Silencer and compressor

Abstract

The invention relates to a silencer and a compressor, relates to the technical field of air conditioner compressor equipment, and aims to solve the problem of poor silencing and noise reduction effects of the silencer. The silencer comprises a mounting disc; the expansion cavity is arranged on the mounting disc, and at least one exhaust port is formed in the expansion cavity; the silencing assembly is arranged in the expansion cavity, one end of the silencing assembly communicates with at least one exhaust port, and the other end of the silencing assembly communicates with the expansion cavity; the to-be-muffled airflow enters the expansion cavity and the muffling assembly in sequence, the silencer is constructed in the mode that the expansion cavity of the silencer is used for eliminating broadband noise of the to-be-muffled airflow, and the muffling assembly is used for eliminating the single-tone peak noise of the to-be-muffled airflow at the preset frequency. The expansion cavity is used for eliminating broadband noise in airflow to be muffled, and the muffling assembly is used for eliminating single-tone peak noise of the preset frequency. In this way, elimination of broadband noise and elimination of single-tone peak noise of the preset frequency are achieved. And therefore, the silencing and noise reduction effects of the silencer are improved.

Description

Technical Field

[0001] This invention relates to the field of air conditioning compressor equipment technology, and particularly to a muffler and a compressor. Background Technology

[0002] During compressor operation, after the refrigerant gas is compressed by the pump body, it is discharged into the lower chamber of the motor through the pump body exhaust port. Because the high temperature and high pressure gas after being compressed by the pump body will generate strong exhaust airflow noise when passing through the pump body exhaust port, a silencer is usually installed to reduce noise.

[0003] Existing silencers only use an expansion cavity for noise reduction. However, while this expansion cavity has a wide noise reduction bandwidth, its noise reduction effect is not significant. That is, the expansion cavity can eliminate broadband noise generated by airflow, but cannot eliminate single-tone peak noise at specific frequencies. This results in the silencer failing to achieve the desired noise reduction effect in certain target frequency bands, thus affecting the overall noise reduction performance.

[0004] In other words, existing silencers have the problem of poor noise reduction effect. Summary of the Invention

[0005] This invention provides a muffler and a compressor to solve the problem of poor noise reduction effect in existing mufflers.

[0006] This invention provides a muffler, comprising:

[0007] Installation disk;

[0008] An expansion chamber is provided on the mounting plate, and the expansion chamber has at least one exhaust port.

[0009] A muffler assembly is disposed within an expansion chamber, with one end of the muffler assembly connected to at least one exhaust port and the other end of the muffler assembly connected to the expansion chamber.

[0010] The airflow to be silenced enters the expansion cavity and the silencing component in sequence. The expansion cavity is designed to eliminate broadband noise from the airflow to be silenced, and the silencing component is designed to eliminate single-tone peak noise at a preset frequency from the airflow to be silenced.

[0011] The noise reduction assembly includes a muffler, one end of which is connected to at least one exhaust port, and the other end of which is connected to the interior of an expansion cavity. The muffler is located inside the expansion cavity and has a resonant cavity inside the muffler. The resonant cavity is used to absorb the single-tone peak noise of a preset frequency of the airflow to be silenced.

[0012] The noise reduction assembly also includes a baffle, which is disposed inside the resonant cavity and is used to reduce the noise of the airflow inside the resonant cavity.

[0013] In one embodiment, the baffle includes a plurality of serrated baffles, which are arranged circumferentially around the muffler. The serrated baffles are used to divide the internal energy dissipation of the airflow in the resonant cavity.

[0014] In the above embodiment, the serrated edges of multiple serrated baffles divide the airflow into multiple smaller streams, dispersing noise energy and thus reducing noise. Multiple serrated baffles cut large-scale eddies into multiple small-scale eddies. According to turbulence energy level theory, smaller eddies are more likely to decay rapidly through viscous dissipation, thereby reducing the overall turbulence intensity. The serrated tips of the baffles can disrupt the continuous development of the boundary layer, delaying flow separation and reducing backflow in the separation zone, thereby reducing noise.

[0015] In one embodiment, multiple sawtooth baffles are evenly spaced, and the spacing angle between two adjacent sawtooth baffles is β. The range of the spacing angle β is: 30°≥β≥20°.

[0016] In one embodiment, multiple sawtooth baffles are evenly spaced, and the interval angle between two adjacent sawtooth baffles is 30° or 20°.

[0017] In one embodiment, the sawtooth spoiler includes a triangular piece, the bottom of which is disposed on the inner wall surface of the resonant cavity. The triangular piece includes a first waist surface and a second waist surface, both of which are inclined planes. The height of both the first waist surface and the second waist surface is H. The length of the first waist surface in a first direction is L1, and the length of the second waist surface in the first direction is L2, wherein L2 > L1 > H.

[0018] In one embodiment, the sawtooth spoiler includes a triangular piece, the bottom of which is disposed on the inner wall surface of the resonant cavity. The triangular piece includes a first waist surface and a second waist surface, both of which are inclined planes. The height of both the first waist surface and the second waist surface is H. The length of the first waist surface in a first direction is L1, and the length of the second waist surface in the first direction is L2, wherein L2 > L1 = H.

[0019] In the above embodiment, the triangular plate guides the airflow smoothly towards the wall during airflow separation, avoiding turbulence caused by sudden expansion. The main function of the first waist surface is to break up and dissipate vortex energy, reducing flow separation losses. The main function of the second waist surface is to make the separation of exhaust airflow smoother.

[0020] In one embodiment, the spoiler is an annular protrusion that divides the resonant cavity into a first cavity, a second cavity, and a third cavity. The second cavity is located between the first cavity and the third cavity, and the radial diameter of the second cavity is smaller than the radial diameters of the first cavity and the third cavity.

[0021] In the above embodiments, noise reduction is achieved through multiple mechanisms such as eddies and impedance abrupt changes. The core of noise reduction is disrupting the coherence of sound waves. The second and third cavities are constructed as a contraction-expansion structure, which features abrupt changes in acoustic impedance. When airflow passes through the contraction section of the serrated structure, the flow velocity increases and the pressure decreases; in the expansion section, the flow velocity slows down and the pressure recovers. This change leads to sound wave reflection and energy dissipation, thereby achieving noise reduction.

[0022] In one embodiment, the annular protrusion has a triangular cross-section in the first direction, the cross-section including a first waist and a second waist, the height of the triangle is N, the length of the first waist in the first direction is C1, and the length of the second waist in the first direction is C2, wherein C2 > C1 > H.

[0023] In one embodiment, the expansion cavity is provided with an assembly shaft hole, and the flange journal of the compressor is provided in the assembly shaft hole. The flange journal and the expansion cavity define a flow channel. The other end of the silencer assembly is connected to the flow channel, and the silencer airflow enters the silencer assembly through the flow channel.

[0024] The present invention also provides a compressor comprising:

[0025] case;

[0026] The motor is housed within the casing;

[0027] The compressor assembly is housed within a casing, and the crankshaft of the compressor assembly is connected to the rotor of the motor.

