CN115750372A - Silencing assembly and scroll compressor - Google Patents
Silencing assembly and scroll compressor Download PDFInfo
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- CN115750372A CN115750372A CN202211591588.3A CN202211591588A CN115750372A CN 115750372 A CN115750372 A CN 115750372A CN 202211591588 A CN202211591588 A CN 202211591588A CN 115750372 A CN115750372 A CN 115750372A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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Abstract
The application provides a amortization subassembly and scroll compressor. The silencing assembly comprises a cover body, a cover buckle air inlet and an exhaust silencing cavity; an exhaust port is arranged on the side wall of the cover body; the silencing cavity is at least internally provided with an annular partition board covering the air inlet, and the partition board divides the silencing cavity into a first cavity and a second cavity which are mutually isolated; the first chamber is positioned on the inner side of the partition plate and communicated with the exhaust port, and the second chamber is positioned on the outer side of the partition plate; the partition plate is provided with an opening for communicating the first chamber with the second chamber. This application sets up the baffle in the amortization intracavity that constitutes between lid and air inlet, has constituted the resistance and has expanded the compound structure of making an uproar of falling that the amortization combined together of chamber amortization and resistance interference, can weaken the compressor air current pulsation noise that quiet whirlpool dish gas vent produced when each frequency channel was moved, and then reduces the running noise of compressor complete machine, and the travelling comfort obtains promoting.
Description
Technical Field
The application belongs to the technical field of scroll compressors, and particularly relates to a silencing assembly and a scroll compressor.
Background
The scroll compressor has the advantages of small volume, light weight, continuous and stable air suction and exhaust, small vibration, small noise, low energy consumption and the like, and is generally applied to the fields of air-conditioning refrigeration, power engineering, transportation and the like. The scroll compressor is mainly formed by mutually meshing a movable scroll plate and a fixed scroll plate which are scrolled by two bifunctional equations, in the process of compression operation, the fixed scroll plate is fixed on a frame, the movable scroll plate is driven by a crankshaft and is limited by an anti-rotation mechanism, the movable scroll plate rotates around the center of a base circle of the fixed scroll plate in a plane with a small radius, gas or refrigerant is sucked from the periphery of the fixed scroll plate and rotates along with an eccentric shaft, so that the gas or refrigerant is compressed step by step in a plurality of crescent-shaped compression cavities formed by meshing the movable scroll plate and the fixed scroll plate, and the compressed gas or refrigerant is finally continuously discharged from an axial exhaust hole in the center of the fixed scroll plate.
Because the exhaust port of the fixed scroll is relatively small, when compressed gas or refrigerant passes through the exhaust port, large aerodynamic noise is generated, and particularly when the compressor runs at high frequency, the larger the airflow pulsation generated at the exhaust port of the fixed scroll is, the larger the generated aerodynamic noise is. The compressor is developed to achieve high frequency and high speed, and the requirement of customers for comfort is higher and higher, so the noise of the compressor is a problem to be solved.
The conventional scheme for reducing the aerodynamic noise of the exhaust port of the fixed scroll is to add an expanding silencing cover with an abrupt-changing cross section area above the exhaust port of the fixed scroll to change the acoustic resistance and reflect the noise back to the direction of a sound source, and the noise interferes with the noise with equal amplitude and opposite phase in the process of reflection back, so that the sound energy is reduced, and the effects of silencing and reducing the noise are achieved. However, the muffling cover structure can only weaken and reduce the noise of a certain frequency band of the compressor, and cannot completely meet the requirements of weakening and reducing the multi-band noise or the full-band noise, and the experience of users is relatively poor.
Disclosure of Invention
Therefore, the application provides a amortization subassembly and scroll compressor, can solve among the prior art traditional amortization lid structure and only can play the problem that weakens the reduction to the noise of a certain frequency channel of compressor.
In order to solve the above problems, the present application provides a noise reduction assembly including:
the cover body covers and buckles the air inlet to form an exhaust silencing cavity; an exhaust port is formed in the side wall of the cover body;
the silencing cavity is at least internally provided with an annular partition board covering the air inlet, and the partition board divides the silencing cavity into a first cavity and a second cavity which are mutually isolated; the first chamber is positioned on the inner side of the partition plate and communicated with the exhaust port, and the second chamber is positioned on the outer side of the partition plate;
the partition plate is provided with an opening for communicating the first chamber with the second chamber.
Optionally, a second partition plate is further disposed in the silencing cavity, and is disposed in the second chamber to divide the second chamber into two third chambers; and the second partition plate is provided with air holes communicated with the two third chambers, and the opening is communicated with the air exhaust port through the two third chambers.
Optionally, the second partition plate is provided with a plurality of partitions for partitioning the third separated chambers in such a manner that the opening communicates with the exhaust port through the plurality of partitioned chambers.
