Silencer for compressor, compressor and air conditioner

Abstract

The application relates to a silencer for a compressor, a compressor and an air conditioner, and belongs to the technical field of air conditioners. The silencer for the compressor comprises a body, a silencing cavity is arranged in the body, the body comprises a first end and a second end which are oppositely arranged, the first end is provided with a first mounting surface, the first mounting surface can be connected with a bearing provided with an exhaust valve plate, a limiting portion is protrudingly arranged on the surface of the body facing the bearing, the limiting portion is configured to be oppositely arranged with the exhaust valve plate, and the limiting portion can limit the opening range of the exhaust valve plate. The structure design that the limiting portion is protrudingly arranged on the surface of the body facing the pump body enables the body of the silencer to cooperate with the limiting portion to limit the opening range of the exhaust valve plate, so that the rigidity of the limiting portion can be improved, the first-order natural frequency of the limiting portion can be improved, and the noise of the compressor during operation can be reduced.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, and in particular to a muffler for a compressor, a compressor, and an air conditioner. Background Technology

[0002] The muffler in an air conditioner compressor plays a role in vibration reduction and noise reduction. However, during the operation of the compressor, the limiter used to limit the opening range of the exhaust valve is prone to damping vibration at the first natural frequency under the periodic impact of the exhaust valve on the limiter. This results in high compressor noise, affects the noise reduction effect of the muffler, and affects the user experience. Summary of the Invention

[0003] In view of this, this application provides a muffler for a compressor, a compressor, and an air conditioner, which can improve the noise reduction effect of the muffler for the compressor.

[0004] In a first aspect, embodiments of this application provide a compressor muffler, the compressor muffler comprising: a body having a muffler cavity therein, the body having a first end and a second end disposed opposite to each other, the first end having a first mounting surface configured to connect with a bearing having an exhaust valve plate; the body having a limiting portion protruding from the surface of the bearing, the limiting portion being configured to be disposed opposite to the exhaust valve plate, the limiting portion being configured to abut against the exhaust valve plate to limit the opening range of the exhaust valve plate.

[0005] Optionally, the limiting portion protrudes from the first mounting surface; or, the limiting portion protrudes from the surface of the second end facing the pump body.

[0006] Optionally, the first end is provided with a mounting part, and the side of the mounting part opposite to the second end forms the first mounting surface; the second end is provided with an exhaust hole communicating with the silencing cavity.

[0007] Optionally, the limiting portion includes a limiting section and a connecting section. The limiting section is configured to extend along the length direction of the exhaust valve plate, and the connecting section is configured to extend along the thickness direction of the exhaust valve plate. The limiting section is connected to the body through the connecting section, and the limiting portion is configured to limit the opening range of the exhaust valve plate through the limiting section. Along the extending direction of the limiting section, the length L of the limiting section is 5mm to 10mm, or the length L of the limiting section is 15mm to 30mm.

[0008] Optionally, along the extension direction of the limiting segment, the height of the connecting segment connected to one end of the limiting segment is H1, 4mm≤H1≤6mm, and the height of the connecting segment connected to the other end of the limiting segment is H2, 1mm≤H2≤1.8mm.

[0009] Optionally, the limiting part is integrally formed with the body; the first natural frequency of the limiting part is 5000Hz~30000Hz.

[0010] Optionally, the first natural frequency of the limiting part is 10000Hz~24000Hz.

[0011] Secondly, embodiments of this application provide a compressor, comprising: a pump body including a cylinder and a bearing disposed at one end of the cylinder, the cylinder having a compression chamber, the bearing having an exhaust port communicating with the compression chamber, the bearing having a second mounting surface; an exhaust valve plate disposed on the second mounting surface, the exhaust valve plate covering the exhaust port; and a compressor muffler as described in the first aspect, the body being fastened to the second mounting surface, the limiting portion being disposed opposite to the exhaust valve plate; wherein the exhaust valve plate is configured to be able to swing to open the exhaust port, and the limiting portion is configured to abut against the exhaust valve plate to limit the opening range of the exhaust valve plate.

[0012] Optionally, the exhaust valve plate includes a fixed end and a free end disposed opposite to each other. The fixed end is connected to the second mounting surface, and the free end covers the exhaust port. The free end is configured to swing relative to the fixed end to open the exhaust port, so that the exhaust port communicates with the silencing cavity. The limiting portion is configured to abut against the free end to limit the opening range of the free end.

[0013] Optionally, along the extending direction of the exhaust valve plate, the exhaust valve plate includes a first segment, a second segment, and a third segment connected in sequence, the first segment forming the fixed end and the third segment forming the free end; the limiting portion has a limiting surface facing the exhaust valve plate, the limiting surface being configured to be opposite to the third segment, or the limiting surface being configured to be opposite to the second segment and the third segment.

[0014] Optionally, the compressor further includes a limiting plate, which is disposed on the side of the exhaust valve plate opposite to the second mounting surface. The limiting plate and the limiting portion are arranged at intervals along the extending direction of the exhaust valve plate. The limiting plate covers the first segment and the second segment and is connected to the first segment, and the limiting surface of the limiting portion is disposed opposite to the third segment. Alternatively, the limiting plate covers and is connected to the first segment, and the limiting surface of the limiting portion is disposed opposite to the second segment and the third segment.

[0015] Optionally, a groove is provided on the second mounting surface, the exhaust valve plate is disposed on the inner bottom wall of the groove, and the limiting plate is disposed on the side of the exhaust valve plate opposite to the inner bottom wall; the limiting part protrudes from the first mounting surface, and the limiting surface of the limiting part is located inside the groove.

[0016] Optionally, the width of the area covering the exhaust port by the free end of the exhaust valve plate is W mm; the limiting part includes a limiting section and a connecting section, the limiting section is configured to extend along the length direction of the exhaust valve plate, the connecting section is configured to extend along the thickness direction of the exhaust valve plate, the limiting section is connected to the body through the connecting section, the side of the limiting section facing the exhaust valve plate forms the limiting surface, and the limiting part limits the opening range of the exhaust valve plate through the limiting section; the width of the portion of the limiting section opposite to the exhaust port is W1 mm; satisfying: W-2mm≤W1≤W+2mm.

[0017] Optionally, the distance between the limiting surface and the exhaust valve plate is H mm along the thickness direction of the exhaust valve plate; along the extension direction of the exhaust valve plate, the value of H increases from the end closer to the fixed end to the end farther away from the fixed end.

[0018] Thirdly, embodiments of this application provide an air conditioner, including the compressor described in the second aspect.

[0019] This application provides a compressor muffler, a compressor, and an air conditioner. The compressor muffler includes a body with a silencing cavity inside. The body includes a first end and a second end disposed opposite to each other. The first end has a first mounting surface configured to connect with a bearing having an exhaust valve plate. A limiting part protrudes from the surface of the body facing the bearing and is configured to be disposed opposite to the exhaust valve plate. The limiting part is configured to abut against the exhaust valve plate to limit the opening range of the exhaust valve plate. The structural design of the limiting part protruding from the surface of the body facing the bearing allows the muffler body and the limiting part to cooperate in limiting the opening range of the exhaust valve plate, thereby increasing the stiffness of the limiting part, increasing the first natural frequency of the limiting part, and reducing the risk of resonance between the exhaust valve plate and the limiting part caused by the excitation frequency of the impact excitation generated by the exhaust valve plate impacting the limiting part being close to or equal to the first natural frequency of the limiting part. Moreover, the structural design of the limiting part protruding from the body can extend the transmission path of vibration caused by the swing of the exhaust valve plate, improve the noise reduction effect of the compressor muffler, and thus reduce the noise of the compressor during operation. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of a first structure of a compressor silencer provided in an embodiment of this application;

[0021] Figure 2 for Figure 1 A sectional view;

[0022] Figure 3 This is a schematic diagram of a second structure of a compressor silencer provided in an embodiment of this application;

[0023] Figure 4 for Figure 3 A sectional view;

[0024] Figure 5 A cross-sectional structural diagram of the first structure of the compressor provided in the embodiments of this application;

[0025] Figure 6 This is a cross-sectional structural diagram of a second structure of the compressor provided in an embodiment of this application;

[0026] Figure 7 for Figure 5 The diagram shown is a partial structural schematic of the compressor.