[0028] The aforementioned muffler is mounted on the flange journal of the compressor assembly, and the crankshaft passes through the flange journal.

[0029] The airflow to be silenced enters the silencer from the output end of the compressor assembly, and the airflow after being silenced by the silencer flows into the inner cavity of the housing.

[0030] Compared with existing technologies, the advantages of this invention lie in the inclusion of an expansion cavity to eliminate broadband noise in the airflow to be silenced, and a silencing component to eliminate single-tone peak noise at a preset frequency. This results in two noise elimination processes for the airflow entering the silencer, achieving both broadband noise elimination and single-tone peak noise elimination at the preset frequency. Consequently, the silencer possesses both the function of eliminating broadband noise and single-tone peak noise, thereby improving its noise reduction effect. Attached Figure Description

[0031] The invention will now be described in more detail with reference to embodiments and the accompanying drawings.

[0032] Figure 1 This is a three-dimensional structural diagram of the silencer in Embodiment 1 of the present invention;

[0033] Figure 2 This is a full sectional view of the muffler in Embodiment 1 of the present invention;

[0034] Figure 3 yes Figure 2 A partially enlarged schematic diagram of the sound-absorbing component;

[0035] Figure 4 This is a full-section three-dimensional structural diagram of the muffler in Embodiment 2 of the present invention;

[0036] Figure 5 yes Figure 4 A partially enlarged schematic diagram of the sound-absorbing component;

[0037] Figure 6 This is a full-section three-dimensional structural diagram of the muffler in Embodiment 3 of the present invention;

[0038] Figure 7 yes Figure 6 A partially enlarged schematic diagram of the sound-absorbing component;

[0039] Figure 8 These are schematic diagrams illustrating the noise reduction principle of the silencer in Embodiments 1 to 3 of the present invention;

[0040] Figure 9 This is a three-dimensional structural diagram of a silencer in the prior art;

[0041] Figure 10 This is a schematic diagram of the noise reduction principle of a muffler in existing technology;

[0042] Figure 11 This is a schematic diagram of the structure of the compressor in Embodiment 4 of the present invention.

[0043] Figure label:

[0044] 10. Mounting plate; 11. Assembly screw hole; 20. Expansion cavity; 21. Exhaust port; 22. Assembly shaft hole; 30. Silencing assembly; 31. Silencing cylinder; 311. Resonance cavity; 3111. First cavity; 3112. Second cavity; 3113. Third cavity; 32. Baffle; 321. Serrated baffle; 3211. First waist surface; 3212. Second waist surface; 322. Annular protrusion; 100. Silencer; 200. Housing; 300. Motor; 301. Rotor; 400. Compressor assembly; 401. Crankshaft; 402. Flange journal; 11'. Assembly screw hole; 20'. Expansion cavity; 21'. Exhaust port; 22'. Assembly shaft hole. Detailed Implementation

[0045] The invention will now be further described with reference to the accompanying drawings.

[0046] Example 1

[0047] like Figure 1 and 2 As shown, the present invention provides a muffler 100, which includes a mounting plate 10, an expansion cavity 20, and a silencing component 30. The expansion cavity 20 is disposed on the mounting plate 10 and has a single exhaust port 21. The silencing component 30 is disposed within the expansion cavity 20, with one end connected to the exhaust port 21 and the other end connected to the expansion cavity 20. The airflow to be silenced sequentially enters the expansion cavity 20 and the silencing component 30. The muffler 100 is configured such that the expansion cavity 20 is used to eliminate broadband noise in the airflow to be silenced, and the silencing component 30 is used to eliminate single-tone peak noise of a preset frequency in the airflow to be silenced.

[0048] The above configuration includes an expansion cavity 20 to eliminate broadband noise in the airflow to be silenced, and a silencing component 30 to eliminate single-tone peak noise at a preset frequency. This performs two noise elimination processes on the airflow entering the silencer 100, achieving both broadband noise elimination and single-tone peak noise elimination at the preset frequency. Therefore, the silencer 100 possesses both broadband noise elimination and single-tone peak noise elimination capabilities, thereby improving its noise reduction effect.

[0049] In addition, a silencing component 30 is provided inside the expansion cavity 20, so that the silencer can eliminate single-tone peak noise without increasing the space occupied by the silencer, thus making the design size of the silencer 100 not limited by the original space.

[0050] It should be noted that while the expansion cavity 20 has a wide noise reduction bandwidth, its noise reduction effect is not significant. The noise reduction component 30 can eliminate single-tone peak noise, but it cannot eliminate broadband noise. In this application, a noise reduction component 30 is added inside the expansion cavity 20, and the expansion cavity 20 and the noise reduction component 30 form a composite noise reduction structure. This composite noise reduction structure enables the silencer 100 in this application to have both a wider noise reduction frequency band and stronger noise reduction frequency selectivity, achieving a better noise reduction effect.

[0051] It should be noted that the airflow to be silenced in this embodiment is a high-temperature, high-pressure gaseous refrigerant that has been compressed by the compressor and is output from the pump body exhaust port. The silencer 100 is used to silence and reduce noise from the high-temperature, high-pressure gaseous refrigerant output from the pump body exhaust port.

[0052] Specifically, such as Figure 1 and Figure 2As shown, in one embodiment, the expansion cavity 20 adopts a four-lobed structure. The top of the expansion cavity 20 is provided with a single exhaust port 21 and an assembly shaft hole 22, wherein the assembly shaft hole 22 is located at the center of the top of the expansion cavity, and the exhaust port 21 is located on one side of the assembly shaft hole 22.

[0053] In the above configuration, the expansion cavity 20 is configured as a four-lobed structure, which enables the expansion cavity 20 to have a noise reduction function. The exhaust noise is reduced by the noise reduction principle of the expansion cavity, and a wider noise reduction frequency is achieved.

[0054] It should be noted that the principle of expansion cavity noise reduction is based on the discontinuous distribution of a four-lobed structure. By changing the cross-section, the sound energy is dissipated through the reflection and cancellation of sound waves, thereby reducing noise.

[0055] Specifically, such as Figure 1 and Figure 2 As shown, in one embodiment, the mounting plate 10 is a circular plate with mounting screw holes 11 on it, through which screws are inserted for fixing the muffler 100 to the flange journal 402.

[0056] Specifically, such as Figure 1 and Figure 2 As shown, in one embodiment, the expansion cavity 20 is provided with an assembly shaft hole 22, and the assembly shaft hole 22 is provided with a flange journal 402 of the compressor. The flange journal 402 and the expansion cavity 20 define a flow channel. The other end of the noise reduction assembly 30 is connected to the flow channel, and the noise reduction airflow enters the noise reduction assembly 30 through the flow channel.

[0057] It should be noted that the flange journal 402 and the expansion cavity 22 form a flow channel with a changing cross section, thereby playing a role in noise reduction.

