Silencer and compressor

Abstract

The utility model discloses a kind of muffler and compressor, it is related to compressor technical field, wherein, compressor includes bearing, bearing is equipped with air inlet hole, muffler includes shell and partition piece;Shell is sleeved in bearing;Partition piece is located in shell, for the inner chamber of shell is separated into first sound attenuation chamber, second sound attenuation chamber and third sound attenuation chamber, first sound attenuation chamber is communicated with air inlet hole, second sound attenuation chamber is communicated with first sound attenuation chamber and third sound attenuation chamber respectively, second sound attenuation chamber and third sound attenuation chamber are located in the side of first sound attenuation chamber away from bearing, second sound attenuation chamber is located in the periphery of third sound attenuation chamber, shell is equipped with the air outlet hole communicated with third sound attenuation chamber;The technical scheme provided by the utility model can solve the problem that traditional double-layer muffler is difficult to meet the requirement of high sound attenuation volume, cannot effectively reduce compressor frequency band noise.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a muffler and a compressor. Background Technology

[0002] In related technologies, to reduce the pulsating noise caused by high-pressure refrigerant fluctuations during compressor discharge, a silencer is often installed at the bearing flange end face of the compressor. To increase the silencer's noise reduction, a double-layer silencer structure is often used to reduce exhaust pulsating noise. However, traditional double-layer silencers are difficult to meet the requirements for high noise reduction and cannot effectively reduce compressor frequency noise. Utility Model Content

[0003] The main purpose of this invention is to propose a silencer and compressor, which aims to solve the problem that traditional double-layer silencers cannot meet the requirements of high noise reduction and cannot effectively reduce the frequency noise of compressors.

[0004] To achieve the above objectives, the present invention proposes a muffler for use in a compressor, the compressor including a bearing having an air inlet, and the muffler comprising: A housing, fitted onto the bearing; A separator, disposed within the housing, is used to divide the inner cavity of the housing into a first silencing chamber, a second silencing chamber, and a third silencing chamber. The first silencing chamber communicates with the air inlet. The second silencing chamber communicates with both the first and third silencing chambers. The second and third silencing chambers are located on the side of the first silencing chamber away from the bearing. The second silencing chamber is located around the third silencing chamber. The housing is provided with an exhaust port communicating with the third silencing chamber.

[0005] In one embodiment, the height ratio of the second silencing cavity to the first silencing cavity in the axial direction of the bearing is not less than 0.3 and not greater than 0.6.

[0006] In one embodiment, the separator includes a separator plate and a separator portion disposed on the separator plate. The separator plate is used to divide the inner cavity of the housing into a first cavity and a second cavity. The first cavity is the first silencing cavity, and the separator portion is used to divide the second cavity into a second silencing cavity and a third silencing cavity.

[0007] In one embodiment, the housing has an open end, a top plate opposite to the open end, and a side plate extending from the periphery of the top plate toward the open end. A partition plate is disposed opposite to the top plate, and a partition portion is provided between the partition plate and the top plate. The partition plate and the side plate are used to enclose the bearing to form the first silencing cavity. A mounting cylinder for the shaft of the bearing to pass through is also provided between the partition plate and the top plate. The mounting cylinder has a first outer wall and a second outer wall connected end to end along the circumference of the bearing. The first outer wall, the outer wall of the partition portion, the partition plate, the side plate, and the top plate enclose the second silencing cavity. The second outer wall, the partition plate, the inner wall of the partition portion, and the top plate enclose the third silencing cavity.

[0008] In one embodiment, the side plate includes five first connecting segments arranged circumferentially along the bearing, each first connecting segment protruding toward a side away from the center of the housing to form a first recess opening toward the center of the housing, and the partition having three or four protrusions on the side facing the side plate; each of the protrusions is respectively provided in a one-to-one correspondence with a corresponding number of the first connecting segments and is partially embedded in the corresponding first recess.

[0009] In one embodiment, the volume ratio of the second silencing cavity to the third silencing cavity is not less than 0.6 and not greater than 1.2.

[0010] In one embodiment, the partition plate is provided with a first vent hole, which connects the first silencing cavity and the second silencing cavity; And / or, the partition is provided with a second vent hole, which connects the second silencing chamber and the third silencing chamber.

[0011] In one embodiment, a plane perpendicular to the axis of the air intake hole is defined as a reference plane, and the line connecting the projection of the axis of the air intake hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is a first connecting line. The line connecting the projection of the axis of the first vent hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the second line, and the angle between the second line and the first line is not less than 120 degrees and not greater than 145 degrees. And / or, the line connecting the projection of the axis of the second vent hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is a third line, and the angle between the third line and the first line is not less than 5 degrees and not greater than 27 degrees.

[0012] In one embodiment, a plane perpendicular to the axis of the air intake is defined as a reference plane; The line connecting the projection of the axis of the first vent hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the fourth line. The exhaust hole includes a first exhaust hole and a second exhaust hole, which are arranged on both sides of the fourth line.

[0013] In one embodiment, the first exhaust port and the second exhaust port are symmetrically arranged about the fourth connecting line.

[0014] In one embodiment, the line connecting the projection of the axis of the air intake hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is a first connecting line. The line connecting the projection of the axis of the first exhaust hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the fifth line, and the angle between the fifth line and the first line is not less than 50 degrees and not greater than 65 degrees. And / or, the line connecting the projection of the axis of the second exhaust hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the sixth line, and the angle between the sixth line and the first line is not less than 190 degrees and not greater than 215 degrees.

[0015] In one embodiment, the ratio of the sum of the opening areas of the first exhaust port and the second exhaust port to the opening area of ​​the air inlet port is not less than 0.4 and not less than 1.1.

[0016] In one embodiment, the ratio of the opening area of ​​the first vent to the opening area of ​​the air inlet is not less than 0.2 and not greater than 0.65. And / or, the ratio of the opening area of ​​the second vent to the opening area of ​​the air inlet is not less than 0.3 and not greater than 0.7.

[0017] This utility model also proposes a compressor, the compressor comprising: The bearing is equipped with an air inlet. As described above, the muffler is sleeved on the bearing, and the first muffler chamber of the muffler is connected to the air inlet. Crankshaft; A cylinder having a working chamber, the bearing being located on one side of the cylinder and sleeved around the crankshaft, and the muffler being located on the side of the bearing opposite to the cylinder; The piston is eccentrically rotatably disposed within the working chamber and sleeved around the crankshaft; An electric motor is connected to the crankshaft drive to drive the crankshaft to rotate.

[0018] In one embodiment, the muffler includes a housing and a partition, wherein a mounting cylinder is provided between the partition plate of the partition and the top plate of the housing, and the bearing has a shaft passing through the mounting cylinder, the axial height of the shaft being greater than the axial height of the housing.

[0019] In one embodiment, the side plate of the muffler includes five second connecting segments arranged circumferentially along the bearing, each second connecting segment being recessed toward the center of the housing to form a second cavity opposite to the central opening of the housing, and the bearing having fastening holes for fasteners to pass through at the positions corresponding to each of the second cavities.