[0027] Figure 8 This is an exploded structural diagram of the compressor muffler, limiting plate, exhaust valve plate and bearing assembly of the first structure provided in the embodiments of this application;

[0028] Figure 9 This is a cross-sectional structural diagram of the compressor muffler, limiting plate, exhaust valve plate and bearing assembly of the first structure provided in the embodiments of this application;

[0029] Figure 10 This is an exploded structural diagram of the compressor muffler, limiting plate, exhaust valve plate and bearing assembly of the second structure provided in the embodiments of this application;

[0030] Figure 11 This is a cross-sectional structural diagram of the compressor muffler, limiting plate, exhaust valve plate and bearing assembly of the second structure provided in the embodiments of this application;

[0031] Figure 12 This is a cross-sectional structural diagram of the compressor muffler, limiting plate, exhaust valve plate and bearing assembly of the third structure provided in the embodiments of this application;

[0032] Figure 13 This is a schematic diagram of the structure of the exhaust valve plate in the compressor provided in the embodiment of this application.

[0033] Explanation of reference numerals in the attached figures

[0034] 100. Silencer for compressors;

[0035] 10. Body; 101. Silencing cavity; 11. First end; 111. First mounting surface; 112. Mounting part; 1121. Second mounting hole; 12. Second end; 120. Exhaust hole; 13. Recessed part;

[0036] 20. Limiting part; 201. Limiting surface; 21. Limiting segment; 21a. First limiting segment; 21b. Second limiting segment; 22. Connecting segment;

[0037] 200. Compressor;

[0038] 210. Pump body; 211. Cylinder; 2110. Compression chamber; 2111. Piston; 212. Bearing; 2120. Exhaust port; 2121. Second mounting surface; 2122. Groove; 2123. First fixing hole; 2124. Second fixing hole; 2125. Hub; 213. Eccentric crankshaft; 214. Partition plate;

[0039] 220, Exhaust valve plate; 2201, First section; 2202, Second section; 2203, Third section; 221, Fixed end; 2211, First mounting hole; 222, Free end;

[0040] 230. Limiting plate; 231. Connecting end; 2311. Connecting hole; 232. Raised end;

[0041] 240. Housing; 241. First air inlet; 242. First air outlet;

[0042] 250. Liquid reservoir; 251. Second air inlet; 252. Second air outlet;

[0043] 260. Motor; 261. Stator; 262. Rotor. Detailed Implementation

[0044] To make the technical solution and beneficial effects of this application more apparent and understandable, a detailed description is provided below by listing specific embodiments. The accompanying drawings are not necessarily drawn to scale, and local features may be enlarged or reduced to more clearly show the details of the local features; unless otherwise defined, the technical and scientific terms used herein have the same meanings as those in the technical field to which this application pertains.

[0045] In this application, the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "height," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the purpose of simplifying the description of this application and do not indicate that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. In other words, they should not be construed as limitations on this application.

[0046] In this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating the relative importance of the indicated features or the number of indicated technical features. Therefore, a feature specified as "first" or "second" may explicitly include at least one of those features. In this application, "multiple" means at least two, such as two, three, etc.; "several" means at least one, such as one, two, three, etc., unless otherwise explicitly specified.

[0047] In this application, unless otherwise expressly defined, the terms "installation," "connection," "linking," "fixing," "setting," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral part; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can also refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0048] In this application, unless otherwise expressly defined, the terms "above," "on top of," "over," "above," "below," "below," "below," or "below" for "first feature over second feature" can refer to the first and second features being in direct contact, or to the first and second features being in indirect contact through an intermediate medium. Furthermore, "above," "over," and "below" for "first feature over second feature" can mean the first feature is directly above or diagonally above the second feature, or simply indicates that the horizontal height of the first feature is higher than the horizontal height of the second feature. Similarly, "below," "below," and "below" for "first feature over second feature" can mean the first feature is directly below or diagonally below the second feature, or simply indicates that the horizontal height of the first feature is lower than the horizontal height of the second feature.

[0049] In some embodiments of this application, a compressor muffler 100 is provided, see reference Figures 1-4The compressor silencer 100 includes a body 10 and a limiting part 20. The body 10 has a silencer cavity 101 inside. The body 10 includes a first end 11 and a second end 12 disposed opposite to each other. The first end 11 is provided with a first mounting surface 111, which is configured to be connected to a bearing 212 having an exhaust valve plate 220.

[0050] Reference Figures 1-4 A limiting part 20 is provided on the surface of the main body 10 facing the bearing 211. The limiting part 20 is configured to be disposed opposite to the exhaust valve plate 220 and is configured to abut against the exhaust valve plate 220 to limit the opening range of the exhaust valve plate 220.

[0051] The compressor in an air conditioner is the "heart" of the refrigeration cycle. Its core principle is to compress a low-temperature, low-pressure gaseous refrigerant into a high-temperature, high-pressure gaseous refrigerant through mechanical work, creating the necessary conditions for the refrigerant to release heat to the outside in the subsequent condenser. Specifically, the evaporator absorbs indoor heat and exchanges heat with the low-temperature, low-pressure liquid refrigerant inside, causing the low-temperature, low-pressure liquid refrigerant to evaporate into a low-temperature, low-pressure gaseous refrigerant. The compressor draws the low-temperature, low-pressure gaseous refrigerant output from the evaporator into the pump body. The pump body compresses the low-temperature, low-pressure gaseous refrigerant, causing it to undergo a phase change, becoming a high-temperature, high-pressure gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant is discharged through the pump body's exhaust port to the condenser, where it exchanges heat with the outside air, causing the high-temperature, high-pressure gaseous refrigerant to undergo another phase change, becoming a medium-temperature, high-pressure liquid refrigerant, thus releasing heat.

[0052] An exhaust valve plate 220 is installed on the bearing 212 of the pump body 210 in the compressor 200. The exhaust valve plate 220 covers the exhaust port 2120 of the bearing 212. The exhaust valve plate 220 functions similarly to a one-way valve in the heart. Its core function is to control the one-way discharge of the high-temperature and high-pressure gaseous refrigerant from the compression chamber 2110 of the cylinder 211 in the pump body 210 and prevent backflow. Specifically, during the compression of the low-temperature and low-pressure gaseous refrigerant in the compression chamber 2110 of the cylinder 211 in the pump body 210, the gas pressure in the compression chamber 2110 is higher than the gas pressure in the exhaust chamber of the compressor 200. The high-temperature and high-pressure gaseous refrigerant generated in the compression chamber 2110 impacts the exhaust valve plate 220 under the action of the pressure difference to be discharged from the compression chamber 2110. At the end of the compression stroke or the beginning of the intake stroke, the gas pressure in the exhaust chamber is higher than the gas pressure in the compression chamber 2110 inside the cylinder 211. At this time, the exhaust valve plate 220 seals the exhaust port 2120 and adheres to the bearing 212 under the action of its own elasticity and gas pressure difference, forming a seal to prevent the discharged high-temperature and high-pressure gaseous refrigerant from flowing back into the compression chamber 2110 of the cylinder 211.

[0053] During the process of discharging high-temperature and high-pressure gaseous refrigerant from the compression chamber 2110, if the exhaust valve plate 220 is opened excessively under the impact of the high-temperature and high-pressure gaseous refrigerant, the exhaust valve plate 220 may fail to return to the sealed state of covering the exhaust port 2120 and adhering to the bearing 212 at the end of the compression stroke or the beginning of the suction stroke, causing the discharged high-temperature and high-pressure gaseous refrigerant to flow back into the compression chamber 2110 of the cylinder 211.

[0054] To prevent the exhaust valve plate 220 from opening excessively, a limiter (not shown in the figure) is usually provided on the side of the exhaust valve plate 220 away from the bearing 212 to limit the opening range of the exhaust valve plate 220. The limiter is plate-shaped, with one end fixed to the bearing 212 and the other end raised. The exhaust valve plate 220 moves between the limiter and the bearing 212, and the opening range of the exhaust valve plate 220 is limited by the raised part of the limiter. However, during the operation of the compressor 200, the exhaust valve plate 220 will rapidly and repeatedly impact the limiter under the impact and pushing action of the high-temperature and high-pressure gaseous refrigerant. Specifically, when the gas pressure in the compression chamber 2110 of the cylinder 211 is balanced with the gas pressure in the exhaust chamber, the exhaust valve plate 220 will rebound at high speed under its own elastic force. When the gas pressure in the compression chamber 2110 of the cylinder 211 is higher than the gas pressure in the exhaust chamber, resulting in a pressure difference, the exhaust valve plate 220 will re-impact the limiter under the impact and pushing action of the high-temperature and high-pressure gaseous refrigerant, thus forming repeated impacts on the limiter.

