Silencing assembly and scroll compressor

Abstract

The application provides a silencing assembly and a scroll compressor. The silencing assembly comprises a cover, a cover fastening air inlet, and a silencing cavity constituting exhaust air; a side wall of the cover is provided with an exhaust port; at least an annular partition plate is arranged in the silencing cavity to cover the air inlet, the partition plate separates the silencing cavity into a first chamber and a second chamber which are isolated from each other; the first chamber is located at the inner side of the partition plate and is communicated with the exhaust port, and the second chamber is located at the outer side of the partition plate; the partition plate is provided with an opening which is communicated with the first chamber and the second chamber. The partition plate is arranged in the silencing cavity formed between the cover and the air inlet, a composite noise reduction structure combining resistive expansion chamber silencing and resistive interference silencing is formed, the airflow pulsation noise generated by the exhaust port of the static scroll when the compressor operates at various frequency bands can be weakened, and then the operating noise of the compressor is reduced, and the comfort is improved.

Description

Technical Field

[0001] This application belongs to the field of scroll compressor technology, specifically relating to a noise reduction component and a scroll compressor. Background Technology

[0002] Scroll compressors have many advantages, including small size, light weight, continuous and stable intake and exhaust, low vibration, low noise, and low energy consumption, and are widely used in air conditioning, power engineering, transportation, and other fields. A scroll compressor mainly consists of two meshing scrolls: a moving scroll and a stationary scroll. During compression, the stationary scroll is fixed to the frame, while the moving scroll, driven by the crankshaft and constrained by an anti-rotation mechanism, rotates around the base circle center of the stationary scroll with a very small radius. Gas or refrigerant is drawn in from the periphery of the stationary scroll and, with the rotation of the eccentric shaft, is compressed stage by stage within several crescent-shaped compression chambers formed by the meshing of the moving and stationary scrolls. The compressed gas or refrigerant is then continuously discharged from the axial exhaust port at the center of the stationary scroll.

[0003] Because the exhaust port of the stationary scroll compressor is relatively small, it generates significant aerodynamic noise when compressed gas or refrigerant passes through it. This noise is particularly pronounced when the compressor is operating at high frequencies; the greater the airflow pulsation at the exhaust port, the louder the aerodynamic noise. As compressors continue to evolve towards higher frequencies and speeds, and customers demand greater comfort, compressor noise is a pressing issue that needs to be addressed.

[0004] The conventional solution for reducing aerodynamic noise at the exhaust port of a stationary scroll compressor is to install an expansion-type silencer with a sudden change in cross-sectional area above the exhaust port. This alters the acoustic impedance and reflects the noise back towards the sound source. During this reflection, the noise interferes with noise of equal amplitude but opposite phase, reducing its acoustic energy and thus achieving noise reduction. However, this silencer structure only weakens and reduces noise in a specific frequency band of the compressor and cannot fully meet the needs for reducing noise across multiple frequency bands or the entire frequency range. Furthermore, the user experience is relatively poor. Summary of the Invention

[0005] Therefore, this application provides a noise reduction component and a scroll compressor, which can solve the problem that the traditional noise reduction cover structure in the prior art can only reduce the noise of a certain frequency band of the compressor.

[0006] To address the aforementioned problems, this application provides a noise reduction component, comprising:

[0007] The cover covers the air inlet, forming a silencing chamber for exhaust; the side wall of the cover is provided with an exhaust port;

[0008] The silencing cavity is provided with at least one annular partition covering the air inlet, and the partition divides the silencing cavity into a first chamber and a second chamber that are isolated from each other; the first chamber is located inside the partition and communicates with the exhaust port, and the second chamber is located outside the partition;

[0009] The partition has an opening that connects the first chamber and the second chamber.

[0010] Optionally, the silencing cavity is further provided with a second partition, which is disposed in the second chamber to divide the second chamber into two third chambers; the second partition is provided with air holes that connect the two third chambers, and the openings are connected to the exhaust port through the two third chambers.

[0011] Optionally, the second partition is provided in multiple parts to divide the separated third chamber, thereby enabling the opening to connect to the exhaust port through multiple separated chambers.

[0012] Optionally, the opening and the vent are positioned such that exhaust flows through the opening in a curved manner to the exhaust port.

[0013] Optionally, the second partition is annular and spaced around the outer periphery of the partition, and the short flow path between the opening and the vent is 1 / 3 to 1 / 5 of the long flow path.