[0020] The technical solution of this utility model is to construct a housing for the compressor bearing, and to divide the inner cavity of the housing into a first silencing chamber, a second silencing chamber, and a third silencing chamber by a separator, forming a three-stage series silencing structure, thereby achieving efficient suppression of exhaust pulsation noise. The first silencing chamber is connected to the air inlet on the bearing, allowing the high-pressure refrigerant discharged from the compressor pump assembly to first enter this chamber for initial buffering and noise reduction. Subsequently, the high-pressure refrigerant enters the second silencing chamber located on the side of the first silencing chamber away from the bearing. This chamber not only further expands the flow space and reduces the airflow velocity, but also extends the sound wave propagation path due to its surrounding the third silencing chamber, enhancing the reflection and attenuation effect on high-frequency noise. Finally, the high-pressure refrigerant flows into the third silencing chamber, which serves as the final noise reduction unit, where residual noise, especially mid-to-low frequency noise, is effectively absorbed before being discharged through the exhaust port on the housing. Compared to traditional double-layer silencers, this three-stage series silencer structure can improve the overall noise reduction, especially in the typical operating frequency range of the compressor, while taking into account the smoothness of airflow and reducing flow loss, thereby achieving a high-efficiency and wide-band noise reduction effect, effectively solving the shortcomings of traditional double-layer silencers in terms of high noise reduction requirements and frequency band matching. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0022] Figure 1 A schematic diagram of the structure of the muffler provided by this utility model; Figure 2 for Figure 1 Internal diagram; Figure 3 for Figure 1 / Figure 2 A schematic diagram of the cross-section and internal structure; Figure 4 for Figure 3 A schematic diagram of the cross-section and internal structure; Figure 5 A schematic diagram of the bearing structure provided by this utility model; Figure 6 A schematic diagram of the air vents of the muffler provided by this utility model; Figure 7 This is a comparison chart of the average noise reduction of the traditional double-layer silencer and the silencer of this utility model under different positions of the second noise reduction cavity and different volume ratios of the second noise reduction cavity to the third noise reduction cavity. Figure 8 This is a comparison chart of the transmission loss curves of the traditional double-layer muffler and the muffler of this invention under different positions of the second muffler cavity and different volume ratios of the second and third muffler cavities. Figure 9 This is a comparison chart of the average noise reduction of the traditional double-layer silencer and the silencer of this invention with the same second silencing cavity position and different volume ratios of the second and third silencing cavities. Figure 10 This is a comparison chart of the transmission loss curves of the traditional double-layer muffler and the present invention, with the same second muffler cavity position and different volume ratios of the second and third muffler cavities.

[0023] Explanation of icon numbers: 1000, Compressor; 100, Silencer; 1, Housing; 101, First Silencing Chamber; 102, Second Silencing Chamber; 103, Third Silencing Chamber; 104, Exhaust Port; 104a, First Exhaust Port; 104b, Second Exhaust Port; 11, Open End; 12, Top Plate; 13, Side Plate; 131, First Connecting Section; 132, Second Connecting Section; 14, Mounting Cylinder; 141, First Outer Wall; 142, Second Outer Wall; 1401, First Recessed Cavity; 1402, Second Recessed Cavity; 2, Separator; 21, Separator Plate; 20 1. First vent; 22. Separator; 202. Second vent; 23. Protrusion; L1. First connecting line; L2. Second connecting line; L3. Third connecting line; L4. Fourth connecting line; L5. Fifth connecting line; L6. Sixth connecting line; V1. Volume of the second silencing cavity; V2. Volume of the third silencing cavity; H1. Axial height of the first silencing cavity; H2. Axial height of the second and / or third silencing cavities; H3. Axial height of the housing; 200. Bearing; 2001. Air inlet; 2002. Fastening hole; 210. Shaft.

[0024] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0025] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0026] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0027] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0028] This utility model proposes a silencer 100.

[0029] Please see Figures 1 to 5 In one embodiment of this utility model, the muffler 100 is used in a compressor 1000, the compressor 1000 includes a bearing 200, the bearing 200 is provided with an air inlet 2001, and the muffler 100 includes: Housing 1, fitted onto bearing 200; The separator 2 is disposed inside the housing 1 and is used to divide the inner cavity of the housing 1 into a first silencing chamber 101, a second silencing chamber 102 and a third silencing chamber 103. The first silencing chamber 101 is connected to the air inlet 2001. The second silencing chamber 102 is connected to both the first silencing chamber 101 and the third silencing chamber 103. The second silencing chamber 102 and the third silencing chamber 103 are located on the side of the first silencing chamber 101 away from the bearing 200. The second silencing chamber 102 is located on the periphery of the third silencing chamber 103. The housing 1 is provided with an exhaust port 104 that is connected to the third silencing chamber 103.

[0030] In this embodiment, the compressor 1000 includes, but is not limited to, a single-cylinder rotary compressor with a single cylinder, or a multi-cylinder rotary compressor with multiple cylinders. For example, the compressor 1000 is a double-cylinder rotary compressor with two cylinders. The compressor 1000 includes a housing and a pump assembly and a motor disposed within the housing. The pump assembly includes a cylinder assembly, a bearing 200, and a muffler 100. The cylinder assembly has an exhaust passage for discharging the compressed high-pressure refrigerant; the bearing 200 is disposed on one side of the cylinder assembly, and the bearing 200 has an air inlet 2001 for introducing the high-pressure refrigerant into the muffler 100; the muffler 100 is disposed on the side of the bearing 200 away from the cylinder assembly for performing multi-stage noise reduction processing on the high-pressure refrigerant entering from the air inlet 2001. The pump assembly also includes a main shaft, and a piston is disposed within the cylinder of the cylinder assembly. The piston is sleeved around the main shaft and rotates eccentrically with the main shaft. The motor's output shaft is connected to the main shaft drive, which drives the main shaft to rotate, thereby causing the piston to rotate against the inner wall of the cylinder, compressing the high-pressure refrigerant in the cylinder's compression chamber to form high-pressure refrigerant. After compression, the high-pressure refrigerant is discharged through the cylinder assembly's exhaust passage. Its outlet end is connected to the muffler 100 via the intake port 2001, allowing the compressed high-pressure refrigerant to enter the muffler 100, thus reducing the pulsating noise generated during exhaust.

[0031] However, in related technologies, to suppress the pulsating noise caused by high-pressure refrigerant fluctuations during compressor discharge and to improve the silencing effect, a double-layer silencer is usually installed on the flange end face of the compressor bearing. Nevertheless, traditional double-layer silencers still have limitations in practical applications. Their silencing capacity is difficult to meet high requirements, especially in the main noise frequency band of the compressor, where the noise reduction effect is not ideal and cannot effectively meet the ever-increasing demand for low-noise performance.