[0058] Specifically, such as Figure 2 As shown, in one embodiment, the silencing component 30 includes a silencing cylinder 31, one end of which is connected to the exhaust port 21, and the other end of the silencing cylinder 31 is connected to the interior of the expansion cavity 20. The silencing cylinder 31 is located inside the expansion cavity 20 and has a resonant cavity 311 inside. The resonant cavity 311 is used to absorb a portion of the single-tone peak noise of a preset frequency in the airflow to be silenced.

[0059] Specifically, such as Figure 2 As shown, in one embodiment, one end of the muffler 31 is connected to the exhaust port 21, and the other end of the muffler 31 extends along the first direction and is disposed in the expansion cavity 20.

[0060] It should be noted that the first direction in this embodiment refers to the height direction of the muffler 100.

[0061] Specifically, such as Figure 2As shown, in one embodiment, the central axis of the muffler 31 coincides with the central axis of the muffler 31 in a first direction.

[0062] Specifically, such as Figure 2 and Figure 3 As shown, in one embodiment, the noise reduction assembly 30 further includes a baffle 32 disposed within the resonant cavity 311, which is used to reduce the noise of the airflow within the resonant cavity 311.

[0063] In the above configuration, the turbulence element 32 has the function of interfering with the airflow in the resonant cavity 311, thereby dissipating the energy of the airflow and improving the noise reduction capability of the noise reduction component 30.

[0064] Specifically, such as Figure 2 and Figure 3 As shown, in one embodiment, the turbulence element 32 includes a plurality of sawtooth turbulence plates 321, which are arranged circumferentially around the muffler 31. The sawtooth turbulence plates 321 are used to divide the internal energy dissipation of the airflow in the resonant cavity 311, so as to reduce the turbulence intensity of the airflow.

[0065] In the above configuration, the serrated edges of multiple serrated baffles 321 divide the airflow into multiple smaller airflow streams, dispersing noise energy and thus reducing noise. Multiple serrated baffles 321 cut large-scale eddies (high-energy turbulence) into multiple small-scale eddies. According to turbulence energy level theory, smaller eddies are more likely to decay rapidly through viscous dissipation, thereby reducing the overall turbulence intensity. The serrated tips of the serrated baffles 321 can disrupt the continuous development of the boundary layer, delay flow separation, and reduce backflow in the separation zone, thereby reducing noise.

[0066] It should be noted that the resonant cavity 311, through its geometry and volume, forms a specific resonant frequency, which can specifically absorb noise in a specific frequency band. This enables the muffler 100 to eliminate single-tone peak noise at a preset frequency, thereby improving the noise reduction effect of the muffler 100.

[0067] It should be noted that the serrated silencer component 30 divides the airflow into multiple fine airflows, dispersing noise energy and thus reducing noise; the desired effect is achieved through geometric design for the noise frequency that needs to be reduced.

[0068] It should be noted that the silencer 31 must be used in conjunction with multiple sawtooth baffles 321, because the resonant cavity 311 alone cannot effectively divide the airflow. Multiple sawtooth baffles 321 can effectively divide the airflow, breaking down large-scale eddies into smaller-scale eddies. These smaller-scale eddies are more likely to decay rapidly through viscous dissipation, thereby reducing the overall turbulence intensity and achieving noise reduction. Specifically, in one embodiment, the multiple sawtooth baffles 321 are evenly spaced, with the angle between two adjacent sawtooth baffles 321 being between 20° and 30°.

[0069] Furthermore, in one embodiment, a plurality of sawtooth baffles 321 are evenly spaced, and the interval angle between two adjacent plurality of sawtooth baffles 321 is 30°.

[0070] It should be noted that the number of airflow streams can be adjusted by changing the spacing angle between two or more adjacent sawtooth baffles 321. This allows for adjustment of the number of airflow streams according to actual conditions, thereby meeting the actual requirements for the number of airflow streams.

[0071] It should be noted that the sawtooth baffle, composed of multiple sawtooth baffles 321, divides the airflow, generating broadband noise. Within the resonant cavity 311, the preset frequencies are selectively absorbed through acoustic impedance matching of the cavity, achieving a composite noise reduction effect of "high frequencies dispersed by the sawtooth baffles + low frequencies absorbed by the resonant cavity." The airflow divided by the sawtooth baffle dissipates energy within the cavity, further reducing turbulence intensity.

[0072] Specifically, such as Figure 2 and Figure 3 As shown, in one embodiment, the sawtooth baffle 321 is a triangular piece, the bottom of which is disposed on the inner wall surface of the resonant cavity 311. The triangular piece has a first waist surface 3211 and a second waist surface 3212, and the first waist surface 3211 and the second waist surface 3212 are inclined surfaces.

[0073] In the above configuration, the triangular plate guides the airflow smoothly towards the wall during airflow separation, avoiding turbulence caused by sudden expansion. The main function of the first waist surface 3211 is to break up and dissipate vortex energy, reducing flow separation losses. The main function of the second waist surface 3212 is to ensure smoother separation of the exhaust airflow.

[0074] Specifically, such as Figure 3 As shown, in one embodiment, the height of the first waist surface 3211 and the second waist surface 3212 is H, the length of the first waist surface 3211 in the first direction is L1, and the length of the second waist surface 3212 in the first direction is L2, wherein L2 > L1 > H.

[0075] It should be noted that the tilt angle of the first waist surface 3211 and the second waist surface 3212 should not be too large. If H is greater than L1 and L2, the tilt angle will be too large, and the airflow cannot be smoothly divided. L1 is less than L2 because after the airflow is divided, the airflow flows smoothly towards the wall to avoid the formation of turbulence. Therefore, the above relationship is satisfied.

[0076] It should be noted that the first waist surface 3211 cannot be a right angle (the angle between it and the aforementioned inner wall surface). If it is a right angle, a backflow zone will form at this location, creating vortices. According to vortex acoustics theory, noise will occur where there are vortices. The angle of the second waist surface 3212 (the angle between it and the aforementioned inner wall surface) cannot be too large or too small. If the angle is too small, such as being close to horizontal, the segmentation effect will be insignificant; if the angle is too large, such as being close to vertical, it may cause premature separation. Optimization through simulation is usually required (e.g., 15°–45°).

[0077] Specifically, such as Figure 8 As shown, in one embodiment, a noise-reducing component 30 is used to segment the airflow, turning large-scale vortices into smaller-scale vortices, reducing the energy of the vortices, and thus reducing noise. Figure 9 As shown, the existing muffler is a sheet metal stamped part, which is fitted onto the flange journal through the mounting shaft hole 22' of the expansion cavity 20'. The muffler is then fixed to the large surface of the flange using screws through the mounting screw holes 11', completing the assembly. After assembly, the mounting shaft hole 22' is a solid flange journal. The flange journal and the expansion cavity 22' form a flow channel with a changing cross-section, thereby achieving a noise reduction effect.

[0078] like Figure 10 As shown, existing silencers reduce noise by using changes in cross-section to dissipate sound energy through the reflection and cancellation of sound waves.