[0014] Optionally, there are multiple second partitions, which are sequentially nested together, and the short flow between the air holes on two adjacent second partitions is 1 / 3 to 1 / 5 of the long flow.

[0015] Optionally, the area of ​​the outer chamber of two adjacent chambers is larger than that of the inner chamber.

[0016] Optionally, the noise reduction frequency of each chamber is set to F, satisfying F = cx / 4L, where x is an odd number, c is the speed of sound in air, and L is half the sum of the short and long paths in each chamber.

[0017] Optionally, the air hole on the outermost second partition plate and the exhaust port are located on the same side of the cover. An inner partition plate is provided inside the silencing cavity. The inner partition plate is arc-shaped and located between the air hole and the exhaust port, which can extend the distance between the two.

[0018] Optionally, one end of the inner insert partition is connected to the inner wall of the cover; the inner insert partition and the outermost second partition form an inner insert cavity tube, and the flow of the inner insert cavity tube is greater than or equal to half the longest flow of the cavity between the cover and the outermost second partition.

[0019] Optionally, the noise reduction frequency of the cavity between the outermost second partition and the cover is set as f, satisfying f = cx / mL', where x is an odd number, c is the speed of sound in air; m is the flow rate of the inner cavity tube; and L' is the longest flow rate of the cavity enclosed by the outermost second partition and the cover.

[0020] According to another aspect of this application, a scroll compressor is provided, including the silencing assembly described above.

[0021] This application provides a noise reduction assembly, comprising: a cover that covers an air inlet, forming a noise reduction chamber for exhaust; an exhaust port is provided on the side wall of the cover; at least one annular partition covering the air inlet is provided inside the noise reduction chamber, the partition dividing the noise reduction chamber into a first chamber and a second chamber that are isolated from each other; the first chamber is located inside the partition and communicates with the exhaust port, and the second chamber is located outside the partition; the partition is provided with an opening communicating with the first chamber and the second chamber.

[0022] This application sets up a baffle in the silencing cavity formed between the cover and the air inlet, forming a composite noise reduction structure that combines resistive cavity expansion silencing and reactive interference silencing. This can reduce the airflow pulsation noise generated by the static scroll exhaust port when the compressor is running in various frequency bands, thereby reducing the overall operating noise of the compressor and improving comfort. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the structure of a scroll compressor according to an embodiment of this application;

[0024] Figure 2 This is a schematic diagram of the pump body assembly according to an embodiment of this application;

[0025] Figure 3 This is a three-dimensional schematic diagram of the cover body according to an embodiment of this application;

[0026] Figure 4 Top view of the cover in an embodiment of this application Figure 1 ;

[0027] Figure 5 Top view of the cover in an embodiment of this application Figure 2 ;

[0028] Figure 6 Top view of the cover in an embodiment of this application Figure 3 ;

[0029] Figure 7 Top view of the cover in an embodiment of this application Figure 4 ;

[0030] Figure 8 Air path for noise reduction of the cover in this application embodiment Figure 1;

[0031] Figure 9 Air path for noise reduction of the cover in this application embodiment Figure 2 ;

[0032] Figure 10 This is a comparison chart of the total noise levels of an 80cc scroll compressor according to an embodiment of this application and a conventional structure.

[0033] Figure 11 The noise spectrum diagram of the 80cc displacement scroll compressor of this application and the conventional structure within 1000Hz is shown.

[0034] The reference numerals in the attached figures are as follows:

[0035] 10. Lower cover assembly; 20. Housing assembly; 30. Upper cover assembly; 40. Lower bracket assembly; 50. Motor assembly; 60. Shaft assembly; 70. Electrical box assembly; 80. Moving disc assembly; 90. Stationary scroll assembly; 91. Stationary scroll; 92. Cover; 93. Intake valve assembly; 93-1. Intake valve cover; 93-2. Spring;

