Silencing bag, compressor and refrigeration equipment

Abstract

The invention discloses a silencing bag, a compressor and refrigeration equipment, and relates to the field of compressors. The silencing bag comprises a shell and a first partition plate, an air inlet and an air outlet are formed in the shell and communicate with each other through an inner cavity, and the first partition plate is arranged in the inner cavity and connected to the shell. A first silencing cavity is defined by the first partition plate and part of the inner wall of the inner cavity, the first partition plate is provided with a first protrusion, the first protrusion is provided with a first ventilation opening, and the first ventilation opening communicates with the first silencing cavity. When a refrigerant enters the first silencing cavity from the inner discharge pipe, the section changes suddenly, sound waves generated by the refrigerant are reflected in the propagation direction of a sound source, sound wave energy can be reduced through reflection, and therefore pneumatic noise is reduced. In addition, the side, facing the air inlet, of the first partition plate is the first reflecting face, so that sound waves can be reflected under the influence of the first reflecting face and interfere with incident sound waves, sound wave energy is counteracted, and the pneumatic noise of the refrigerant is further reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a silencer bag, a compressor and a refrigeration device. Background Art

[0002] A compressor is installed in the refrigerator to achieve refrigeration. When the compressor is running, the flow rate of the refrigerant is fast, which causes the compressor to generate a lot of noise. In the related art, a silencer bag is arranged at the air outlet of the compressor, and a plurality of cavities are arranged in the silencer bag. After the refrigerant passes through these cavities, the energy of the refrigerant can be consumed, thereby reducing the aerodynamic noise. However, the noise reduction effect is limited, and it is difficult to achieve a better noise reduction effect. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a silencer package that can further reduce the aerodynamic noise of the refrigerant.

[0004] The present invention also provides a compressor and a refrigeration device having the above-mentioned silencer bag.

[0005] According to the first aspect of the present invention, a silencer bag includes: an outer shell, provided with an inner cavity and an air inlet and an air outlet connected to the inner cavity; a first partition plate, provided in the inner cavity and connected to the outer shell, the first partition plate being configured to separate the inner cavity into a first silencer cavity located on the side of the air inlet, the first partition plate protruding toward the first silencer cavity to form a first protrusion, the first protrusion being provided with a first vent connected to the first silencer cavity, and the first partition plate having a first reflecting surface extending from the first protrusion toward the outer shell on the side facing the first silencer cavity.

[0006] The noise reduction package according to the embodiment of the present invention has at least the following beneficial effects: An inner cavity and an air inlet and an air outlet connected to the inner cavity are arranged in the outer shell, and a first partition is arranged in the inner cavity and connected to the outer shell. A first silencing cavity is formed between the first partition and a part of the inner wall of the inner cavity, and the first partition is provided with a first protrusion, and the first protrusion is provided with a first vent connected to the first silencing cavity. Therefore, the refrigerant enters the first silencing cavity through the air inlet, then passes through the first vent, and finally exits the air outlet. Since the silencing bag is usually connected to the inner row pipe, the inner row pipe is arranged in the air inlet and extends into the first silencing cavity, the cross section of the refrigerant will suddenly change when entering the first silencing cavity from the inner row pipe, so that the acoustic impedance suddenly changes, so that the sound wave generated by the refrigerant is reflected in the propagation direction of the sound source, and the reflection will reduce the sound wave energy, thereby reducing the aerodynamic noise. Since the side of the first partition facing the air inlet is the first reflection surface, the sound wave will be reflected under the influence of the first reflection surface and interfere with the incident sound wave, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0007] According to some embodiments of the present invention, the sound absorbing package further includes a second partition, which is located on a side of the first partition away from the first sound absorbing chamber and is spaced apart from the first partition, a second sound absorbing chamber is formed between the second partition and the first partition, the second partition is provided with a second air vent, and the second sound absorbing chamber connects the first air vent and the second air vent.

[0008] According to some embodiments of the present invention, the second partition protrudes toward the first partition to form a second protrusion, the second protrusion is provided with the second vent, and the side of the second partition facing the first partition has a second reflecting surface extending from the second protrusion toward the shell.

