A silencer, a compressor and an air conditioner

Abstract

The present invention provides a silencer, a compressor and an air conditioner, wherein the silencer (2) is arranged on a motor rotor (1) of the compressor, the motor rotor (1) has a rotor circulation hole (11), the silencer (2) is provided with a second circulation hole (20), the second circulation hole (20) is arranged opposite to the rotor circulation hole (11), and the silencer (2) has a silencer cavity (21) in communication with the second circulation hole (20), the second circulation hole (20) and the rotor circulation hole (11) are arranged one-to-one, and the silencer cavity (21) and the second circulation hole (20) are arranged one-to-one. Through the present invention, the gas flowing out of each rotor circulation hole can enter the silencer cavity corresponding to it and be silenced, and each independent silencer cavity performs a separate silencer effect on each rotor circulation hole, which can effectively reduce noise, especially in the medium and high frequency bands.

Description

Technical Field

[0001] The invention belongs to the technical field of compressors, and in particular relates to a silencer, a compressor and an air conditioner. Background Art

[0002] As customers' living standards improve, air conditioning noise has become an important indicator for evaluating product quality. Air conditioning noise mainly comes from the compressor in the outdoor unit, so reducing compressor noise will greatly improve the quality of air conditioning. The noise of the compressor mainly includes aerodynamic noise, mechanical noise, and electromagnetic noise. The aerodynamic noise of the compressor is due to intermittent suction and exhaust, which causes the pressure and speed of the refrigerant airflow to change periodically, resulting in airflow pulsation. The airflow pulsation radiates noise outward through the compressor casing and pipeline. The aerodynamic noise of the compressor is generally periodic exhaust noise. After the airflow is compressed, the gas is discharged instantly and expands, generating an amplified transient impact force. This impact force can excite the movement structure vibration within a wider frequency band. The aerodynamic noise has a very high magnitude.

[0003] The compressor is mainly composed of three parts: the shell, the pump body, and the motor. The motor has a rotor and a stator. The rotor is connected to the pump body through a crankshaft. The rotor includes a rotor core, an oil baffle, an oil baffle cap, and a balance block. During operation, the stator is connected to a three-phase power supply, and the rotating magnetic field drives the rotor to rotate, and together with the crankshaft, drives the pump body to perform compression movement. When the refrigerant is compressed, the refrigerant oil is mixed, and the compressed high-pressure gas is discharged and enters the upper chamber of the compressor through the rotor flow hole. At the same time, after the high-pressure oil and gas pass through the rotor flow hole, they are buffered by the oil baffle seat and the oil baffle cap, and the refrigerant and the refrigerant oil are separated. The existing oil baffle seat and oil baffle cap structure have a small contact area with the high-pressure gas, and the buffering is insufficient, resulting in poor separation effect. The compressor refrigerant oil flows into the air conditioning system, affecting the heat exchange efficiency and reducing the air conditioning performance. At the same time, the gas is disturbed by the high-speed rotating rotor, the air flow pulsation is amplified, the noise band is widened, and the noise problem is further aggravated.

[0004] The existing method of reducing noise in compressors is to install a silencer cover above the exhaust port of the pump body, thereby staggering the resonance frequency inside and outside the silencer cavity and reducing the exhaust noise. The defect is that the silencer cover structure can only reduce some obvious peak noises in the compressor, and cannot effectively reduce all peak noises in a wider silencer frequency band.

[0005] As described in the reference document CN107917081A, the oil retaining structure used in the industry is a combination of an oil retaining cap and a rotor or an oil retaining cap, an oil retaining seat and a rotor. At the same time, the industry uses a silencing method, which is to install a silencing cover above the exhaust port of the flange on the pump body, and the silencing band is a peak noise within 2KHz.

[0006] Since the compressor in the prior art usually has only a first-stage silencer at the upper flange, the noise in the gas in the mid-frequency band or the high-frequency band cannot be eliminated, resulting in a large compressor noise and a poor noise reduction ability; the existing oil baffle seat and oil baffle cap structure have a small contact area with the high-pressure gas and insufficient buffering, resulting in poor separation effect, and the compressor refrigeration oil flows into the air-conditioning system, affecting the heat exchange efficiency and reducing the air-conditioning performance. At the same time, the gas is disturbed by the high-speed rotating rotor, the air flow pulsation is amplified, the noise frequency band is widened, and the noise problem is further aggravated. Therefore, the present invention studies and designs a silencer, a compressor and an air conditioner. Summary of the invention

[0007] Therefore, the technical problem to be solved by the present invention is to overcome the defect in the prior art that the noise in the compressor within the mid-frequency band or the high-frequency band cannot be eliminated, resulting in the compressor having high noise and poor noise reduction ability, thereby providing a silencer device, a compressor and an air conditioner.

[0008] The present invention provides a silencing device, wherein:

[0009] The silencer is arranged on the motor rotor of the compressor, and the motor rotor has a rotor circulation hole. The silencer is provided with a second circulation hole, and the second circulation hole is arranged opposite to the rotor circulation hole. The silencer has a silencer cavity connected to the second circulation hole inside, and the second circulation holes are arranged one-to-one with the rotor circulation holes, and the silencer cavity and the second circulation holes are arranged one-to-one with each other.

[0010] Preferably,

[0011] The silencer device comprises a first plate and a second plate, the first plate and the second plate are interlocked to form the silencer cavity therebetween, and the second flow hole is arranged on the second plate and penetrates two opposite end surfaces of the second plate.

[0012] Preferably,

[0013] The first plate and the second plate are arranged up and down, and the second plate is located at the bottom and is a lower flat plate, and the first plate is located at the top and is an upper flat plate.

[0014] Preferably,

[0015] A first pillar is protrudingly provided on the first plate and extends in a direction toward the second plate, and a second pillar is protrudingly provided on the second plate and extends in a direction toward the first plate, and when the first plate and the second plate are buckled together, the first pillar and the second pillar are connected to form a joint pillar, the number of the first pillar and the second pillar is equal to the number of the rotor circulation holes, and a silencer cavity is formed between two adjacent joint pillars.