[0036] 92A, First partition; 92B, Second partition; 92C, Third partition; 92D, Fourth partition; 92 外 92-1. Muffler outer wall; 92-2. First exhaust port; 92-3. Second exhaust port; 92-4. Third exhaust port; 92-5. Fourth exhaust port; 92 口 92a, Exhaust port; 92b, First exhaust chamber; 92c, Third exhaust chamber; 92d, Fourth exhaust chamber; 92 腔 1. Exhaust chamber; D2. Inner diameter of the second exhaust chamber; D3. Inner diameter of the third exhaust chamber; D4. Inner diameter of the fourth exhaust chamber; D 腔 d1, the inner diameter of the exhaust chamber formed by the Nth partition plate and the outer wall of the muffler; d2, the width of the first exhaust port; d3, the width of the third exhaust port; d4, the width of the fourth exhaust port; d 腔 Width of the exhaust port;

[0037] L1, the distance between the first exhaust port and the second exhaust port in the second exhaust chamber (short flow path); L2, the distance between the first exhaust port and the second exhaust port in the second exhaust chamber (long flow path); L3, the distance between the second exhaust port and the third exhaust port in the third exhaust chamber (short flow path); L4, the distance between the second exhaust port and the third exhaust port in the third exhaust chamber (long flow path); L5, the distance between the third exhaust port and the fourth exhaust port in the fourth exhaust chamber (short flow path); L6, the distance between the third exhaust port and the fourth exhaust port in the fourth exhaust chamber (long flow path); L 腔 The length of the flow channel in the exhaust chamber formed by the Nth partition plate and the outer wall of the muffler;

[0038] S1, Area of ​​the first exhaust chamber; S2, Area of ​​the second exhaust chamber; S3, Area of ​​the third exhaust chamber; S4, Area of ​​the fourth exhaust chamber; 腔 The area of ​​the fifth exhaust chamber;

[0039] 90 插 Internal partition plate; 92 管 , Internal insertion tube; 92 出 1. Outlet; m, length of the internal cavity tube flow channel; P, gas pressure discharged from the static vortex disk. Detailed Implementation

[0040] To make the objectives, technical solutions, and advantages of this application clearer, the technical solutions of this application will be clearly and completely described below in conjunction with specific embodiments and corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0041] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0042] See also Figures 1 to 11 As shown, according to an embodiment of this application, a noise reduction component includes:

[0043] The cover 92 covers the air inlet, forming a silencing chamber for exhaust; an exhaust port is provided on the side wall of the cover;

[0044] The silencing cavity is provided with at least one annular partition covering the air inlet, and the partition divides the silencing cavity into a first chamber and a second chamber that are isolated from each other; the first chamber is located inside the partition and communicates with the exhaust port, and the second chamber is located outside the partition;

[0045] The partition has an opening that connects the first chamber and the second chamber.

[0046] This application sets up a baffle in the silencing cavity formed between the cover 92 and the air inlet, forming a composite noise reduction structure that combines resistive cavity expansion silencing and reactive interference silencing. This can reduce the airflow pulsation noise generated by the static scroll exhaust port when the compressor is running in various frequency bands, thereby reducing the overall operating noise of the compressor and improving comfort.

[0047] The silencing chamber of this application expands and reduces the pressure of the high-pressure airflow entering the silencing chamber through the inlet to reduce noise, and then exits the silencing chamber through the exhaust port.

[0048] In scroll compressors, the inlet is the high-pressure exhaust port on the stationary scroll. Because the diameter of this high-pressure exhaust port is small and its cross-sectional area is reduced, the high-pressure gas or refrigerant passing through it easily generates airflow pulsation noise. This noise not only increases the overall noise level of the compressor but also produces harsh, unpleasant noises at certain frequencies. A silencer cover is installed above the high-pressure exhaust port on the stationary scroll to reduce this airflow pulsation noise and prevent harsh noises, thereby reducing the overall operating noise of the compressor. Simultaneously, an annular baffle is installed within the silencer chamber, dividing it into two compartments, increasing the silencer frequency and further reducing noise.

[0049] Resistive expansion and pressure reduction silencing refers to the process where compressed gas or refrigerant with pressure P is discharged from the high-pressure exhaust port on the stationary scroll plate. After passing through the first chamber 92a and the second chamber between the partition and the cover, the pressure and velocity of the gas are reduced. This reduces the noise generated by the gas impacting the inner wall of the cover, thus achieving the purpose of resistive silencing and noise reduction. In this way, the medium and high frequency airflow pulsation noise generated at the high-pressure exhaust port of the compressor stationary scroll plate 91 is weakened.