[0055] The vibration generated by the periodic impact of the exhaust valve plate 220 on the limit switch is ultimately radiated as audible noise. This process can be described by the frequency domain relationship in vibration theory, i.e., response = excitation force × frequency response function. The repeated impact of the exhaust valve plate 220 on the limit switch generates an impact excitation, and the impact force of the exhaust valve plate 220 on the limit switch is the excitation force. The behavior of the exhaust valve plate 220 impacting the limit switch manifests as periodic transient pulsations in the time domain, and the duration of the impact is extremely short (milliseconds or even microseconds; for example, when the compressor 200 rotates at 120Hz, the contact time is <1 / 120s), but the impact force on the limit switch is relatively large. The ideal instantaneous impact can be represented by the Dirac function, but the mixed frequency components cannot be directly separated from the time-domain signal. A Fourier transform is needed to obtain a frequency-domain signal with a wide frequency range. This ensures that the impact excitation of the exhaust valve plate 220 on the limiter is not a single-frequency excitation, but a wide-band pulse. That is, the excitation frequency domain of the impact excitation of the exhaust valve plate 220 on the limiter is wide-band. This wide-band pulse necessarily contains an excitation frequency equal to the first natural frequency of the limiter. Therefore, the frequency response function exhibits a sharp peak with a high amplitude at this excitation frequency. This means that when the external force excitation approaches the first natural frequency of the limiter, a significant vibration amplification effect will occur, thereby exciting the limiter to generate damped vibration at its first natural frequency. Therefore, the periodic impact of the exhaust valve plate 220 on the limiter effectively excites the limiter to generate damped vibration at its first natural frequency. This periodic impact (synchronized with the compressor speed) and the resulting structural transient response are one of the main sources of compressor exhaust noise.

[0056] The first natural frequency, also known as the fundamental frequency or first-order modal frequency, is the lowest natural frequency of an object or structure during free vibration. An object also possesses a second and a third natural frequency. The first natural frequency is the lowest, and because it requires the least amount of excitation energy, it is the easiest to excite under broadband random excitations (such as impacts or turbulence).

[0057] The muffler in the compressor is mounted on bearing 212. Through a specific acoustic structural design, it attenuates or reflects noise waves without significantly obstructing gas flow, thereby improving the overall noise performance of the compressor. However, because the exhaust valve plate 220 periodically impacts the limiter, generating impact excitation, the limiter undergoes damped free vibration (i.e., transient response) at its first natural frequency after each impact. The muffler's attenuation effect on the structural radiated noise directly generated by this impact excitation is poor, resulting in high compressor noise and affecting the user experience.

[0058] The compressor muffler 100 provided in this application embodiment includes a body 10 and a limiting part 20. The body 10 has a muffler cavity 101 inside. The first end 11 of the body 10 is provided with a first mounting surface 111. The first mounting surface 111 is configured to be connected to a bearing 212 having an exhaust valve plate 220. The limiting part 20 protrudes from the surface of the body 10 facing the bearing 212. The limiting part 20 is configured to be opposite to the exhaust valve plate 220 provided on the bearing 212. The limiting part 20 can abut against the exhaust valve plate 220 to limit the opening range of the exhaust valve plate 220. This allows the limiting part 20 to replace the limiter in the traditional compressor to limit the opening range of the exhaust valve plate 220. Moreover, the structural design of the limiting part 20 protruding from the surface of the body 10 facing the bearing 212 makes the body 10 and the limiting part 20 form an integral whole to cooperate in limiting the opening range of the exhaust valve plate 220, thereby improving the overall rigidity of the limiting part 20 and increasing the first natural frequency of the limiting part 20.

[0059] When the exhaust valve plate 220 impacts the limiting part 20 and generates an impact excitation, this impact excitation is a wideband pulse. The frequency spectrum of the pulse covers a continuous range from zero to higher frequencies. After Fourier transform, the shorter the pulse duration, the wider the frequency spectrum. Therefore, the pulse spectrum still contains an excitation frequency component equal to the first natural frequency of the limiting part 20. Due to the structural design of connecting the limiting part 20 to the body 10 in this embodiment, the first natural frequency of the limiting part 20 is increased. The impact of the exhaust valve plate 220 on the limiting part 20 will generate a wideband impact excitation, and its spectral energy will significantly decrease as the frequency increases. After increasing the first natural frequency of the limiting part 20, the energy of the excitation component corresponding to the first natural frequency is weaker, which can prevent the limiting part 20 from resonating and amplifying, thereby achieving noise reduction of the compressor 200.

[0060] In addition, the structural design of the limiting part 20 protruding from the surface of the body 10 facing the bearing 212 makes the body 10 and the limiting part 20 form an integral whole. The vibration generated by the exhaust valve plate 220 impacting the limiting part 20 can be transmitted to the body 10 through the limiting part 20, thereby attenuating the vibration generated by the exhaust valve plate 220 impacting the limiting part 20 and improving the noise reduction effect of the compressor muffler 100.

[0061] In addition, the traditional compressor uses a limiter to restrict the opening range of the exhaust valve plate. This results in a short vibration transmission path for the vibration caused by the exhaust valve plate impacting the limiter: exhaust valve plate - limiter - pump body bearing - compressor housing. This is not conducive to the dissipation of vibration energy.

[0062] In the compressor muffler 100 provided in this application embodiment, the limiting part 20 is designed to protrude from the surface of the body 10 facing the bearing 212. When the exhaust valve plate 220 is opened, it abuts against the limiting part 20, so that the transmission path of the vibration caused by the exhaust valve plate 220 impacting the limiting part 20 is exhaust valve plate 220-limiting part 20-body 10-bearing 212-compressor 200 housing 240. This extends the vibration transmission path, which is beneficial to the dissipation of vibration energy and improves the vibration attenuation effect of the compressor muffler 100.

[0063] In some embodiments, refer to Figures 1-4 as well as Figure 9 and Figure 11 The limiting part 20 protrudes from the first mounting surface 111. The structural design of the limiting part 20 protruding from the first mounting surface 111 allows the vibration generated by the exhaust valve plate 220 impacting the limiting part 20 to be transmitted along the side wall of the body 10 to the second end 12, thereby extending the vibration transmission path, improving the vibration attenuation effect of the compressor silencer 100, and improving the noise reduction effect of the compressor 200.

[0064] In some embodiments, refer to Figure 12 The limiting part 20 protrudes from the surface of the second end 12 facing the bearing 212. This structural design allows the limiting part 20 to be located within the silencing cavity 101 of the main body 10, thereby improving the space utilization of the silencing cavity 101. Furthermore, it allows the vibration generated by the exhaust valve plate 220 impacting the limiting part 20 to be transmitted from the second end 12 through the side wall of the main body 10 to the first end 11 and the bearing 212 of the pump body 210, thus extending the vibration transmission path, facilitating the dissipation of vibration energy, and improving the vibration damping effect of the compressor silencer 100.

[0065] In some embodiments, refer to Figures 1-4 The first end 11 is provided with a mounting part 112, and the side of the mounting part 112 facing away from the second end 12 forms a first mounting surface 111. The structural design of the mounting part 112 on the first end 11 of the body 10 can improve the connection stability between the body 10 and the bearing 212 of the pump body 210, and can ensure the sealing between the first mounting surface 111 and the bearing 212, preventing the gas discharged from the exhaust port 2120 from leaking through the gap between the first mounting surface 111 and the bearing 212, and ensuring the noise reduction effect of the compressor silencer 100.

[0066] In some embodiments, refer to Figures 1-4The second end 12 has an exhaust port 120 communicating with the silencing cavity 101. The structural design of the exhaust port 120 at the second end 12 of the main body 10 allows the high-temperature, high-pressure gaseous refrigerant discharged from the exhaust port 2120 of the pump body 210 to be discharged into the exhaust cavity of the compressor 200 via the exhaust port 120. This also extends the exhaust path of the high-temperature, high-pressure gaseous refrigerant in the silencing cavity 101, improving the attenuation and reflection effect of the compressor silencer 100 during the discharge of the high-temperature, high-pressure gaseous refrigerant, thus enhancing the noise reduction effect on the compressor 200. (Refer to...) Figures 1-3 The exhaust port 120 is located in the middle of the second end 12, forming an intermediate exhaust.

[0067] In some embodiments, refer to Figure 2 , Figure 4 and Figure 12 The limiting part 20 includes a limiting section 21 and a connecting section 22, as shown in the figure. Figure 9 , Figure 11 and Figure 12 The limiting section 21 is configured to extend along the length direction of the exhaust valve plate 220, the connecting section 22 is configured to extend along the thickness direction of the exhaust valve plate 220, the limiting section 21 is connected to the body 10 through the connecting section 22, and the limiting part 20 is configured to limit the opening range of the exhaust valve plate 220 through the limiting section 21.