[0032] To address this issue, the muffler 100 in this embodiment includes a housing 1 fitted onto the bearing 200. Since the high-pressure refrigerant, after compression, needs to be discharged through the exhaust channel of the cylinder assembly and enter the muffler 100 via the air inlet 2001 on the bearing 200 for noise reduction, directly fitting the housing 1 onto the bearing 200 allows for the reception and guidance of the high-pressure refrigerant along the shortest path, reducing energy loss and noise regeneration during transmission. This also facilitates a more compact overall design. The housing 1 is preferably a petal-shaped structure, rather than a traditional rectangular or other regular shape. The purpose of using a petal-shaped structure is twofold: firstly, its irregular outer contour breaks the symmetry of sound wave propagation, increasing the number of reflections between the inner walls of the cavity, thereby enhancing the sound energy attenuation effect; secondly, this structural form is more easily adapted to the limited space inside the compressor 1000, improving space utilization and helping to improve airflow distribution, reducing secondary noise caused by local eddies.

[0033] A partition 2 is provided inside the housing 1, which divides the inner cavity of the housing 1 into three interconnected silencing chambers: a first silencing chamber 101, a second silencing chamber 102, and a third silencing chamber 103. Specifically, the first silencing chamber 101 is connected to the air inlet 2001 on the bearing 200 and is used to receive the high-pressure refrigerant discharged from the pump assembly and introduced through the bearing 200; the second silencing chamber 102 is connected to both the first silencing chamber 101 and the third silencing chamber 103, serving as an intermediate transition chamber to guide the flow of the high-pressure refrigerant and provide initial noise reduction; while the third silencing chamber 103 is located outside the second silencing chamber 102 and discharges the high-pressure refrigerant, after multi-stage noise reduction, to the external environment through the exhaust port 104 provided on the housing 1.

[0034] With this configuration, the high-pressure refrigerant undergoes multiple physical processes, including reflection, diffusion, and resonance, as it flows sequentially from the first silencing chamber 101 through the second silencing chamber 102 and the third silencing chamber 103. This effectively reduces the pulsating noise caused by high-pressure refrigerant fluctuations. In particular, the design of the third silencing chamber 103 surrounding the second silencing chamber 102 not only extends the sound wave propagation path but also enhances the absorption capacity for broadband noise, especially effectively suppressing the main noise frequencies generated during the operation of the compressor 1000.

[0035] In summary, this embodiment involves fitting the housing 1 onto the bearing 200 and dividing the inner cavity of the housing 1 into a first silencing chamber 101, a second silencing chamber 102, and a third silencing chamber 103 using a separator 2. The first silencing chamber 101 communicates with the air inlet 2001, and the second silencing chamber 102 communicates with both the first silencing chamber 101 and the third silencing chamber 103. The second silencing chamber 102 and the third silencing chamber 103 are located on the side of the first silencing chamber 101 away from the bearing 200. The cavity 102 is located on the periphery of the third silencing cavity 103. The housing 1 is provided with an exhaust port 104 that communicates with the third silencing cavity 103. This can increase the additional buffer and sound absorption layers, improve the overall noise reduction, and especially exhibit stronger noise suppression capabilities in the typical operating frequency band of the compressor 1000. At the same time, it takes into account the smoothness of airflow and reduces flow loss, thereby achieving a high-efficiency and wide-band noise reduction effect, effectively solving the shortcomings of traditional double-layer silencers 100 in terms of high noise reduction requirements and frequency band matching.

[0036] Please see Figure 2 and Figure 3 In one embodiment of the present invention, the separator 2 includes a separator plate 21 and a separator portion 22 disposed on the separator plate 21. The separator plate 21 is used to divide the inner cavity of the housing 1 into a first cavity and a second cavity. The first cavity is a first silencing cavity 101. The separator portion 22 is used to divide the second cavity into a second silencing cavity 102 and a third silencing cavity 103.

[0037] In this embodiment, the partition 22 is located on the side of the partition plate 21 opposite to the bearing 200. The partition plate 21 is fixedly disposed inside the housing 1 and is used to divide the inner cavity of the housing 1 into two regions along the axial direction of the bearing 200: a first cavity located below and a second cavity located above. The first cavity constitutes a first silencing chamber 101, which is connected to the air inlet 2001 on the bearing 200, allowing high-pressure refrigerant to enter the chamber for preliminary noise reduction treatment; while the second cavity is further divided by the partition 22 into two interconnected parts: a third silencing chamber 103 located in the central region and a second silencing chamber 102 surrounding it.

[0038] Thus, the entire housing 1 forms a three-tiered interconnected structure consisting of a first silencing cavity 101, a second silencing cavity 102, and a third silencing cavity 103. The high-pressure refrigerant sequentially flows from the first silencing cavity 101 into the second silencing cavity 102, and then into the third silencing cavity 103. During this flow, it undergoes multiple sound wave reflections, diffusions, and resonances, gradually absorbing and attenuating noise energy. In particular, the arrangement of the second silencing cavity 102 surrounding the third silencing cavity 103 enhances the suppression of broadband noise generated during the exhaust process of the compressor 1000. Simultaneously, this structure, through the rational guidance of the high-pressure refrigerant flow path, reduces airflow resistance, improves refrigerant flow efficiency, and enhances overall noise reduction performance.

[0039] Please see Figure 2 and Figure 3 In one embodiment of the present invention, the housing 1 has an open end 11, a top plate 12 opposite to the open end 11, and a side plate 13 extending from the periphery of the top plate 12 toward the open end 11. A partition plate 21 is disposed opposite to the top plate 12, and a partition portion 22 is provided between the partition plate 21 and the top plate 12. The partition plate 21 and the side plate 13 are used to enclose the bearing 200 to form a first silencing cavity 101. A mounting cylinder 14 for the shaft body 210 of the bearing 200 to pass through is also provided between the partition plate 21 and the top plate 12. The mounting cylinder 14 has a first outer wall 141 and a second outer wall 142 connected end to end along the circumference of the bearing 200. The first outer wall 141, the outer wall of the partition portion 22, the partition plate 21, the side plate 13, and the top plate 12 enclose to form a second silencing cavity 102. The second outer wall 142, the partition plate 21, the inner wall of the partition portion 22, and the top plate 12 enclose to form a third silencing cavity 103.