Optionally, the opening and the air vent are positioned such that exhaust flows from the opening to the exhaust port via a bend.
Optionally, the second partition plate is annular and is sleeved on the periphery of the partition plate at intervals, and the short flow between the opening and the air hole is 1/3-1/5 of the long flow.
Optionally, the second partition plates are sequentially sleeved, and the short flow between the air holes in two adjacent second partition plates is 1/3-1/5 of the long flow.
Optionally, the area of two adjacent chambers is larger on the outer side than on the inner side.
Optionally, the muffling frequency of each chamber is set to F, satisfying F = cx/4L, where x is an odd number and c is the speed of sound in air; l is half the distance sum of the short flow path and the long flow path in each chamber.
Optionally, the air hole in the second partition plate located at the outermost side and the air outlet are located on the same side of the cover body, an inserted partition plate is arranged in the silencing cavity, the inserted partition plate is arc-shaped and is arranged between the air hole and the air outlet, and the distance between the air hole and the air outlet can be prolonged.
Optionally, one end of the inserted partition plate is connected to the inner wall of the cover body; an inner inserting cavity pipe is formed between the inner inserting partition plate and the second partition plate on the outermost side, and the flow path of the inner inserting cavity pipe is more than or equal to half of the longest flow path of a cavity between the cover body and the second partition plate on the outermost side.
Optionally, the chamber sound damping frequency between the outermost second partition and the cover is set to f, satisfying f = cx/mL', where x is an odd number and c is the speed of sound in air; m is the flow of the interpolation lumen; l' is the longest flow path of a cavity surrounded by the second partition plate at the outermost side and the cover body.
According to another aspect of the present application, there is provided a scroll compressor including a sound attenuation assembly as described above.
The application provides a amortization subassembly includes: the cover body covers and buckles the air inlet to form an exhaust silencing cavity; an exhaust port is formed in the side wall of the cover body; the silencing cavity is at least internally provided with an annular partition board covering the air inlet, and the partition board divides the silencing cavity into a first cavity and a second cavity which are mutually isolated; the first chamber is positioned on the inner side of the partition plate and communicated with the exhaust port, and the second chamber is positioned on the outer side of the partition plate; the partition plate is provided with an opening for communicating the first chamber and the second chamber.
This application sets up the baffle in the amortization intracavity that constitutes between lid and air inlet, has constituted the resistance and has expanded the compound structure of making an uproar of falling that the amortization combined together of chamber amortization and resistance interference, can weaken the compressor air current pulsation noise that quiet whirlpool dish gas vent produced when each frequency channel was moved, and then reduces the running noise of compressor complete machine, and the travelling comfort obtains promoting.
Drawings
FIG. 1 is a schematic view of a scroll compressor according to an embodiment of the present application;
FIG. 2 is a schematic structural view of a pump body assembly according to an embodiment of the present application;
FIG. 3 is a three-dimensional schematic view of a cover according to an embodiment of the present application;
FIG. 4 is a first top view of a cover according to an embodiment of the present disclosure;
FIG. 5 is a second top view of the cover according to the embodiment of the present application;
FIG. 6 is a third top view of the cover according to the embodiment of the present disclosure;
FIG. 7 is a fourth top view of the cover according to the embodiment of the present application;
FIG. 8 is a first gas path diagram for noise reduction of the cover body according to the embodiment of the present application;
FIG. 9 is a second gas path diagram for noise reduction of the cover body according to the embodiment of the present application;
FIG. 10 is a graph comparing the total noise level of an 80cc displacement scroll compressor of the disclosed embodiment with a conventional configuration;
FIG. 11 is a plot of the noise spectrum within 1000Hz for the 80cc displacement scroll compressor of the present application embodiment versus the conventional configuration.