[0068] Reference Figure 9 and Figure 12 Along the extension direction of the limiting segment 21, the length L of the limiting segment 21 is 5mm~10mm. The first natural frequency of the limiting part 20 is negatively correlated with its length; that is, the longer the limiting part 20 is, the lower the first natural frequency, and vice versa. The length L of the limiting segment 21 is within the range of 5mm~10mm, making the limiting segment 21 and the limiting part 20 relatively short. This results in relatively high rigidity for the limiting part 20, giving it a relatively high first natural frequency. When the exhaust valve plate 220 impacts the limiting part 20, it generates a wide-band impact excitation, the spectral energy of which attenuates significantly with increasing frequency. By increasing the first natural frequency of the limiting part 20, the energy of the excitation component corresponding to this first natural frequency is weaker, which can prevent the limiting part 20 from resonating and amplifying, thereby reducing noise in the compressor 200.

[0069] In some embodiments, refer to Figure 11The length L of the limiting section 21 is 15mm to 30mm. The length L of the limiting section 21 being within the range of 15mm to 30mm ensures that the limiting part 20 has a high first-order natural frequency and can increase the length of the exhaust valve plate 220 corresponding to the limiting section 21, thereby improving the limiting effect on the opening amplitude of the exhaust valve plate 220. This prevents the exhaust valve plate 220 from opening too wide, affecting the speed at which the exhaust valve plate 220 returns to the closed exhaust port 2120. It ensures that the exhaust valve plate 220 returns to the sealed exhaust port 2120 and adheres to the bearing 212 in a timely manner at the end of the compression stroke or the beginning of the intake stroke, preventing the discharged high-temperature, high-pressure gaseous refrigerant from flowing back into the compression chamber 2110 of the cylinder 211.

[0070] In some embodiments, refer to Figure 4 Along the extension direction of the limiting segment 21, the height of the connecting segment 22 connected to one end of the limiting segment 21 is H1, 4mm≤H1≤6mm, and the height of the connecting segment 22 connected to the other end of the limiting segment 21 is H2, 1mm≤H2≤1.8mm. This structural design, with 4mm≤H1≤6mm and 1mm≤H2≤1.8mm, ensures that H2 < H1, resulting in an inclined slope design for the limiting surface 201. This design limits the opening range of the exhaust valve plate 220 while preventing fatigue fracture due to stress concentration, thus extending the service life of the exhaust valve plate 220. In other implementations, the shape of the limiting surface 201 can be a smoothly transitioned curved surface, a plane, or a composite surface composed of a plane and a curved surface, thereby preventing fatigue fracture of the exhaust valve plate 220 due to stress concentration. In other implementations, the contact between the limiting surface 201 and the free end 222 can be point contact or line contact.

[0071] In some embodiments, refer to Figure 4 The thickness S1 of the body 10 is 0.5mm to 2.5mm. This structural design, where the thickness S1 of the body 10 is 0.5mm to 2.5mm, ensures the stability of the connection between the body 10 and the bearing 212 of the pump body 210 via the mounting part 112, thereby ensuring the stability of the connection between the compressor silencer 100 and the bearing 212. Here, S1 of 0.5mm to 2.5mm refers to the average thickness of the body 10. The body 10 is formed by stamping from a single flat plate, and after forming, the thickness of the sidewalls and the second end 12 of the body 10 is lower than the thickness of the mounting part 112.

[0072] In some embodiments, refer to Figure 4The thickness S2 of the limiting section 21 is 0.5mm to 2.5mm. The first natural frequency of the limiting section 20 is related to its thickness. In one example, the thicker the limiting section 20, the higher its first natural frequency; conversely, the thinner the limiting section 20, the lower its first natural frequency. The structural design of the limiting section 21 with a thickness S2 of 0.5mm to 2.5mm ensures the structural rigidity of the limiting section 20, thereby increasing its first natural frequency. The exhaust valve plate 220 impacting the limiting section 20 generates a wide-band impact excitation, the spectral energy of which significantly decreases with increasing frequency. By increasing the first natural frequency of the limiting section 20, the excitation component energy corresponding to this first natural frequency is weaker, which can prevent the limiting section 20 from resonating and amplifying, thus achieving noise reduction for the compressor 200.

[0073] In some embodiments, the limiting part 20 is integrally formed with the body 10. Specifically, it can be formed in one step by stamping, casting, or injection molding. In one example, the compressor muffler 100 is manufactured by providing a plate, stamping a muffler cavity 101 on one side of the plate, and stamping a limiting part 20 on the other side of the plate. The structural design of the limiting part 20 being integrally formed with the body 10 can eliminate assembly errors between parts, thereby improving the structural rigidity and reliability of the limiting part 20. In addition, the structural design of the limiting part 20 being integrally formed with the body 10 allows for noise reduction while limiting the opening range of the exhaust valve plate 220, reducing the number of parts in the compressor 200 and lowering processing costs.

[0074] In some embodiments, the first natural frequency of the limiting part 20 is 5000Hz to 30000Hz. Since the first natural frequency of the limiting part 20 is within the range of 5000Hz to 30000Hz, the limiting part 20 has a relatively high first natural frequency. When the exhaust valve plate 220 impacts the limiting part 20, it generates a wide-band impact excitation, the spectral energy of which significantly decreases as the frequency increases. By increasing the first natural frequency of the limiting part 20, the excitation component energy corresponding to this first natural frequency is weaker, which can prevent the limiting part 20 from resonating and amplifying, thereby achieving noise reduction for the compressor 200.

[0075] Furthermore, in traditional compressors, the cantilever beam structure used for the limiter to restrict the opening amplitude of the exhaust valve plate 220 has a first-order natural frequency of 1600Hz~2500Hz. When the exhaust valve plate 220 impacts the limiter, the excitation frequency in the pulse spectrum that is equal to the first-order natural frequency of the limiter is low, the energy amplitude of the frequency is high, and the excitation energy of the excitation frequency is strong, causing the limiter to resonate and amplify, resulting in high compressor noise. However, the compressor muffler 100 provided in this application has a first-order natural frequency of the limit part 20 in the range of 5000Hz~30000Hz, which is significantly higher than the first-order natural frequency of the limiter. The impact of the exhaust valve plate 220 on the limit part 20 will form a wide-band impact excitation, and its spectral energy will significantly decrease as the frequency increases. By increasing the first-order natural frequency of the limit part 20, the excitation component energy corresponding to the first-order natural frequency is weaker, which can avoid the limit part 20 from resonating and amplifying, thereby achieving noise reduction of the compressor 200.

[0076] In some embodiments, the first natural frequency of the limiting portion 20 is 10000Hz to 24000Hz.

[0077] In some embodiments, refer to Figure 2 , Figure 8 and Figure 10 The body 10 has recesses 13 formed on its sidewalls. These recesses 13 create at least two interconnected cavities within the silencing cavity 101, thereby improving the noise reduction effect of the compressor silencer 100. In one example, there are five recesses 13, spaced apart along the circumferential direction of the body 10, forming a five-lobed structure and creating five cavities within the silencing cavity 101 to increase energy dissipation from vibration transmission.

[0078] In some embodiments of this application, a compressor 200 is provided, with reference to... Figures 5-12 The compressor 200 includes: a pump body 210, an exhaust valve plate 220, and a compressor muffler 100 as described above.

[0079] Reference Figures 5-7 The pump body 210 includes a cylinder 211 and a bearing 212 disposed at one end of the cylinder 211. The cylinder 211 has a compression chamber 2110 inside. (Refer to...) Figure 7 , Figure 9 as well as Figures 11-12 The bearing 212 has an exhaust port 2120 that communicates with the compression chamber 2110, as shown in the reference. Figures 8-12 The bearing 212 has a second mounting surface 2121. Specifically, the second mounting surface 2121 is the surface of the bearing 212 that faces away from the compression chamber 2110. (Refer to...) Figure 9 , Figure 11 and Figure 12 An exhaust valve plate 220 is disposed on the second mounting surface 2121 and covers the exhaust port 2120. The body 10 of the compressor muffler 100 is fastened to the second mounting surface 2121, and a limiting portion 20 is disposed opposite to the exhaust valve plate 220. The exhaust valve plate 220 is configured to swing to open the exhaust port 2120, and the limiting portion 20 is configured to abut against the exhaust valve plate 220 to limit the opening range of the exhaust valve plate 220.

[0080] Specifically, refer to Figure 5 and Figure 6 The compressor 200 also includes a housing 240 and a receiver 250. The housing 240 is provided with a first inlet end 241 and a first outlet end 242. The first inlet end 241 of the housing 240 is connected to the receiver 250 through a pipeline. The second inlet end 251 of the receiver 250 is connected to the output end of an evaporator (not shown in the figure) to receive the low-temperature, low-pressure gaseous refrigerant output by the evaporator. The receiver 250, also known as a gas-liquid separator, is used to separate any liquid low-temperature, low-pressure refrigerant that may be drawn in, preventing liquid low-temperature, low-pressure refrigerant from entering the housing and damaging the compressor 200. The first outlet end 242 on the housing 240 is connected to a condenser (not shown in the figure) through a pipeline to deliver high-temperature, high-pressure gaseous refrigerant to the condenser. A pump body 210 is disposed in the housing 240, and a bearing 212 is connected to the inner wall of the housing 240.