[0016] Preferably,

[0017] A third pillar is protrudingly provided on the first plate in a direction extending toward the second plate, and when the first plate and the second plate are buckled, the third pillar is connected to the second plate, the number of the third pillars is equal to the number of the rotor flow holes, and one muffler cavity is formed between two adjacent third pillars; or,

[0018] A fourth pillar is protrudingly provided on the second plate and extending in the direction of the first plate, and the fourth pillar is connected to the first plate when the first plate and the second plate are buckled, the number of the fourth pillars is equal to the number of the rotor flow holes, and a silencer cavity is formed between two adjacent fourth pillars.

[0019] Preferably,

[0020] There are multiple first pillars, which are evenly distributed along the circumferential direction of the motor rotor, and / or there are multiple second pillars, which are evenly distributed along the circumferential direction of the motor rotor; and / or at least one of the first plate, the second plate, the first pillar and the second pillar is made of powder metallurgy or high manganese steel.

[0021] Preferably,

[0022] A groove structure is provided on an end surface of one side opposite to the second plate, in a direction away from the second plate, to form a muffler chamber. The groove structure is located at the position of the muffler cavity and is communicated with the muffler cavity.

[0023] Preferably,

[0024] The groove structure includes a first groove and a second groove which are connected to each other. The volumes of the first groove and the second groove are different. The volume of the first groove is smaller than that of the second groove. The first groove is opposite to and connected to the second flow hole.

[0025] Preferably,

[0026] A corresponding groove structure is arranged in each of the silencer chambers; and / or the first groove and / or the second groove is a blind groove structure; and / or the first groove and the second groove are both circular grooves, and the radius of the first groove is smaller than the radius of the second groove; and / or the junction between the first groove and the second groove is an arc-shaped transition.

[0027] Preferably,

[0028] A first side plate protruding toward the second plate is also provided on the outer peripheral side of the first plate, and an exhaust port allowing gas to be discharged from the silencing chamber includes a portion of the outer peripheral side of the first plate where the first side plate is not provided, and the exhaust port is connected to the silencing chamber.

[0029] Preferably,

[0030] When a first pillar is included, the first side panel includes a first side panel a extending circumferentially from a radial outer end of the first pillar on one side of the silencer chamber and a first side panel b extending circumferentially from a radial outer end of the first pillar on the other side of the silencer chamber, the first side panel a extends in the direction of the first side panel b, the first side panel b extends in the direction of the first side panel a, and the exhaust port includes a circumferential spacing portion between the first side panel a and the first side panel b.

[0031] Preferably,

[0032] The first side panel a is an arc-shaped panel, the first side panel b is also an arc-shaped panel, the first panel is a disc, the sum of the circumferential lengths of the first side panel a and the first side panel b is greater than or equal to 1 / 3 of the circumferential length between two adjacent first pillars; and / or the height of the first side panel a is equal to the height of the first pillar, and the height of the first side panel b is equal to the height of the first pillar.

[0033] Preferably,

[0034] A second side plate protruding toward the first plate is also provided on the outer peripheral side of the second plate, and the exhaust port allowing gas to be discharged from the silencer chamber also includes a portion of the outer peripheral side of the second plate where the second side plate is not provided, and the second side plate extends to connect with the first side plate.

[0035] Preferably,

[0036] When a second pillar is included, the second side plate includes a second side plate a extending circumferentially from the radial outer end of the second pillar on one side of the silencer chamber and a second side plate b extending circumferentially from the radial outer end of the second pillar on the other side of the silencer chamber, the second side plate a extends in the direction of the second side plate b, and the second side plate b extends in the direction of the second side plate a, and the exhaust port includes a circumferential spacing portion between the second side plate a and the second side plate b.

[0037] Preferably,

[0038] The second side plate a is an arc-shaped plate, the second side plate b is also an arc-shaped plate, the second plate is a disc, the sum of the circumferential lengths of the second side plate a and the second side plate b is greater than or equal to 1 / 3 of the circumferential length between two adjacent second pillars; and / or, the height of the second side plate a is equal to the height of the second pillar, and the height of the second side plate b is equal to the height of the second pillar.

[0039] Preferably,

[0040] The line segment shape of one circumferential side of the first pillar in the cross section satisfies the formula y(x)=a+bx+cx 2 +dx 3 ; and / or, the line segment shape of the other circumferential side of the first pillar in the cross section satisfies the formula y(x)=a+bx+cx 2 +dx 3 .

[0041] Preferably,

[0042] The height of the motor rotor is H1, the area of ​​the second flow hole is S1, the sum of the volumes of the muffler cavity and the muffler chamber is V1, and The range is (1, 2.5).

[0043] Preferably,

[0044] V1=600mm 3 , S1=5mm 2 , rotor height H1 = 60 mm,

[0045] Preferably,

[0046] It also includes a first-stage silencer cover arranged on the compressor flange, and the volume of the first-stage silencer cover is V3, the total volume of the pump cylinder of the compressor is V4, and

[0047] Preferably,

[0048] V3=150mm 3 , V4=200mm 3 ,

[0049] Preferably,

[0050] The total height of the first pillar and the second pillar when connected is H2, the length of the second flow hole in the cross section is L, the depths of the first groove and the second groove are equal and the depth is W1, the area of ​​the second flow hole is S1, and (H2+W1)×L≥S1.

[0051] Preferably,

[0052] W1=2mm,H2=6mm,L=2,then (H2+W1)×L=16mm 2 , S1=5mm 2 .

[0053] Preferably,

[0054] The first support column and the second support column are both provided with rivet holes, and are fixed to the motor rotor by rivets.

[0055] The present invention also provides a compressor, comprising the silencer device described in any of the preceding items.

[0056] The present invention also provides an air conditioning system, which comprises the aforementioned compressor.