The reference numerals are represented as:
10. a lower cover assembly; 20. a housing assembly; 30. an upper cover assembly; 40. a lower bracket assembly; 50. a motor assembly; 60. a shafting assembly; 70. an electrical box assembly; 80. a movable disc assembly; 90. a stationary scroll assembly; 91. a static scroll pan; 92. a cover body; 93. a suction valve assembly; 93-1, an air suction valve cover; 93-2, a spring;
92A, a first divider plate; 92B, a second partition plate; 92C, a third partition plate; 92D, a fourth separating plate; 92 Outer cover An outer wall of the muffler; 92-1, a first exhaust port; 92-2, a second exhaust port; 92-3, a third exhaust port; 92-4, a fourth exhaust port; 92 Mouth piece An exhaust port; 92a, first exhaust gasA cavity; 92b, a second exhaust cavity; 92c, a third exhaust chamber; 92d, a fourth exhaust chamber; 92 Chamber An exhaust cavity; d 2 The inner diameter of the second exhaust cavity; d 3 The inner diameter of the third exhaust cavity; d 4 The inner diameter of the fourth exhaust cavity; d Chamber The inner diameter of an exhaust cavity defined by the Nth partition plate and the outer wall of the silencer; d 1 The width of the first exhaust port; d is a radical of 2 The width of the second exhaust port; d 3 The width of the third exhaust port; d is a radical of 4 The width of the fourth exhaust port; d is a radical of Chamber The width of the exhaust port;
L 1 the distance from the first exhaust port in the second exhaust cavity to the short flow channel of the second exhaust port; l is a radical of an alcohol 2 The distance from the first exhaust port in the second exhaust cavity to the long flow channel of the second exhaust port; l is a radical of an alcohol 3 The distance from the second exhaust port to the short runner of the third exhaust port in the third exhaust cavity; l is 4 The distance from the second exhaust port to the long flow channel of the third exhaust port in the third exhaust cavity; l is a radical of an alcohol 5 The distance from the third exhaust port to the short runner of the fourth exhaust port in the fourth exhaust cavity; l is a radical of an alcohol 6 The distance between the third exhaust port and the long flow passage of the fourth exhaust port in the fourth exhaust cavity, L Chamber The length of a flow passage of the exhaust cavity enclosed by the Nth partition plate and the outer wall of the silencer;
S 1 the area of the first exhaust cavity; s 2 The area of the second exhaust cavity; s 3 The area of the third exhaust chamber; s 4 The area of the fourth exhaust chamber; s. the Chamber The area of the fifth exhaust chamber;
90 plug-in The partition plate is inserted; 92 Pipe The inner inserting cavity tube; 92 Go out An outlet; m, the length of the internal inserted cavity pipe flow channel; p, gas pressure discharged by the static scroll.
Detailed Description
To make the objects, technical solutions and advantages of the present application more clear, the technical solutions of the present application will be clearly and completely described below with reference to specific embodiments of the present application and the accompanying drawings. It should be apparent that the described embodiments are only some of the embodiments of the present application, and not all of the embodiments. All other embodiments obtained by a person of ordinary skill in the art based on the embodiments in the present application without making any creative effort belong to the protection scope of the present application.
It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the application described herein are capable of operation in sequences other than those illustrated or described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
Referring collectively to fig. 1-11, in accordance with an embodiment of the present application, a muffler assembly, comprises:
a cover body 92 covering and covering the air inlet to form an exhaust silencing cavity; an exhaust port is formed in the side wall of the cover body;
the silencing cavity is at least internally provided with an annular partition plate covering the air inlet, and the partition plate divides the silencing cavity into a first cavity and a second cavity which are mutually isolated; the first chamber is positioned on the inner side of the partition plate and communicated with the exhaust port, and the second chamber is positioned on the outer side of the partition plate;
the partition plate is provided with an opening for communicating the first chamber and the second chamber.
This application sets up the baffle in the amortization intracavity that constitutes between lid 92 and air inlet, has constituted the compound noise reduction structure of making an uproar that resistance expanding chamber amortization, resistance interfere the amortization and combine together, can weaken the air current pulsation noise that the compressor quiet whirlpool gas vent produced when each frequency channel operation, and then reduce the running noise of compressor complete machine, and the travelling comfort obtains promoting.
The application discloses amortization chamber, after the high-pressure draught dilatation step-down amortization that gets into the amortization chamber to the air inlet, by the exhaust vent exhaust amortization chamber.
In the scroll compressor, the air inlet is a high-pressure air outlet on the static scroll, because the caliber of the high-pressure air outlet of the static scroll is small, and the sectional area is contracted, high-pressure gas or refrigerant passing through the high-pressure air outlet is easy to generate airflow pulsation noise, the noise not only increases the total noise value of the whole compressor, but also generates harsh abnormal sound in certain frequency bands by the generated airflow pulsation, a silencing cover is arranged above the high-pressure air outlet of the static scroll to weaken the airflow pulsation noise, the harsh abnormal sound is avoided, and the purpose of reducing the running noise of the whole compressor is achieved. Meanwhile, the annular partition plate is arranged in the silencing cavity, so that the silencing cavity is divided into two cavities, the silencing frequency is increased, and the noise is reduced.
The resistance capacity-expanding pressure-reducing noise reduction means that the pressure of compressed gas or refrigerant discharged from a high-pressure discharge port on a static scroll is P, and the pressure and the flow rate of the gas are reduced under the capacity-expanding pressure-reducing action of a first cavity 92a and a second cavity between a partition plate and a cover body, so that the blocking injection noise generated by the gas impacting the inner wall of the cover body can be correspondingly reduced, the purpose of resistance noise reduction is achieved, and the medium-frequency and high-frequency airflow pulsation noise generated by the high-pressure discharge port of the static scroll 91 of the compressor is weakened.