[0050] Resistant interference silencing refers to the existence of short and long paths between the air inlet and the second exhaust port. When the sound waves on the short and long paths meet, interference occurs, thus achieving the effect of resistive interference silencing. After several interference-type silencing and noise reduction processes involving the long and short paths during compressor operation, the low-frequency airflow pulsation noise generated at the air inlet is further weakened.

[0051] Resistive silencing: Resistive silencing uses acoustic resistance to reduce noise, that is, it only considers the contribution of acoustic resistance to silencing, while ignoring the influence of acoustic impedance. This is because when sound energy flows through the surface of the silencing device, it has to overcome frictional resistance and adhesive force to become heat energy, thereby achieving the purpose of reducing aerodynamic noise.

[0052] Reactive silencing: Reactive silencing is the process of reducing the sound energy radiated outward by the silencer by reflecting and interfering with the sound energy caused by changes in impedance during sound propagation at abrupt changes in the cross-section of the pipeline or by a resonant cavity.

[0053] Expansion and pressure reduction noise reduction: Expansion and pressure reduction noise reduction is a subcategory of resistive silencing. It involves abruptly expanding the cross-sectional area in the gas discharge direction, thereby reducing the gas pressure and flow rate. This also reduces the noise from the gas impacting the inner wall of the silencing device and causing blockage.

[0054] In some embodiments, the silencing cavity is further provided with a second partition, which is disposed in the second chamber and divides the second chamber into two third chambers; the second partition is provided with air holes connecting the two third chambers, and the openings connect to the exhaust port through the two third chambers. Preferably, multiple second partitions are provided to separate the divided third chambers, so that the openings connect to the exhaust port through multiple separated chambers.

[0055] The addition of a second partition increases the number of silencing chambers. The second partition can either cover only the opening on the partition or enclose the entire partition. This increases the number of resistive expansion and voltage reduction silencing and reactive interference silencing processes, resulting in a better silencing effect.

[0056] In some embodiments, the opening and the vent are positioned such that exhaust gas flows through the opening in a curved path to the exhaust port. Preferably, the second partition is annular and spaced around the outer periphery of the partition, with the short flow path between the opening and the vent being 1 / 3 to 1 / 5 of the long flow path. Preferably, there are multiple second partitions, arranged sequentially, with the short flow path between vents on two adjacent second partitions being 1 / 3 to 1 / 5 of the long flow path. More preferably, the short flow path is 1 / 4 of the long flow path.

[0057] In the aforementioned resistance interference silencing process, the short path is 1 / 3 to 1 / 5, or even 1 / 4, of the long path, so that the phase difference between the sound wave frequency of the short path and the sound wave frequency of the long path is close to 180°. At this time, the interference effect is better when the two sound waves meet.

[0058] In some embodiments, the area of ​​the outer chamber is larger than that of the inner chamber. Preferably, the anechoic frequency of each chamber is set to F, satisfying F = cx / 4L, where x is an odd number, c is the speed of sound in air, and L is half the sum of the short and long paths in each chamber.

[0059] By setting different areas for two adjacent chambers, the noise reduction frequency is increased, thus improving the noise reduction effect.

[0060] Example 1

[0061] like Figure 1 and Figure 2As shown, the scroll compressor comprises 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 system assembly 60, an electrical box assembly 70, a moving disc assembly 80, and a stationary disc assembly 90.

[0062] Among them, the stationary disk assembly 90 is fixed on the upper bracket of the shaft system assembly 60, which is welded and fixed on the compressor housing. The pump body assembly that compresses the gas in the scroll compressor mainly consists of two meshing double-function equation scrolls, the moving disk and the stationary scroll 91. The moving disk is constrained by the cross slip rings in the grooves of the upper bracket and the moving disk respectively. At the same time, the motor assembly 50 drives the crankshaft of the shaft system assembly 60, which drives the moving disk of the moving disk assembly 80 to rotate in a plane around the small radius base circle center of the stationary scroll 91 of the stationary disk assembly 90. The gas or refrigerant is drawn into the several crescent-shaped compression chambers formed by the meshing of the moving disk and the stationary disk from the suction port on the periphery of the stationary scroll 91 and compressed step by step. The compressed gas or refrigerant is finally continuously discharged from the axial exhaust port in the center of the stationary scroll 91.