[0057] The silencing device, compressor and air conditioner provided by the present invention have the following beneficial effects:

[0058] The present invention provides a silencer on the compressor motor rotor, and a silencer cavity corresponding to the second flow hole is provided inside the silencer, and the second flow hole corresponds to the rotor flow hole one by one, so that the gas flowing out of each rotor flow hole can enter the corresponding silencer cavity to be silenced, and each rotor flow hole is effectively silenced by each independent silencer cavity, which can effectively reduce the noise, especially in the medium and high frequency bands; and the present application also forms the silencer cavity between the first and second pillars by providing a first pillar spaced apart on the first plate and a second pillar spaced apart on the second plate, so that the volume space of the fluid is effectively increased, thereby effectively reducing the noise of the gas; the present application also forms the silencer cavity between the first and second pillars by providing a first pillar spaced apart on the first plate and a second pillar spaced apart on the second plate, so as to effectively increase the volume space of the fluid, thereby effectively reducing the noise of the gas; The groove structure provided can make the fluid from the second flow hole impact into the groove structure, effectively achieving the purpose of reducing energy and completing the elimination of medium and high frequency noise. Through two grooves of unequal volumes, and the fluid first enters the small volume groove and then enters the large volume groove, the gas can be silenced in steps, further improving the silencing effect. And the present application fixes the silencing device to the rotor so that it can rotate with the rotor, so that the oil separated from the gas from the silencing chamber is radially thrown out by centrifugal force, effectively improving the oil-gas separation effect. And the side plate structure provided at the periphery of the first plate can block the gas moving radially outward, further improving the silencing effect of the gas in the silencing chamber and improving the oil-gas separation effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0059] Figure 1 It is a three-dimensional structural schematic diagram of the silencer device (two-stage rotor silencer) of the present invention;

[0060] Figure 2It is a cross-sectional schematic diagram of the silencer device (two-stage rotor silencer) of the present invention;

[0061] Figure 3 is a three-dimensional cross-sectional view of the first plate (upper plate) in the muffler device of the present invention;

[0062] Figure 4 is a three-dimensional cross-sectional view of the second plate (lower plate) in the muffler device of the present invention;

[0063] Figure 5 is a front cross-sectional view of the first plate (upper plate) in the muffler device of the present invention;

[0064] Figure 6 is a front cross-sectional view of the second plate (lower plate) in the muffler device of the present invention;

[0065] Figure 7 is a rear view of the second plate (lower plate) in the muffler device of the present invention;

[0066] Figure 8 is a rear view of the first plate (upper plate) in the muffler device of the present invention;

[0067] Fig. 9 It is a cross-sectional schematic diagram of the silencer device (primary silencer cover) of the present invention;

[0068] Fig.10 1 is a schematic top view of the muffler device (primary muffler cover) of the present invention;

[0069] Fig.11 is a top view of the structure of the rotor core of the present invention;

[0070] Fig.12 is a longitudinal cross-sectional view of a rotor core of the present invention;

[0071] Fig.13 It is a noise comparison diagram of the secondary silencer of the present invention compared with the primary silencer.

[0072] The reference numerals in the figure are as follows:

[0073] 1. Motor rotor; 11. Rotor flow hole; 12. Rotor rivet hole; 13. Magnetic steel groove; 2. Silencer; 20. Second flow hole; 21. Silencer cavity; 22. First plate; 221. First pillar; 222. Groove structure; 222a. First groove; 222b. Second groove; 223. First side plate; 223a. First side plate a; 223b. First side plate b; 23. Second plate; 231. Second pillar; 232. Second side plate; 232a. Second side plate a; 232b. Second side plate b; 24. Exhaust port; 25. Rivet hole; 3. Primary silencer cover. DETAILED DESCRIPTION

[0074] like Figure 1-12 As shown, the present invention provides a silencing device, wherein:

[0075] The silencer 2 is arranged on the motor rotor 1 of the compressor, and the motor rotor 1 has a rotor circulation hole 11. The silencer 2 is provided with a second circulation hole 20, and the second circulation hole 20 is arranged opposite to the rotor circulation hole 11, and the silencer 2 has a silencer cavity 21 connected with the second circulation hole 20 inside, and the second circulation hole 20 is arranged one-to-one with the rotor circulation hole 11, and the silencer cavity 21 is arranged one-to-one with the second circulation hole 20.

[0076] The present invention provides a silencer on the compressor motor rotor, and a silencer cavity corresponding to the second flow hole is provided inside the silencer, and the second flow hole corresponds to the rotor flow hole one by one, so that the gas flowing out of each rotor flow hole can enter the silencer cavity corresponding to it and be silenced, and each rotor flow hole is effectively silenced separately through each independent silencer cavity, which can effectively reduce the noise, especially in the medium and high frequency bands. The present invention solves the problem of the noise generated by the high-pressure gas discharged from the pump body, which is amplified by the rotor after the noise is reduced by the first-stage silencer cover, and at the same time increases the gas-liquid buffer area to fully separate the refrigeration oil and the refrigerant. The core technology of the present invention is to improve the oil blocking effect, reduce the oil discharge rate of the compressor, and at the same time widen the noise reduction frequency band, and design a two-stage rotor silencer used in conjunction with the rotor, optimize the gas path, and orderly discharge the high-temperature and high-pressure gas compressed by the pump body, which can effectively reduce the peak noise in the 2KHz-6KHz frequency band.

[0077] The high-temperature and high-pressure gas-liquid gas discharged from the exhaust port of the pump body of the traditional compressor structure has a periodic change in airflow pressure and speed, and produces airflow pulsation. After the airflow is compressed, the exhaust gas expands instantly, generating a large transient impact force, which can excite the movement structure to vibrate within a wider frequency band. After the airflow passes through the first-stage silencer cover, a part of the peak noise is eliminated. When it passes through the high-speed rotating or variable-speed rotor flow hole, its gas pulsation will increase, turbulence will increase, and aerodynamic noise will increase significantly. After searching for relevant literature, there is no directly related background technology research to reduce the noise here.