[0040] In this embodiment, the partition plate 21 is disposed inside the housing 1 and is opposite to the top plate 12, with a partition 22 between them. The partition plate 21, the side plate 13 and the bearing 200 of the compressor 1000 together form a first silencing cavity 101, which is used to receive high-pressure refrigerant from the air inlet 2001 of the bearing 200 to achieve preliminary noise reduction. Based on this, a mounting cylinder 14 for the shaft 210 of the bearing 200 to pass through is provided between the partition plate 21 and the top plate 12. The mounting cylinder 14 has a first outer wall 141 and a second outer wall 142 connected end to end along the circumference of the bearing 200. The first outer wall 141, the outer wall of the partition 22, the partition plate 21, the side plate 13 and the top plate 12 together form a second silencing cavity 102 located on the periphery, while the second outer wall 142, the partition plate 21, the inner wall of the partition 22 and the top plate 12 together form a third silencing cavity 103 located in the central region. Thus, a multi-chamber silencing structure with a clear hierarchical distribution is constructed as a whole, in which the first silencing cavity 101, the second silencing cavity 102 and the third silencing cavity 103 are connected in sequence. After the high-pressure refrigerant enters from the first silencing cavity 101, it flows sequentially through the second silencing cavity 102 and the third silencing cavity 103. During this process, the sound waves undergo multiple reflections, diffusions, and resonances, and the noise energy is gradually absorbed and attenuated. In particular, the arrangement of the second silencing cavity 102 surrounding the third silencing cavity 103 enhances the suppression capability of broadband noise. At the same time, this structure, through the rational arrangement of the spatial relationship between the silencing cavities, can also achieve a compact and modular structural design, improving the space utilization rate of the compressor 1000.

[0041] Please see Figure 4In one embodiment of the present invention, the side plate 13 includes five first connecting segments 131 arranged circumferentially along the bearing 200. Each first connecting segment 131 protrudes toward the side away from the center of the housing 1 to form a first recess 1401 open toward the center of the housing 1. The partition 22 is provided with three or four protrusions 23 on the side facing the side plate 13. Each protrusion 23 is respectively provided in a one-to-one correspondence with the corresponding number of first connecting segments 131 and is partially embedded in the corresponding first recess 1401.

[0042] In this embodiment, the side plate 13 includes five first connecting segments 131 and five second connecting segments 132 arranged circumferentially along the bearing 200. The five first connecting segments 131 and five second connecting segments 132 are alternately connected, forming a five-petal-like structure. Each first connecting segment 131 protrudes outward toward the side away from the center of the housing 1, thereby creating a first cavity 1401 open toward the center of the housing 1 on the first connecting segment 131. At the same time, the partition 22 has three or four protrusions 23 on the side facing the side plate 13. The number and position of these protrusions 23 can be set according to the actual structural design requirements. Each protrusion 23 is correspondingly arranged with a corresponding number of first connecting segments 131 and is partially embedded in its corresponding first cavity 1401, forming a mutually cooperating and reliably positioned fitting structure. For example, when the partition 22 has three protrusions 23 on the side facing the side plate 13, these three protrusions 23 are respectively embedded in the three corresponding first cavities 1401, thereby confining the second silencing cavity 102 within the space formed by the two petals, while the third silencing cavity 103 occupies the area of ​​the remaining three petals. Measurements show that the volume ratio of the second silencing cavity 102 to the third silencing cavity 103 is approximately 0.6. Simulation experiments verify that the muffler with this structure achieves a noise reduction of 33.9 dB, demonstrating good noise reduction performance.

[0043] As can be seen, by designing the side plate 13 as multiple circumferentially distributed first connecting segments 131 and embedding the protrusions 23 on the partition 22 into the corresponding first concave cavities 1401, this embodiment can not only achieve a stable structural fit between the partition 22 and the side plate 13, but also flexibly divide the spatial layout of the second silencing cavity 102 and the third silencing cavity 103 through the distribution of petals, thereby optimizing the volume ratio and acoustic path of the two silencing cavities and improving the muffler's ability to suppress broadband noise, especially the exhaust noise frequency band of the compressor 1000.

[0044] Please see Figure 4 , Figures 7 to 10 In one embodiment of the present invention, the ratio of the volume V1 of the second silencing cavity 102 to the volume V2 of the third silencing cavity 103, V1 / V2, is not less than 0.6 and not greater than 1.2.

[0045] Understandably, in a traditional double-layer silencer, the volume ratio of the upper cavity to the lower cavity, V1' and V2', is usually 0.5. Under this configuration, the average silencer volume is approximately 36.4 dB.

[0046] However, in this embodiment, the noise reduction performance can be improved by adjusting the position of the second noise reduction cavity 102 and its volume ratio V1 / V2 with that of the third noise reduction cavity 103.

[0047] In this embodiment, when the partition 22 has four protrusions 23 on the side facing the side plate 13, the four protrusions 23 are respectively embedded in the four corresponding first cavities 1401, thereby confining the second silencing cavity 102 within the area formed by one petal, while the third silencing cavity 103 occupies the space surrounded by the other four petals. Experiments show that when the second silencing cavity 102 is located in the first petal and the volume ratio V1 / V2 is 1.0, the average silencing power of the muffler 100 can reach 46.2dB, which is significantly better than the traditional double-layer muffler.

[0048] Furthermore, the position of the second silencing cavity 102 affects the noise reduction performance of the muffler 100. For example, when it is located in the second petal and the volume ratio V1 / V2 remains at 1.0, the average noise reduction is 41.1 dB; when it is moved to the third petal, under the same volume ratio V1 / V2, the average noise reduction increases to 45.6 dB. This shows that regardless of which petal the second silencing cavity 102 is located in, it can achieve good noise reduction, and in most cases, its performance far exceeds that of traditional double-layer mufflers.

[0049] Further research shows that when the second silencing cavity 102 is located in the second petal, adjusting its volume ratio can also achieve excellent silencing effect. When the volume ratio V1 / V2 is adjusted from 1.0 to 1.2, the average silencing volume reaches 44.8 dB; if the volume ratio V1 / V2 is reduced to 0.6, the average silencing volume remains at a high level of 44.6 dB. This result indicates that, in this position, the silencer 100 has strong adaptability and stability to changes in the volume ratio V1 / V2, and can maintain efficient silencing capability under different operating conditions.

[0050] In other words, the specific location of the second silencing cavity 102 is one of the key factors determining the overall noise reduction performance. By rationally selecting its placement area within the petal structure and combining it with an appropriate volume ratio V1 / V2, superior acoustic performance compared to traditional double-layer silencers can be achieved in various configurations. This conclusion has been verified. Figure 8 The comparison of the transmission loss curves validated this. Figure 8The figure shows the comparison of the average noise reduction of the muffler 100 in the 0-5000Hz frequency range under different positions of the second silencing cavity 102 and the volume ratio V1 / V2 of the second silencing cavity 102 to the third silencing cavity 103. As can be seen from the figure, when the second silencing cavity 102 is located in the second petal and the volume ratio of its volume V1 to the volume V2 of the third silencing cavity is 0.6, the average noise reduction of the muffler 100 in this frequency band can be improved by 8.2dB compared with the traditional double-layer muffler, demonstrating enhanced noise reduction capability.