[0079] Because the existing silencer structure is limited by screw hole positions, internal space of the press, flange structure, etc., the silencer range that can be designed is small, the silencer volume is poor, and the silencer frequency selectivity is poor.

[0080] like Figures 1 to 3 As shown, this embodiment designs a novel noise reduction structure for a muffler, which is assembled with the flange journal 402 via mounting screw holes 11 and mounting shaft holes 22. During operation, compressed high-pressure gas (high-temperature, high-pressure gaseous refrigerant) enters the muffler 100 through the inlet (bottom port of the expansion cavity 20). The high-pressure gas first undergoes noise reduction within the flow channel and then enters the resonant cavity 311. After being diverted by the flow-dispersing element 32, it exits the muffler through the exhaust port 21 and enters the lower cavity of the motor (the cavity located at the bottom of the motor within the housing 200). The flow-dispersing element 32 within the resonant cavity 311 is structurally designed for different noise reduction frequencies.

[0081] After the high-pressure gas enters the muffler, it enters the flow channel. The flow channel structure is designed as a conventional expansion cavity. The principle is the same as the noise reduction principle of existing mufflers. The noise reduction effect is achieved by the expansion and contraction of the flow channel cross section. After being silenced by the expansion cavity, it enters the resonance cavity 311. After being diverted by the turbulence component 32, it is discharged from the muffler 100 through the exhaust port 21.

[0082] Specifically, after the high-pressure gas enters the muffler, it enters the flow channel. After being silenced in the flow channel, it enters the resonance cavity 311. The inner wall of the resonance cavity 311 is circumferentially distributed with baffles 32. The function of the baffles 32 is to divide the airflow. On the one hand, it cuts the large vortex formed when the high-pressure gas exits the muffler into smaller vortices. On the other hand, it increases the mixing of the exhaust airflow with the low-pressure gas and refrigerant (low-pressure gas and refrigerant inside the shell 200) from the outside, thereby reducing noise.

[0083] It should be noted that since the muffler exhausts high-temperature, high-pressure gas, mixing it with some low-pressure gas and refrigerant can reduce the propagation energy of exhaust pulsations and improve noise composition. The mixing of low-temperature, low-pressure airflow can reduce gas viscosity, making vortices easier to break up and further increasing dissipation.

[0084] Furthermore, in this embodiment, the silencing frequency of the muffler 100 is controlled by the dimensions L1, L2, and H of the baffle 32. The corresponding silencing frequency can be obtained through simple dimensional design according to actual needs. The dimensional design must be based on the actual silencing frequency of the muffler to determine the noise level at the required reduction.

[0085] In this embodiment, the noise reduction structure of the muffler first achieves initial noise reduction through the design of a conventional expansion cavity, and then performs secondary noise reduction through the design of a baffle on the inner wall of the resonant cavity. This combination of the noise reduction effects of the conventional expansion cavity and the baffle in the resonant cavity not only increases the noise reduction amount of the muffler but also provides excellent frequency selectivity for noise reduction. Designed according to actual noise reduction requirements, it significantly reduces compressor aerodynamic noise and improves the sound quality of the product.

[0086] Example 2

[0087] like Figure 4As shown, the present invention provides a muffler 100, which includes a mounting plate 10, an expansion cavity 20, and a silencing component 30. The expansion cavity 20 is disposed on the mounting plate 10 and has two exhaust ports 21. The silencing component 30 is disposed within the expansion cavity 20, with one end connected to one of the exhaust ports 21 and the other end connected to the expansion cavity 20. The airflow to be silenced sequentially enters the expansion cavity 20 and the silencing component 30. The muffler 100 is configured such that the expansion cavity 20 is used to eliminate broadband noise in the airflow to be silenced, and the silencing component 30 is used to eliminate single-tone peak noise of a preset frequency in the airflow to be silenced.

[0088] The above configuration includes an expansion cavity 20 to eliminate broadband noise in the airflow to be silenced, and a silencing component 30 to eliminate single-tone peak noise at a preset frequency. This performs two noise elimination processes on the airflow entering the silencer 100, achieving both broadband noise elimination and single-tone peak noise elimination at the preset frequency. Therefore, the silencer 100 possesses both broadband noise elimination and single-tone peak noise elimination capabilities, thereby improving its noise reduction effect.

[0089] It should be noted that while the expansion cavity 20 has a wide noise reduction bandwidth, its noise reduction effect is not significant. The noise reduction component 30 can eliminate single-tone peak noise, but it cannot eliminate broadband noise. In this application, a noise reduction component 30 is added inside the expansion cavity 20, and the expansion cavity 20 and the noise reduction component 30 form a composite noise reduction structure. This composite noise reduction structure enables the silencer 100 in this application to have both a wider noise reduction frequency band and stronger noise reduction frequency selectivity, achieving a better noise reduction effect.

[0090] It should be noted that the airflow to be silenced in this embodiment is a high-temperature, high-pressure gaseous refrigerant that has been compressed by the compressor and is output from the pump body exhaust port. The silencer 100 is used to silence and reduce noise from the high-temperature, high-pressure gaseous refrigerant output from the pump body exhaust port.

[0091] Specifically, such as Figure 4 As shown, in one embodiment, the expansion cavity 20 adopts a four-lobed structure. The top of the expansion cavity 20 is provided with two exhaust ports 21 and an assembly shaft hole 22, wherein the assembly shaft hole 22 is located at the center of the top of the expansion cavity, and the two exhaust ports 21 are respectively located on both sides of the assembly shaft hole 22.

[0092] In the above configuration, the expansion cavity 20 is configured as a four-lobed structure, which enables the expansion cavity 20 to have a noise reduction function. The exhaust noise is reduced by the noise reduction principle of the expansion cavity, and a wider noise reduction frequency is achieved.

[0093] It should be noted that the principle of expansion cavity noise reduction is based on the discontinuous distribution of a four-lobed structure. By changing the cross-section, the sound energy is dissipated through the reflection and cancellation of sound waves, thereby reducing noise.

[0094] Specifically, such as Figure 4 As shown, in one embodiment, the mounting plate 10 is a circular plate with mounting screw holes 11 on it, through which screws are inserted for fixing the muffler 100 to the flange journal 402.

[0095] Specifically, such as Figure 4 As shown, in one embodiment, the expansion cavity 20 is provided with an assembly shaft hole 22, and the assembly shaft hole 22 is provided with a flange journal 402 of the compressor. The flange journal 402 and the expansion cavity 20 define a flow channel. The other end of the noise reduction assembly 30 is connected to the flow channel, and the noise reduction airflow enters the noise reduction assembly 30 through the flow channel.

[0096] It should be noted that the flange journal 402 and the expansion cavity 22 form a flow channel with a changing cross section, thereby playing a role in noise reduction.

[0097] Specifically, such as Figure 4 As shown, in one embodiment, the silencing component 30 includes a silencing cylinder 31, one end of which is connected to the exhaust port 21, and the other end of the silencing cylinder 31 is connected to the interior of the expansion cavity 20. The silencing cylinder 31 is located inside the expansion cavity 20 and has a resonant cavity 311 inside. The resonant cavity 311 is used to absorb a portion of the single-tone peak noise of a preset frequency in the airflow to be silenced.

