner side radius of the muffling cavity close to an axis of the cylinder is R1, an outer side radius of the muffling cavity far from the axis of the cylinder is R2, a span central angle between start and stop positions of the muffling cavity in a cylinder circumferential direction is θ, a cross-sectional diameter of the communicating channel is d, a length of the communicating channel is L, an axial height of the cylinder body is H, and a sound velocity under a condition of a refrigerant medium for a compressor application system is c, and the parameters satisfy:

the present disclosure also provides a compressor comprising the cylinder of any one of the preceding claims.

The present disclosure also provides an air conditioner including the compressor of any one of the preceding claims.

The cylinder, the compressor and the air conditioner have the following beneficial effects:

1. this disclosure is through the intercommunication passageway that sets up on the cylinder body, the intercommunication passageway communicates with the radial inside wall of cylinder body, communicate with the cylinder chamber promptly, can follow the cylinder chamber and introduce gas, the other end and amortization cavity intercommunication, make the gas that introduces in the cylinder chamber pass through the intercommunication passageway and get into the amortization cavity, because the amortization cavity extends at the circumferential direction of cylinder and extends at the axial direction, make gas can take place resonance in the amortization cavity, in order to carry out the amortization, gas in the amortization cavity has certain natural frequency, the compressor is at rotatory compression in-process, produce resonance when the sound wave frequency in the compression cavity is close to or unanimous with seal chamber's gas natural frequency, thereby greatly reduced acoustic energy, reach the anechoic effect.

2. This is disclosed still through radial inboard radius R1 of amortization cavity, radial outside radius R2, span central angle theta between the start-stop position of amortization cavity, the cross-sectional diameter d of intercommunication passageway, length L, cylinder body's axial height is set up to satisfying the relational expression between H and the sound velocity for c:the resonance frequency point of the resonant cavity can be adjusted by limiting the relation range between the parameters, so that the noise reduction frequency band is matched with the target frequency band, the noise peak value in the frequency band range of 1KHz-5KHz can be effectively reduced, particularly, the compressed high-frequency pneumatic noise has a better noise elimination effect, and the frequency band range of the noise reduction frequency band of 1KHz-5KHz is also the noise frequency band mainly embodied by the pneumatic noise.

Drawings

FIG. 1 is a background art view, a cross-sectional view, of a conventional rotary compressor pump block assembly;

FIG. 1a is a three-dimensional line drawing of the pump block assembly of FIG. 1 (with the upper flange removed);

FIG. 2 is a top view of a cylinder according to a preferred embodiment of the present disclosure;

FIG. 2a is a partial enlarged view of portion M of FIG. 2;

FIG. 2B is a cross-sectional view taken along line B-B of FIG. 2 a;

FIG. 2c is a cross-sectional view of the preferred embodiment pump block assembly;

FIG. 2d is an enlarged view of a portion K of FIG. 2 c;

FIG. 3a is an enlarged, partially sectioned longitudinal view of a cylinder according to an alternative embodiment of the present disclosure;

FIG. 3b is an enlarged, partially sectioned longitudinal view of a cylinder according to a second alternative embodiment of the present disclosure;

FIG. 4a is an enlarged, partial top view of a cylinder according to a third alternative embodiment of the present disclosure;

FIG. 4b is an enlarged, partial top view of a cylinder according to a fourth alternative embodiment of the present disclosure.

The reference numerals are represented as:

1. an upper flange; 12. an upper flange exhaust port; 2. a cylinder; 20. an exhaust port; 21. a silencing cavity; 211. a first shaft end; 212. a second shaft end; 213. a first circumferential end; 214. a second circumferential end; 22. a communication channel; 23. a cylinder body; 24. a cylinder cavity; 241. a high pressure chamber; 242. a low pressure chamber; 25. an air suction port; 26. a slide groove; 27. a spring hole; 28. a first axial end face; 29. a second axial end face; 3. a crankshaft; 4. a roller; 5. a lower flange; 6. a valve plate; 7. and (4) sliding a sheet.