[0009] According to some embodiments of the present invention, a third silencing chamber is formed on a side of the second partition facing away from the first partition and a portion of the inner wall of the inner cavity, and the third silencing chamber is connected to the second vent and the outlet.

[0010] According to some embodiments of the present invention, the second silencing chamber includes a first diffusion chamber, the first diffusion chamber is formed on a side of the first partition away from the first silencing chamber, the first diffusion chamber is connected to the first vent, and the cross-sectional area of ​​the first diffusion chamber gradually increases along the direction from the first partition to the second partition; and / or, The third silencer chamber includes a second diffusion chamber, which is formed on a side of the second partition away from the first partition, and the second diffusion chamber is connected to the second vent. Along the direction in which the second partition is away from the first partition, the cross-sectional area of ​​the second diffusion chamber gradually increases.

[0011] According to some embodiments of the present invention, along the direction of the central axis of the second vent, the height of the second protrusion protruding from the outer edge of the second partition is H2, which satisfies: 2mm≤H2≤4mm.

[0012] According to some embodiments of the present invention, a central axis of the first vent coincides with a central axis of the second vent.

[0013] According to some embodiments of the present invention, the diameter of the largest inscribed circle of the first vent is D1, and the diameter of the largest inscribed circle of the second vent is D2, satisfying: 0.9≤D1 / D2≤1.1.

[0014] According to some embodiments of the present invention, the diameter of the maximum inscribed circle of the second vent is D2, satisfying: 1mm≤D2≤2mm.

[0015] According to some embodiments of the present invention, the diameter of the largest inscribed circle of the first vent is D1, which satisfies: 1mm≤D1≤2mm.

[0016] According to some embodiments of the present invention, on a cross section coinciding with a central axis of the first vent, a contour line of the first reflective surface is an arc line, and the arc line is recessed in a direction away from the first silencing cavity.

[0017] According to some embodiments of the present invention, the angle between the tangent line of the intersection of the arc line and the cavity wall of the inner cavity and the central axis of the first vent is α, which satisfies: 60°≤α≤90°.

[0018] According to some embodiments of the present invention, along the direction of the central axis of the first vent, the height of the first protrusion protruding from the outer edge of the first partition is H1, which satisfies: 2mm≤H1≤4mm.

[0019] According to the second aspect of the present invention, the compressor comprises a shell, a compression assembly, an inner row pipe, an exhaust pipe and the silencer bag described in the above embodiment, wherein the compression assembly is arranged inside the shell, one end of the exhaust pipe is connected to the air outlet end of the compression assembly, the other end of the exhaust pipe is connected to the air inlet of the silencer bag, the air outlet of the silencer bag is connected to the exhaust pipe, and the exhaust pipe passes through the shell.

[0020] The compressor according to the embodiment of the present invention has at least the following beneficial effects: By adopting the silencer bag of the first aspect embodiment, the silencer bag is provided with an inner cavity and an air inlet and an air outlet connected to the inner cavity in the outer shell, and the first partition is provided in the inner cavity and connected to the outer shell. The first partition and the inner wall of the inner cavity enclose a first silencer cavity, the first partition is provided with a first protrusion, and the first protrusion is provided with a first vent connected to the first silencer cavity. Therefore, the refrigerant enters the first silencer cavity through the air inlet, then passes through the first vent, and finally exits the air outlet. Since the silencer bag is usually connected to the inner row pipe, the inner row pipe is arranged in the air inlet and extends into the first silencer cavity, the cross section of the refrigerant will suddenly change when entering the first silencer cavity from the inner row pipe, so that the acoustic impedance suddenly changes, so that the sound wave generated by the refrigerant is reflected in the propagation direction of the sound source, and the reflection will reduce the sound wave energy, thereby reducing the aerodynamic noise. Since the side of the first partition facing the air inlet is the first reflection surface, the sound wave will be reflected under the influence of the first reflection surface and interfere with the incident sound wave, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0021] A refrigeration device according to an embodiment of the third aspect of the present invention comprises the compressor described in the above embodiment.