[0081] The low-temperature, low-pressure gaseous refrigerant discharged from the second outlet 252 of the receiver 250 enters the housing 240 through the first inlet 241 and enters the compression chamber 2110 of the cylinder 211. The cylinder 211 compresses the low-temperature, low-pressure gaseous refrigerant, turning it into a high-temperature, high-pressure gaseous refrigerant. The high-temperature, high-pressure gaseous refrigerant is discharged to the condenser through the exhaust port 2120 of the bearing 212, the exhaust port 120 of the compressor silencer 100, and the first outlet 242 of the housing 240.

[0082] Among them, reference Figure 5 and Figure 6 The compressor 200 also includes a motor 260, which is disposed in the housing 240. The motor 260 includes a stator 261 and a rotor 262. The stator 261 is fixedly connected to the inner wall of the housing 240 to achieve fixed installation of the motor 260 in the housing 240.

[0083] Reference Figures 5-6The pump body 210 also includes an eccentric crankshaft 213, one end of which is inserted into the cylinder 211. A bearing 212 is fitted onto the eccentric crankshaft 213 via a hub 2125, which is inserted into the body 10. The eccentric crankshaft 213 extends outward from the hub 2125. A piston 2111 is provided in the compression chamber 2110 of the cylinder 211, and the piston 2111 is fitted onto the eccentric crankshaft 213 located in the compression chamber 2110. The motor 260 and the pump body 210 are arranged at intervals along the axial direction of the eccentric crankshaft 213, and the rotor 262 of the motor 260 is fitted onto the eccentric crankshaft 213.

[0084] When the stator 261 of the motor 260 is energized, it generates a magnetic pull. The rotor 262 of the motor 260 rotates under the magnetic pull of the stator 261, and drives the eccentric crankshaft 213 to rotate as well. The rotation of the eccentric crankshaft 213 drives the piston 2111 sleeved on it to make eccentric circular motion in the compression chamber 2110 of the cylinder 211. The eccentric crankshaft 213 drives the piston 2111 to rotate once to complete one exhaust, thereby compressing the low temperature and low pressure gaseous refrigerant that enters the compression chamber 2110. The high temperature and high pressure gaseous refrigerant generated after compression is discharged from the exhaust port 2120.

[0085] The compressor 200 provided in this application embodiment features a design where a limiting part 20 protrudes from the body 10 of the compressor muffler 100 on the side facing the bearing 212. This limiting part 20 replaces the limiter in a traditional compressor to restrict the opening range of the exhaust valve plate 220. Furthermore, the design of the limiting part 20 protruding from the surface of the body 10 facing the bearing 212 allows the body 10 and the limiting part 20 to cooperate in restricting the opening range of the exhaust valve plate 220, thereby increasing the overall rigidity of the limiting part 20 and raising its first natural frequency. The exhaust valve plate 220 impacting the limiting part 20 generates a wide-band impact excitation, the spectral energy of which significantly decreases with increasing frequency. By raising the first natural frequency of the limiting part 20, the excitation component energy corresponding to this first natural frequency is weaker, preventing resonance amplification in the limiting part 20 and thus achieving noise reduction in the compressor 200.

[0086] Furthermore, the structural design of the limiting part 20 protruding from the surface of the body 10 facing the bearing 212, when the exhaust valve plate 220 is opened, abuts against the limiting part 20, so that the transmission path of the vibration caused by the exhaust valve plate 220 impacting the limiting part 20 is exhaust valve plate 220 - limiting part 20 - body 10 - bearing 212 of pump body 210 - housing 240 of compressor 200, thereby extending the vibration transmission path and improving the energy dissipation of vibration.

[0087] In some embodiments, refer to Figures 8-11 as well as Figure 13The exhaust valve plate 220 includes a fixed end 221 and a free end 222 disposed opposite to each other. Specifically, the fixed end 221 and the free end 222 are disposed opposite to each other along the extending direction of the exhaust valve plate 220. The fixed end 221 is connected to the second mounting surface 2121, and the free end 222 covers the exhaust port 2120, forming a cap on the exhaust port 2120. In one example, the exhaust valve plate 220 is elongated, and the extending direction of the exhaust valve plate 220 is parallel to the length direction of the exhaust valve plate 220.

[0088] The free end 222 is configured to swing relative to the fixed end 221 to open the exhaust port 2120 so that the exhaust port 2120 communicates with the muffler 101, and the limiting part 20 is configured to abut against the free end 222 to limit the opening range of the free end 222.

[0089] Specifically, during the compression of the low-temperature, low-pressure gaseous refrigerant in cylinder 211, the gas pressure in compression chamber 2110 is higher than the gas pressure in the exhaust chamber of compressor 200. The high-temperature, high-pressure gaseous refrigerant generated in compression chamber 2110 impacts the free end 222 of exhaust valve plate 220 under the pressure difference, causing the free end 222 to swing relative to the fixed end 221 to open exhaust port 2120, allowing the high-temperature, high-pressure gaseous refrigerant to exit compression chamber 2110. At the end of the compression stroke or the beginning of the suction stroke, the gas pressure in the exhaust chamber is higher than the gas pressure in compression chamber 2110 of cylinder 211. At this time, under the action of its own elasticity and the gas pressure difference, the free end 222 of exhaust valve plate 220 returns to seal the exhaust port 2120, forming a seal and preventing the discharged high-temperature, high-pressure gaseous refrigerant from flowing back into compression chamber 2110 of cylinder 211. The exhaust chamber can be understood as the space in the housing 240 of the compressor 200 located between the bearing 212 and the first exhaust end 242 of the housing 240.

[0090] In some embodiments, refer to Figure 5 and Figure 7 The pump body 210 contains one cylinder 211, and the number of bearings 212, cylinders 211, and compressor silencers 100 corresponds one-to-one. The bearing 212 is located at the exhaust end of cylinder 211. Figure 5 and Figure 7 The compressor 200 shown is a single-cylinder rolling rotor compressor.

[0091] In some embodiments, refer to Figure 6The pump body 210 contains two cylinders 211, with a partition plate 214 between them. The exhaust ends of the two cylinders 211 are positioned opposite each other. Each cylinder 211 has a bearing 212 at its exhaust end, and each bearing 212 has a compressor silencer 100. This allows for simultaneous exhaust from both the upper and lower ends of the pump body 210. Figure 9 The compressor 200 shown is a twin-cylinder rolling rotor compressor, meaning that the pump body 210 includes two cylinders 211, two bearings 212 (i.e., a main bearing and a secondary bearing), and two compressor mufflers 100. Each bearing 212 is equipped with a corresponding compressor muffler 100. The two cylinders 211, two bearings 212, and two compressor mufflers 100 share a single eccentric crankshaft 213. (Refer to...) Figure 9 The bearing 212 of the first air outlet 242 adjacent to the housing 240 is connected to the inner wall of the housing 10, while the bearing 212 away from the first air outlet 242 is not connected to the housing 10 and is locked to the adjacent cylinder 211 by screws.

[0092] In some embodiments, refer to Figure 1 , Figure 3 , Figure 8 and Figure 10 The mounting portion 112 of the main body 10 has a plurality of second mounting holes 1121 that penetrate the mounting portion 112. The plurality of second mounting holes 1121 surround the main body 10 along the circumferential direction of the main body 10, as shown in the figure. Figure 8 and Figure 10 The bearing 212 has a plurality of second fixing holes 2124 on its second mounting surface 2121, with each second mounting hole 1121 corresponding to one of the second fixing holes 2124. The body 10 is fastened to the second mounting surface 2121, and a second fastener (not shown in the figure) is inserted into the second mounting hole 1121 and the second fixing hole 2124, so that the body 10 is connected to the second mounting surface 2121 through the mounting part 112. In one example, the second fastener is a rivet. In other examples, the second fastener can be a screw or a bolt, and this application embodiment does not make a specific limitation. In other implementations, the first mounting surface 111 and the second mounting surface 2121 can be fixed by means of snap-fit, welding, etc.

[0093] In some embodiments, refer to Figure 8 and Figure 10 Multiple second fixing holes 2124 surround the hub 2125 along the circumferential direction of the hub 2125. The body 10 of the compressor muffler 100 is covered by the second mounting surface 2121. The exhaust port 120 is sleeved on the hub 2125. One end of the hub 2125 extends to the outside of the second end 12 of the body 10. There is a gap between the exhaust port 120 and the hub 2125.