Detailed Description

As shown in fig. 2-4b, the present disclosure provides a cylinder comprising:

the cylinder body 23 and the cylinder cavity 24, the cylinder cavity 24 is located on the inner side of the cylinder body 23, the cylinder body 23 is further provided with a communication channel 22 and a silencing cavity 21, one end of the communication channel 22 is communicated to the radial inner side wall of the cylinder body 23, the other end of the communication channel extends and is communicated to the silencing cavity 21, the silencing cavity 21 extends along the circumferential direction of the cylinder body 23, and meanwhile, the silencing cavity 21 also extends along the axial direction of the cylinder body 23. This disclosure is through the intercommunication passageway that sets up on the cylinder body, the intercommunication passageway communicates with the radial inside wall of cylinder body, communicate with the cylinder chamber promptly, can follow the cylinder chamber and introduce gas, the other end and amortization cavity intercommunication, make the gas that introduces in the cylinder chamber pass through the intercommunication passageway and get into the amortization cavity, because the amortization cavity extends at the circumferential direction of cylinder and extends at the axial direction, make gas can take place resonance in the amortization cavity, in order to carry out the amortization, gas in the amortization cavity has certain natural frequency, the compressor is at rotatory compression in-process, produce resonance when the sound wave frequency in the compression cavity is close to or unanimous with seal chamber's gas natural frequency, thereby greatly reduced acoustic energy, reach the anechoic effect.

The present disclosure provides a pump body structure with a compression noise reduction channel, which optimizes compressor noise vibration by designing the compression noise reduction channel at the side of a compression cavity of the pump body. The method has the following specific beneficial effects:

1) the compressed pneumatic noise generated by the pressure change and pressure pulsation of a compression cavity caused by the continuous change of the volume of the compression cavity of the pump body in the periodic air suction, compression and exhaust processes of the rotor compressor is reduced;

2) the bottleneck problem of design space limitation is solved (the silencing cavity is not required to be arranged on one end face of the cylinder or the end face matched with the flange, the diameter size of the silencing cavity and the cavity volume are prevented from being limited), the silencing passage structure is simplified, the process is simpler, and the processing is easy;

3) and at the compression end stage of the pump body, a return channel is provided, so that the reliability risk of the compressor with overlarge torque fluctuation caused by overpressure, oil pressure or unsmooth exhaust at the exhaust end stage is reduced to a great extent.

As shown in fig. 1, which is an assembly and operation schematic diagram of a pump body of a conventional compressor, a pump body assembly of a rotor compressor is formed by an upper flange 1, a cylinder 2, a crankshaft 3, a roller 4, a lower flange 5 and a slide 7 which are mutually matched to form a closed high-pressure cavity 241 (an exhaust cavity) and a closed low-pressure cavity 242 (a suction cavity). One part of the upper flange exhaust port 12 covers the high-pressure cavity 241 and is directly communicated with the cylinder high-pressure cavity, the other part of the upper flange exhaust port covers the upper part of the cylinder exhaust port 20 to form an exhaust flow channel of a compressor pump body, and the valve plate 6 and a valve plate limiting baffle are covered above the flange exhaust port. In the process of compressing the gas in the compression cavity, the valve plate 6 for exhausting is tightly attached to the exhaust port 12 of the upper flange, the sealing of the compression cavity is realized, when the volume of the high-pressure cavity 241 is reduced to a certain degree along with the rotation of the crankshaft 3, and when the gas pressure in the compression cavity reaches or exceeds the back pressure of the valve plate 6, the valve plate is opened, the gas in the compression cavity is exhausted out of the pump body through the exhaust port 20 of the cylinder and the exhaust port 12 of the upper flange, and the periodic air suction and exhaust of the compressor are realized. The conventional compressor pump body exhaust structure is easy to cause overlarge exhaust resistance or unsmooth exhaust of the compressor pump body, so that the energy consumption of the compressor is increased, and on the other hand, the pneumatic noise generated by periodic air suction and exhaust of the compressor is one of main noise sources of the compressor, the pneumatic noise is reduced to meet the low-noise development requirement of the rotor compressor, and the conventional compressor pump body exhaust structure is one of the difficult problems which need to be mainly solved in the research and development process of the compressor product at present.

The utility model provides a compressor is with pump body improvement structure, through designing the amortization chamber for extending along cylinder axial and circumference direction and expanding volumetric cavity structures, when effectively reducing the pneumatic noise of rotor compressor compression, solved the bottleneck problem of design space restriction to simplify amortization access structure, the technology is more simple, easily processing.