[0063] like Figure 2 As shown, due to the small exhaust port of the stationary scroll 91 and the shrinkage of its cross-sectional area, the high-pressure gas or refrigerant passing through the exhaust port is prone to generating airflow pulsation noise. This noise not only increases the overall noise level of the compressor, but also produces harsh noises in certain frequency bands due to the airflow pulsation. A sound-absorbing cover is provided above the exhaust port of the stationary scroll 91 to weaken the airflow pulsation noise, avoid the occurrence of harsh noises, and thus achieve the purpose of reducing the overall operating noise of the compressor.

[0064] Among them, the outer wall 92 of the silencer of the cover 92 壁 A chamber is formed by surrounding the exhaust port on the back of the stationary vortex disk 91. For example... Figure 3 As shown, N partition plates are arranged sequentially outward from the center of the exhaust port of the static vortex disk 91 in the cavity of the cover 92, and the partition plates include the first partition plate 92A, the second partition plate 92B, the third partition plate 92C, the fourth partition plate 92D, ..., the Nth partition plate.

[0065] like Figure 4 As shown, several Nth exhaust chambers are formed between two adjacent Nth partition plates. The first partition plate 92A forms the first exhaust chamber 92a, the first partition plate 92A and the second partition plate 92B form the second exhaust chamber 92b, the second partition plate 92B and the third partition plate 92C form the third exhaust chamber 92c, the third partition plate 92C and the fourth partition plate 92D form the fourth exhaust chamber 92d, and the fourth partition plate 92D and the outer wall 92 of the muffler form the fourth exhaust chamber 92d. 壁 Enclosed exhaust chamber 92 腔 That is, the Nth partition plate and the outer wall of the muffler 92 壁 The space between them forms an exhaust chamber 92 腔 .

[0066] like Figure 3 As shown, in order to connect each of the Nth exhaust chambers one by one, and also to connect the Nth exhaust chamber with exhaust chamber 92 腔 The connection is made such that an Nth exhaust port with an opening that does not correspond to each other is opened on each of the Nth partition plates. The exhaust ports opened on the Nth partition plates include the first exhaust port 92-1, the second exhaust port 92-2, the third exhaust port 92-3, the fourth exhaust port 92-4, ..., the Nth exhaust port, and the Nth exhaust port is opened on the corresponding Nth partition plate. That is, the first exhaust port 92-1 is opened on the first partition plate 92A, the second exhaust port 92-2 is opened on the second partition plate 92B, the third exhaust port 92-3 is opened on the third partition plate 92C, and the fourth exhaust port 92-4 is opened on the fourth partition plate 92D.

[0067] Furthermore, to allow high-pressure gas or refrigerant to escape from the cover 92, the Nth partition plate and the outer wall of the silencer 92 are connected. 壁 The formed exhaust chamber 92 腔 The outer wall of the muffler at the tail end 92 壁 The top has an exhaust port 92 口 .

[0068] like Figure 4 As shown, when the sound wave of noise enters the (N+1)th exhaust chamber from the Nth exhaust port of the Nth exhaust chamber, in order to make the Nth exhaust port a single sound source, the inner diameter D of the Nth exhaust chamber must be ensured. N-1 The width d of the (N-1)th exhaust port N The ratio is not less than 3, where N takes the value: N≥2, that is, the ratio of the inner diameter D1 of the second exhaust chamber 92b to the width d1 of the first exhaust port 92-1 is not less than 3, the ratio of the inner diameter D2 of the third exhaust chamber 92c to the width d2 of the second exhaust port 92-2 is not less than 3, and the ratio of the inner diameter D3 of the fourth exhaust chamber 92d to the width d3 of the third exhaust port 92-3 is not less than 3. 腔 The ratio of the inner diameter D4 to the width d4 of the fourth exhaust port 92-4 is not less than 3.

[0069] Furthermore, to prevent entry into the exhaust chamber 92 腔 Premature discharge of contents into the cover 92, and also to ensure that the exhaust chamber 92 is properly vented. 腔 To create a cavity-expanding silencing structure similar to a straight pipe, the mid- and high-frequency airflow pulsation noise generated during compressor operation is significantly reduced. This requires expanding the exhaust chamber 92... 腔 Inner diameter D 腔 With the exhaust port 92 口 Width d 口 The ratio should be controlled within 5 / 2 to 5 / 3.