[0098] Specifically, such as Figure 4 As shown, in one embodiment, one end of the muffler 31 is connected to one of the exhaust ports 21, and the other end of the muffler 31 extends along a first direction and is disposed in the expansion cavity 20.

[0099] It should be noted that the first direction in this embodiment refers to the height direction of the muffler 100.

[0100] Specifically, such as Figure 4 As shown, in one embodiment, the central axis of the muffler 31 coincides with the central axis of the muffler 31 in a first direction.

[0101] Specifically, such as Figure 4 As shown, in one embodiment, the noise reduction assembly 30 further includes a baffle 32 disposed within the resonant cavity 311, which is used to reduce the noise of the airflow within the resonant cavity 311.

[0102] In the above configuration, the turbulence element 32 has the function of interfering with the airflow in the resonant cavity 311, thereby dissipating the energy of the airflow and improving the noise reduction capability of the noise reduction component 30.

[0103] Specifically, such as Figure 4 As shown, in one embodiment, the turbulence element 32 includes a plurality of sawtooth turbulence plates 321, which are arranged circumferentially around the muffler 31. The sawtooth turbulence plates 321 are used to divide the internal energy dissipation of the airflow in the resonant cavity 311, so as to reduce the turbulence intensity of the airflow.

[0104] In the above configuration, the serrated edges of multiple serrated baffles 321 divide the airflow into multiple smaller airflow streams, dispersing noise energy and thus reducing noise. Multiple serrated baffles 321 cut large-scale eddies (high-energy turbulence) into multiple small-scale eddies. According to turbulence energy level theory, smaller eddies are more likely to decay rapidly through viscous dissipation, thereby reducing the overall turbulence intensity. The serrated tips of the serrated baffles 321 can disrupt the continuous development of the boundary layer, delay flow separation, and reduce backflow in the separation zone, thereby reducing noise.

[0105] It should be noted that the resonant cavity 311, through its geometry and volume, forms a specific resonant frequency, which can specifically absorb noise in a specific frequency band. This enables the muffler 100 to eliminate single-tone peak noise at a preset frequency, thereby improving the noise reduction effect of the muffler 100.

[0106] It should be noted that the serrated silencer component 30 divides the airflow into multiple fine airflows, dispersing noise energy and thus reducing noise; the desired effect is achieved through geometric design for the noise frequency that needs to be reduced.

[0107] It should be noted that the silencer 31 must be used in conjunction with multiple sawtooth baffles 321, because the resonant cavity 311 alone cannot divide the airflow. Multiple sawtooth baffles 321 can divide the airflow, breaking down large-scale eddies into smaller-scale eddies. Small-scale eddies are more likely to decay rapidly through viscous dissipation, thereby reducing the overall turbulence intensity and achieving the purpose of noise reduction.

[0108] Specifically, in one embodiment, a plurality of sawtooth baffles 321 are evenly spaced, and the spacing angle between two adjacent plurality of sawtooth baffles 321 is between 20° and 30°.

[0109] Furthermore, in one embodiment, a plurality of sawtooth baffles 321 are evenly spaced, and the spacing angle between two adjacent plurality of sawtooth baffles 321 is 20°.

[0110] It should be noted that the number of airflow streams can be adjusted by changing the spacing angle between two or more adjacent sawtooth baffles 321. This allows for adjustment of the number of airflow streams according to actual conditions, thereby meeting the actual requirements for the number of airflow streams.

[0111] It should be noted that the sawtooth baffle, composed of multiple sawtooth baffles 321, divides the airflow, generating broadband noise. Within the resonant cavity 311, the preset frequencies are selectively absorbed through acoustic impedance matching of the cavity, achieving a composite noise reduction effect of "high frequencies dispersed by the sawtooth baffles + low frequencies absorbed by the resonant cavity." The airflow divided by the sawtooth baffle dissipates energy within the cavity, further reducing turbulence intensity.

[0112] Specifically, such as Figure 5 As shown, in one embodiment, the sawtooth baffle 321 is a triangular piece, the bottom of which is disposed on the inner wall surface of the resonant cavity 311. The triangular piece has a first waist surface 3211 and a second waist surface 3212, and the first waist surface 3211 and the second waist surface 3212 are inclined surfaces.

[0113] In the above configuration, the triangular plate guides the airflow smoothly towards the wall during airflow separation, avoiding turbulence caused by sudden expansion. The main function of the first waist surface 3211 is to break up and dissipate vortex energy, reducing flow separation losses. The main function of the second waist surface 3212 is to ensure smoother separation of the exhaust airflow.

[0114] Specifically, such as Figure 5 As shown, in one embodiment, the height of the first waist surface 3211 and the second waist surface 3212 is H, the length of the first waist surface 3211 in the first direction is L1, and the length of the second waist surface 3212 in the first direction is L2, wherein L2 > L1 = H.

[0115] It should be noted that the tilt angle of the first waist surface 3211 and the second waist surface 3212 should not be too large. If H is greater than L1 and L2, the tilt angle will be too large, and the airflow cannot be smoothly divided. L1 is less than L2 because after the airflow is divided, the airflow flows smoothly towards the wall to avoid the formation of turbulence. Therefore, the above relationship is satisfied.

[0116] It should be noted that the first waist surface 3211 cannot be a right angle (the angle between it and the aforementioned inner wall surface). If it is a right angle, a backflow zone will form at this location, creating vortices. According to vortex theory, noise will occur where there are vortices. The angle of the second waist surface 3212 (the angle between it and the aforementioned inner wall surface) cannot be too large or too small. If the angle is too small, such as being close to horizontal, the segmentation effect will be insignificant; if the angle is too large, such as being close to vertical, it may cause premature separation. Optimization through simulation is usually required (e.g., 15°–45°). Figure 4 and Figure 5As shown, this embodiment designs a novel noise reduction structure for a muffler, which is assembled with the flange journal 402 via mounting screw holes 11 and mounting shaft holes 22. During operation, compressed high-pressure gas (high-temperature, high-pressure gaseous refrigerant) enters the muffler 100 through the inlet (bottom port of the expansion cavity 20). The high-pressure gas is first silenced within the flow channel and then enters the resonant cavity 311. After being diverted by the flow-dispersing element 32, it exits the muffler through the exhaust port 21 and enters the lower cavity of the motor. The flow-dispersing element 32 within the resonant cavity 311 is structurally designed for different noise reduction frequencies.

[0117] After the high-pressure gas enters the muffler, it enters the flow channel. The flow channel structure is designed as a conventional expansion cavity. The principle is the same as the noise reduction principle of existing mufflers. The noise reduction effect is achieved by the expansion and contraction of the flow channel cross section. After being silenced by the expansion cavity, it enters the resonance cavity 311. After being diverted by the turbulence component 32, it is discharged from the muffler 100 through the exhaust port 21.

