Compressor exhaust structure and refrigeration appliance

Abstract

The present invention provides a compressor exhaust structure and refrigeration appliance, in the field of compressors. It includes a cylinder seat and a sound-absorbing chamber and an air inlet formed on the cylinder seat; a sound-absorbing assembly is provided in the sound-absorbing chamber, and the sound-absorbing assembly includes a first partition and a second partition, and the first partition and the second partition divide the sound-absorbing chamber into a first sound-absorbing chamber, a second sound-absorbing chamber and a pressure chamber, and the air inlet is connected to the first sound-absorbing chamber; a plurality of bypass holes are provided on the surface of the first partition, and the bypass holes are configured to conduct or separate the first sound-absorbing chamber and the second sound-absorbing chamber; the second partition can be adjusted and sleeved on the outside of the first partition to open or close the bypass holes on the first partition. The present invention can solve the multi-band noise reduction needs of the compressor without increasing the number and volume of the sound-absorbing chambers by arranging the sound-absorbing assembly in the sound-absorbing chamber.

Description

Technical Field

[0001] The present invention belongs to the field of compressors, and in particular relates to a compressor exhaust structure and a refrigeration appliance. Background Art

[0002] Indoor refrigeration appliances, such as refrigerators, ice makers, and wine cabinets, have even stricter noise requirements. Because the matching compressor generates pulse pressure during operation, it can produce noise at different frequencies in the gas system, affecting customers' experience with our products and leading to complaints and after-sales service issues.

[0003] The current general measure is to achieve the purpose of noise reduction by increasing the number of anechoic chambers, but this approach will increase the volume, weight and material cost of the compressor, which is obviously not in line with the requirements of the trend of high efficiency and lightweight.

[0004] In view of this, the present invention is proposed. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to overcome the deficiencies of the prior art and provide a compressor exhaust structure and a refrigeration appliance.

[0006] To solve the above technical problems, on the one hand, an embodiment of the present application provides a compressor exhaust structure, including a cylinder seat and a muffler chamber and an air inlet formed on the cylinder seat;

[0007] A silencer assembly is provided in the silencer chamber, comprising a first partition and a second partition movably mounted on the first partition, the first partition and the second partition dividing the silencer chamber into a first silencer chamber, a second silencer chamber and a pressure chamber, and the air inlet is connected to the first silencer chamber;

[0008] A plurality of bypass holes are opened on the surface of the first partition, and the bypass holes are configured to connect or separate the first muffler cavity and the second muffler cavity;

[0009] The second partition can adjust the number of the bypass holes on the first partition according to the pressure in the first muffler cavity and simultaneously adjust the volume of the first muffler cavity.

[0010] In the above technical solution, the second partition is slidably mounted on the outside of the first partition.

[0011] In the above technical solution, the exhaust structure further includes an adjustment component, which is an elastic component installed in the pressure chamber and linked to the second partition;

[0012] The elastic member is configured to adjust a position of the second partition relative to the first partition;

[0013] The exhaust structure further includes a pressure relief hole in communication with the pressure chamber, the pressure relief hole being configured to maintain a constant pressure in the pressure chamber when the position of the second partition is adjusted.

[0014] In the above technical solution, the first partition is a sound-absorbing inner spacer ring arranged in the sound-absorbing chamber, and the second partition is a sound-absorbing outer spacer ring slidably sleeved on the outside of the sound-absorbing inner spacer ring;

[0015] The outer silencer spacer ring includes a sleeve portion and a sealing portion. The sleeve portion is slidably mounted on the outside of the inner silencer spacer ring. The sealing portion is formed at the bottom end of the sleeve portion and extends toward the inner wall surface of the silencer chamber. One end of the sleeve portion extending toward the inner wall surface of the silencer chamber is in contact with the inner wall surface of the silencer chamber to separate the first silencer chamber and the pressure chamber.

[0016] In the above technical solution, the silencer inner spacer ring is a cylindrical spacer ring, the sleeve portion is a cylindrical sleeve slidably sleeved on the outside of the silencer inner spacer ring, and the sealing portion is a sealing flange formed at the bottom edge of the sleeve.

[0017] In the above technical solution, a first sealing ring and a second sealing ring are respectively provided on the inner ring surface and the outer ring surface of the sealing flange. The inner ring surface of the flange is indirectly in contact with the outer wall surface of the silencer inner spacer ring through the first sealing ring to form a first sealing section, and the outer ring surface of the flange is in contact with the inner wall surface of the silencer chamber through the second sealing ring to form a second sealing section.