[0094] In some embodiments, the portion of the second end 12 of the body 10 surrounding the exhaust port 120 is formed by a flanging process to form a protruding ridge (not shown in the figure) around the exhaust port 120. The formation of the protruding ridge enhances the structural strength of the body 10 of the compressor silencer 100 and can guide the exhaust airflow formed by the high-temperature and high-pressure gaseous refrigerant.

[0095] In some embodiments, along the thickness direction of the exhaust valve plate 220, the opening range of the free end 222 of the exhaust valve plate 220 is 1mm to 3mm. That is, the maximum opening height of the free end 222 corresponding to the central axis of the exhaust port 2120 is 1mm to 3mm. Wherein, refer to... Figures 8-9 as well as Figure 12 The limiting part 20 has a circular cross-sectional shape, and the exhaust port 2120 has a circular cross-sectional shape. The exhaust port 2120 is arranged opposite to the limiting part 20. The distance between the center of the end face of the exhaust port 2120 near the second mounting surface 2121 and the center of the limiting part 20 is the maximum opening height of the exhaust valve plate 220.

[0096] In some embodiments, refer to Figures 8-9 as well as Figure 12 The opening radius of the free end 222 of the exhaust valve plate 220 is 1.8mm.

[0097] In some embodiments, refer to Figure 10 The fixed end 221 of the exhaust valve plate 220 has a first mounting hole 2211 that passes through the exhaust valve plate 220, as shown in the figure. Figure 9 , Figure 11 and Figure 12 A first fixing hole 2123 is provided on the second mounting surface 2121 of the bearing 212. The first mounting hole 2211 communicates with the first fixing hole 2123. A first fixing member (not shown in the figure) is inserted into the first mounting hole 2211 and the first fixing hole 2123 to fix the exhaust valve plate 220 on the second mounting surface 2121, so that the fixing end 221 is connected to the second mounting surface 2121. In one example, the first fixing member is a rivet. In other examples, the first fixing member can be a screw or a bolt, and this application embodiment does not make a specific limitation. In other implementations, the fixing end 221 can be fixed to the second mounting surface 2121 by means of snap-fit, welding, etc.

[0098] In some embodiments, refer to Figure 9 , Figure 11 and Figure 12Along the extending direction of the exhaust valve plate 220, the exhaust valve plate 220 includes a first segment 2201, a second segment 2202 and a third segment 2203 connected in sequence. The first segment 2201 forms the fixed end 221 of the exhaust valve plate 220, and the third segment 2203 forms the free end 222 of the exhaust valve plate 220. Specifically, the exhaust valve plate 220 is elongated, with the first segment 2201 forming the root of the exhaust valve plate 220 and connected to the second mounting surface 2121. The second segment 2202 forms the waist of the exhaust valve plate 220, and the third segment 2203 forms the head of the exhaust valve plate 220. The third segment 2203 covers the exhaust port 2120. The high-temperature and high-pressure gaseous refrigerant formed in the compression chamber 2110 impacts the third segment 2203 of the exhaust valve plate 220. Under the impact of the high-temperature and high-pressure gaseous refrigerant, the third segment 2203 drives the second segment 2202 to swing away from the second mounting surface 2121, thereby forming the swing of the free end 222 relative to the fixed end 221.

[0099] In some embodiments, refer to Figures 1-4 as well as Figure 9 , Figure 11 and Figure 12 The limiting portion 20 has a limiting surface 201 facing the exhaust valve plate 220. (Refer to...) Figure 7 and Figure 10 The limiting surface 201 is configured to be opposite to the third segment 2203. The structural design of the limiting surface 201 being opposite only to the third segment 2203 (i.e., the free end 222) of the exhaust valve plate 220 can shorten the length of the limiting surface 201 along the extension direction of the exhaust valve plate 220. While ensuring the limitation of the opening range of the third segment 2203 of the exhaust valve plate 220, it can also increase the rigidity of the limiting part 20, thereby increasing the first natural frequency of the limiting part 20 and reducing the noise of the compressor 200 during operation.

[0100] In some embodiments, refer to Figure 11 The limiting surface 201 is configured to be opposite to the second segment 2202 and the third segment 2203. The structural design of the limiting surface 201 being opposite to the second segment 2202 and the third segment 2203 of the exhaust valve plate 220 ensures the rigidity of the limiting part 20. Moreover, during the opening process of the exhaust valve plate 220, the limiting part 20 not only restricts the maximum opening position of the third segment 2203, but also restricts the opening range of the second segment 2202 relative to the first segment 2201, thereby controlling the overall deformation shape of the exhaust valve plate 220, avoiding excessive bending of the second segment 2202 (i.e., the waist of the exhaust valve plate 220) relative to the first segment 2201, improving the service life of the exhaust valve plate 220, and ensuring that the third segment 2203 seals the exhaust port 2120 when the pump body 210 is not venting.

[0101] In some embodiments, refer to Figures 8-12 The compressor 200 also includes a limiting plate 230, which is disposed on the side of the exhaust valve plate 220 away from the second mounting surface 2121. The limiting plate 230 and the limiting part 20 are arranged at intervals along the extending direction of the exhaust valve plate 220.

[0102] In some embodiments, refer to Figure 9 and Figure 12 The limiting plate 230 covers and connects to the first segment 2201 and the second segment 2202, and the limiting surface 201 of the limiting part 20 is opposite to the third segment 2203. This structural design, where the limiting plate 230 covers and connects to the first segment 2201 and the second segment 2202, restricts the opening range (i.e., lift) of the second segment 2202 of the exhaust valve plate 220. Combined with the structural design where the limiting surface 201 and the third segment 2203 are opposite to each other, the limiting part 20 and the limiting plate 230 work together to limit the opening range of the second segment 2202 and the third segment 2203 of the exhaust valve plate 220. This results in a relatively short length for the limiting surface 201 of the limiting part 20, giving the limiting part 20 relatively high rigidity and improving the noise reduction effect of the compressor 200.

[0103] In some embodiments, refer to Figure 11 A limiting plate 230 is installed on and connected to the first segment 2201, and the limiting surface 201 of the limiting part 20 is opposite to the second segment 2202 and the third segment 2203. Thus, the limiting plate 230 ensures the installation stability of the first segment 2201 on the second mounting surface 2121, and the limiting surface 201 of the limiting part 20 restricts the opening range of the second segment 2202 and the third segment 2203. While ensuring the rigidity of the limiting part 20, the limiting part 20 and the limiting plate 230 cooperate to more precisely control the overall deformation shape of the exhaust valve plate 220, preventing excessive bending of the second segment 2202 (i.e., the waist of the exhaust valve plate 220) relative to the first segment 2201, improving the service life of the exhaust valve plate 220, ensuring the third segment 2203 seals the exhaust port 2120 when the pump body 210 is not venting, and reducing the tolerance accumulation problem caused by using the limiting plate 230 alone to limit the opening range of the exhaust valve plate 220.

[0104] In some embodiments, refer to Figures 8-11A groove 2122 is provided on the second mounting surface 2121. An exhaust valve plate 220 is disposed on the inner bottom wall of the groove 2122. A first fixing hole 2123 is provided on the inner bottom wall of the groove 2122. A limiting plate 230 is disposed on the side of the exhaust valve plate 220 that is away from the inner bottom wall of the groove 2122. A limiting part 20 protrudes from the mounting part 112 on the side facing the second mounting surface 2121. The limiting surface 201 of the limiting part 20 is located inside the groove 2122. The groove 2122 on the second mounting surface 2121 provides installation space for the exhaust valve plate 220, thereby ensuring the installation stability of the exhaust valve plate 220 on the second mounting surface 2121. The groove 2122 also limits the movement of the exhaust valve plate 220, ensuring that the free end 222 of the exhaust valve plate 220 can only swing along its thickness direction under the impact of high-pressure gas, and not along its width direction, thus ensuring the stability of the exhaust valve plate 220's swing. The limiting part 20 protrudes from the first mounting surface 111, and combined with the groove 2122, the limiting surface 201 is located inside the groove 2122, thus limiting the opening range of the exhaust valve plate 220 and improving the space utilization rate of the compressor muffler 100 in the thickness direction of the exhaust valve plate 220.

[0105] In some embodiments, the groove 2122 is a keyway on the bearing 212.