[0078] After the first-stage silencer cover eliminates part of the peak noise, part of the peak noise of the full frequency band of the high-pressure gas is weakened, but after the high-speed rotation or variable speed rotor disturbance, the high-pressure gas becomes disordered. The structure of the present invention can further reduce the noise of the high-pressure gas at this time, and eliminate the remaining peak noise of the full frequency band after the first-stage silencer cover is silenced through the second-stage rotor silencer, and optimize the gas path, reduce the rotor selection wind resistance, reduce losses, and improve performance;

[0079] The first-level silencer cover of the compressor has obvious effect on the noise within 2KHz in the whole frequency band. It selects obvious resonant frequency points within 2KHz through the resonance principle, so that the high-temperature and high-pressure gas discharged from the pump body radiates in the silencer cavity of the silencer cover, staggering the selected resonant frequency to achieve the function of silencer. However, due to structural limitations, the silencer cover has poor noise reduction effect on peak noise outside 2KHz, and cannot stagger its resonant frequency well. The structure of the present invention is mainly aimed at the noise of 2KHz-6KHz of the compressor. The high-temperature and high-pressure gas discharged from the pump body passes through the first-level silencer cover to eliminate the peak noise within 2KHz, and then passes through the second-level rotor silencer to eliminate the obvious resonant frequency points within 2KHz-6KHz, thereby improving the noise reduction ability of the compressor.

[0080] Preferably,

[0081] The muffler 2 comprises a first plate 22 and a second plate 23, the first plate 22 and the second plate 23 are interlocked to form the muffler cavity 21 therebetween, and the second flow hole 20 is provided on the second plate 23 and penetrates through two opposite end faces of the second plate 23. This is the preferred structural form of the muffler of the present invention, the muffler cavity can be formed together by interlocking the structural form of the two plates, and the two plates are fixed together on the rotor core, and as the rotor rotates together, the oil-gas mixture coming out of the rotor flow hole is introduced into the muffler cavity to perform an effective muffler effect, and the oil is thrown out by centrifugal force to achieve the effect of oil-gas separation.

[0082] Preferably,

[0083] The first plate 22 and the second plate 23 are arranged up and down, and the second plate 23 is located at the bottom and is a lower flat plate, and the first plate 22 is located at the top and is an upper flat plate. This is the preferred arrangement of the two plates of the present invention, that is, the upper flat plate and the lower flat plate are arranged up and down, the lower flat plate is connected to the rotor core and fixed on the rotor core, and is connected to the rotor flow hole through the second flow hole to introduce the gas into the silencer chamber for effective silencing and oil-gas separation.

[0084] Preferably,

[0085] The first plate 22 is provided with a first pillar 221 extending and protruding in the direction of the second plate 23, and the second plate 23 is provided with a second pillar 231 extending and protruding in the direction of the first plate 22. When the first plate 22 and the second plate 23 are buckled, the first pillar 221 and the second pillar 231 are connected to form a joint pillar. The number of the first pillar 221 and the second pillar 231 is equal to the number of the rotor flow holes 11, and a muffler cavity 21 is formed between two adjacent joint pillars. The inner wall of the first pillar and / or the second pillar is provided with a protruding structure, which can enhance the turbulence effect on the airflow and improve the muffler effect.

[0086] This is the first preferred structural form of the silencer chamber formed jointly by the first plate and the second plate of the present invention, that is, a first pillar protruding from the first plate and a second pillar protruding from the second plate are connected to effectively form an independent silencer chamber between the two joined pillars, thereby effectively increasing the volume space of the fluid, and there are two independent silencer chambers on both sides of the joined pillars, which effectively perform separate silencer effects on each rotor flow hole, thereby improving the silencer effect on mid- and high-frequency noise.

[0087] When the compressor is running, the refrigerant enters the pump body and is compressed, and high-temperature and high-pressure gas is discharged. At the same time, part of the refrigeration oil will be carried up to the upper chamber of the compressor. The refrigeration oil has the function of lubricating the moving parts of the pump body, reducing the friction loss of the pump body, and also has the function of cooling the compressor to generate heat and preventing the compressor from freezing in a low-temperature environment. The traditional structure of the compressor uses an oil baffle seat and an oil baffle cap. The oil baffle cap is generally a U-shaped structure. The vertical U-shaped outer wall has a small contact area with the mixed refrigerant and refrigeration oil disturbance, and the structure is single, resulting in poor separation effect. The refrigeration oil in the compressor flows into the air-conditioning system, affecting the heat exchange efficiency and reducing the air-conditioning performance. At the same time, the bottom surface of the existing oil baffle cap fits the end surface of the rotor core, and only the vertical U-shaped surface is used for oil-gas separation. The separation efficiency is low, the compressor has a high oil discharge rate, and the air-conditioning performance is poor. The structure of the present invention can rotate together with the rotor. After the high-pressure gas enters the silencer cavity, it hits the cavity wall. Because the cavity wall area of ​​the structure is much larger than that of the existing structure, the separation effect of the refrigeration oil and the refrigerant is better. At the same time, due to the fan blade-shaped pillar structure, the refrigeration oil is thrown out along the fan blade pillar during rotation and slides along the shell into the bottom oil pool. The fan-shaped pillars also optimize the gas path, and the high-pressure gas is discharged from the silencer cavity in an orderly manner.

[0088] Preferably,

[0089] A third pillar (not shown) is protruded from the first plate 22 in a direction extending toward the second plate 23, and when the first plate 22 and the second plate 23 are buckled, the third pillar is connected to the second plate 23, the number of the third pillars is equal to the number of the rotor flow holes 11, and one muffler cavity 21 is formed between two adjacent third pillars; or,

[0090] A fourth pillar (not shown) is protrudingly provided on the second plate 23 and extending in the direction of the first plate 22, and the fourth pillar is connected to the first plate 22 when the first plate 22 and the second plate 23 are buckled together. The number of the fourth pillars is equal to the number of the rotor flow holes 11, and a silencer chamber 21 is formed between two adjacent fourth pillars.

[0091] This is the second and third preferred structural form of the silencer chamber formed jointly by the first plate and the second plate of the present invention, that is, the third pillar protruding from the first plate is connected to the second plate, and an independent silencer chamber is effectively formed between the two third pillars, which effectively increases the volume space of the fluid, and there are two independent silencer chambers on both sides of the third pillar, which effectively performs a separate silencer effect on each rotor flow hole, thereby improving the silencer effect on mid- and high-frequency noise; the fourth pillar protruding from the second plate is connected to the first plate, and an independent silencer chamber is effectively formed between the two fourth pillars, thereby effectively increasing the volume space of the fluid, and there are two independent silencer chambers on both sides of the fourth pillar, thereby effectively performing a separate silencer effect on each rotor flow hole, thereby improving the silencer effect on mid- and high-frequency noise.