[0018] In the above technical solution, the inner ring surface and the outer ring surface of the sealing flange are respectively provided with a first mounting groove and a second mounting groove, and the first sealing ring and the second sealing ring are respectively installed in the first mounting groove and the second mounting groove.

[0019] In the above technical solution, the central cross section of the first sealing ring and / or the second sealing ring coincides with the central cross section of the flange.

[0020] In the above technical solution, the elastic component is a spring installed in the pressure chamber and sleeved on the outside of the silencer inner ring. One end of the spring is installed on the bottom surface of the silencer chamber, and the other end is installed on the bottom surface of the flange.

[0021] In the above technical solution, the inner diameter of the spring is larger than the outer diameter of the silencer outer spacer ring.

[0022] In the above technical solution, there is a clearance fit between the sleeve portion and the silencer inner spacer ring, the clearance is 2 μm to 4 μm, and the clearance is filled with refrigeration oil.

[0023] In the above technical solution, multiple bypass holes are evenly distributed along the circumference and axial direction of the silencer inner spacer ring. Among the multiple bypass holes distributed axially along the silencer inner spacer ring, the distance between two adjacent bypass holes in the axial direction is 2.5mm~5mm, and the bypass holes are circular holes.

[0024] In the above technical solution, a chip removal hole is provided through the cylinder seat, and the chip removal hole serves as a pressure relief hole.

[0025] In the above technical solution, the exhaust structure also includes a cylinder head installed at the opening of the silencer chamber, and a first sealing gasket and a second sealing gasket are installed on the upper end surfaces of the silencer chamber and the silencer inner spacer ring respectively. The cylinder head is fitted with the first sealing gasket and the second sealing gasket and is locked by fastening screws to isolate the gas inside the silencer chamber from the external gas.

[0026] In the above technical solution, a mounting seat is further provided in the muffler chamber, the mounting seat is arranged at the bottom center of the muffler chamber, and the fastening screw passes through the cylinder head and is fixed on the mounting seat;

[0027] The mounting seat is a cylindrical seat body, and the silencer inner spacer ring is installed on the mounting seat with interference fit.

[0028] In the above technical solution, multiple groups of silencer components are provided, and two adjacent groups of silencer components are nested with each other. The multiple groups of silencer components divide the silencer chamber into multiple first silencer chambers, multiple pressure chambers and one second silencer chamber. The first silencer chamber close to the inner wall of the silencer chamber among the multiple first silencer chambers is connected to the air inlet.

[0029] On the other hand, an embodiment of the present application further provides a refrigeration appliance comprising the compressor exhaust structure according to any one of claims 1 to 16.

[0030] After adopting the above technical solution, the present invention has the following beneficial effects compared with the prior art:

[0031] First, the present invention effectively improves noise levels without adding an additional anechoic chamber, boasting a simple structure, minimal space occupation, and straightforward component processing. The adaptive volume structure of the Helmholtz resonance chamber in this resonant anechoic chamber allows for adaptive volume adjustment based on exhaust pressure during compressor operation. This adaptively changes the volume of the resonance chamber to absorb noise corresponding to different frequency bands, avoiding increased power input for compressor anechoic band control and reducing control complexity.

[0032] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] The accompanying drawings are part of the present invention and are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention, but do not constitute an undue limitation of the present invention. Obviously, the drawings described below are only some embodiments. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without inventive effort. In the accompanying drawings:

[0034] Figure 1 This is a schematic diagram of the explosion structure of Example 1 of the compressor exhaust structure of this application;

[0035] Figure 2 This is a schematic diagram of a first cross-sectional structure of Example 1 of the compressor exhaust structure of the present application;

[0036] Figure 3 For this application Figure 2 A schematic cross-sectional view of the silencer assembly in Example 1;

[0037] Figure 4 For this application Figure 2 A schematic diagram of a first partial cross-sectional structure in Example 1, showing a state diagram of the silencer assembly in the first extreme position when the compressor is turned on;

[0038] Figure 5 For this application Figure 2 A second partial cross-sectional structural diagram of Example 1, showing a state diagram of the silencer assembly in the second extreme position when the compressor is turned off;

[0039] Figure 6 This is a schematic diagram of the second cross-sectional structure of the compressor exhaust structure embodiment 1 of the present application, showing the chip removal hole;