The reactive interference silencing is that a short flow and a long flow exist in the path between the air inlet and the second air outlet, and when sound waves on the short flow and the long flow meet, interference occurs, so that the reactive interference silencing effect is achieved, and after noises with different frequencies during the operation of the compressor are subjected to interference type silencing and noise reduction of the long flow and the short flow for a plurality of times, low-frequency airflow pulsation noise generated by the air inlet is further weakened.
Resistive silencing: the resistive silencing is to utilize the acoustic resistance to carry out silencing, namely only the contribution of the acoustic resistance to silencing is considered, and the influence of the acoustic resistance is ignored, and the acoustic energy is changed into heat energy by overcoming the friction resistance and the viscous force when flowing through the surface of the silencing device, so that the aim of reducing the pneumatic noise is fulfilled.
Resistance silencing: the reactive silencing is produced by changing impedance in the sound transmission process through the abrupt change position of the pipeline section or a bypass resonant cavity and the like to generate reflection and interference of sound energy, so that the sound energy radiated outwards by the silencer is reduced, and the aim of silencing is achieved.
Capacity expansion, pressure reduction and noise reduction: the expansion decompression noise reduction is a subclass of resistive noise reduction, and the expansion decompression noise reduction is to make the sectional area in the gas discharge direction suddenly expand, so that the pressure and the flow speed of gas are reduced, and the blocking injection noise of the inner wall of the gas impact silencing device is correspondingly reduced.
In some embodiments, a second partition plate is further arranged in the silencing cavity and is arranged in the second chamber to divide the second chamber into two third chambers; and the second partition plate is provided with air holes communicated with the two third chambers, and the opening is communicated with the exhaust port through the two third chambers. Preferably, the second partition plate is provided with a plurality of partitions for partitioning the third chambers in such a manner that the openings communicate with the exhaust port through the plurality of partitioned chambers.
Set up the cavity that the second baffle made the amortization and increase, the second baffle can be for only covering the opening on the baffle, also can be established to wrap up whole baffle, foretell hindering nature dilatation decompression amortization and resistance interfere the amortization number of times and increase, and noise cancelling effect can be better.
In some embodiments, the opening and the air vent are positioned such that exhaust flows from the opening to the exhaust port via a bend. Preferably, the second partition plate is annular and is sleeved on the periphery of the partition plate at intervals, the short flow between the opening and the air hole is 1/3-1/5 of the long flow, preferably, the second partition plates are multiple and are sequentially sleeved, and the short flow between the air holes on two adjacent second partition plates is 1/3-1/5 of the long flow. More preferably, the short run is 1/4 of the long run.
In the resistant interference silencing process, the short flow is 1/3-1/5, even 1/4 of the long flow, so that the phase difference between the sound wave frequency of the short flow and the sound wave frequency of the long flow is close to 180 degrees, and the interference effect is better when the two sound waves meet.
In some embodiments, the area of two adjacent chambers, outboard is larger than inboard. Preferably, the muffling frequency of each chamber is set to F, satisfying F = cx/4L, where x is an odd number and c is the speed of sound in air; l is half the distance sum of the short flow path and the long flow path in each chamber.
The areas of two adjacent chambers are set to be different, so that the silencing frequency is increased, and the silencing effect is improved.
Example 1
As shown in fig. 1 and 2, the scroll compressor includes a lower cover assembly 10, a housing assembly 20, an upper cover assembly 30, a lower support assembly 40, a motor assembly 50, a shaft assembly 60, an appliance box assembly 70, a movable plate assembly 80 and a stationary plate assembly 90.
The static disc assembly 90 is fixed on an upper bracket of the shafting assembly 60 and welded on a compressor shell, and a pump body assembly for compressing gas in the scroll compressor mainly plays a role of a movable disc and a static scroll disc 91 which are two double function equation scrolls which are meshed with each other, the movable disc is under the restriction action of a cross slip ring in a chute which is respectively assembled on the upper bracket and the movable disc, meanwhile, the motor assembly 50 drives a crankshaft of the shafting assembly 60 to drive the movable disc of the movable disc assembly 80 to rotate around the center of a base circle with smaller radius of the static scroll disc 91 of the static disc assembly 90 in a plane mode, gas or refrigerant is sucked into a plurality of crescent compression cavities formed by meshing of the movable disc and the static disc from an air suction port on the periphery of the static scroll disc 91 to be compressed step by step, and finally, the compressed gas or refrigerant is continuously discharged from an axial exhaust hole on the center of the static scroll disc 91.
As shown in fig. 2, since the exhaust port of the fixed scroll 91 is small and the sectional area is reduced, the high-pressure gas or refrigerant passing through the exhaust port is likely to generate airflow pulsation noise, which not only increases the total noise value of the compressor, but also generates harsh abnormal noise in some frequency bands, and a silencing cover is disposed above the exhaust port of the fixed scroll 91 to weaken the airflow pulsation noise, thereby avoiding the harsh abnormal noise and further achieving the purpose of reducing the operation noise of the compressor.