[0106] In some embodiments, refer to Figure 12 The limiting part 20 protrudes from the second end 12 of the body 10 facing the second mounting surface 2121. This design is suitable for compressor 200 structures where a groove 2122 does not need to be formed on the second mounting surface 2121. The exhaust valve plate 220 is disposed on the second mounting surface 2121, and the limiting part 20 protrudes from the second end 12 facing the second mounting surface 2121. This design ensures the distance between the limiting surface 201 of the limiting part 20 and the free end 222 of the exhaust valve plate 220 along the thickness direction of the exhaust valve plate 220, thereby providing space for the swing of the free end 222 of the exhaust valve plate 220. Furthermore, the limiting part 20 can limit the opening amplitude of the free end 222 of the exhaust valve plate 220, thus enabling the compressor 200 provided in this embodiment to meet the usage requirements of different scenarios.

[0107] In some embodiments, refer to Figure 2 , Figure 9 and Figure 12Along the extension direction of the limiting segment 21, the length L of the limiting segment 21 is 5mm to 10mm. The length L of the limiting segment 21 is within the range of 5mm to 10mm, allowing the limiting segment 21 of the limiting part 20 to be positioned opposite to the third segment 2203 (i.e., the free end 222) of the exhaust valve plate 220. This allows the limiting segment 21 to limit the opening amplitude of the third segment 2203 of the exhaust valve plate 220 with a relatively short length, and also gives the limiting segment 21 a relatively high first-order natural frequency. When the exhaust valve plate 220 impacts the limiting part 20, it generates a wide-band impact excitation, the spectral energy of which significantly decreases as the frequency increases. By increasing the first-order natural frequency of the limiting part 20, the excitation component energy corresponding to this first-order natural frequency is weaker, preventing resonance amplification in the limiting part 20, thereby achieving noise reduction for the compressor 200.

[0108] In some embodiments, refer to Figure 4 and Figure 11 Along the extension direction of the limiting segment 21, the length L of the limiting segment 21 is 15mm to 30mm. The length L of the limiting segment 21 is within the range of 15mm to 30mm, so that the limiting segment 21 of the limiting part 20 can be set opposite to the second segment 2202 and the third segment 2203 of the exhaust valve plate 220. While ensuring the rigidity of the limiting part 20, it can also limit the opening range of the second segment 2202 relative to the first segment 2201, thereby controlling the overall deformation shape of the exhaust valve plate 220, avoiding excessive bending of the second segment 2202 (i.e., the waist of the exhaust valve plate 220) relative to the first segment 2201, and improving the service life of the exhaust valve plate 220.

[0109] In some embodiments, refer to Figure 13 The width of the area covered by the free end 222 of the exhaust valve plate 220 over the exhaust port 2120 is W mm, that is, the width of the area where the orthographic projection of the exhaust port 2120 onto the free end 222 is W. (Refer to...) Figure 1 and Figure 3 The width of the portion of the limiting section 21 opposite to the exhaust port 2120 is W1 mm, satisfying: W-2mm≤W1≤W+2mm. The width of this portion can be understood as the width of the exhaust port 2120 along the width direction of the exhaust valve plate 220, where the orthographic projection of the exhaust port 2120 onto the plane containing the limiting surface 201 of the limiting section 21 is located. The setting of W-2mm≤W1≤W+2mm ensures that the width of the area where the limiting section 21 and the exhaust port 2120 are opposite corresponds to the width of the area where the free end 222 of the exhaust valve plate 220 covers the exhaust port 2120. This effectively limits the opening range of the free end 222 due to the limiting section 21 and avoids unnecessary obstruction of the high-pressure gas discharged from the exhaust port 2120 due to excessive width of the limiting section 21, thus ensuring smooth exhaust flow.

[0110] In some embodiments, refer to Figure 1 The limiting segment 21 has a circular cross-sectional shape and is only positioned opposite to the free end 222 of the exhaust valve plate 220. W1 is the outer diameter of the limiting segment 21. In other implementations, the cross-sectional shape of the limiting segment 21 can be elliptical, arc-shaped, or polygonal, depending on the layout or spatial constraints of the exhaust valve plate 220. This application embodiment does not impose specific limitations, as long as the constraint W-2mm≤W1≤W+2mm is met.

[0111] In some embodiments, refer to Figure 3 The limiting segment 21 includes a first limiting segment 21a and a second limiting segment 21b connected in sequence. The first limiting segment 21a is disposed opposite to the free end 222 of the exhaust valve plate 220. The width of the area of ​​the first limiting segment 21a disposed opposite to the exhaust port 2120 along the width direction of the exhaust valve plate 220 is W1. The cross-sectional shape of the first limiting segment 21a is arc-shaped, and W1 is the outer diameter of the first limiting segment 21a.

[0112] In some embodiments, refer to Figure 9 and Figure 11 Along the thickness direction of the exhaust valve plate 220, the distance between the limiting surface 201 and the exhaust valve plate 220 is H mm. Along the extension direction of the exhaust valve plate 220, the value of H increases from the end closer to the fixed end 221 to the end farther from the fixed end 221. This structural design, where the distance H between the limiting surface 201 and the exhaust valve plate 220 increases from the end closer to the fixed end 221 to the end farther from the fixed end 221, causes the limiting surface 201 to be inclined, forming a slope. This ensures that when the exhaust valve plate 220 abuts against the limiting surface 201, the limiting surface 201 and the free end 222 of the exhaust valve plate 220 form a surface contact, increasing the contact area between the limiting surface 201 and the free end 222 of the exhaust valve plate 220. This prevents the exhaust valve plate from fatigue fracture due to stress concentration and extends the service life of the exhaust valve plate 220.

[0113] In some embodiments, refer to Figure 12The height of the connecting segment 22 near the fixed end 221 along the extension direction of the exhaust valve plate 220 is H1, where 4mm ≤ H1 ≤ 6mm. The height of the connecting segment 22 away from the fixed end 221 along the extension direction of the exhaust valve plate 220 is H2, where 1mm ≤ H2 ≤ 1.8mm. This structural design, where the height H1 of the connecting segment 22 near the fixed end 221 is in the range of 4mm to 6mm, and the height H2 of the connecting segment 22 away from the fixed end 221 is in the range of 1mm to 1.8mm, ensures that H2 < H1. This results in the limiting surface 201 having an inclined slope design, which limits the opening range of the exhaust valve plate 220 while preventing fatigue fracture due to stress concentration, thus extending the service life of the exhaust valve plate 220. In other implementations, the shape of the limiting surface 201 can be a smoothly transitioned curved surface, a plane, or a composite surface composed of a plane and a curved surface, thereby preventing fatigue fracture of the exhaust valve plate 220 due to stress concentration.

[0114] In some embodiments, the first natural frequency of the limiting part 20 is determined by simulation analysis.

[0115] Specifically, the simulation analysis method includes the following steps:

[0116] (a) Use 3D design software to create a 3D model of the compressor muffler 100 as a whole. The 3D design software is PRO / E, Solidworks, Creo or CATIA.

[0117] (b) Establish a finite element model of the compressor muffler 100 using finite element preprocessing software, such as Hypemesh, SpaceClaim, or MSC.Patran.

[0118] (c) Import the finite element model into the analysis software and apply boundary adjustment at the actual assembly constraint position of the first mounting surface 111 of the body 10 of the compressor silencer 100 and the second mounting surface 2121 of the bearing 212 of the pump body 210, for example, at the position where the second fastener is inserted into the second mounting hole 1121 and the second fixing hole 2124. The analysis software is AnsysWorkbench or Abaqus.

[0119] (d) Using analysis software, assign physical properties such as density, Young's modulus, and Poisson's ratio of the actual material to each part of the finite element model;

[0120] (e) Use analysis software to perform mesh generation, and control the global mesh size between 1 mm and 2 mm to ensure a balance between computational accuracy and efficiency;

[0121] (f) Use analysis software to perform modal analysis and extract the first natural frequency and corresponding mode shape of the limiting part 20.

[0122] The "first natural frequency of the limiting part 20" refers to the frequency at which the limiting part 20 exhibits a significant bending or torsional vibration mode in the lowest-order mode under the boundary conditions applied in step (c) above. The first natural frequency of the limiting part 20 can be changed by altering the length L, thickness S2, height H1, and / or height H2 of the limiting segment 21, the shape of the limiting segment 21 positioned opposite the exhaust port 2120, and the material properties of the limiting part 20. The overall material of the compressor muffler 100 affects the manufacturability of the compressor muffler 100 body 10 and the limiting part 20. The material density, Young's modulus, and Poisson's ratio also affect the stiffness of the limiting part 20, thus influencing its first natural frequency. Generally, the higher the material density, the lower the first natural frequency. The higher the Young's modulus, the higher the first natural frequency.

[0123] In some embodiments, the compressor muffler 100 is made entirely of at least one material selected from low-carbon steel, stainless steel, copper, aluminum, alloys, and high-performance engineering plastics.