[0040] Figure 7 This is a cross-sectional structural diagram of Example 2 of the compressor exhaust structure of the present application, showing two silencer components arranged in the silencer chamber;

[0041] Figure 8 This is a schematic diagram of the explosion structure of Example 2 of the compressor exhaust structure of this application, showing that two silencer components are set in the silencer chamber;

[0042] Figure 1-8 Middle: 1-cylinder seat, 2-muffler chamber, 21-muffler assembly, 211-first partition, 2111-bypass hole, 212-second partition, 2121-sleeve part, 2122-sealing part, 3-air inlet, 4-first muffler chamber, 5-second muffler chamber, 6-pressure chamber, 7-first sealing ring, 8-second sealing ring, 9-elastic component, 10-chip removal hole, 11-cylinder head, 12-fastening screw, 13-mounting seat, 14-first sealing gasket, 15-second sealing gasket.

[0043] It should be noted that these drawings and textual descriptions are not intended to limit the conceptual scope of the present invention in any way, but rather to illustrate the concept of the present invention for those skilled in the art by referring to specific embodiments. DETAILED DESCRIPTION

[0044] In the description of the present invention, it should be noted that the terms "inside" and "outside" etc. indicating orientations or positional relationships are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0045] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," "connected," "in contact," and "connected" should be understood broadly. For example, they may refer to fixed, detachable, or integral connections; mechanical or electrical connections; and direct or indirect connections through an intermediary. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0046] Existing compressors generate pulse pressure during operation, producing noise at different frequency bands in the air circuit system, which affects customers' experience with our products and leads to complaints and after-sales service issues. Existing technologies typically achieve noise reduction by increasing the number of anechoic chambers, but this approach increases the size, weight, and material costs of the compressor, clearly not meeting the requirements of high-efficiency and lightweight design trends. The present invention addresses the multi-band noise reduction needs of compressors by installing anechoic components within the anechoic chambers without increasing the number or size of the chambers.

[0047] To further illustrate the technical solution of the present invention, Figures 1-8 As shown, the following specific embodiments are provided.

[0048] Example 1

[0049] On the one hand, this embodiment provides a Figure 1 and Figure 2The compressor exhaust structure shown is preferably applied to a piston compressor, comprising a cylinder block 1 and a muffler chamber 2 and an air inlet 3 formed on the cylinder block 1. A muffler assembly 21 is provided in the muffler chamber 2. The muffler assembly 21 is used to muffle the high-pressure gas generated when the compressor is working. Specifically, the muffler assembly 21 includes a first partition 211 and a second partition 212. The first partition 211 and the second partition 212 divide the muffler chamber 2 into a first muffler cavity 4 and a second muffler cavity 4. The first silencer chamber 4 is connected to the air inlet 3 and the second silencer chamber 5. The air inlet 3 is connected to the first silencer chamber 4. A plurality of bypass holes 2111 are provided on the surface of the first partition 211. The bypass holes 2111 are configured to connect or separate the first silencer chamber 4 and the second silencer chamber 5 so that the high-pressure gas discharged into the first silencer chamber 4 can be introduced into the second silencer chamber 5. The second partition 212 can adjust the number of openings of the bypass holes 2111 on the first partition 211 according to the exhaust pressure in the first silencer chamber 4 and adjust the volume of the first silencer chamber 4 at the same time. When the bypass hole 2111 is opened, the high-pressure gas in the first silencer chamber 4 enters the second silencer chamber 5 through the bypass hole 2111. At this time, the first silencer chamber 4 is connected to the second silencer chamber 5, and the first silencer chamber 4 and the pressure chamber 6 remain relatively independent and sealed. When the bypass hole 2111 is closed, the first silencer chamber 4 and the second silencer chamber 5 remain relatively independent and sealed, and the first silencer chamber 4 and the pressure chamber 6 also remain relatively independent and sealed, that is, the first silencer chamber 4 and the pressure chamber 6 always remain in a relatively independent and sealed state.

[0050] Specifically, such as Figure 2 As shown, the second partition 212 is slidably mounted on the outside of the first partition 211. When the compressor is exhausted, the second partition 212 slides downward relative to the first partition 211 due to the exhaust pressure, thereby changing the volume of the first muffler chamber 4 and opening the bypass hole 2111.