[0118] Specifically, after the high-pressure gas enters the muffler, it enters the flow channel. After being silenced in the flow channel, a portion of the silenced high-pressure gas then enters the resonance cavity 311. The inner wall of the resonance cavity 311 is circumferentially distributed with baffles 32. The function of the baffles 32 is to divide the airflow. On the one hand, it cuts the large vortex formed when the high-pressure gas exits the muffler into smaller vortices. On the other hand, it increases the mixing of the exhaust airflow with the low-pressure gas and refrigerant in the outside, thereby reducing noise.

[0119] It should be noted that since the exhaust port discharges high-temperature, high-pressure gas, mixing in some low-pressure gas and refrigerant can reduce the propagation energy of exhaust pulsations and improve noise composition. The mixing of low-temperature, low-pressure airflow can reduce gas viscosity, making the vortex more easily broken up and further increasing dissipation.

[0120] Furthermore, in this embodiment, the silencing frequency of the muffler 100 is controlled by the dimensions of L1, L2 and H of the turbulence element 32. According to actual needs, the corresponding silencing frequency can be obtained through simple size design.

[0121] In this embodiment, the noise reduction structure of the muffler first achieves initial noise reduction through the design of a conventional expansion cavity, and then performs secondary noise reduction through the design of a baffle on the inner wall of the resonant cavity. This combination of the noise reduction effects of the conventional expansion cavity and the baffle in the resonant cavity not only increases the noise reduction amount of the muffler but also provides excellent frequency selectivity for noise reduction. Designed according to actual noise reduction requirements, it significantly reduces compressor aerodynamic noise and improves the sound quality of the product.

[0122] It should be noted that the differences between Example 2 and Example 1 are as follows:

[0123] 1. The number of exhaust ports 21 is different. In Example 2, there are two exhaust ports 21.

[0124] It should be noted that the number of exhaust ports on a muffler is not unique, and their location is not limited. Some mufflers may have one exhaust port, while others may have two. Some airflow may exit the muffler from the normal exhaust port without passing through the resonant cavity, while other airflow may pass through the resonant cavity first and then through the resonant cavity. The number of exhaust ports should be determined based on actual needs.

[0125] 2. The height H of the first waist surface 3211 and the second waist surface 3212, the length L1 of the first waist surface 3211 in the first direction, and the length L2 of the second waist surface 3212 in the first direction, wherein the relationship between L2, L1 and H is different.

[0126] 3. The spacing angles between two adjacent sawtooth baffles 321 are not the same.

[0127] Example 3

[0128] like Figure 6 As shown, the present invention provides a muffler 100, which includes a mounting plate 10, an expansion cavity 20, and a silencing component 30. The expansion cavity 20 is disposed on the mounting plate 10 and has two exhaust ports 21. The silencing component 30 is disposed within the expansion cavity 20, with one end connected to one of the exhaust ports 21 and the other end connected to the expansion cavity 20. The airflow to be silenced sequentially enters the expansion cavity 20 and the silencing component 30. The muffler 100 is configured such that the expansion cavity 20 is used to eliminate broadband noise in the airflow to be silenced, and the silencing component 30 is used to eliminate single-tone peak noise of a preset frequency in the airflow to be silenced.

[0129] The above configuration includes an expansion cavity 20 to eliminate broadband noise in the airflow to be silenced, and a silencing component 30 to eliminate single-tone peak noise at a preset frequency. This performs two noise elimination processes on the airflow entering the silencer 100, achieving both broadband noise elimination and single-tone peak noise elimination at the preset frequency. Therefore, the silencer 100 possesses both broadband noise elimination and single-tone peak noise elimination capabilities, thereby improving its noise reduction effect.

[0130] It should be noted that while the expansion cavity 20 has a wide noise reduction bandwidth, its noise reduction effect is not significant. The noise reduction component 30 can eliminate single-tone peak noise, but it cannot eliminate broadband noise. In this application, a noise reduction component 30 is added inside the expansion cavity 20, and the expansion cavity 20 and the noise reduction component 30 form a composite noise reduction structure. This composite noise reduction structure enables the silencer 100 in this application to have both a wider noise reduction frequency band and stronger noise reduction frequency selectivity, achieving a better noise reduction effect.

[0131] It should be noted that the airflow to be silenced in this embodiment is a high-temperature, high-pressure gaseous refrigerant that has been compressed by the compressor and is output from the pump body exhaust port. The silencer 100 is used to silence and reduce noise from the high-temperature, high-pressure gaseous refrigerant output from the pump body exhaust port.

[0132] Specifically, such as Figure 6 As shown, in one embodiment, the expansion cavity 20 adopts a four-lobed structure. The top of the expansion cavity 20 is provided with two exhaust ports 21 and an assembly shaft hole 22, wherein the assembly shaft hole 22 is located at the center of the top of the expansion cavity, and the two exhaust ports 21 are respectively located on both sides of the assembly shaft hole 22.

[0133] Specifically, such as Figure 6 As shown, in one embodiment, the mounting plate 10 is a circular plate with mounting screw holes 11 on it, through which screws are inserted for fixing the muffler 100 to the flange journal 402.

[0134] Specifically, such as Figure 6 As shown, in one embodiment, the expansion cavity 20 is provided with an assembly shaft hole 22, and the assembly shaft hole 22 is provided with a flange journal 402 of the compressor. The flange journal 402 and the expansion cavity 20 define a flow channel. The other end of the noise reduction assembly 30 is connected to the flow channel, and the noise reduction airflow enters the noise reduction assembly 30 through the flow channel.

[0135] Specifically, such as Figure 6 As shown, in one embodiment, the silencing component 30 includes a silencing cylinder 31, one end of which is connected to the exhaust port 21, and the other end of the silencing cylinder 31 is connected to the interior of the expansion cavity 20. The silencing cylinder 31 is located inside the expansion cavity 20 and has a resonant cavity 311 inside. The resonant cavity 311 is used to absorb a portion of the single-tone peak noise of a preset frequency in the airflow to be silenced.

[0136] In the above configuration, the resonant cavity 311 forms a specific resonant frequency through its geometry and volume, which can specifically absorb noise in a specific frequency band. This enables the muffler 100 to eliminate single-tone peak noise at a preset frequency, thereby improving the noise reduction effect of the muffler 100.

[0137] Specifically, such as Figure 6 As shown, in one embodiment, one end of the muffler 31 is connected to one of the exhaust ports 21, and the other end of the muffler 31 extends along a first direction and is disposed in the expansion cavity 20.

[0138] It should be noted that the first direction in this embodiment refers to the height direction of the muffler 100.

[0139] Specifically, such as Figure 6As shown, in one embodiment, the central axis of the muffler 31 coincides with the central axis of the muffler 31 in a first direction.

[0140] Specifically, such as Figure 6 As shown, in one embodiment, the noise reduction assembly 30 further includes a baffle 32 disposed within the resonant cavity 311, which is used to reduce the noise of the airflow within the resonant cavity 311.