[0022] The refrigeration device according to the embodiment of the present invention has at least the following beneficial effects: By adopting the compressor of the second embodiment, the silencer bag of the compressor is provided with an inner cavity and an air inlet and an air outlet connected to the inner cavity in the outer shell, and the first partition is provided in the inner cavity and connected to the outer shell. The first partition and the inner wall of the inner cavity enclose a first silencer cavity, the first partition is provided with a first protrusion, and the first protrusion is provided with a first vent connected to the first silencer cavity. Therefore, the refrigerant enters the first silencer cavity through the air inlet, then passes through the first vent, and finally discharges out of the air outlet. Since the silencer bag is usually connected to the inner row pipe, the inner row pipe is passed through the air inlet and extends into the first silencer cavity, the cross section of the refrigerant will suddenly change when entering the first silencer cavity from the inner row pipe, so that the acoustic impedance suddenly changes, so that the sound wave generated by the refrigerant is reflected in the propagation direction of the sound source, and the reflection will reduce the sound wave energy, thereby reducing the aerodynamic noise. Since the side of the first partition facing the air inlet is the first reflection surface, the sound wave will be reflected under the influence of the first reflection surface and interfere with the incident sound wave, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0023] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein: Figure 1 It is a schematic diagram of the structure of a noise reduction package according to an embodiment of the present invention; Figure 2 yes Figure 1 Sectional view at AA in the middle; Figure 3 is a cross-sectional view of a muffler bag according to an embodiment of the present invention; Figure 4 is a schematic structural diagram of a first baffle according to an embodiment of the present invention; Figure 5 is a side view of a first baffle according to an embodiment of the present invention; Figure 6 It is a curve diagram showing the influence of a silencer package of an embodiment of the present invention and a silencer package in related technology on the transmission loss of noises of different frequencies.

[0025] Reference numerals: Silencer package 1000; Shell 100; inner cavity 110; air inlet 120; air outlet 130; third muffler cavity 140; first shell 150; second shell 160; third shell 170; First baffle 200; first muffler cavity 210; first protrusion 220; first reflective surface 230; first vent 240; first diffusion cavity 250; The second partition plate 300 ; the second silencing chamber 310 ; the second protrusion 320 ; the second reflecting surface 330 ; the second vent 340 ; and the second diffusion chamber 350 . DETAILED DESCRIPTION

[0026] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0027] In the description of the present invention, it is necessary to understand that descriptions involving orientation, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply 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.

[0028] In the description of the present invention, "several" means one or more, "more" means more than two, "greater than", "less than", "exceed" etc. are understood as not including the number itself, and "above", "below", "within" etc. are understood as including the number itself. If there is a description of "first" or "second", it is only used for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0029] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0030] Reference Figure 1 and Figure 2 As shown, a silencer bag 1000 according to an embodiment of the present invention can be used for a compressor, especially a reciprocating compressor; or other equipment with an exhaust pipe, such as an exhaust system of a car. The silencer bag 1000 according to the embodiment of the present invention includes a shell 100 and a first partition 200. An inner cavity 110 is provided in the shell 100, and an air inlet 120 and an air outlet 130 are provided in the shell 100 at intervals, and the air inlet 120 and the air outlet 130 are both connected to the inner cavity 110. For example, the air inlet 120 is arranged at the left end of the shell 100, and the air outlet 130 is arranged at the right end of the shell 100, and the inner cavity 110 is located between the air inlet 120 and the air outlet 130, so that the refrigerant enters the inner cavity 110 from the air inlet 120, flows in a left-to-right direction, and is finally discharged from the air outlet 130.

[0031] Reference Figure 2As shown, the first partition 200 is arranged in the inner cavity 110 and connected to the outer shell 100, that is, the outer edge of the first partition 200 is fixedly connected to the inner wall of the inner cavity 110, and the fixed connection method can be welding, so that the outer edge of the first partition 200 and the inner wall of the inner cavity 110 are sealed and matched, so as to prevent the refrigerant from directly leaking through the gap between the first partition 200 and the inner wall of the inner cavity 110, and can improve the stability and reliability of the connection. Of course, the first partition 200 and the outer shell 100 can also be fixedly connected by fasteners, clamping, etc., and a seal is arranged at the fixed connection between the first partition 200 and the outer shell 100, which can also ensure the sealing. Among them, the first partition 200 is configured to separate the inner cavity 110 into a first silencing chamber 210 located on the side of the air inlet 120, that is, the first silencing chamber 210 is enclosed between the side of the first partition 200 facing the air inlet 120 and the part of the inner wall of the inner cavity 110.