[0051] When the compressor is working, the high-pressure gas it generates first enters the first silencer chamber 4 through the air inlet 3. At this time, the gas pressure in the first silencer chamber 4 is greater than the gas pressure in the pressure chamber 6. Under the action of the pressure difference, the second partition 211 is driven downward, the volume of the first silencer chamber 4 increases, the volume of the pressure chamber 6 decreases, and the pressure increases. The bypass hole 2111 on the first partition 211 opens, and the high-pressure gas in the first silencer chamber 4 enters the second silencer chamber 5 through the opened bypass hole 2111. During the circulation of high pressure, the air column formed in the bypass hole 2111 by the circulating gas forms an elastic resonance system with the gas in the first silencer chamber 4 and the second silencer chamber 5. When the external excitation frequency is consistent with the natural frequency of the resonance system, resonance will occur and generate violent friction on the wall of the bypass hole 2111, consuming energy, thereby achieving the effect of noise reduction and vibration reduction. When the compressor has completed exhaust, the gas pressure in the pressure chamber 6 is greater than the gas pressure in the first muffler chamber 4. Under the action of the pressure difference, the second partition 212 is driven to reset so that the pressure in the first muffler chamber 4 and the pressure chamber 6 are kept balanced and the bypass hole 2111 on the first partition 211 is closed at the same time. It is worth noting that the number of bypass holes 2111 opened is determined according to the exhaust pressure value, that is, the greater the exhaust pressure, the more bypass holes 2111 are opened, and the lower the exhaust pressure, the fewer bypass holes 2111 are opened, thereby achieving different numbers of bypass holes 2111 opened according to different exhaust pressures, thereby making the muffler chamber 2 have a more effective broadband muffler effect.

[0052] From the above content, it can be seen that the position of the second partition 212 in the silencer assembly is adjusted by the pressure difference between the pressure chamber 6 and the first silencer chamber 4. This adjustment method is applicable to the noise generated by gas pulsation within the allowable noise reduction frequency range.

[0053] When the noise generated by gas pulsation is outside the allowable noise reduction frequency range, in an embodiment of the present application, the exhaust structure also includes an adjustment component, which is an elastic component 9 installed in the pressure chamber 6 and linked to the second partition 212, wherein the elastic component 9 is configured to adjust the position of the second partition 212 relative to the first partition 211. When the compressor is running, under the action of the pressure difference between the first silencer chamber 4 and the pressure chamber 6, the first partition 211 moves downward and drives the elastic component 9 to undergo elastic deformation to adjust the position of the second partition 212 relative to the first partition 211. When the compressor is turned off, the elastic reset function of the elastic component 9 drives the second partition 212 to automatically reset, thereby adaptively adjusting the volume of the first silencer chamber 4 and the pressure chamber 6. In order to ensure that when the second partition 212 adjusts the volume of the first silencer chamber 4, the volume change in the pressure chamber 6 does not affect the pressure change of the gas in the pressure chamber 6, a pressure relief hole 10 connected to the pressure chamber 6 is also provided in the exhaust structure. The pressure relief hole 10 is configured to keep the pressure in the pressure chamber 6 constant when the position of the second partition 212 is adjusted, thereby ensuring that the first silencer chamber 4 and the pressure chamber 6 are only controlled by the elastic component 9 during the adaptive volume adjustment process, thereby making the adaptive volume adjustment process more controllable.

[0054] The first separator 211 and the second separator 212 are described in detail below:

[0055] like Figure 3-Figure 5 As shown, the first partition 211 is a sound-absorbing inner spacer ring provided in the sound-absorbing chamber 2, and the second partition 212 is a sound-absorbing outer spacer ring slidably sleeved on the outside of the sound-absorbing inner spacer ring;

[0056] The outer silencer spacer includes a sleeve portion 2121 and a sealing portion 2122, and the sleeve portion 2121 and the sealing portion 2122 are integrally formed, wherein the sleeve portion 2121 is slidably sleeved on the outside of the inner silencer spacer, and the sealing portion 2122 is formed at the bottom end of the sleeve portion 2121 and extends toward the inner wall surface of the silencer chamber 2. One end of the sleeve portion 2112 extending toward the inner wall surface of the silencer chamber 2 is in contact with the inner wall surface of the silencer chamber 2 to separate the first silencer chamber 4 and the pressure chamber 6.