[0051] It is worth noting that when the second silencing cavity 102 is fixedly located on the second petal, changes in its volume ratio V1 / V2 also affect the silencing performance. Experiments show that when the volume ratio V1 / V2 increases from 0.6 to 1.0, the average silencing volume of the muffler 100 reaches 45.3 dB; however, when the volume ratio V1 / V2 further increases to 1.2, the average silencing volume drops to 33.9 dB. Therefore, it can be seen that, while keeping the position of the second silencing cavity 102 unchanged, as long as its volume ratio is between 0.6 and 1.2, the silencing performance of the muffler 100 is superior to that of a traditional double-layer muffler. This conclusion can also be drawn through… Figure 10 Verification is required. Figure 10 The diagram compares the transmission loss curves of a conventional double-layer silencer and this embodiment, where the second silencer cavity 102 is located at the same petal position (the second petal), but the volume ratio V1 / V2 of the second and third silencer cavities 103 differs. The diagram clearly shows that, within the frequency range of 0Hz to 5000Hz, this embodiment exhibits superior acoustic performance compared to the conventional double-layer silencer under various volume ratio configurations, particularly demonstrating better noise suppression capabilities in the mid-to-low frequency range. This comparison further validates the effectiveness of improving overall noise reduction performance through reasonable adjustment of cavity position and volume ratio.

[0052] Please see Figure 3 and Figure 4 In one embodiment of this utility model, the height ratio H2 / H1 of the second silencing cavity 102 and the first silencing cavity 101 in the axial direction of the bearing 200 is not less than 0.3 and not greater than 0.6.

[0053] Understandably, the first silencing cavity 101, as the first buffer and noise reduction area after the high-pressure refrigerant enters the silencer 100, has an axial height H1 that determines the flow path length of the high-pressure refrigerant within the cavity and the effective space required for sound wave reflection and diffusion. The second silencing cavity 102 is responsible for smoothly guiding the high-pressure refrigerant, after initial noise reduction, to the third silencing cavity 103, and its axial height H2 directly affects the acoustic performance and aerodynamic characteristics of the entire silencer 100.

[0054] When the height ratio H2 / H1 of the second silencing cavity 102 to the first silencing cavity 101 is less than 0.3, it means that the second silencing cavity 102 is relatively too short, while the first silencing cavity 101 is relatively too tall. In this case, the space of the second silencing cavity 102 is severely limited, resulting in a shortened diffusion path for the high-pressure refrigerant within this cavity. This makes it difficult for sound waves to be fully reflected and attenuated, weakening its ability to further reduce noise. Simultaneously, an excessively small H2 will cause a sharp contraction of the flow cross-section, increasing local flow velocity and easily triggering turbulence, eddies, and secondary noise. This not only affects the stability of the compressor 1000's operation but may also increase flow resistance, thereby reducing system energy efficiency.

[0055] Conversely, if H2 / H1 is greater than 0.6, meaning the second anechoic cavity 102 is too high relative to the first anechoic cavity 101, the height H1 of the first anechoic cavity 101 will be relatively insufficient. In this case, although the second anechoic cavity 102 has ample space, the internal space of the first anechoic cavity 101, as a key area for initial noise attenuation, is compressed, the sound wave propagation path becomes shorter, reflection and interference effects weaken, and the initial noise reduction capability decreases. Furthermore, from a structural design perspective, when the shell 1 adopts a petal-shaped structure, an excessively large H2 / H1 ratio makes it difficult to achieve the rounded transition between adjacent first connecting sections 131, affecting the molding processability and other properties of the shell 1. Simulation results also show that when this ratio exceeds 0.6, the overall noise reduction tends to saturate or even slightly decreases, indicating that simply increasing the axial height of the second anechoic cavity 102 cannot continuously improve the noise reduction effect.

[0056] In summary, controlling the height ratio H2 / H1 between the second silencing cavity 102 and the first silencing cavity 101 to be between 0.3 and 0.6 achieves an optimal balance between noise reduction performance and aerodynamic characteristics. On the one hand, it ensures that the first silencing cavity 101 has sufficient height to achieve effective initial noise attenuation; on the other hand, it provides reasonable space for the second silencing cavity 102, enabling it to effectively receive and further weaken residual noise. Simultaneously, this ratio range is beneficial for optimizing the geometric design of the petal-shaped shell, improving structural manufacturability, assembly reliability, and mechanical strength. Therefore, without increasing the structural complexity of the silencer 100, its overall performance is improved, meeting the actual requirements of the compressor 1000 for efficient, wide-band noise control.

[0057] Please see Figure 5 and Figure 6 In one embodiment of the present invention, the partition plate 21 is provided with a first vent hole 201, which connects the first silencing cavity 101 and the second silencing cavity 102. And / or, the partition 22 is provided with a second vent 202, which connects the second silencing chamber 102 and the third silencing chamber 103.

[0058] In this embodiment, by providing a first vent 201 on the partition plate 21, high-pressure refrigerant can smoothly enter the second silencing chamber 102 from the first silencing chamber 101, realizing the transmission and attenuation of sound waves between different silencing chambers. At the same time, the first vent 201 can also adjust the pressure difference between the first silencing chamber 101 and the second silencing chamber 102 to a certain extent, avoiding airflow disturbance and noise regeneration caused by excessive local pressure. Similarly, by providing a second vent 202 on the partition 22, the second silencing chamber 102 and the third silencing chamber 103 are kept connected. This not only helps to further guide the refrigerant flow path and extend the sound wave propagation distance, but also enhances the synergistic noise reduction effect between the second silencing chamber 102 and the third silencing chamber 103.

[0059] Furthermore, the first vent 201 is positioned away from the air inlet 2001; and / or, the second vent 202 is positioned away from the first vent 201. With this arrangement, after the high-pressure refrigerant enters the first silencing chamber 101 from the air inlet 2001 of the bearing 200, it needs to travel a longer distance to reach the first vent 201, thus extending the flow path within the first silencing chamber 101 and increasing the time and space for sound wave reflection and diffusion, which helps improve the initial noise reduction effect. Similarly, after the refrigerant enters the second silencing chamber 102 from the first silencing chamber 101 through the first vent 201, it still needs to travel a certain distance to reach the second vent 202 and further enter the third silencing chamber 103. This not only extends the entire silencing path but also increases the propagation distance and attenuation opportunity of sound waves between different chambers, improving the overall noise reduction performance.

[0060] Please see Figure 5 and Figure 6 In one embodiment of this utility model, a plane perpendicular to the axis of the air inlet 2001 is defined as a reference plane. The line connecting the projection of the axis of the air inlet 2001 onto the reference plane and the projection of the axis of the bearing 200 onto the reference plane is the first line L1. The line connecting the projection of the axis of the first vent 201 onto the reference plane and the projection of the axis of the bearing 200 onto the reference plane is the second line L2. The angle θ3 between the second line L2 and the first line L1 is not less than 120 degrees and not more than 145 degrees. And / or, the line connecting the projection of the axis of the second vent 202 onto the reference plane and the projection of the axis of the bearing 200 onto the reference plane is the third line L3. The angle θ1 between the third line L3 and the first line L1 is not less than 5 degrees and not more than 27 degrees.