[0092] Preferably,

[0093] The first pillars 221 are multiple and evenly distributed along the circumferential direction of the motor rotor, and / or the second pillars 231 are multiple and evenly distributed along the circumferential direction of the motor rotor; and / or, at least one of the first plate 22, the second plate 23, the first pillar 221 and the second pillar 231 is made of powder metallurgy or high manganese steel. This is the preferred structural form of the first pillar of the present invention. Through multiple first pillars and multiple second pillars, which are evenly distributed along the circumferential direction of the motor rotor, the volume of the separated silencer chambers can be equal, so that the gas flowing out of each rotor flow hole has the same silencer effect, and the uniformity of silencer is improved; by making at least one of the first plate 22, the second plate 23, the first pillar 221 and the second pillar 231 of powder metallurgy or high manganese steel, it can effectively play a role in gas silencer and oil-gas separation (will not react with gas), and the structure is more stable.

[0094] Preferably,

[0095] A groove structure 222 is also provided on the end surface of one side opposite to the second plate 23, and is recessed in a direction away from the second plate 23 to form a muffler chamber. The groove structure 222 is located at the position of the muffler chamber 21 and is connected to the muffler chamber 21. The present application also uses the groove structure provided on the first plate to allow the fluid in the second flow hole to impact the groove structure, effectively achieving the purpose of reducing energy and eliminating medium and high frequency noise. Through two grooves of unequal volumes, the fluid first enters the small volume groove and then enters the large volume groove, so that the gas can be silenced in steps, further improving the muffler effect.

[0096] Preferably,

[0097] The groove structure 222 includes a first groove 222a and a second groove 222b that are connected, and the volumes of the first groove 222a and the second groove 222b are different, the volume of the first groove 222a is smaller than the volume of the second groove 222b, and the first groove 222a is arranged opposite to and in communication with the second flow hole 20. By providing two grooves and the fluid first flows into the first groove and then into the second groove, the fluid first enters the small volume groove and then enters the large volume groove, so that the gas can be silenced in steps, further improving the silencer effect.

[0098] Preferably,

[0099] A groove structure 222 is correspondingly arranged in each of the muffler chambers 21; and / or, the first groove 222a and / or the second groove 222b are blind groove structures; and / or, the first groove 222a and the second groove 222b are both circular grooves, and the radius of the first groove 222a is smaller than the radius of the second groove 222b; and / or, the position where the first groove 222a and the second groove 222b meet is an arc transition. This is the preferred shape and structural form of the first groove and the second groove of the present invention. The blind groove allows the gas to enter therein and be silenced, but will not pass through the blind groove. Both grooves are circular grooves, which can allow the gas to be reflected multiple times along the inner wall after entering therein, forming a maximum offsetting effect of the stacking effect and the best muffler effect; the arc transition can improve the reflection of the gas noise at the junction, enhance the offsetting ability, and further improve the muffler effect.

[0100] Preferably,

[0101] The first plate 22 is also provided with a first side plate 223 protruding toward the second plate 23 on the outer circumference side. The exhaust port 24 for allowing gas to be discharged from the muffler cavity 21 includes a portion of the outer circumference side of the first plate 22 where the first side plate 223 is not provided. The exhaust port 24 is communicated with the muffler cavity 21. The side plate structure provided at the outer circumference of the first plate can block the gas moving radially outward, further improving the muffler effect of the gas in the muffler cavity and the oil-gas separation effect.

[0102] Preferably,

[0103] When the first pillar 221 is included, the first side plate 223 includes a first side plate a223a extending circumferentially from the radial outer end of the first pillar 221 on one side of the muffler chamber and a first side plate b223b extending circumferentially from the radial outer end of the first pillar 221 on the other side of the muffler chamber, the first side plate a223a extends in the direction of the first side plate b223b, and the first side plate b223b extends in the direction of the first side plate a223a, and the exhaust port 24 includes a circumferential spacing portion between the first side plate a223a and the first side plate b223b. This is the preferred structural form of the first side plate of the present invention, that is, the first side plates a and the first side plates b on both sides can form a blocking effect on the gas at both ends, strengthen the degree of gas impacting back and forth in the muffler chamber, and finally discharge through the exhaust port (discharged from the gap between the first side plate a and the first side plate b), thereby improving the effect of silencing medium and high frequency noise.

[0104] Preferably,

[0105] The first side plate a223a is an arc-shaped plate, the first side plate b223b is also an arc-shaped plate, the first plate 22 is a disc, the sum of the circumferential lengths of the first side plate a223a and the first side plate b223b is greater than or equal to 1 / 3 of the circumferential length between two adjacent first pillars 221; and / or, the height of the first side plate a223a is equal to the height of the first pillar 221, and the height of the first side plate b223b is equal to the height of the first pillar 221. This is a further preferred structural form of the first side plate a and the first side plate b of the present invention. The arc-shaped side plate is designed to partially surround the two pillars in order to shape the cavity. The sum of the circumferential lengths of the first side plate a223a and the first side plate b223b is greater than or equal to 1 / 3 of the circumferential length between two adjacent first pillars 221, which can achieve the maximum degree of silencing and ensure gas discharge.

[0106] Preferably,

[0107] The outer circumference of the second plate 23 is also provided with a second side plate 232 protruding toward the first plate 22, and the exhaust port 24 allowing the gas to be discharged from the muffler chamber 21 also includes a portion of the outer circumference of the second plate 23 where the second side plate 232 is not provided, and the second side plate 232 extends to connect with the first side plate 223. The side plate structure provided at the outer circumference of the second plate can block the gas moving radially outward, further improving the muffler effect of the gas in the muffler chamber and the oil-gas separation effect.

[0108] Preferably,

[0109] When the second pillar 231 is included, the second side plate 232 includes a second side plate a232a extending circumferentially from the radial outer end of the second pillar 231 on one side of the muffler chamber 21 and a second side plate b232b extending circumferentially from the radial outer end of the second pillar 231 on the other side of the muffler chamber, the second side plate a232a extends in the direction of the second side plate b232b, and the second side plate b232b extends in the direction of the second side plate a232a, and the exhaust port 24 includes a circumferential spacing portion between the second side plate a232a and the second side plate b232b. This is the preferred structural form of the second side plate of the present invention, that is, the second side plates a and the second side plates b on both sides can form a blocking effect on the gas at both ends, strengthen the degree of gas impacting back and forth in the muffler chamber, and finally discharge through the exhaust port (discharged from the gap between the second side plate a and the second side plate b), thereby improving the effect of silencing the mid- and high-frequency noise.