[0070] like Figure 5 As shown, taking the Nth exhaust port as the sound source, the sound wave from this source propagates through two channels, a short channel and a long channel, to the next (N+1)th exhaust port. To ensure that the interference distance between the sound waves from the short channel and the long channel when they meet is an odd multiple of 1 / 4 wavelength of a certain frequency sound wave, the distance L between the Nth exhaust port and the short channel of the Nth exhaust port must be such that... 短N The distance L of the long flow path from the (N+1)th exhaust port to the Nth exhaust port. 长(N+1) The distance L1 between the short channels of the first exhaust port 92-1 and the second exhaust port 92-2 in the second exhaust chamber 92b is 1 / 4 of the distance L2 between the long channels of the first exhaust port 92-1 and the second exhaust port 92-2. The distance L3 between the short channels of the second exhaust port 92-2 and the third exhaust port 92-3 in the third exhaust chamber 92c is 1 / 4 of the distance L4 between the long channels of the second exhaust port 92-2 and the third exhaust port 92-3. The distance L5 between the short channels of the third exhaust port 92-3 and the fourth exhaust port 92-4 in the fourth exhaust chamber 92d is 1 / 4 of the distance L6 between the long channels of the third exhaust port 92-3 and the fourth exhaust port 92-4. In this way, the phase difference between the sound wave frequency of the short channel and the sound wave frequency of the long channel is 180°. When the sound waves of the short channel and the long channel meet, interference occurs, thereby achieving the purpose of anti-interference silencing. Furthermore, the distance L of the short flow channel within the Nth exhaust chamber 短N The distance L of the short flow channel within the (N+1)th exhaust chamber is less than 短(N+1) That is, L1 < L3 < L5 < ... < L N The distance L of the long flow channel in the Nth exhaust chamber 长N The distance L of the long flow channel within the (N+1)th exhaust chamber is less than 长(N+1) That is, L2 < L4 < L6 < ... < L N+1 .

[0071] Furthermore, the noise frequency F of the short and long channels within each exhaust chamber, which perform interference-based noise reduction, satisfies the interference silencing formula: F = cx / 4L (where x takes values ​​of 1, 3, 5, 7, ...), where F is the frequency of the noise wave; c is the speed of sound in air; and L is half the sum of the distances between the short and long channels within the exhaust chamber, i.e., L = 1 / 2 (L 短N +L 长(N+1) ).

[0072] like Figure 6 As shown, in order to gradually reduce the sound pressure P within the cover 92 through cavity expansion, thereby achieving the goal of gradually reducing sound energy, the area S of the Nth exhaust cavity needs to be increased. N The area S of the (N+1)th exhaust chamber is smaller than that of the other chamber. N+1 And the Nth partition plate is 92mm from the outer wall of the muffler. 壁 Enclosed exhaust chamber 92 腔area S 腔 The maximum area is defined as follows: the area S1 of the first exhaust chamber 92a is smaller than the area S2 of the second exhaust chamber 92b; the area S2 of the second exhaust chamber 92c is smaller than the area S3 of the third exhaust chamber 92c; the area S3 of the third exhaust chamber 92c is smaller than the area S4 of the fourth exhaust chamber 92d; and the area S4 of the fourth exhaust chamber 92d is smaller than the area of ​​the exhaust chamber 92b. 腔 area S 腔 .

[0073] The cover 92, which has both resistive cavity expansion silencing and reactive interference silencing, can be used in one of the following compressors: scroll compressor, rotary compressor, vane compressor, piston compressor, swashplate compressor, positive displacement compressor, or centrifugal compressor.

[0074] like Figure 4 As shown, the compressed gas or refrigerant enters the cover 92 from the exhaust port of the static vortex disk 91, and then flows sequentially through the first exhaust chamber 92a, the second exhaust chamber 92b, the third exhaust chamber 92c, the fourth exhaust chamber 92d, and the exhaust chamber 92. 腔 Finally, from the exhaust port 92 口 discharge.

[0075] In some embodiments, the air hole on the outermost second partition plate and the second exhaust port are located on the same side of the cover. An inner partition plate is provided inside the silencing cavity. The inner partition plate is arc-shaped and is located between the air hole and the second exhaust port, which can extend the distance between the two.

[0076] In structures with multiple second baffles, there may be situations where the air vent on the outermost second baffle is very close to the second exhaust port. In this case, an inner baffle is added to extend the distance between them and improve the noise reduction effect.