[0057] Specifically, the silencer inner spacer ring is a cylindrical spacer ring, the sleeve portion 2121 is a cylindrical sleeve that is slidably sleeved on the outside of the silencer inner spacer ring, and the sealing portion 2122 is a sealing flange formed at the bottom edge of the sleeve, which seals and separates the first silencer chamber 4 and the pressure chamber 6.

[0058] In order to further improve the sealing between the first muffler chamber 4 and the pressure chamber 6, as shown in FIG. Figure 3As shown, in the embodiment of the present application, a first sealing ring 7 and a second sealing ring 8 are respectively provided on the inner and outer ring surfaces of the sealing flange. The material of the first sealing ring 7 and the second sealing ring 8 is fluororubber, and the hardness of the material of the first sealing ring 7 and the second sealing ring is controlled to be between 45-55HA. Of course, in some alternative embodiments, the material of the first sealing ring 7 and the second sealing ring 8 can also be nitrile rubber or silicone. The material of the sealing ring is not limited in this embodiment. After the sealing flange is installed, the inner ring surface of the flange indirectly contacts the outer wall surface of the silencer inner spacer ring through the first sealing ring 7 to form a first sealing section, and the outer ring surface of the flange contacts the inner wall surface of the silencer chamber 2 through the second sealing ring 8 to form a second sealing section, thereby improving the sealing between the first silencer chamber 4 and the pressure chamber 6 and preventing gas from flowing between the first silencer chamber 4 and the pressure chamber 6.

[0059] In order to facilitate the installation of the first sealing ring 7 and the second sealing ring 8, as shown in FIG. Figure 3 As shown, in the embodiment of the present application, a first mounting groove and a second mounting groove are respectively provided on the inner annular surface and the outer annular surface of the sealing flange, wherein the first sealing ring and the second sealing ring are respectively installed in the first mounting groove and the second mounting groove. Specifically, the central cross-section of the first sealing ring 7 and / or the second sealing ring 8 after installation coincides with the central cross-section of the flange, thereby ensuring that the sealing ring will not fall off during the operation of the sealing flange, thereby improving the sealing stability of the sealing flange.

[0060] The elastic component 9 is described in detail below:

[0061] like Figure 1 and Figure 3 As shown, the elastic component 9 in the embodiment of the present application is a spring installed in the pressure chamber 6 and sleeved on the outside of the silencer inner spacer ring, wherein one end of the spring is installed on the bottom surface of the silencer chamber 2, and the other end is installed on the bottom surface of the flange. Specifically, the inner diameter of the spring is larger than the outer diameter of the silencer outer spacer ring, and a gap is left between the spring and the outer wall surface of the cylindrical spacer ring (i.e., the first partition 211), thereby ensuring that the spring of the second partition 212 will not generate radial vibration along the cylindrical spacer ring during the adjustment process, thereby preventing the spring from colliding and generating noise.

[0062] In order to improve the smoothness of the second partition 212 when it is adjusted on the first partition 211, as shown in FIG. Figure 3 As shown, the sleeve portion 2121 on the second partition 212 and the silencer inner spacer ring are installed with a clearance fit, and the clearance is between 2μm and 4μm. Preferably, the clearance is set to 3μm, and refrigeration oil is filled in the clearance, thereby ensuring the sealing effect while ensuring the opening and closing control of the bypass hole 2111.

[0063] As described above, a plurality of bypass holes 2111 are provided for connecting the first muffler chamber 4 and the second muffler chamber 5. Specifically, the plurality of bypass holes 2111 are evenly distributed along the circumference and axial direction of the muffler inner spacer ring, and the distance between two adjacent bypass holes 2111 in the axial direction of the plurality of bypass holes 2111 distributed along the axial direction of the muffler inner spacer ring is 2.5 mm to 5 mm. Preferably, the distance between two adjacent bypass holes 2111 is set to 3.5 mm, thereby ensuring that the second partition 212 controls and seals the opening and closing of the bypass hole. More specifically, the shape of the bypass hole 2111 is circular. Of course, in some alternative embodiments, the shape of the bypass hole 2111 can also be other shapes, for example, the bypass hole 2111 is set to be square, rectangular or triangular, etc. The specific shape of the bypass hole 2111 is not limited in this embodiment. Furthermore, in the embodiment of the present application, the size and number of the bypass holes 2111 are not limited, and the radius size and number of the bypass holes 2111 can be specifically adjusted according to the requirements of sound insulation.