[0110] Preferably,

[0111] The second side plate a232a is an arc-shaped plate, the second side plate b232b is also an arc-shaped plate, the second plate 23 is a disc, the sum of the circumferential lengths of the second side plate a232a and the second side plate b232b is greater than or equal to 1 / 3 of the circumferential length between two adjacent second pillars 231; and / or, the height of the second side plate a232a is equal to the height of the second pillar 231, and the height of the second side plate b232b is equal to the height of the second pillar 231. This is a further preferred structural form of the second side plate a and the second side plate b of the present invention. The arc-shaped side plate is designed to partially surround the two pillars in order to shape the cavity. The sum of the circumferential lengths of the second side plate a232a and the second side plate b232b is greater than or equal to 1 / 3 of the circumferential length between two adjacent second pillars 231, which can achieve the maximum degree of silencing and ensure gas discharge.

[0112] Preferably,

[0113] The line segment shape of one circumferential side of the first pillar 221 in the cross section satisfies the formula y(x)=a+bx+cx 2+dx 3 and / or, the line segment shape of the other circumferential side of the first support 221 in the cross section satisfies the formula y(x)=a+bx+cx 2 +dx 3 This is the preferred curve shape of the first pillar and the second pillar of the present invention. By forming a cubic curve, the side can have a more curved shape following the flow of the fluid, and the gas can produce a larger angle and a larger range of reflection when it hits the wall, further effectively improving its silencing ability.

[0114] Preferably,

[0115] The height of the motor rotor 1 is H1, the area of ​​the second flow hole 20 is S1, the sum of the volumes of the muffler cavity and the muffler chamber is V1, and The range is within (1, 2.5). The product of the motor rotor height and the area of ​​the second flow hole (the area of ​​the second flow hole is basically equal to the area of ​​the rotor flow hole) is basically equal to the volume of the gas in the rotor flow hole. The above relationship effectively ensures that the volume of the silencer cavity and the silencer chamber is greater than the volume of the rotor flow hole, ensuring that the high-pressure gas entering the secondary rotor silencer from the rotor flow hole fully enters the silencer cavity, making the volume larger, reducing the peak noise in the 2KHz-6KHz frequency band, and allowing the gas to fully hit the cavity wall, separating the refrigeration oil and the refrigerant. The fan-shaped pillar drives the gas to rotate, and the refrigeration oil is thrown out and flows into the bottom oil pool along the inner wall of the shell, reducing the oil discharge rate.

[0116] Preferably,

[0117] V1=600mm 3 , S1=5mm 2 , rotor height H1 = 60 mm, This is the preferred relationship between the volume of the above-mentioned silencer cavity and silencer chamber and the volume of the rotor flow hole of the present invention, so that the volume of the above-mentioned silencer cavity and silencer chamber is twice the volume of the rotor flow hole, which can maximize the silencer effect and achieve the best silencer effect on peak noise in the 2KHz-6KHz frequency band.

[0118] Preferably,

[0119] It also includes a first-stage silencer cover 3 arranged on the compressor flange, and the volume of the first-stage silencer cover 3 is V3, the total volume of the pump cylinder of the compressor is V4, and By setting up a first-level silencer cover, the silencing effect on the gas can be enhanced together with the second-level silencer, and the first-level silencer has a significant effect mainly on the noise within 2KHz in the full frequency band of the compressor. The volume ratio of the second-level silencer is greater than that of the first-level silencer, and the buffer space provided is larger, further improving the silencing effect.

[0120] Preferably,

[0121] V3=150mm 3 , V4=200mm 3 , This is the preferred relationship between the above-mentioned first-stage silencer cover and the total volume of the pump body cylinder of the compressor of the present invention, which can maximize the silencer effect and achieve the best silencer effect on peak noise within the frequency band within 2KHz.

[0122] Preferably,

[0123] The total height of the first support 221 and the second support 231 when they are joined is H2, the length of the second flow hole 20 in the cross section is L, the depths of the first groove and the second groove are equal and W1, the area of ​​the second flow hole 20 is S1, and (H2+W1)×L≥S1. The design of the blind hole depth and support height meets the requirement of reducing the 2KHz-6KHz frequency band of the high-pressure gas rising from the lower plate to the muffler chamber, and the buffer space margin is sufficient to ensure that the gas is discharged in an orderly manner after passing through the secondary rotor muffler, reducing the rotor rotation wind resistance, reducing friction loss, and improving the compressor performance.

[0124] Preferably,

[0125] W1=2mm,H2=6mm,L=2,then (H2+W1)×L=16mm 2 , S1=5mm 2 This is the preferred relationship between the depth of the first groove and the second groove and the total height of the first support 221 and the second support 231 when they are connected, which can maximize the silencing effect and achieve the best silencing effect on peak noise within the frequency band within 2KHz.

[0126] Preferably,

[0127] The first support 221 and the second support 231 are both provided with rivet holes 25, which are fixed to the motor rotor by rivets. The first plate and the second plate can be effectively fixed to the rotor core through the rivet holes, so that they rotate together with the motor rotor.

[0128] The present invention also provides a compressor, comprising the silencer device described in any of the preceding items.

[0129] The present invention also provides an air conditioning system, which comprises the aforementioned compressor.

[0130] The present invention discloses a two-stage rotor silencer structure for a variable frequency compressor. By designing a fan blade-shaped support group A, an upper flat plate B, and a lower flat plate C, the oil blocking effect of the compressor is optimized and the oil discharge rate is reduced. At the same time, the high-temperature and high-pressure gas that has passed through the first-stage silencer is subjected to a second-stage noise reduction, thereby eliminating the peak noise in the 2KHz-6KHz frequency band of the compressor.

[0131] The embodiment of the present invention only takes the compressor used in the large-capacity air-conditioning system as an example, but the conclusion includes but is not limited to the compressor used in the large-capacity air-conditioning system.