Wherein the muffler outer wall 92 of the cover 92 Wall(s) A back discharge port of the fixed scroll 91 is surrounded to form a chamber. As shown in fig. 3, N partition plates are sequentially provided outward at a center portion of an exhaust port of the fixed scroll 91 in a cavity of the cover body 92, and the partition plates include a first partition plate 92A, a second partition plate 92B, a third partition plate 92C, a fourth partition plate 92D, a \8230andan nth partition plate.
As shown in fig. 4, a plurality of nth exhaust chambers are enclosed between two adjacent nth partition plates, the first partition plate 92A encloses a first exhaust chamber 92A, the first partition plate 92A and the second partition plate 92B enclose a second exhaust chamber 92B, the second partition plate 92B and the third partition plate 92C enclose a third exhaust chamber 92C, the third partition plate 92C and the fourth partition plate 92D enclose a fourth exhaust chamber 92D, and the fourth partition plate 92D and the silencer outer wall 92D Wall(s) Enclose into an exhaust cavity 92 Chamber I.e. the Nth partition plate and the muffler outer wall 92 Wall(s) Between them form an exhaust cavity 92 Chamber 。
As shown in FIG. 3, the N-th exhaust chamber is connected to the exhaust chamber 92 so that the N-th exhaust chambers are communicated with each other Chamber And the N-th exhaust ports comprise a first exhaust port 92-1, a second exhaust port 92-2, a third exhaust port 92-3, a fourth exhaust port 92-4 and 8230, and the N-th exhaust ports are formed in the N-th partition plate and respectively correspond to the N-th partition plate, namely the first exhaust port 92-1 is formed in the first partition plate 92A, the second exhaust port 92-2 is formed in the second partition plate 92B, the third exhaust port 92-3 is formed in the third partition plate 92C, and the fourth exhaust port 92-4 is formed in the fourth partition plate 92D.
Furthermore, in order to discharge the high pressure gas or refrigerant out of the cover 92, the nth partition plate and the muffler outer wall 92 Wall(s) Formed exhaust chamber 92 Chamber The muffler outer wall 92 of the tail end Wall(s) Is provided with an exhaust port 92 Mouth with a filter 。
As shown in FIG. 4, when the sound wave of the noise enters the (N + 1) th exhaust chamber from the nth exhaust port of the nth exhaust chamber, the inner diameter D of the nth exhaust chamber is secured so that the nth exhaust port becomes a single sound source N-1 Width d of (N-1) th exhaust port N Is not less than 3, wherein the value of N is: n is not less than 2, i.e. the inner diameter D of the second exhaust chamber 92b 1 Width d of the first exhaust port 92-1 1 Is not less than 3, and the inner diameter D of the third exhaust chamber 92c 2 And the width d of the second exhaust port 92-2 2 Is not less than 3, and the inner diameter D of the fourth exhaust chamber 92D 3 And the width d of the third exhaust port 92-3 3 Is not less than 3, the exhaust chamber 92 Chamber Inner diameter D of 4 And the width d of the fourth exhaust port 92-4 4 Is not less than 3.
Further, to prevent access to the exhaust chamber 92 Chamber The interior is exhausted to the outside of the cover body 92 at an early stage, and the exhaust cavity 92 is also formed Chamber A straight pipe-like cavity-expanding silencing structure is formed, so that the medium and high frequency air flow pulsation noise generated during the operation of the compressor is greatly weakened, and the exhaust cavity 92 needs to be formed Chamber Inner diameter D of Chamber And the exhaust port 92 Mouth piece Width d of Mouth piece The ratio of (A) to (B) is controlled within the range of 5/2 to 5/3.