[0064] It should be noted that, in general, the larger the spacing between the bypass holes 211, the better the sealing effect. However, considering the fitting accuracy between the first partition 211 and the second partition 212, as well as the compressor space utilization, noise reduction and vibration reduction effects and other factors, in the embodiment of the present application, the minimum axial gap between the bypass holes 211 is set to no more than 5 mm.

[0065] In addition, if Figure 6 As shown, a chip removal hole is also provided on the cylinder seat 1. The traditional chip removal hole of the cylinder seat is a blind hole. In the embodiment of the present application, the blind hole of the chip removal hole is changed into a through hole. The production and processing technology of the pressure relief hole 10 mentioned above is formed on the basis of the chip removal hole, so that the production cost is not increased during production and the processing accuracy requirement is reduced.

[0066] Further, such as Figure 1 As shown, the exhaust structure in the embodiment of the present application also includes a cylinder head 11 installed at the opening of the silencer chamber 2, and a first sealing gasket 14 and a second sealing gasket 15 are respectively installed on the upper end surface of the silencer chamber 2 and the silencer inner spacer ring. The cylinder head 11 is fitted with the first sealing gasket 14 and the second sealing gasket 15 and is locked by fastening screws 12 to isolate the internal gas of the silencer chamber 2 from the external gas. The cylinder head 11 is fitted with the first sealing gasket 14 and the second sealing gasket 15 and is fastened and installed by fastening screws 12 to isolate the gas in the silencer chamber 2 from the external gas, thereby ensuring the airtightness of the exhaust end of the compressor during the compression process.

[0067] Furthermore, in order to improve the stability of the silencer inner spacer ring (i.e., the first partition 211) after installation, a mounting seat 13 is further provided inside the silencer chamber 2 in the embodiment of the present application. The mounting seat 13 is a cylindrical protrusion formed at the center of the bottom of the silencer chamber 2. The fastening screw 12 passes through the cylinder head 11 and is fixed on the mounting seat (13). The silencer inner spacer ring is fixed on the mounting seat 13 in an interference fit installation manner, and the lower end face of the silencer inner spacer ring is in contact with the bottom surface of the silencer chamber 2 as a reference to ensure the installation height of the silencer inner spacer ring, thereby ensuring the sealing effect of the cylinder head 11, the first sealing gasket 14 and the second sealing gasket 15 on the silencer chamber 2.

[0068] The following is a detailed description of the working principle of the exhaust structure during exhaust:

[0069] Such as 4 and Figure 5 As shown, when the compressor is working, the compressed gas generated by the reciprocating motion of the piston first enters the first silencer chamber 4 through the air inlet 3 of the silencer chamber 2, and the gas pressure in the first silencer chamber 4 increases and is greater than the gas pressure in the pressure chamber 6, thereby driving the second partition 212 slidingly mounted on the first partition 211 to slide downward. In the process of the second partition 212 sliding downward, the volume in the first silencer chamber 4 increases, and the volume in the pressure chamber 6 decreases, and the spring (i.e., the elastic component 9) undergoes elastic deformation, and the number of bypass holes 2111 opened is adjusted according to the volume change of the first silencer chamber 4, that is, the greater the exhaust pressure, the greater the volume change of the first silencer chamber 4, and the more bypass holes 2111 are opened. Conversely, the smaller the change of the first silencer chamber 4, the fewer bypass holes 2111 are opened.

[0070] When the bypass hole 2111 is opened, the gas in the first silencer chamber 4 enters the second silencer chamber 5 through the multiple bypass holes 2111 on the first partition 211. The air column formed by the circulating gas in the bypass hole 2111 forms an elastic resonance system with the gas in the first silencer chamber 4 and the second silencer chamber 5. When the external excitation frequency is consistent with the natural frequency of the resonance system, resonance will occur and generate violent friction on the wall of the bypass hole, consuming energy, thereby achieving the effect of noise reduction and vibration reduction. When the compressor stops working, the second partition 212 is reset under the drive of the spring (elastic component 9), so that the volume of the first silencer chamber 4 can be adaptively adjusted according to the exhaust pressure.

[0071] According to the resonance muffler silencing frequency formula It can be seen that different resonance cavity volumes correspond to different effective sound-absorbing frequency ranges. In the embodiment of the present application, the volume of the Helmholtz resonance cavity formed by the first partition 211, the second partition 212, and the elastic component 9 can be adaptively adjusted according to the exhaust pressure, thereby absorbing noise corresponding to different frequency bands by adaptively changing the volume of the resonance cavity.