[0124] In some embodiments, the compressor muffler 100 is made entirely of at least one material selected from cold-rolled sheet, deep-drawing cold-rolled sheet, ultra-deep-drawing cold-rolled sheet, and aluminum.

[0125] In some embodiments, refer to Figure 1 and Figure 12 The compressor muffler 100 is made of SPCC cold-rolled carbon steel sheet with a density of 7.69e-06 kg / mm². 3 The Young's modulus is 2.12e+0.5 MPa, Poisson's ratio is 0.3, the limiting segment 21 of the limiting part 20 has a length L of 10 mm, a thickness S2 of 1.0 mm, and a width W1 of 10 mm along its extension direction, and the cross-sectional shape of the limiting part 20 is quasi-circular. Through simulation analysis, the first natural frequency of the limiting part 20 is approximately 22500 Hz, which is significantly higher than the first natural frequency (1600 Hz~2500 Hz) of the limiter in a traditional compressor. Moreover, the first natural frequency of the limiting part 20 is as high as 22500 Hz. The impact excitation generated by the exhaust valve plate 220 impacting the limiting part 20 has a significantly reduced spectral energy as the frequency increases. Therefore, the excitation energy near 22500Hz has been significantly reduced, and the limiting part 20 will not produce obvious resonance amplification (or a significant reduction in transient vibration amplitude). Moreover, the first natural frequency of up to 22500Hz is significantly higher than the frequency range of 20Hz~20kHz that the human ear is sensitive to, so that the user cannot hear the noise generated by the exhaust valve plate 220 impacting the limiting part 20. This greatly improves the high-frequency noise performance of the compressor 200 and enhances the noise reduction effect of the compressor silencer 100 on the compressor 200.

[0126] In some embodiments, refer to Figure 4 and Figure 11 The compressor muffler 100 is made of SPCC cold-rolled carbon steel sheet with a density of 7.69e-06 kg / mm². 3 The Young's modulus is 2.12e+05MPa, and the Poisson's ratio is 0.3. The length L of the limiting segment 21 of the limiting part 20 along its extension direction is 23.8mm, the thickness S2 is 1.0mm, and the width W1 is 8mm. The width of the second limiting segment 21b is 5mm, H1 is 4.8mm, and H2 is 1.8mm. Through simulation analysis, the first natural frequency of the limiting part 20 is approximately 14659Hz, which is significantly higher than the first natural frequency of the limiter in a traditional compressor (1600Hz~2500Hz). The impact excitation generated by the exhaust valve plate 220 impacting the limiting part 20 has a significantly reduced spectral energy as the frequency increases. Therefore, the excitation energy near 14659Hz has been significantly reduced, and the limiting part 20 will not produce significant resonance amplification (or a significant reduction in transient vibration amplitude), thus improving the noise reduction effect on the compressor 200.

[0127] In some embodiments of this application, an air conditioner is also provided, which includes the compressor 200 as described above.

[0128] It should be understood that the above embodiments are exemplary and are not intended to encompass all possible implementations included in the claims. Various modifications and changes can be made to the above embodiments without departing from the scope of this disclosure. Similarly, the various technical features of the above embodiments can be arbitrarily combined to form other embodiments of this application that may not be explicitly described. Therefore, the above embodiments only illustrate several implementations of this application and do not limit the scope of protection of this patent application.

Claims

1. A silencer for a compressor, characterized in that, The compressor silencer includes: The body includes a sound-absorbing cavity and comprises a first end and a second end disposed opposite to each other. The first end has a first mounting surface configured to connect with a bearing having an exhaust valve plate. The main body has a limiting portion protruding from the surface facing the bearing. The limiting portion is configured to be disposed opposite to the exhaust valve plate and is configured to abut against the exhaust valve plate to limit the opening range of the exhaust valve plate.

2. The compressor muffler according to claim 1, characterized in that, The limiting part protrudes from the first mounting surface; Alternatively, the limiting portion protrudes from the surface of the second end facing the pump body.

3. The compressor muffler according to claim 1 or 2, characterized in that, The first end is provided with a mounting part, and the side of the mounting part opposite to the second end forms the first mounting surface; The second end has an exhaust port that communicates with the silencing cavity.

4. The compressor muffler according to claim 3, characterized in that, The limiting part includes a limiting section and a connecting section. The limiting section is configured to extend along the length direction of the exhaust valve plate, and the connecting section is configured to extend along the thickness direction of the exhaust valve plate. The limiting section is connected to the body through the connecting section, and the limiting part is configured to limit the opening range of the exhaust valve plate through the limiting section. Along the extending direction of the limiting segment, the length L of the limiting segment is 5mm~10mm, or the length L of the limiting segment is 15mm~30mm.

5. The compressor muffler according to claim 4, characterized in that, Along the extending direction of the limiting segment, the height of the connecting segment connected to one end of the limiting segment is H1, 4mm≤H1≤6mm, and the height of the connecting segment connected to the other end of the limiting segment is H2, 1mm≤H2≤1.8mm.

6. The compressor muffler according to claim 1, characterized in that, The limiting part is integrally formed with the body; the first natural frequency of the limiting part is 5000Hz~30000Hz.

7. The compressor muffler according to claim 6, characterized in that, The first natural frequency of the limiting part is 10000Hz~24000Hz.

8. A compressor, characterized in that, include: The pump body includes a cylinder and a bearing disposed at one end of the cylinder. The cylinder has a compression chamber, and the bearing has an exhaust port communicating with the compression chamber. The bearing has a second mounting surface. An exhaust valve plate is disposed on the second mounting surface, and the exhaust valve plate covers the exhaust port; as well as The compressor muffler as described in any one of claims 1 to 7, wherein the body is fastened to the second mounting surface, and the limiting portion is disposed opposite to the exhaust valve plate; The exhaust valve plate is configured to swing to open the exhaust port, and the limiting portion is configured to abut against the exhaust valve plate to limit the opening range of the exhaust valve plate.

9. The compressor according to claim 8, characterized in that, The exhaust valve plate includes a fixed end and a free end disposed opposite to each other. The fixed end is connected to the second mounting surface, and the free end covers the exhaust port. The free end is configured to swing relative to the fixed end to open the exhaust port so that the exhaust port communicates with the muffler cavity. The limiting part is configured to abut against the free end to limit the opening range of the free end.

10. The compressor according to claim 9, characterized in that, Along the extending direction of the exhaust valve plate, the exhaust valve plate includes a first section, a second section, and a third section connected in sequence, wherein the first section forms the fixed end and the third section forms the free end; The limiting portion has a limiting surface facing the exhaust valve plate, the limiting surface being configured to be opposite to the third segment, or the limiting surface being configured to be opposite to the second segment and the third segment.

11. The compressor according to claim 10, characterized in that, The compressor also includes a limiting plate, which is disposed on the side of the exhaust valve plate opposite to the second mounting surface. The limiting plate and the limiting part are arranged at intervals along the extending direction of the exhaust valve plate. The limiting plate is disposed over the first segment and the second segment and connected to the first segment, and the limiting surface of the limiting part is disposed opposite to the third segment; Alternatively, the limiting plate may be installed on and connected to the first segment, and the limiting surface of the limiting part may be disposed opposite to the second segment and the third segment.

12. The compressor according to claim 10, characterized in that, A groove is provided on the second mounting surface, the exhaust valve plate is disposed on the inner bottom wall of the groove, and the limiting plate is disposed on the side of the exhaust valve plate opposite to the inner bottom wall; The limiting part protrudes from the first mounting surface, and the limiting surface of the limiting part is located inside the groove.

13. The compressor according to claim 9 or 10, characterized in that, The width of the area covering the exhaust port by the free end of the exhaust valve plate is W mm; The limiting part includes a limiting section and a connecting section. The limiting section is configured to extend along the length direction of the exhaust valve plate, and the connecting section is configured to extend along the thickness direction of the exhaust valve plate. The limiting section is connected to the body through the connecting section. The side of the limiting section facing the exhaust valve plate forms the limiting surface. The limiting part limits the opening range of the exhaust valve plate through the limiting section. The width of the portion of the limiting section opposite to the exhaust port is W1 mm; It satisfies: W-2mm≤W1≤W+2mm.

14. The compressor according to claim 9 or 10, characterized in that, Along the thickness direction of the exhaust valve plate, the distance between the limiting surface and the exhaust valve plate is H mm; Along the extension direction of the exhaust valve plate, the value of H increases from the end closer to the fixed end to the end farther away from the fixed end.

15. An air conditioner, characterized in that, The air conditioner includes a compressor as described in any one of claims 8 to 14.

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