[0077] In some embodiments, one end of the inner insert partition is connected to the inner wall of the cover; the inner insert partition and the outermost second partition form an inner insert cavity tube, the flow of the inner insert cavity tube being greater than or equal to half the longest flow of the cavity between the cover and the outermost second partition.

[0078] Preferably, the noise reduction frequency of the cavity between the outermost second partition and the cover is set as f, satisfying f = cx / mL', where x is an odd number, c is the speed of sound in air; m is the flow rate of the inner cavity tube; and L' is the longest flow rate of the cavity enclosed by the outermost second partition and the cover.

[0079] Example 2

[0080] like Figure 7 As shown, the difference from Example 1 is that:

[0081] The Nth partition plate and the outer wall of the muffler 92 外 An internal partition plate 92 is added between them. 插 And at the Nth partition plate and the outer wall of the muffler 92 壁 The formed exhaust chamber 92 腔 The front muffler has an exhaust port 92 on its outer wall. 出 .

[0082] The internal partition plate 92 插 One end is connected to the outer wall 92 of the silencer 外 Link, insert separator 92 插 The other end is located at the Nth partition plate and the outer wall 92 of the silencer. 壁 Enclosed exhaust chamber 92 腔 Inside, that is, the inner partition plate 92 插 The other end is located at the fourth partition plate 92D and the outer wall 92 of the muffler. 壁 Enclosed exhaust chamber 92 腔 Inside.

[0083] The intercalation partition 92 插 The portion of the Nth partition plate forms an internal cavity tube 92. 管 The lumen region, and the inserted lumen tube 92 管 The flow channel length m is not less than 1 / 2 times the flow channel length L of the exhaust chamber enclosed by the Nth partition plate and the outer wall of the muffler. 腔 This arrangement allows the Nth partition plate to be flush with the outer wall of the muffler by 92 degrees. 外 The exhaust chamber 92 腔 An internal, anti-interference noise-absorbing structure, similar to an internally inserted tube, is formed, also known as a Helmholtz resonance noise-absorbing structure. Within this Helmholtz resonance cavity, when noise waves originate from the internally inserted tube 92... 管 The exhaust gas enters the Helmholtz resonant cavity (i.e., the exhaust cavity 92) at the tail end outlet. 腔 It can reflect off the inner wall of the cavity through countless paths and then return to the inner insertion tube 92. 管 During the process at the tail end exit, the half-length of all reflection paths is equal to 1 / 2 times the length from the outlet of the inner cavity tube to the exhaust chamber 92. 腔 The distances between various parts within the cavity ensure that noise waves of the same frequency do not travel through reflection paths of varying lengths before returning to the sound source. (Internal cavity tube 92) 管 At the exit point, the phase changes, so when some noise waves encounter noise waves of the same frequency, the reflected noise waves will be 180° out of phase with the incoming noise waves of the same frequency, resulting in interference and noise reduction. Some noise waves will resonate, and some noise waves will undergo forced vibration. This allows the noise reduction effect of the Helmholtz resonant cavity to reach its optimal level.

[0084] Furthermore, the noise frequency f in the Nth exhaust cavity formed between the Nth partition plate 92' and the outer wall of the muffler, which performs interference noise reduction, satisfies the interference noise reduction formula: f = cx / mL' (where x takes values ​​of 1, 3, 5, 7, ...), where f is the frequency of the noise wave; c is the speed of sound in air; m is the flow channel length of the inner cavity tube; L 腔 The length of the exhaust channel formed by the Nth partition plate and the outer wall of the muffler.

[0085] like Figure 9 As shown, the compressed gas or refrigerant enters the cover 92 from the exhaust port of the static vortex disk 91, and then flows sequentially through the first exhaust chamber 92a, the second exhaust chamber 92b, the third exhaust chamber 92c, the fourth exhaust chamber 92d, and the inner insert tube 92. 管 and exhaust chamber 92 腔 Finally, from the exhaust port 92 口 discharge.