As shown in fig. 2-2a, the present disclosure designs a compression silencing passage on the cylinder compression chamber side, and the compression silencing passage is formed by a neck passage (communication passage 22) and a silencing chamber 21. Wherein, the inlet of the neck channel of the communicating channel 22 is designed on the circumferential surface of the inner wall of the cylinder compression cavity side and extends along the radial direction of the cylinder, and the outlet is communicated with the silencing cavity. The silencing cavity is a part of an annular cavity surrounding the axis of the cylinder, as shown in fig. 2b, the annular cavity penetrates through the upper end surface and the lower end surface of the cylinder, and is assembled and matched with the upper flange end surface and the lower flange end surface through the cylinder to form a closed cavity (as shown in fig. 2c-2 d). The gas in the sealed cavity has certain natural frequency, and the compressor generates resonance when the sound wave frequency in the compression cavity is close to or consistent with the natural frequency of the gas in the sealed cavity in the rotary compression process, so that the sound energy is greatly reduced, and the silencing effect is achieved.

As shown in fig. 2b-2d, in some embodiments, the cylinder body 23 includes a first axial end surface 28 at one axial end thereof and a second axial end surface 29 at the other axial end thereof, and the sound-deadening chamber 21 includes a first axial end 211 and a second axial end 212 along the axial direction of the cylinder body 23, the first axial end 211 being located on the first axial end surface 28, and the second axial end 212 being located on the second axial end surface 29, so that the sound-deadening chamber 21 penetrates from the first axial end surface 28 to the second axial end surface 29. This is the preferred structural style of this disclosure's best embodiment, and the amortization cavity link up to the second axial terminal surface from the first axial terminal surface of cylinder body promptly, because the upper and lower both ends of cylinder body carry out laminating effectively through the flange respectively and seal, consequently the axial both ends of amortization cavity are also sealed to make gas can produce the effect of resonance amortization in this amortization cavity.

As shown in fig. 3a-3b, in some embodiments, the cylinder body 23 includes a first axial end surface 28 at one axial end thereof and a second axial end surface 29 at the other axial end thereof, and the sound-deadening chamber 21 includes a first axial end 211 and a second axial end 212 along the axial direction of the cylinder body 23, wherein the first axial end 211 is spaced from the first axial end surface 28 by a first predetermined distance, the second axial end 212 is spaced from the second axial end surface 29 by a second predetermined distance, the first predetermined distance is greater than or equal to 0, and the second predetermined distance is greater than or equal to 0. The first axial end of the silencing cavity can penetrate through to the first axial end face, the second axial end is located inside the cylinder body and does not penetrate through to the second axial end face, so that the effect of resonance silencing can be effectively achieved, the second axial end and the communication channel can be located at the same axial height, or the second axial end is located below the communication channel, and gas can be sucked from the communication channel to enter the silencing cavity for effective silencing.

In some embodiments, the cylinder body 23 includes a first axial end surface 28 at one axial end thereof, and a second axial end surface 29 at the other axial end, the communication passage 22 extends in a radial direction of the cylinder body 23, the communication passage 22 is located between the first axial end surface 28 and the second axial end surface 29 in the axial direction of the cylinder body 23, an axial minimum distance between the communication passage 22 and the first axial end surface 28 is greater than 0, and an axial minimum distance between the communication passage 22 and the second axial end surface 29 is greater than 0. This is the preferred structural style of the communicating channel of this disclosure, and the communicating channel is located the position between two axial terminal surfaces of cylinder body, can inhale gas from the cylinder chamber effectively and get into the amortization cavity and carry out the amortization.

As shown in fig. 2a, 4a-4b, in some embodiments, the sound-deadening chamber 21 is a cylindrical chamber that surrounds the center of the cylinder 2, and the sound-deadening chamber 21 has a fan-ring shape, a circular shape, or a kidney shape in a cross section of the cylinder. This disclosed amortization cavity can play the effect that holds the chamber at axial direction for the column cavity, extends in the circumference direction and forms fan ring shaped structure, circular structure or waist shape structure homoenergetic and play the effect that holds the chamber in the circumference direction, and then effectively improves and holds the effect that gas got into and resonance amortization.