[0061] In this embodiment, when the included angle θ3 is not less than 120 degrees and not greater than 145 degrees, the first vent 201 is set away from the initial flow direction of the air inlet 2001, so that the high-pressure refrigerant cannot flow directly to the first vent 201 after entering the first silencing cavity 101, but needs to take a longer detour to reach the vent position. This effectively extends the flow path of the refrigerant in the first silencing cavity 101, increases the time and space for sound wave reflection, diffusion and resonance, and helps to improve the initial noise reduction effect. When the included angle θ1 is not less than 5 degrees and not greater than 27 degrees, the second vent 202 is located in the petal area between the first vent 201 and the air inlet 2001. This layout makes the refrigerant form a certain backflow or meandering flow in the second silencing cavity 102, further enhancing the propagation complexity of sound waves in the second silencing cavity 102, improving the noise attenuation capability, and also helping the refrigerant to smoothly transition to the third silencing cavity 103, reducing secondary noise caused by sudden flow changes.

[0062] By defining the spatial relative positions of the air inlet 2001, the first vent 201, and the second vent 202, the flow path of the high-pressure refrigerant between the silencers is optimized, the sound wave propagation distance is extended, the noise reduction efficiency is improved, and the overall acoustic performance of the silencer 100 is enhanced. This also avoids problems such as local eddies and pressure fluctuations caused by improper positions of the first vent 201 and the second vent 202, ensuring the stability and energy efficiency of the compressor 1000.

[0063] Please see Figure 5 and Figure 6 In one embodiment of this utility model, a plane perpendicular to the axis of the air inlet 2001 is defined as a reference plane; the line connecting the projection of the axis of the first vent 201 onto the reference plane and the projection of the axis of the bearing 200 onto the reference plane is the second connecting line L2; the exhaust port 104 includes a first exhaust port 104a and a second exhaust port 104b, and the first exhaust port 104a and the second exhaust port 104b are arranged on both sides of the second connecting line L2.

[0064] In this embodiment, by setting the first exhaust port 104a and the second exhaust port 104b on both sides of the second connecting line L2, it means that the exhaust path is no longer concentrated in a single direction, but forms a decentralized or multi-directional exhaust pattern, which helps to reduce the local airflow speed and reduce turbulence noise caused by concentrated airflow. At the same time, this symmetrical or asymmetrical arrangement of exhaust ports 104 distributed in different areas also helps to guide the refrigerant to form a more complex sound wave propagation path in the third silencing cavity 103, extend the propagation distance of the sound wave in the third silencing cavity 103, and enhance its reflection, diffusion and resonance effects in the third silencing cavity 103, thereby further improving the noise reduction effect. Furthermore, considering that the second connection L2 connects the projection points of the axis of the first vent 201 and the axis of the bearing 200, it already reflects the flow direction of the refrigerant between the first silencing cavity 101 and the second silencing cavity 102. Distributing the exhaust port 104 on both sides of the second connection L2 can realize a "non-linear" path from intake to exhaust, avoiding the acoustic short-circuit problem caused by the traditional straight-through structure and improving the synergistic effect between the multi-stage silencing cavities.

[0065] In summary, by defining the spatial positional relationship between the exhaust port 104 and the first vent 201 and the axis of the bearing 200, this embodiment can not only optimize the flow path of the high-pressure refrigerant inside the muffler and enhance the acoustic coupling effect between the various muffler cavities, but also improve the overall noise reduction capability and operational stability of the compressor 1000 without increasing structural complexity.

[0066] Please see Figure 5 and Figure 6 In one embodiment of this utility model, the first exhaust port 104a and the second exhaust port 104b are symmetrically arranged about the second connecting line L2.

[0067] In this embodiment, the first exhaust port 104a and the second exhaust port 104b are symmetrically arranged about the second connecting line L2. This symmetrical layout makes the refrigerant flow distribution from the third silencing cavity 103 more uniform, effectively balancing the airflow pressure on both sides, reducing eddies and secondary noise caused by flow asymmetry, and at the same time extending the propagation path of sound waves in the third silencing cavity 103, enhancing the reflection and attenuation effect, thereby further improving the overall noise reduction performance.

[0068] Please see Figure 5 and Figure 6In one embodiment of this utility model, the line connecting the projection of the axis of the air inlet 2001 onto the reference plane and the projection of the axis of the bearing 200 onto the reference plane is the first connecting line L1; the line connecting the projection of the axis of the first exhaust hole 104a onto the reference plane and the projection of the axis of the bearing 200 onto the reference plane is the fourth connecting line L4, and the angle θ2 between the fourth connecting line L4 and the first connecting line L1 is not less than 50 degrees and not greater than 65 degrees; and / or, the line connecting the projection of the axis of the second exhaust hole 104b onto the reference plane and the projection of the axis of the bearing 200 onto the reference plane is the fifth connecting line L5, and the angle θ4 between the fifth connecting line L5 and the first connecting line L1 is not less than 190 degrees and not greater than 215 degrees.

[0069] In this embodiment, when the angle θ2 between the fourth line L4 and the first line L1 is not less than 50 degrees and not greater than 65 degrees, the first exhaust port 104a is located on the side of the direction of the air inlet 2001, which is slightly upstream. This means that the refrigerant needs to go around a certain path before it can be discharged from the exhaust port 104, thereby effectively extending its flow path in the third silencing cavity 103 and increasing the number of sound wave reflections.

[0070] When the angle θ4 between the fifth line L5 and the first line L1 is not less than 190 degrees and not greater than 215 degrees, the second exhaust port 104b is located opposite to the intake port 2001, that is, on the other side of the housing 1, so that the refrigerant forms a wider flow area in the third silencing cavity 103, avoiding pressure fluctuations and secondary noise caused by local concentrated flow, while enhancing the synergistic noise reduction effect of the dual exhaust.

[0071] Please see Figure 5 and Figure 6 In one embodiment of this utility model, the ratio of the sum of the opening areas of the first exhaust hole 104a and the second exhaust hole 104b to the opening area of ​​the air inlet 2001 is not less than 0.4 and not less than 1.1.

[0072] In this embodiment, when the ratio of the sum of the opening areas of the first exhaust port 104a and the second exhaust port 104b to the opening area of ​​the air inlet 2001 is too large (exceeding 1.1), although it is beneficial to improve the exhaust flow capacity and reduce the flow resistance, it will cause more sound waves to "leak" through the exhaust port 104, weaken the muffler's reflection and attenuation effect on noise, thereby reducing the overall noise reduction effect.

[0073] When this ratio is too small (below 0.4), the exhaust passage is too narrow, which will cause poor exhaust and increased local airflow velocity, potentially leading to eddies and secondary noise. This not only affects the operational stability of the compressor 1000, but also reduces efficiency due to increased flow losses. In addition, although it theoretically helps to enhance the noise reduction effect, the improvement is not significant in practice.