As shown in fig. 5, when the nth exhaust port is used as a sound source, and the sound wave of the sound source is transmitted to the next (N + 1) th exhaust port through two flow passages of the short flow passage and the long flow passage, in order to make the distance of interference when the sound waves of the short flow passage and the long flow passage meet each other be 1/4 wavelength which is an odd multiple of the sound wave of a certain frequency, the distance L from the nth exhaust port to the short flow passage of the nth exhaust port needs to be made Short N The distance L from the (N + 1) th exhaust port to the long flow passage of the Nth exhaust port Long (N + 1) 1/4 times the distance L from the first exhaust port 92-1 to the short flow path of the second exhaust port 92-2 in the second exhaust chamber 92b 1 Distance L of long flow path from the first exhaust port 92-1 to the second exhaust port 92-2 2 1/4 times of the distance L from the short flow path from the second exhaust port 92-2 to the third exhaust port 92-3 in the third exhaust chamber 92c 3 A distance L of a long flow path from the second exhaust port 92-2 to the third exhaust port 92-3 4 1/4 times of the distance L from the short flow path from the third exhaust port 92-3 to the fourth exhaust port 92-4 in the fourth exhaust chamber 92d 5 The distance L between the third exhaust port 92-3 and the fourth exhaust port 92-4 is a long flow path 6 1/4 times of the sound wave frequency of the short flow passage and the sound wave frequency of the long flow passageThe difference is 180 degrees, and at the moment, the short flow passage and the long flow passage interfere when the sound waves meet, so that the aim of resistance interference and noise reduction is fulfilled. And the distance L of the short flow passage in the Nth exhaust cavity Short N Is less than the distance L of the short flow passage in the (N + 1) th exhaust cavity Short (N + 1) I.e. L 1 ＜L 3 ＜L 5 ＜…＜L N Distance L of long flow passage in Nth exhaust chamber Long N Is less than the distance L of the long flow passage in the (N + 1) th exhaust cavity Long (N + 1) I.e. L 2 ＜L 4 ＜L 6 ＜…＜L N+1 。
Further, the noise frequency F of the short flow passage and the long flow passage in each exhaust cavity for noise interference type noise reduction meets the interference noise reduction formula: f = cx/4L (wherein x is 1, 3, 5, 7, \ 8230;), where F is the frequency of the noise sound wave; c is the speed of sound in air; l is half of the sum of the distances of the short flow passage and the long flow passage in the exhaust cavity, namely L =1/2 (L) Short N +L Long (N + 1) )。
As shown in fig. 6, in order to expand and reduce the sound pressure P in the cover 92 step by step to reduce the sound energy step by step, the area S of the nth exhaust chamber is required to be increased N Is smaller than the area S of the (N + 1) th exhaust cavity N+1 And the Nth partition plate and the muffler outer wall 92 Wall(s) Enclose into an exhaust cavity 92 Chamber Area S of Chamber Maximum, i.e. area S of first exhaust chamber 92a 1 Is smaller than the area S of the second exhaust chamber 92b 2 Area S of the second exhaust chamber 92c 2 Is smaller than the area S of the third exhaust chamber 92c 3 Area S of the third exhaust chamber 92c 3 Is smaller than the area S of the fourth exhaust chamber 92d 4 Area S of the fourth exhaust chamber 92d 4 Is smaller than the exhaust chamber 92 Chamber Area S of Chamber 。
The cover 92 having the composite structure of the resistive expanded cavity noise reduction and the resistive interference noise reduction can be used for a scroll compressor, a rotor compressor, a vane compressor, a piston compressor, a swash plate compressor, a positive displacement compressor or a centrifugal compressor.
As shown in fig. 4, the compressed gas or refrigerant enters the cover 92 from the discharge port of the fixed scroll 91Sequentially flows through a first exhaust cavity 92a, a second exhaust cavity 92b, a third exhaust cavity 92c, a fourth exhaust cavity 92d and an exhaust cavity 92 Chamber And finally from the exhaust port 92 Mouth piece And (4) discharging.
In some embodiments, the air hole on the second partition plate located at the outermost side and the second exhaust port are located on the same side of the cover body, an inserted partition plate is arranged in the silencing cavity, the inserted partition plate is arc-shaped, and the inserted partition plate is arranged between the air hole and the second exhaust port, so that the distance between the air hole and the second exhaust port can be prolonged.
For the structure that a plurality of second baffles cover was established, the condition that the gas pocket was very close to the second gas vent on the second baffle of periphery exists, adds an interpolation baffle this moment, prolongs both routes, improves the noise cancelling effect.
In some embodiments, one end of the inserted partition is connected to the inner wall of the cover; an inner inserting cavity pipe is formed between the inner inserting partition plate and the second partition plate on the outermost side, and the flow path of the inner inserting cavity pipe is more than or equal to half of the longest flow path of a cavity between the cover body and the second partition plate on the outermost side.
Preferably, the chamber sound deadening frequency between the outermost second partition and the cover is set to f, satisfying f = cx/mL', where x is an odd number and c is the speed of sound in air; m is the flow of the interpolation lumen; l' is the longest flow path of a cavity surrounded by the second partition plate at the outermost side and the cover body.
Example 2
As shown in fig. 7, the difference from embodiment 1 is that:
at the Nth partition plate and the silencer outer wall 92 Outer cover An interpolation partition plate 92 is additionally arranged between Plug-in And between the Nth partition plate and the silencer outer wall 92 Wall(s) Formed exhaust cavity 92 Chamber The outer wall of the silencer at the front end is provided with a discharge port 92 Go out 。
The insert partition plate 92 Plug-in And an end of the muffler outer wall 92 Outer cover Chained, interpolated divider plates 92 Plug-in The other end of (2) is arranged at the Nth partition plate and the outer wall 92 of the silencer Wall(s) Enclosed exhaust chamber 92 Chamber Inner, i.e. the interposed divider plate 92 Plug-in Is disposed between the fourth dividing plate 92D and the muffler outer wall 92 Wall(s) Enclosed exhaust chamber 92 Chamber And (4) the following steps.