In some embodiments, the cylinder body 23 is provided with an intake port 25 and an exhaust port 20, the communication passage 22 is located close to the exhaust port 20 with respect to the intake port 25, and the sound-deadening chamber 21 is located close to the exhaust port 20 with respect to the intake port 25. The communicating channel and the silencing cavity are preferably arranged at positions close to the exhaust port, high-pressure gas can be effectively introduced from the cylinder cavity to enter the silencing cavity to perform resonance vibration damping and silencing, the energy of the gas introduced from the low-pressure cavity is low, the gas cannot cause vibration of a cylinder and the like generally, and therefore the gas introduced into the high-pressure cavity can improve the resonance silencing effect.

In some embodiments, the communication passage 22 intersects the exhaust port 20 in an axial projection plane of the cylinder body 23, the sound-deadening chamber 21 includes a first circumferential end 213 and a second circumferential end 214 in the circumferential direction of the cylinder, and the communication passage 22 communicates to a position between the first circumferential end 213 and the second circumferential end 214; a span center angle between the first circumferential end 213 and the second circumferential end 214 in the cylinder circumferential direction is θ, θ < 45 °. This is this is the further preferred structural style of intercommunication passageway and amortization cavity of this disclosure, and the intercommunication passageway is located the crossing position with the gas vent in axial direction promptly, can guarantee that the gas in the cylinder chamber that introduces from the intercommunication passageway is high-pressure gas, and the intercommunication passageway communicates to between the both ends of the circumferential direction of amortization cavity, can make gas flow toward two directions after getting into the amortization cavity, can form the damping amortization effect of two directions, further improves the effect of resonance amortization.

In some embodiments, the radius of the inner side surface of the sound-deadening chamber 21 close to the axial center of the cylinder is R1, the radius of the outer side surface of the sound-deadening chamber 21 away from the axial center of the cylinder is R2, the span central angle between the start and stop positions of the sound-deadening chamber 21 in the cylinder circumferential direction is θ, the cross-sectional diameter of the communicating passage 22 is d, the length thereof is L, the axial height of the cylinder body is H, and the sound velocity under the condition of the refrigerant medium for the compressor application system is c, and the respective parameters satisfy:as shown in fig. 2a-2b, the radius of the inner side surface of the annular muffling cavity close to the axis of the cylinder is R1, the radius of the outer side surface far away from the axis of the cylinder is R2, the span angle of the start-stop position along the circumferential direction is θ, the cross-sectional diameter of the neck passage of the annular muffling cavity is d, the length of the neck passage is L, the height of the cylinder is H, the sound velocity under the condition of the refrigerant medium for the compressor application system is set as c, and preferably, the parameters satisfy:the noise peak value in the frequency range of 1KHz-5KHz can be effectively reduced, and particularly, the compressed high-frequency pneumatic noise has a better noise elimination effect.

The resonance frequency point of the resonant cavity can be adjusted by limiting the relation range between the parameters, so that the noise reduction frequency band is matched with the target frequency band, the noise peak value in the frequency band range of 1KHz-5KHz can be effectively reduced under the action of the formula, particularly, the compressed high-frequency pneumatic noise has better noise elimination effect, and the frequency band range of the noise reduction frequency band of 1KHz-5KHz is also the noise frequency band mainly embodied by the pneumatic noise.

The muffling cavity of the compression muffling channel of the innovative structure of the pump body can also be a sink groove structure with an opening facing one end face of the cylinder, and at the moment, H in the optimal size range described in the most practical embodiments is the depth value of the sink groove.

The present disclosure also provides a compressor comprising the cylinder of any one of the preceding claims.

The pump body structure of the compressor is optimized, the compression silencing channel is designed on the side of the compression cavity of the pump body, so that the compressed pneumatic noise of the compressor is reduced, the reliability risk of the compressor caused by moment fluctuation caused by overpressure, oil pressure or unsmooth exhaust when the exhaust is finished is reduced, the bottleneck problem of design limitation is solved, and the structure and the processing technology are simplified.

The present disclosure also provides an air conditioner including the aforementioned compressor.

The above description is only exemplary of the present disclosure and should not be taken as limiting the disclosure, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present disclosure should be included in the scope of the present disclosure. The foregoing is only a preferred embodiment of the present disclosure, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present disclosure, and these modifications and variations should also be regarded as the protection scope of the present disclosure.