[0141] In the above configuration, the turbulence element 32 has the function of interfering with the airflow in the resonant cavity 311, thereby dissipating the energy of the airflow and improving the noise reduction capability of the noise reduction component 30.

[0142] Specifically, such as Figure 6 As shown, in one embodiment, the spoiler 32 is an annular protrusion 322, which divides the resonant cavity 311 into a first cavity 3111, a second cavity 3112, and a third cavity 3113. The second cavity 3112 is located between the first cavity 3111 and the third cavity 3113, and the diameter of the second cavity 3112 is smaller than the diameters of the first cavity 3111 and the third cavity 3113.

[0143] It should be noted that noise reduction is achieved through multiple mechanisms such as eddies and impedance abrupt changes, with the core of noise reduction being the disruption of sound wave coherence. The second cavity 3112 and the third cavity 3113 are constructed as a contraction-expansion structure, which features abrupt changes in acoustic impedance. When airflow passes through the contraction section of the serrated section (second cavity 3112), the flow velocity increases and the pressure decreases; in the expansion section, the flow velocity slows down and the pressure recovers. This change leads to sound wave reflection and energy dissipation, thereby achieving noise reduction.

[0144] Specifically, such as Figure 7 As shown, in one embodiment, the annular protrusion 322 has a triangular cross-section in the first direction, the cross-section having a first waist and a second waist, the height of the triangle being N, the length of the first waist in the first direction being C1, and the length of the second waist in the first direction being C2, wherein C2 > C1 > H.

[0145] like Figure 6 and Figure 7 As shown, this embodiment designs a novel noise reduction structure for a muffler, which is assembled with the flange journal 402 via mounting screw holes 11 and mounting shaft holes 22. During operation, compressed high-pressure gas (high-temperature, high-pressure gaseous refrigerant) enters the muffler 100 through the air inlet (bottom port of the expansion cavity 20). The high-pressure gas first undergoes noise reduction within the flow channel and then enters the resonant cavity 311. After being disturbed by the flow-dissipating element 32, it exits the muffler through the exhaust port 21 and enters the lower cavity of the motor. The flow-dissipating element 32 within the resonant cavity 311 is structurally designed for different noise reduction frequencies.

[0146] After the high-pressure gas enters the muffler, it enters the flow channel. The flow channel structure is designed as a conventional expansion cavity. The principle is the same as the noise reduction principle of existing mufflers. The noise reduction effect is achieved by the expansion and contraction of the flow channel cross section. After being silenced by the expansion cavity, it enters the resonance cavity 311. After being diverted by the turbulence component 32, it is discharged from the muffler 100 through the exhaust port 21.

[0147] Specifically, after the high-pressure gas enters the silencer, it enters the flow channel. After being silenced in the flow channel, a portion of the silenced high-pressure gas then enters the resonant cavity 311. The inner wall of the resonant cavity 311 is circumferentially distributed with turbulence-dissipating elements 32. The turbulence-dissipating elements 32 cause the airflow sound wave to be reflected and the airflow energy to be dissipated, thereby achieving noise reduction.

[0148] It should be noted that since the exhaust port discharges high-temperature, high-pressure gas, mixing in some low-pressure gas and refrigerant can reduce the propagation energy of exhaust pulsations and improve noise composition. The mixing of low-temperature, low-pressure airflow can reduce gas viscosity, making the vortex more easily broken up and further increasing dissipation.

[0149] In this embodiment, the noise reduction structure of the muffler first achieves initial noise reduction through the design of a conventional expansion cavity, and then performs secondary noise reduction through the design of a baffle on the inner wall of the resonant cavity. This combination of the noise reduction effects of the conventional expansion cavity and the baffle in the resonant cavity not only increases the noise reduction amount of the muffler but also provides excellent frequency selectivity for noise reduction. Designed according to actual noise reduction requirements, it significantly reduces compressor aerodynamic noise and improves the sound quality of the product.

[0150] It should be noted that the resonant cavity 311, through its geometry and volume, forms a specific resonant frequency, which can specifically absorb noise in a specific frequency band. This enables the muffler 100 to eliminate single-tone peak noise at a preset frequency, thereby improving the noise reduction effect of the muffler 100.

[0151] It should be noted that the annular protruding sound-absorbing component 30 causes a sudden change in airflow acoustic impedance, disperses noise energy, and thus reduces noise; the desired effect is achieved through geometric design for the noise frequency that needs to be reduced.

[0152] It should be noted that the differences between Example 3 and Example 1 are as follows:

[0153] 1. The number of exhaust ports is different. In Example 3, there are two exhaust ports, while in Example 1, there is one exhaust port.

[0154] It should be noted that the number of exhaust ports on a muffler is not unique, and their location is not limited. Some mufflers may have one exhaust port, while others may have two. Some airflow may exit the muffler from the normal exhaust port without passing through the resonant cavity, while other airflow may pass through the resonant cavity first and then through the resonant cavity. The number of exhaust ports should be determined based on actual needs.

[0155] 2. The structures of the spoilers are completely different. In Embodiment 3, the spoiler is an annular protrusion, while in Embodiment 1, it is multiple sawtooth spoilers.

[0156] Example 4

[0157] like Figure 11 As shown, the present invention provides a compressor, which includes a housing 200, a compressor assembly 400, and a silencer 100. A motor 300 is disposed within the housing 200, and the compressor assembly 400 is disposed within the housing 200. The crankshaft 401 of the compressor assembly 400 is connected to the rotor 301 of the motor 300. The silencer 100 is disposed on the flange journal 402 of the compressor assembly 400, and the crankshaft 401 passes through the flange journal 402. The airflow to be silenced enters the silencer 100 from the output end of the compressor assembly 400, and the airflow after being silenced by the silencer 100 flows into the inner cavity of the housing 200.

[0158] Specifically, such as Figure 1 and Figure 2 As shown, in one embodiment, the muffler 100 includes a mounting plate 10, an expansion cavity 20, and a silencing component 30. The expansion cavity 20 is disposed on the mounting plate 10 and has a single exhaust port 21. The silencing component 30 is disposed within the expansion cavity 20, with one end connected to the exhaust port 21 and the other end connected to the expansion cavity 20. The airflow to be silenced sequentially enters the expansion cavity 20 and the silencing component 30. The muffler 100 is configured such that the expansion cavity 20 is used to eliminate broadband noise in the airflow to be silenced, and the silencing component 30 is used to eliminate single-tone peak noise of a preset frequency in the airflow to be silenced.

[0159] Specifically, such as Figure 1 and Figure 2 As shown, in one embodiment, the expansion cavity 20 adopts a four-lobed structure. The top of the expansion cavity 20 is provided with a single exhaust port 21 and an assembly shaft hole 22, wherein the assembly shaft hole 22 is located at the center of the top of the expansion cavity, and the exhaust port 21 is located on one side of the assembly shaft hole 22.

[0160] Specifically, such as Figure 1 and Figure 2 As shown, in one embodiment, the mounting plate 10 is a circular plate with mounting screw holes 11 on it, through which screws are inserted for fixing the muffler 100 to the flange journal 402.