[0132] The compressor described in this embodiment includes a motor, a pump body, and a housing. The motor includes a stator assembly and a rotor assembly. The stator assembly mainly includes a stator core, a winding, an insulating frame, and a lead wire assembly. The rotor assembly mainly includes a rotor core, a magnetic steel, a secondary rotor silencer, a balance block, and a rivet. The pump body includes a cylinder, a roller, an upper flange, and a primary silencer cover. The secondary rotor silencer includes a fan blade-shaped support group A, an upper plate B, and a lower plate C. The fan blade-shaped support has a rivet hole, which is matched with the rotor core through the rivet. The lower plate C has a flow hole corresponding to the rotor core, and the upper plate has a silencer chamber.

[0133] The blade-shaped support group A is composed of 4 blade-shaped supports and is evenly distributed along the circumference. The blade-shaped support is obtained by two spline lines according to the axis. The bottom surface of the plate is the x-axis and y-axis coordinate system. A spatial rectangular coordinate system is established, and the point (1, 0, 2) is determined and substituted into the formula y(x) = a + bx + cx 2 +dx 3 The first spline is obtained; then the point (2, 0, 2) is determined and substituted into the formula y(x) = a + bx + cx 2 +dx 3 The second spline is obtained. The two splines are combined to form a blade-shaped pillar. At the same time, the volume of the silencer chamber V1 = 600mm3, the flow hole area S1 = 5mm2, and the rotor height H1 = 60mm are determined. Then it satisfies Within the range (1, 2.5). Ensure that the high-pressure gas entering the secondary rotor silencer from the rotor flow hole fully enters the silencer cavity, reduces the peak noise in the 2KHz-6KHz frequency band, and makes the gas fully hit the cavity wall, the refrigeration oil and the refrigerant are separated, and the gas is driven to rotate by the fan blade-shaped pillar, and the refrigeration oil is thrown out and flows into the bottom oil pool along the inner wall of the shell, reducing the oil discharge rate.

[0134] As described in claim 2, the first-stage silencer cover volume V3 of the compressor is 150 mm3, and the single cylinder volume of the pump body is V4 = 200 mm3. The ratio of the silencer cover volume V3 to the cylinder volume V4 is 3:4. Substituting into the formula Less than ratio In order not to reduce the cooling capacity, twice the ratio of the silencer cover volume to the cylinder volume must be smaller than the ratio of the secondary rotor silencer to the flow volume in the rotor, to ensure that the high-pressure gas discharged from the pump body can be fully silenced in the secondary rotor silencer after the noise reduction of the primary silencer cover, and to ensure smooth exhaust to meet the cooling capacity requirements.

[0135] In the two-stage rotor silencer, the silencer chamber of the upper plate is connected by two blind holes. The two blind holes are directly above the flow holes of the lower plate. The silencer chamber is formed by two large and small circles connected together. The small circle is close to the axis, with a radius of R1=2, and the large circle is closely connected to the small circle, with a radius of R2=4. The middle is connected by the fillet of R2. The depth of the two blind holes is W1=2mm, the height of the pillar is H2=6mm, and the length of the flow hole of the lower plate is L=2. Then the formula (H2+W1)×L=16mm2, combined with the above-mentioned S1=5mm2, satisfies (H2+W1)×L≥S1. The design of the blind hole depth and the pillar height meets the requirement of reducing the 2KHz-6KHz frequency band of the high-pressure gas rising from the lower plate to the silencer chamber. The buffer space margin is sufficient to ensure that the gas is discharged in an orderly manner after passing through the two-stage rotor silencer, reducing the rotor rotation wind resistance, reducing friction loss, and improving the performance of the compressor.

[0136] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present invention. These improvements and variations should also be regarded as the protection scope of the present invention.

Claims

1. A silencing device, characterized in that: The silencer (2) is arranged on a motor rotor (1) of a compressor, the motor rotor (1) has a rotor circulation hole (11), the silencer (2) is provided with a second circulation hole (20), the second circulation hole (20) is arranged opposite to the rotor circulation hole (11), and the silencer (2) has a silencer cavity (21) in communication with the second circulation hole (20), the second circulation hole (20) and the rotor circulation hole (11) are arranged in a one-to-one correspondence, and the silencer cavity (21) and the second circulation hole (20) are arranged in a one-to-one correspondence; The muffler device (2) comprises a first plate (22) and a second plate (23), the first plate (22) and the second plate (23) being interlocked to form the muffler cavity (21) therebetween, and the second flow hole (20) is arranged on the second plate (23) and penetrates through two opposite end surfaces of the second plate (23); A first pillar (221) is provided on the first plate (22) so as to protrude in a direction extending toward the second plate (23), and a second pillar (231) is provided on the second plate (23) so as to protrude in a direction extending toward the first plate (22). When the first plate (22) and the second plate (23) are buckled together, the first pillar (221) and the second pillar (231) are connected to form a joint pillar. The number of the first pillar (221) and the second pillar (231) are both equal to the number of the rotor circulation holes (11), and a muffler cavity (21) is formed between two adjacent joint pillars.

2. The silencing device according to claim 1, characterized in that: The first plate (22) and the second plate (23) are arranged up and down, and the second plate (23) is located at the bottom and is a lower flat plate, and the first plate (22) is located at the top and is an upper flat plate.

3. The silencing device according to claim 1, characterized in that: A third pillar is protrudingly provided on the first plate (22) in a direction extending toward the second plate (23), and when the first plate (22) and the second plate (23) are buckled, the third pillar is connected to the second plate (23), the number of the third pillars is equal to the number of the rotor flow holes (11), and one muffler cavity (21) is formed between two adjacent third pillars; or, A fourth pillar is protrudingly provided on the second plate (23) in a direction extending toward the first plate (22), and when the first plate (22) and the second plate (23) are buckled, the fourth pillar is connected to the first plate (22), the number of the fourth pillars is equal to the number of the rotor flow holes (11), and a muffler cavity (21) is formed between two adjacent fourth pillars.