[0086] Helmholtz interference and resonance silencing: when noise sound waves originate from the inner cavity tube 92 管 The exhaust gas enters the Helmholtz resonant cavity (i.e., the exhaust cavity 92) at the tail end outlet. 腔 It can reflect off the inner wall of the cavity through countless paths and then return to the inner insertion tube 92. 管 During the process at the tail end exit, the half-length of all reflection paths is equal to 1 / 2 times the length from the outlet of the inner cavity tube to the exhaust chamber 92. 腔 The distances between various parts within the cavity ensure that noise waves of the same frequency do not travel through reflection paths of varying lengths before returning to the sound source. (Internal cavity tube 92) 管 At the tail end outlet, due to the change in phase, some noise waves will encounter noise waves of the same frequency. When the reflected noise waves meet the noise waves of the same frequency that continue to enter, they will interfere and be silenced by a phase difference of 180°. Some noise waves will resonate, and some noise waves will undergo forced vibration. This will further leverage the noise reduction advantage of the Helmholtz resonant cavity, further weakening the airflow pulsation noise generated at the exhaust port of the compressor's stationary scroll 91.

[0087] According to another aspect of this application, a scroll compressor is provided, including the silencing assembly described above.

[0088] After installation and verification on an 80cc compressor, the noise comparison test results between the compressor equipped with this cover (92) and a conventional compressor are as follows: Figure 10 and Figure 11As shown, the total noise level of the compressor equipped with the cover 92 is lower than that of the conventional compressor in all operating frequency bands, and the noise reduction increases with the increase of operating frequency. At the same time, the noise spectrum waveform curve of the compressor equipped with the cover 92 in the range of 1000Hz is basically below that of the conventional compressor, that is, the noise of the compressor equipped with the cover 92 is much lower than that of the conventional compressor.

[0089] It will be readily understood by those skilled in the art that the above embodiments can be freely combined and superimposed without conflict.

[0090] The above description is merely a preferred embodiment of this application and is not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application. The above description is merely a preferred embodiment of this application. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of this application, and these improvements and modifications should also be considered within the protection scope of this application.

Claims

1. A noise reduction component, characterized in that, include: The cover (92) covers the air inlet and forms a silencing chamber for exhaust. The cover (92) has an exhaust port on its side wall; The silencing cavity is provided with at least one annular partition covering the air inlet, and the partition divides the silencing cavity into a first chamber and a second chamber that are isolated from each other; the first chamber is located inside the partition and communicates with the exhaust port, and the second chamber is located outside the partition; The partition is provided with an opening connecting the first chamber and the second chamber; The silencing cavity is further provided with a second partition, which is located in the second chamber and divides the second chamber into two third chambers; the second partition is provided with air holes that connect the two third chambers, and the openings are connected to the exhaust port through the two third chambers; The second partition is designed in a ring shape and is spaced out on the outer periphery of the partition. The short flow path between the opening and the air hole is 1 / 3 to 1 / 5 of the long flow path. The second partition is multiple and is installed in sequence. The air hole on the outermost second partition is located on the same side of the cover (92) as the exhaust port. The silencing cavity is provided with an inner partition. The inner partition is arc-shaped and is located between the air hole and the exhaust port, which can extend the distance between the two. One end of the inner insert partition is connected to the inner wall of the cover (92); the inner insert partition and the outermost second partition form an inner insert cavity tube, and the flow of the inner insert cavity tube is greater than or equal to half the longest flow of the cavity between the cover (92) and the outermost second partition.

2. The noise reduction assembly according to claim 1, characterized in that, The second partition has multiple partitions to separate the third chamber, and this separation method allows the opening to connect to the exhaust port through multiple separated chambers.

3. The noise reduction assembly according to claim 1 or 2, characterized in that, The opening and the vent are positioned such that exhaust flows through the opening in a curved manner to the exhaust port.

4. The noise reduction assembly according to claim 1, characterized in that, The short flow path between the pores on two adjacent second partitions is 1 / 3 to 1 / 5 of the long flow path.

5. The noise reduction assembly according to claim 4, characterized in that, The area of ​​the outer chamber is larger than that of the inner chamber.

6. The noise reduction assembly according to claim 1, 4, or 5, characterized in that, The noise reduction frequency of each chamber is set to F, which satisfies F=cx / 4L, where x is an odd number, c is the speed of sound in air, and L is half the sum of the short and long paths in each chamber.

7. The noise reduction assembly according to claim 4 or 5, characterized in that, The noise reduction frequency of the chamber between the outermost second partition and the cover (92) is set as f, which satisfies f=cx / mL', where x is an odd number, c is the speed of sound in air; m is the flow rate of the inner cavity tube; and L' is the longest flow rate of the chamber enclosed by the outermost second partition and the cover (92).

8. A scroll compressor, characterized in that, Includes the noise reduction assembly as described in any one of claims 1-7.

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