[0072] On the other hand, an embodiment of the present application also provides a refrigeration appliance that utilizes the aforementioned compressor exhaust structure. Specifically, the refrigeration appliance is a refrigerator. Of course, in some alternative embodiments, the refrigeration appliance may also be an ice maker or a wine cabinet, etc. The specific form of the refrigeration appliance is not limited in this embodiment. The refrigeration appliance utilizing the aforementioned exhaust structure can significantly reduce the noise generated during operation of the refrigeration appliance, thereby improving user comfort.

[0073] Example 2

[0074] The difference between this embodiment and embodiment 1 is that: the silencer components 21 in this embodiment are provided in multiple groups, and two adjacent groups of silencer components 21 are nested with each other, such as Figure 7 and Figure 8 As shown, multiple groups of silencer components 21 divide the silencer chamber 2 into multiple first silencer chambers 4, multiple pressure chambers 6 and a second silencer chamber 5. The first silencer chamber 4 close to the inner wall of the silencer chamber 2 is connected to the air inlet 3. By setting multiple groups of silencer components 21 nested together, the exhaust noise of the compressor can be further reduced. Figure 7 As shown in FIG, the figure shows a schematic diagram of the installation structure when the silencer components 21 are in two groups.

[0075] It should also be noted that: within the noise reduction frequency range allowed by the noise generated by gas pulsation, the pressure chamber vent hole (that is, there is no need to set the chip removal hole 10 to a through form) and the setting of the elastic component can be eliminated to form a closed pressure chamber 6, and the adjustment of the silencer chamber volume by the second partition 212 is directly controlled by the actual pressure change of the gas volume in the pressure chamber 6.

[0076] The above description is merely a preferred embodiment of the present invention and does not constitute any form of limitation to the present invention. Although the present invention has been disclosed as above in terms of a preferred embodiment, it is not intended to limit the present invention. Any technician familiar with this patent can make slight changes or modifications to equivalent embodiments using the above technical content without departing from the scope of the technical solution of the present invention. However, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention are still within the scope of the solution of the present invention.

Claims

1. A compressor exhaust structure, characterized in that: It comprises a cylinder seat (1) and a muffler chamber (2) and an air inlet hole (3) formed on the cylinder seat (1); A muffler assembly (21) is provided in the muffler chamber (2), the muffler assembly (21) comprising a first partition (211) and a second partition (212) movably mounted on the outside of the first partition (211), the first partition (211) and the second partition (212) dividing the muffler chamber (2) into a first muffler cavity (4), a second muffler cavity (5) and a pressure cavity (6), and the air inlet (3) is in communication with the first muffler cavity (4); A plurality of bypass holes (2111) are provided on the surface of the first partition (211), and the bypass holes (2111) are configured to connect or separate the first muffler cavity (4) and the second muffler cavity (5); The second partition (212) can adjust the number of bypass holes (2111) on the first partition (211) to be opened according to the pressure in the first muffler cavity (4), wherein when the bypass holes are opened, the gas in the first muffler cavity (4) enters the second muffler cavity through the bypass holes and is discharged through the second muffler cavity; The exhaust structure further includes an adjustment component, which is an elastic component (9) installed in the pressure chamber (6) and linked to the second partition (212); The elastic component (9) is configured to adjust the position of the second partition (212) relative to the first partition (211); The exhaust structure further comprises a pressure relief hole (10) in communication with the pressure chamber (6), wherein the pressure relief hole (10) is configured to maintain a constant pressure in the pressure chamber (6) when the position of the second partition (212) is adjusted.

2. The compressor exhaust structure according to claim 1, characterized in that: The second partition (212) is slidably mounted on the outside of the first partition (211).

3. The compressor exhaust structure according to claim 1, characterized in that: The first partition (211) is a sound-absorbing inner spacer ring arranged in the sound-absorbing chamber (2), and the second partition (212) is a sound-absorbing outer spacer ring slidably sleeved on the outside of the sound-absorbing inner spacer ring; The outer muffler spacer ring includes a sleeve portion (2121) and a sealing portion (2122), wherein the sleeve portion (2121) is slidably mounted on the outside of the inner muffler spacer ring, and the sealing portion (2122) is formed at the bottom end of the sleeve portion (2121) and extends toward the inner wall surface of the muffler chamber (2). One end of the sleeve portion (2121) extending toward the inner wall surface of the muffler chamber (2) is in contact with the inner wall surface of the muffler chamber (2) to separate the first muffler chamber (4) and the pressure chamber (6).