4. The silencing device according to claim 1, characterized in that: The first pillars (221) are multiple and evenly distributed along the circumferential direction of the motor rotor, and / or the second pillars (231) are multiple and evenly distributed along the circumferential direction of the motor rotor; and / or the material of at least one of the first plate (22), the second plate (23), the first pillar (221) and the second pillar (231) is powder metallurgy or high manganese steel.

5. The silencing device according to claim 1, characterized in that: A groove structure (222) is provided on the end surface of one side of the first plate (22) opposite to the second plate (23), and is recessed in a direction away from the second plate (23) to form a muffler chamber; the groove structure (222) is located at the position of the muffler cavity (21) and is in communication with the muffler cavity (21).

6. The silencing device according to claim 5, characterized in that: The groove structure (222) comprises a first groove (222a) and a second groove (222b) which are connected to each other, and the volumes of the first groove (222a) and the second groove (222b) are different, the volume of the first groove (222a) is smaller than the volume of the second groove (222b), and the first groove (222a) is arranged opposite to and in communication with the second flow hole (20).

7. The silencing device according to claim 6, characterized in that: One groove structure (222) is correspondingly arranged in each of the muffler chambers (21); and / or the first groove (222a) and / or the second groove (222b) are blind groove structures; and / or the first groove (222a) and the second groove (222b) are both circular grooves, and the radius of the first groove (222a) is smaller than the radius of the second groove (222b); and / or the position where the first groove (222a) and the second groove (222b) meet is an arc transition.

8. The silencing device according to any one of claims 1 to 7, characterized in that: A first side plate (223) protruding in the direction of the second plate (23) is also provided on the outer peripheral side of the first plate (22); an exhaust port (24) allowing gas to be discharged from the silencer chamber (21) includes a portion of the outer peripheral side of the first plate (22) where the first side plate (223) is not provided; and the exhaust port (24) is connected to the silencer chamber (21).

9. The silencing device according to claim 8, characterized in that: When the first pillar (221) is included, the first side plate (223) includes a first side plate a (223a) extending circumferentially from the radial outer end of the first pillar (221) on one side of the muffler chamber and a first side plate b (223b) extending circumferentially from the radial outer end of the first pillar (221) on the other side of the muffler chamber, the first side plate a (223a) extends in the direction of the first side plate b (223b), and the first side plate b (223b) extends in the direction of the first side plate a (223a), and the exhaust port (24) includes a circumferential spacing portion between the first side plate a (223a) and the first side plate b (223b).

10. The silencing device according to claim 9, characterized in that: The first side plate a (223a) is an arc-shaped plate, the first side plate b (223b) is also an arc-shaped plate, the first plate (22) is a disc, the sum of the circumferential lengths of the first side plate a (223a) and the first side plate b (223b) is greater than or equal to 1 / 3 of the circumferential length between two adjacent first pillars (221); and / or the height of the first side plate a (223a) is equal to the height of the first pillar (221), and the height of the first side plate b (223b) is equal to the height of the first pillar (221).

11. The silencing device according to claim 8, characterized in that: A second side plate (232) protruding toward the first plate (22) is also provided on the outer peripheral side of the second plate (23), and an exhaust port (24) allowing gas to be discharged from the silencer chamber (21) also includes a portion of the outer peripheral side of the second plate (23) where the second side plate (232) is not provided, and the second side plate (232) extends to connect with the first side plate (223).

12. The silencing device according to claim 11, characterized in that: When a second pillar (231) is included, the second side plate (232) includes a second side plate a (232a) extending circumferentially from the radial outer end of the second pillar (231) on one side of the muffler chamber (21) and a second side plate b (232b) extending circumferentially from the radial outer end of the second pillar (231) on the other side of the muffler chamber, the second side plate a (232a) extends in the direction of the second side plate b (232b), and the second side plate b (232b) extends in the direction of the second side plate a (232a), and the exhaust port (24) includes a circumferential spacing portion between the second side plate a (232a) and the second side plate b (232b).

13. The silencing device according to claim 12, characterized in that: The second side plate a (232a) is an arc-shaped plate, the second side plate b (232b) is also an arc-shaped plate, the second plate (23) is a disc, the sum of the circumferential lengths of the second side plate a (232a) and the second side plate b (232b) is greater than or equal to 1 / 3 of the circumferential length between two adjacent second pillars (231); and / or the height of the second side plate a (232a) is equal to the height of the second pillar (231), and the height of the second side plate b (232b) is equal to the height of the second pillar (231).

14. The silencing device according to claim 1, characterized in that: The line segment shape of one circumferential side of the first support (221) in the cross section satisfies the formula y(x)=a+bx+cx 2 +dx 3 ; and / or, the line segment shape of the other circumferential side of the first support (221) in the cross section satisfies the formula y(x)=a+bx+cx 2 +dx 3 .

15. The silencing device according to claim 5, characterized in that: The height of the motor rotor (1) is H1, the area of ​​the second flow hole (20) is S1, the sum of the volumes of the muffler cavity and the muffler chamber is V1, and The range is (1,2.5).

16. The silencing device according to claim 15, characterized in that: V1=600mm 3 , S1=5mm 2 , rotor height H1 = 60 mm, 17. The silencing device according to claim 15, characterized in that: It also includes a first-stage silencer cover (3) arranged on the compressor flange, and the volume of the first-stage silencer cover (3) is V3, the total volume of the pump cylinder of the compressor is V4, and 18. The silencing device according to claim 17, characterized in that: V3=150mm 3 ,V4=200mm 3 , 19. The silencing device according to claim 6, characterized in that: The total height of the first pillar (221) and the second pillar (231) when connected is H2, the length of the second flow hole (20) in the cross section is L, the depths of the first groove and the second groove are equal and the depth is W1, the area of ​​the second flow hole (20) is S1, and (H2+W1)×L≥S1.

20. The silencing device according to claim 19, characterized in that: W1=2mm,H2=6mm,L=2,then (H2+W1)×L=16mm 2 , S1=5mm 2 .

21. The silencing device according to claim 1, characterized in that: The first support (221) and the second support (231) are both provided with rivet holes (25) and are fixed to the motor rotor via rivets.

22. A compressor, characterized in that: A silencing device comprising the silencing device described in any one of claims 1-21.

23. An air conditioning system, characterized in that: Comprising the compressor of claim 22.

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