The insert partition plate 92 Plug-in An inner insertion cavity tube 92 is enclosed with part of the Nth separation plate Pipe And inserting a lumen 92 therein Pipe The length m of the flow passage is not less than 1/2 times of the length L of the flow passage of an exhaust cavity formed by the Nth partition plate and the outer wall of the silencer Chamber So arranged that the Nth partition plate and the muffler outer wall 92 are engaged Outer cover Exhaust chamber 92 therebetween Chamber A similar inner-tube-like resistive interference type muffling structure, also called a helmholtz resonance muffling structure, is formed. Within the Helmholtz cavity, as the noise waves pass from the interior lumen 92 Pipe At the outlet of the trailing end, into a Helmholtz cavity (i.e., exhaust cavity 92) Chamber ) It may travel an infinite number of paths to reflect off the inner walls of the lumen and back to the inner lumen tube 92 Pipe During the exit of the tail end, the half-way length of all the reflection paths is equal to 1/2 times of the outlet of the inserted cavity tube to the exhaust cavity 92 Chamber The distances between the various locations within the chamber, so that all of the noise sound waves of the same frequency do not travel different lengths of the reflection paths back to the interior chamber 92 at the source Pipe When the phase of the reflected noise sound wave is different from the phase of the continuously entering noise sound wave with the same frequency by 180 degrees, interference and silencing are generated, and resonance is generated on part of the reflected noise sound wave and forced vibration is generated on part of the reflected noise sound wave, so that the silencing and noise reduction effects of the Helmholtz resonant cavity can be optimal.
Further, the noise sound wave frequency f for performing interference noise reduction and noise reduction on noise in the nth exhaust cavity formed between the nth partition plate with the inserted partition plate 92' and the outer wall of the silencer meets the interference noise reduction formula: f = cx/mL' (where x is 1, 3, 5, 7, \ 8230;), where f is the frequency of the noise sound wave; c is the speed of sound in air; m is the length of the flow channel of the inserted cavity tube; l is a radical of an alcohol Chamber Is divided by the NthThe length of the flow passage of the exhaust cavity enclosed by the plate and the outer wall of the silencer.
As shown in fig. 9, the compressed gas or refrigerant enters the cover 92 from the discharge port of the fixed scroll 91, and then flows through the first discharge chamber 92a, the second discharge chamber 92b, the third discharge chamber 92c, the fourth discharge chamber 92d, and the inner insertion chamber 92 in this order Pipe And an exhaust chamber 92 Chamber And finally from the exhaust port 92 Mouth piece And (4) discharging.
Helmholtz dry relates to resonance damping: while the noise sound wave is inserted from the lumen 92 Pipe At the outlet of the trailing end, into a Helmholtz cavity (i.e., exhaust cavity 92) Chamber ) It may travel an infinite number of paths to reflect off the inner walls of the lumen and back to the inner lumen tube 92 Pipe During the exit from the tail end, the half-way length of all the reflection paths is equal to 1/2 times the length of the exit of the inserted cavity tube to the exhaust cavity 92 Chamber The distances between the various locations within the chamber, so that all of the noise sound waves of the same frequency do not travel different lengths of the reflection paths back to the interior chamber 92 at the source Pipe When the phase of the reflected noise wave is different from the phase of the continuously entering noise wave with the same frequency by 180 degrees, the reflected noise wave interferes and silences, and the reflected noise wave resonates and the noise wave is forced to vibrate, so that the advantages of silencing and noise reduction of a Helmholtz resonant cavity can be further exerted, and the air flow pulsation noise generated at the exhaust outlet of the static scroll disc 91 of the compressor is further weakened again.
According to another aspect of the present application, there is provided a scroll compressor including a sound attenuation assembly as described above.
After the compressor with the displacement of 80cc is installed and verified, the noise comparison test result of the compressor provided with the cover body 92 and the conventional compressor is shown in fig. 10 and 11, the total noise value of the compressor provided with the cover body 92 in each operating frequency band is lower than that of the conventional compressor, and the noise reduction amplitude is larger and larger with the increase of the operating frequency; meanwhile, the noise spectrum waveform curve of the compressor with the cover 92 within 1000Hz is basically below the noise spectrum waveform curve of the conventional compressor, i.e. the noise of the compressor with the cover 92 is much lower than that of the conventional compressor.
It is easily understood by those skilled in the art that the above embodiments can be freely combined and superimposed without conflict.