[0161] Specifically, such as Figure 1 and Figure 2 As shown, in one embodiment, the expansion cavity 20 is provided with an assembly shaft hole 22, and the assembly shaft hole 22 is provided with a flange journal 402 of the compressor. The flange journal 402 and the expansion cavity 20 define a flow channel. The other end of the noise reduction assembly 30 is connected to the flow channel, and the noise reduction airflow enters the noise reduction assembly 30 through the flow channel.

[0162] Specifically, such as Figure 1 and Figure 2 As shown, in one embodiment, the silencing component 30 includes a silencing cylinder 31, one end of which is connected to the exhaust port 21, and the other end of the silencing cylinder 31 is connected to the interior of the expansion cavity 20. The silencing cylinder 31 is located inside the expansion cavity 20 and has a resonant cavity 311 inside. The resonant cavity 311 is used to absorb a portion of the single-tone peak noise of a preset frequency in the airflow to be silenced.

[0163] Specifically, such as Figure 2 As shown, in one embodiment, one end of the muffler 31 is connected to the exhaust port 21, and the other end of the muffler 31 extends along the first direction and is disposed in the expansion cavity 20.

[0164] It should be noted that the first direction in this embodiment refers to the height direction of the muffler 100.

[0165] Specifically, such as Figure 2 As shown, in one embodiment, the central axis of the muffler 31 coincides with the central axis of the muffler 31 in a first direction.

[0166] Specifically, such as Figure 2 As shown, in one embodiment, the noise reduction assembly 30 further includes a baffle 32 disposed within the resonant cavity 311, which is used to reduce the noise of the airflow within the resonant cavity 311.

[0167] Specifically, such as Figure 2 and Figure 3 As shown, in one embodiment, the turbulence element 32 includes a plurality of sawtooth turbulence plates 321, which are arranged circumferentially around the muffler 31. The sawtooth turbulence plates 321 are used to divide the internal energy dissipation of the airflow in the resonant cavity 311, so as to reduce the turbulence intensity of the airflow.

[0168] Specifically, such as Figure 3 As shown, in one embodiment, a plurality of sawtooth baffles 321 are evenly spaced, and the interval angle between two adjacent plurality of sawtooth baffles 321 is 30°.

[0169] Specifically, such as Figure 3As shown, in one embodiment, the sawtooth baffle 321 is a triangular piece, the bottom of which is disposed on the inner wall surface of the resonant cavity 311. The triangular piece has a first waist surface 3211 and a second waist surface 3212, and the first waist surface 3211 and the second waist surface 3212 are inclined surfaces.

[0170] Specifically, such as Figure 3 As shown, in one embodiment, the height of the first waist surface 3211 and the second waist surface 3212 is H, the length of the first waist surface 3211 in the first direction is L1, and the length of the second waist surface 3212 in the first direction is L2, wherein L2 > L1 > H.

[0171] It should be noted that the specific structures of the compressor assembly 400 and the motor 300 are existing structures, and the working principle of the compressor assembly 400 is existing technology, which will not be described in detail here. Please refer to Chinese Invention Patent CN100487251C.

[0172] Although the invention has been described with reference to preferred embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, the technical features mentioned in the various embodiments can be combined in any manner as long as there is no structural conflict. The invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A silencer, characterized in that, It includes: Installation disk; An expansion chamber is provided on the mounting plate, and the expansion chamber is provided with at least one exhaust port; A muffler assembly is disposed within the expansion cavity, one end of the muffler assembly is connected to the at least one exhaust port, and the other end of the muffler assembly is connected to the expansion cavity; The airflow to be silenced enters the expansion cavity and the silencing component in sequence. The expansion cavity is configured to eliminate broadband noise of the airflow to be silenced, and the silencing component is configured to eliminate single-tone peak noise of a preset frequency of the airflow to be silenced. The silencing assembly includes a muffler, one end of which is connected to the at least one exhaust port, and the other end of which is connected to the interior of the expansion cavity. The muffler is located inside the expansion cavity and has a resonant cavity inside. The resonant cavity is used to absorb the single-tone peak noise of a preset frequency of the airflow to be silenced. The noise reduction assembly also includes a baffle, which is disposed within the resonant cavity and is used to reduce the noise of the airflow within the resonant cavity.

2. The silencer according to claim 1, characterized in that, The baffle includes multiple serrated baffles, which are circumferentially spaced around the muffler. The serrated baffles are used to divide the internal energy dissipation of the airflow in the resonant cavity.

3. The silencer according to claim 2, characterized in that, The plurality of sawtooth baffles are evenly spaced, and the interval angle between two adjacent sawtooth baffles is β. The range of the interval angle β is: 30°≥β≥20°.

4. The silencer according to claim 3, characterized in that, The interval angle β is either 30° or 20°.

5. The silencer according to claim 3 or 4, characterized in that, The sawtooth spoiler includes a triangular piece, the bottom of which is disposed on the inner wall surface of the resonant cavity. The triangular piece includes a first waist surface and a second waist surface, both of which are inclined planes. The height of both the first waist surface and the second waist surface is H. The length of the first waist surface in a first direction is L1, and the length of the second waist surface in the first direction is L2, wherein L2 > L1 > H.

6. The silencer according to claim 3 or 4, characterized in that, The sawtooth spoiler includes a triangular piece, the bottom of which is disposed on the inner wall surface of the resonant cavity. The triangular piece includes a first waist surface and a second waist surface, both of which are inclined planes. The height of both the first waist surface and the second waist surface is H. The length of the first waist surface in a first direction is L1, and the length of the second waist surface in the first direction is L2, wherein L2 > L1 = H.

7. The silencer according to claim 1, characterized in that, The disturbance component is an annular protrusion that divides the resonant cavity into a first cavity, a second cavity, and a third cavity. The second cavity is located between the first cavity and the third cavity, and the radial diameter of the second cavity is smaller than the diameters of the first cavity and the third cavity.

8. The muffler according to claim 7, characterized in that, The annular protrusion has a triangular cross-section in the first direction, the cross-section including a first waist and a second waist, the height of the triangle is H, the length of the first waist in the first direction is C1, the length of the second waist in the first direction is C2, where C2 > C1 > H.

9. The muffler according to claim 7, characterized in that, The expansion cavity is provided with an assembly shaft hole, and the flange journal of the compressor is provided in the assembly shaft hole. The flange journal and the expansion cavity define a flow channel. The other end of the noise reduction assembly is connected to the flow channel, and the airflow to be noise-reduced enters the noise reduction assembly through the flow channel.

10. A compressor, characterized in that, It includes: case; The motor is housed within the housing; A compressor assembly disposed within the housing, wherein the crankshaft of the compressor assembly is connected to the rotor of the motor; The muffler as described in any one of claims 1 to 9 is disposed on the flange journal of the compressor assembly, and the crankshaft passes through the flange journal; The airflow to be silenced enters the silencer from the output end of the compressor assembly, and the airflow after being silenced by the silencer flows into the inner cavity of the housing.

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