4. The compressor exhaust structure according to claim 3, characterized in that: The silencer inner spacer ring is a cylindrical spacer ring, the sleeve portion (2121) is a cylindrical sleeve slidably sleeved on the outside of the silencer inner spacer ring, and the sealing portion (2122) is a sealing flange formed at the bottom edge of the sleeve.

5. The compressor exhaust structure according to claim 4, characterized in that: A first sealing ring (7) and a second sealing ring (8) are respectively provided on the inner annular surface and the outer annular surface of the sealing flange; the inner annular surface of the flange is in indirect contact with the outer wall surface of the muffler inner spacer ring through the first sealing ring (7) to form a first sealing section; and the outer annular surface of the flange is in contact with the inner wall surface of the muffler chamber (2) through the second sealing ring (8) to form a second sealing section.

6. The compressor exhaust structure according to claim 5, characterized in that: A first mounting groove and a second mounting groove are respectively formed on the inner annular surface and the outer annular surface of the sealing flange, and the first sealing ring and the second sealing ring are respectively installed in the first mounting groove and the second mounting groove.

7. The compressor exhaust structure according to claim 6, characterized in that: The central cross section of the first sealing ring (7) and / or the second sealing ring (8) coincides with the central cross section of the flange.

8. The compressor exhaust structure according to claim 7, characterized in that: The elastic component (9) is a spring installed in the pressure chamber (6) and sleeved on the outside of the silencer inner spacer ring. One end of the spring is installed on the bottom surface of the silencer chamber (2), and the other end is installed on the bottom surface of the flange.

9. The compressor exhaust structure according to claim 8, characterized in that: The inner diameter of the spring is greater than the outer diameter of the silencer outer spacer ring.

10. The compressor exhaust structure according to claim 9, characterized in that: There is a clearance fit between the sleeve portion (2121) and the silencer inner spacer ring, the clearance is 2 μm to 4 μm, and the clearance is filled with refrigeration oil.

11. The compressor exhaust structure according to claim 9, characterized in that: The plurality of bypass holes (2111) are evenly distributed along the circumference and axial direction of the silencer inner spacer ring. Among the plurality of bypass holes (2111) distributed along the axial direction of the silencer inner spacer ring, the distance between two adjacent bypass holes (2111) in the axial direction is 2.5 mm to 5 mm, and the bypass holes (2111) are circular holes.

12. The compressor exhaust structure according to claim 11, characterized in that: A chip removal hole is provided through the cylinder seat (1), and the chip removal hole serves as the pressure relief hole (10).

13. The compressor exhaust structure according to claim 12, characterized in that: The exhaust structure further comprises a cylinder head (11) mounted at the opening of the muffler chamber (2), a first sealing gasket (14) and a second sealing gasket (15) being mounted on the upper end surfaces of the muffler chamber (2) and the muffler inner spacer ring, respectively, and the cylinder head (11) is fitted with the first sealing gasket (14) and the second sealing gasket (15) and is locked by means of a fastening screw (12) to isolate the internal gas of the muffler chamber (2) from the external gas.

14. The compressor exhaust structure according to claim 13, characterized in that: A mounting seat (13) is further provided in the muffler chamber (2), the mounting seat (13) being arranged at the bottom center of the muffler chamber (2), and the fastening screw (12) passing through the cylinder head (11) and being fixed on the mounting seat (13); The mounting seat (13) is a cylindrical seat body, and the silencer inner spacer ring is installed on the mounting seat (13) in an interference fit.

15. The compressor exhaust structure according to any one of claims 12 to 14, characterized in that: The muffler components (21) are provided in multiple groups, and two adjacent groups of muffler components (21) are nested with each other. The multiple groups of muffler components (21) divide the muffler chamber (2) into multiple first muffler cavities (4), multiple pressure cavities (6) and one second muffler chamber (5). Among the multiple first muffler cavities (4), the first muffler cavity (4) close to the inner wall of the muffler chamber (2) is connected to the air inlet (3).

16. A refrigeration appliance, characterized in that: The compressor exhaust structure comprises the compressor exhaust structure according to any one of claims 1 to 15.

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