The above description is only exemplary of the present application and should not be taken as limiting the present application, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present application should be included in the protection scope of the present application. The foregoing is only a preferred embodiment of the present application, and it should be noted that, for those skilled in the art, many modifications and variations can be made without departing from the technical principle of the present application, and these modifications and variations should also be regarded as the protection scope of the present application.
Claims (12)
1. A sound attenuating assembly, comprising:
a cover body (92) covering the air inlet to form an exhaust silencing cavity; an exhaust port (92) is arranged on the side wall of the cover body (92) Mouth piece )；
The silencing cavity is at least internally provided with an annular partition board covering the air inlet, and the partition board divides the silencing cavity into a first cavity and a second cavity which are mutually isolated; the first chamber is located inside the partition and is connected to the exhaust port (92) Mouth with a filter ) The second chamber is positioned outside the partition plate;
the partition plate is provided with an opening for communicating the first chamber and the second chamber.
2. The muffler assembly of claim 1, wherein a second baffle is further disposed within the muffler chamber and disposed within the second chamber to separate the second chamber into two third chambers; the second partition plate is provided with air holes communicated with the two third chambers, and the openings are communicated with the exhaust port (92) through the two third chambers Mouth piece )。
3. The muffler assembly of claim 2 wherein the second partition is provided in plurality to divide the third chamber in such a manner that the opening communicates with the exhaust port (92) through the plurality of divided chambers Mouth piece )。
4. The muffler assembly of any of claims 1-3 wherein the opening and the air vent are positioned such that exhaust flows from the opening to the exhaust outlet (92) via a bend Mouth with a filter )。
5. The muffler assembly as defined in claim 4, wherein the second partition is formed in a ring shape and is disposed around the outer circumference of the partition at intervals, and the short flow path between the opening and the air hole is 1/3 to 1/5 of the long flow path.
6. The silencing assembly of claim 5, wherein the second partition plates are sequentially sleeved, and the short flow path between the air holes of two adjacent second partition plates is 1/3 to 1/5 of the long flow path.
7. The acoustic silencer assembly of claim 6, wherein the areas of adjacent chambers are larger on the outside than on the inside.
8. The acoustic dampening assembly of claim 5, 6 or 7, wherein the acoustic dampening frequency of each chamber is set to F, satisfying F = cx/4L, where x is an odd number and c is the speed of sound in air; l is half the distance sum of the short and long runs in each chamber.
9. The silencer assembly of claim 6 or 7, wherein the outermost second partition vents to the exhaust port (92) Mouth piece ) Is positioned at the same side of the cover body (92), an inserted clapboard is arranged in the silencing cavity, and the inserted clapboard is arranged in the inserted clapboardThe baffle plate is arc-shaped and is arranged at the air hole and the exhaust port (92) Mouth with a filter ) The distance between the two can be extended.
10. The muffler assembly of claim 9 wherein one end of the internal insert partition is attached to an inner wall of the cap (92); an inner inserting cavity pipe is formed between the inner inserting partition plate and the outermost second partition plate, and the flow path of the inner inserting cavity pipe is more than or equal to half of the longest flow path of a cavity between the cover body (92) and the outermost second partition plate.
11. The muffler assembly of claim 10 wherein the chamber muffler frequency between the outermost second partition and the cover (92) is set to f, satisfying f = cx/mL', where x is an odd number and c is the speed of sound in air; m is the flow of the interpolation lumen; l' is the longest flow path of a cavity surrounded by the second partition plate at the outermost side and the cover body (92).
12. A scroll compressor including a sound reduction assembly as claimed in any one of claims 1 to 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211591588.3A CN115750372A (en) | 2022-12-12 | 2022-12-12 | Silencing assembly and scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211591588.3A CN115750372A (en) | 2022-12-12 | 2022-12-12 | Silencing assembly and scroll compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115750372A true CN115750372A (en) | 2023-03-07 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202211591588.3A Pending CN115750372A (en) | 2022-12-12 | 2022-12-12 | Silencing assembly and scroll compressor |
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| Country | Link |
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| CN (1) | CN115750372A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117703717A (en) * | 2024-02-05 | 2024-03-15 | 亚新科智能汽车技术(仪征)有限公司 | Air compressor with air inlet silencing function |
| CN117703717B (en) * | 2024-02-05 | 2024-05-03 | 亚新科智能汽车技术(仪征)有限公司 | Air compressor with air inlet silencing function |
-
2022
- 2022-12-12 CN CN202211591588.3A patent/CN115750372A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117703717A (en) * | 2024-02-05 | 2024-03-15 | 亚新科智能汽车技术(仪征)有限公司 | Air compressor with air inlet silencing function |
| CN117703717B (en) * | 2024-02-05 | 2024-05-03 | 亚新科智能汽车技术(仪征)有限公司 | Air compressor with air inlet silencing function |
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