[0074] Therefore, controlling this ratio within the range of 0.4 to 1.1 can effectively suppress noise propagation while ensuring smooth exhaust.

[0075] Please see Figure 5 and Figure 6 In one embodiment of the present invention, the ratio of the opening area of ​​the first vent 201 to the opening area of ​​the air inlet 2001 is not less than 0.2 and not more than 0.65; and / or, the ratio of the opening area of ​​the second vent 202 to the opening area of ​​the air inlet 2001 is not less than 0.3 and not more than 0.7.

[0076] In this embodiment, when the ratio of the opening area of ​​the first vent 201 to the opening area of ​​the air inlet 2001 is within the range of 0.2 to 0.65, it can be ensured that during the flow of high-pressure refrigerant from the first silencing cavity 101 to the second silencing cavity 102, neither the local flow velocity will be too high due to the first vent 201 being too small, causing eddies and secondary noise, nor will the sound waves be directly penetrated due to the first vent 201 being too large, weakening the reflection and attenuation effect. Thus, effective initial noise reduction is achieved while ensuring good flowability.

[0077] Similarly, when the ratio of the opening area of ​​the second vent 202 to the opening area of ​​the air inlet 2001 is in the range of 0.3 to 0.7, it helps to regulate the flow of refrigerant from the second silencing cavity 102 to the third silencing cavity 103, so that the sound waves can obtain more sufficient opportunities for reflection and resonance in the subsequent cavity, and further improve the silencer's ability to suppress broadband noise.

[0078] In summary, by limiting the opening area ratio of the first vent 201 and the second vent 202 within the aforementioned range, not only can the contradiction between the high-pressure refrigerant flow resistance and the noise reduction performance be balanced, but the synergistic effect of the multi-stage noise reduction cavity can also be enhanced, thereby improving the overall noise reduction efficiency of the muffler without increasing the structural complexity.

[0079] This utility model also proposes a compressor 1000, please refer to [link / reference needed]. Figures 1 to 6 The compressor 1000 includes a muffler 100. The specific structure of the muffler 100 is as described in the above embodiments. Since the compressor 1000 adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0080] The compressor 1000 may include a housing, a pump assembly, and a motor housed within the housing. The pump assembly includes a cylinder assembly, a bearing 200, and a muffler 100. The cylinder assembly has an exhaust passage for discharging compressed high-pressure refrigerant. The bearing 200 is located on one side of the cylinder assembly and has an inlet port 2001 for introducing high-pressure refrigerant into the muffler 100. The muffler 100 is located on the side of the bearing 200 away from the cylinder assembly and performs multi-stage noise reduction on the high-pressure refrigerant entering through the inlet port 2001 of the bearing 200. The pump assembly also includes a main shaft. A piston is housed within the cylinder of the cylinder assembly, fitted around the main shaft and rotating eccentrically with it. The motor's output shaft is connected to the main shaft, driving the main shaft to rotate, which in turn causes the piston to rotate against the inner wall of the cylinder, compressing the high-pressure refrigerant within the cylinder's compression chamber to form high-pressure refrigerant. After compression, the high-pressure refrigerant is discharged through the exhaust passage of the cylinder assembly. Its outlet end is connected to the muffler 100 through the air inlet 2001 of the bearing 200, so that the compressed high-pressure refrigerant can enter the muffler 100, thereby reducing the pulsating noise generated during the exhaust process.

[0081] In this embodiment, the silencer 100 includes a housing 1. The housing 1 is fitted onto the bearing 200 of the compressor 1000. A partition 2 is provided inside the housing 1, which divides the inner cavity of the housing 1 into three interconnected silencer chambers: a first silencer chamber 101, a second silencer chamber 102, and a third silencer chamber 103. Specifically, the first silencer chamber 101 communicates with the air inlet 2001 on the bearing 200 and is used to receive high-pressure refrigerant discharged from the pump assembly and introduced through the bearing 200; the second silencer chamber 102 communicates with both the first silencer chamber 101 and the third silencer chamber 103, serving as an intermediate transition chamber to guide the flow of high-pressure refrigerant and provide initial noise reduction; while the third silencer chamber 103 is located around the second silencer chamber 102 and discharges the high-pressure refrigerant, after multi-stage noise reduction, to the external environment through an exhaust port 104 provided on the housing 1. With this configuration, the high-pressure refrigerant undergoes multiple physical processes, including reflection, diffusion, and resonance, as it flows sequentially from the first silencing chamber 101 through the second silencing chamber 102 and the third silencing chamber 103. This effectively reduces the pulsating noise caused by high-pressure refrigerant fluctuations. In particular, the design of the third silencing chamber 103 surrounding the second silencing chamber 102 not only extends the sound wave propagation path but also enhances the absorption capacity for broadband noise, especially effectively suppressing the main noise frequencies generated during the operation of the compressor 1000.

[0082] Please see Figures 1 to 5In one embodiment of the present invention, the muffler 100 includes a housing 1 and a partition 2. A mounting cylinder 14 is provided between the partition plate 21 of the partition 2 and the top plate 12 of the housing 1. The bearing 200 has a shaft 210 passing through the mounting cylinder 14. The axial height H0 of the shaft 210 is greater than the axial height H3 of the housing 1.

[0083] Understandably, during actual operation, high-pressure refrigerant may leak from the assembly gap between bearing 200 and housing 1, affecting the airtightness and noise reduction performance of the muffler. However, by making the axial height H0 of the first shaft section 210 greater than the axial thickness H3 of housing 1, a good axial limiting and sealing fit is ensured between bearing 200 and housing 1, improving the fit and sealing between the two, thereby preventing refrigerant leakage, enhancing the overall structural stability, and helping to maintain the pressure balance of the acoustic cavity inside the muffler, ensuring its normal multi-stage silencing function.

[0084] Please see Figures 1 to 5 In one embodiment of the present invention, the side plate 13 of the muffler 100 includes five second connecting sections 132 arranged circumferentially along the bearing 200. Each second connecting section 132 is recessed toward the side closer to the center of the housing 1 to form a second cavity 1402 that is open away from the center of the housing 1. The bearing 200 is provided with fastening holes 2002 for fasteners to pass through at the positions corresponding to each second cavity 1402.

[0085] In this embodiment, the side plate 13 includes five first connecting segments 131 and five second connecting segments 132 arranged circumferentially along the bearing 200. The five first connecting segments 131 and the five second connecting segments 132 are alternately connected to form a structure similar to "five petals".

[0086] Each first connecting segment 131 protrudes outward toward the side away from the center of the housing 1, thereby creating a first recess 1401 open toward the center of the housing 1 on the first connecting segment 131. Simultaneously, the partition 22 has three or four protrusions 23 on the side facing the side plate 13. The number and position of these protrusions 23 can be set according to actual structural design requirements. Each protrusion 23 corresponds one-to-one with a corresponding number of first connecting segments 131 and is partially embedded in its corresponding first recess 1401, forming a mutually cooperating and reliably positioned fitting structure, which helps improve the assembly accuracy and structural stability between the partition 2 and the housing 1.

[0087] Furthermore, each second connecting segment 132 is recessed inward toward the center of the housing 1, thereby creating a second cavity 1402 that is open away from the center of the housing 1. On the bearing 200 of the compressor 1000, a fastening hole 2002 is provided corresponding to each second cavity 1402 for fasteners (such as screws) to pass through, achieving a stable connection between the muffler, bearing 200, and cylinder assembly. Since the second connecting segment 132 is an inwardly recessed arc-shaped structure, an arc-shaped support surface naturally forms on both sides. When the fastener passes through the fastening hole 2002 on the bearing 200 and connects to the cylinder assembly, this arc-shaped support surface provides good limiting and support for the fastener head, preventing slippage or misalignment during assembly, thereby improving the stability and reliability of the connection between the muffler, bearing 200, and cylinder assembly.

[0088] The above are merely exemplary embodiments of this utility model and do not limit the patent scope of this utility model. Any equivalent structural transformations made based on the technical concept of this utility model and the contents of this utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this utility model.

Claims

1. A silencer, characterized in that, For use in a compressor, the compressor including a bearing having an air inlet, the muffler including: A housing, fitted onto the bearing; A separator, disposed within the housing, is used to divide the inner cavity of the housing into a first silencing chamber, a second silencing chamber, and a third silencing chamber. The first silencing chamber communicates with the air inlet. The second silencing chamber communicates with both the first and third silencing chambers. The second and third silencing chambers are located on the side of the first silencing chamber away from the bearing. The second silencing chamber is located around the third silencing chamber. The housing is provided with an exhaust port communicating with the third silencing chamber.

2. The silencer as described in claim 1, characterized in that, The height ratio of the second silencing cavity to the first silencing cavity in the axial direction of the bearing is not less than 0.3 and not greater than 0.

6.

3. The silencer as described in claim 1, characterized in that, The separator includes a separator plate and a separator portion disposed on the separator plate. The separator plate is used to divide the inner cavity of the housing into a first cavity and a second cavity. The first cavity is the first silencing cavity. The separator portion is used to divide the second cavity into a second silencing cavity and a third silencing cavity.

4. The silencer as described in claim 3, characterized in that, The housing has an open end, a top plate opposite the open end, and a side plate extending from the periphery of the top plate toward the open end. A partition plate is disposed opposite to the top plate, and a partition portion is provided between the partition plate and the top plate. The partition plate and the side plate are used to enclose the bearing to form the first silencing cavity. A mounting cylinder for the shaft of the bearing to pass through is also provided between the partition plate and the top plate. The mounting cylinder has a first outer wall and a second outer wall connected end to end along the circumference of the bearing. The first outer wall, the outer wall of the partition portion, the partition plate, the side plate, and the top plate enclose the second silencing cavity. The second outer wall, the partition plate, the inner wall of the partition portion, and the top plate enclose the third silencing cavity.

5. The silencer as described in claim 4, characterized in that, The side plate includes five first connecting segments arranged circumferentially along the bearing. Each first connecting segment protrudes toward the side away from the center of the housing to form a first recess that opens toward the center of the housing. The partition has three or four protrusions on the side facing the side plate. Each of the protrusions is respectively provided in a one-to-one correspondence with a corresponding number of the first connecting segments and is partially embedded in the corresponding first recess.

6. The silencer as described in claim 5, characterized in that, The volume ratio of the second silencing cavity to the third silencing cavity is not less than 0.6 and not greater than 1.

2.

7. The silencer as described in claim 3, characterized in that, The partition plate is provided with a first vent hole, which connects the first silencing cavity and the second silencing cavity. And / or, the partition is provided with a second vent hole, which connects the second silencing chamber and the third silencing chamber.

8. The muffler as described in claim 7, characterized in that, A plane perpendicular to the axis of the air intake hole is defined as a reference plane, and the line connecting the projection of the axis of the air intake hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the first connecting line. The line connecting the projection of the axis of the first vent hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the second line, and the angle between the second line and the first line is not less than 120 degrees and not greater than 145 degrees. And / or, the line connecting the projection of the axis of the second vent hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is a third line, and the angle between the third line and the first line is not less than 5 degrees and not greater than 27 degrees.

9. The silencer as described in claim 7, characterized in that, Define the plane perpendicular to the axis of the air intake as the reference plane; The line connecting the projection of the axis of the first vent hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the second line. The exhaust hole includes a first exhaust hole and a second exhaust hole, which are arranged on both sides of the second line.

10. The silencer as described in claim 9, characterized in that, The first exhaust port and the second exhaust port are symmetrically arranged about the second connecting line.

11. The silencer as described in claim 9, characterized in that, The line connecting the projection of the axis of the air intake hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the first connecting line. The line connecting the projection of the axis of the first exhaust hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is the fourth line, and the angle between the fourth line and the first line is not less than 50 degrees and not more than 65 degrees. And / or, the line connecting the projection of the axis of the second exhaust hole onto the reference plane and the projection of the axis of the bearing onto the reference plane is a fifth line, and the angle between the fifth line and the first line is not less than 190 degrees and not greater than 215 degrees.

12. The silencer as described in claim 9, characterized in that, The ratio of the sum of the opening areas of the first exhaust port and the second exhaust port to the opening area of ​​the air inlet port is not less than 0.4 and not less than 1.

1.

13. The silencer as described in claim 7, characterized in that, The ratio of the opening area of ​​the first vent to the opening area of ​​the air inlet is not less than 0.2 and not greater than 0.

65. And / or, the ratio of the opening area of ​​the second vent to the opening area of ​​the air inlet is not less than 0.3 and not greater than 0.

7.

14. A compressor, characterized in that, The compressor includes: The bearing is equipped with an air inlet. The muffler as described in any one of claims 1 to 13, wherein the muffler is sleeved on the bearing, and the first muffler chamber of the muffler is in communication with the air inlet; Crankshaft; A cylinder having a working chamber, the bearing being located on one side of the cylinder and sleeved around the crankshaft, and the muffler being located on the side of the bearing opposite to the cylinder; The piston is eccentrically rotatably disposed within the working chamber and sleeved around the crankshaft; An electric motor is connected to the crankshaft drive to drive the crankshaft to rotate.

15. The compressor as claimed in claim 14, characterized in that, The muffler includes a housing and a partition. A mounting cylinder is provided between the partition plate of the partition and the top plate of the housing. The bearing has a shaft passing through the mounting cylinder, and the axial height of the shaft is greater than the axial height of the housing.

16. The compressor as claimed in claim 14, characterized in that, The muffler's side plate includes five second connecting sections arranged circumferentially along the bearing. Each second connecting section is recessed toward the center of the housing to form a second cavity opposite to the center opening of the housing. The bearing is provided with fastening holes for fasteners to pass through at the positions corresponding to each second cavity.

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