[0032] Continue to refer to Figure 2 As shown, the first baffle 200 protrudes toward the direction of the first muffler cavity 210 to form a first protrusion 220, and the first protrusion 220 is located in the middle of the first baffle 200. For example, when the air inlet 120 is located at the left end of the housing 100, the first baffle 200 protrudes toward the direction of the air inlet 120, that is, the first baffle 200 protrudes from the right to the left to form the first protrusion 220. The first protrusion 220 is provided with a first vent 240 connected to the first muffler cavity 210, and the first baffle 200 has a first reflecting surface 230 extending from the first protrusion 220 to the housing 100 on one side facing the first muffler cavity 210. The first reflecting surface 230 is a curved surface, for example, on a cross section coinciding with the central axis of the first vent 240, the contour line of the first reflecting surface 230 is a straight line; or the contour line of the first reflecting surface 230 is a curve, and the curve is bent in a direction away from the first muffler cavity 210.

[0033] With the above solution, the refrigerant enters the first silencing chamber 210 through the air inlet 120, then passes through the first vent 240, and finally exits the air outlet 130. Since the silencing package 1000 is usually connected to an inner row pipe, which is arranged through the air inlet 120 and extends into the first silencing chamber 210, when the refrigerant enters the first silencing chamber 210 from the inner row pipe, the cross section will suddenly change, that is, the acoustic impedance will suddenly change, so that the sound waves generated by the refrigerant are reflected in the propagation direction of the sound source, and the reflection will reduce the sound wave energy, thereby reducing the aerodynamic noise. Figure 3 As shown, Figure 3 The dotted arrow in the figure indicates the transmission direction of the sound wave. Since the side of the first partition 200 facing the air inlet 120 is the first reflecting surface 230, the sound wave will be reflected on the first reflecting surface 230 and interfere with other sound waves, which is conducive to the reflected sound wave and the incident sound wave to overlap or overlap as much as possible, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0034] Reference Figure 2 and Figure 4 As shown, in an embodiment of the present invention, the silencer package 1000 further includes a second partition plate 300, which is disposed in the inner cavity 110 and fixedly connected to the outer shell 100. The fixed connection scheme may be welding, for example, the outer edge of the second partition plate 300 is connected to the inner wall of the inner cavity 110 by welding to ensure the sealing between the outer edge of the second partition plate 300 and the inner wall of the inner cavity 110, and to prevent the refrigerant from leaking through the gap between the second partition plate 300 and the inner wall of the inner cavity 110. Of course, the second partition plate 300 and the outer shell 100 may also be fixedly connected by fasteners, snap-on connection, etc., and a suitable scheme may be selected according to actual conditions. The second partition plate 300 is located on the side of the first partition plate 200 away from the first silencer cavity 210 and is spaced apart from the first partition plate 200, that is, the second partition plate 300 is located on the right side of the first partition plate 200. A second silencing chamber 310 communicating with the first vent 240 is formed between the second partition plate 300 and the first partition plate 200 . The second partition plate 300 is further provided with a second vent 340 communicating with the second silencing chamber 310 .

[0035] It is understandable that when the refrigerant enters the second silencing chamber 310 from the first silencing chamber 210 through the first vent 240, since the aperture of the first vent 240 is smaller than the inner diameter of the second silencing chamber 310, the refrigerant will experience a sudden change in cross-section, causing the sound waves generated by the refrigerant to reflect in the propagation direction of the sound source, that is, the reflected sound waves interfere with the sound waves along the original propagation direction, thereby reducing the sound wave energy and reducing the aerodynamic noise.

[0036] Reference Figure 2 As shown, in the embodiment of the present invention, the second partition 300 protrudes toward the first partition 200 to form a second protrusion 320, the second protrusion 320 is located in the middle of the second partition 300, the second protrusion 320 is provided with a second vent 340, and the second partition 300 has a second reflection surface 330 extending from the second protrusion toward the housing 100 on the side facing the first partition 200. The second reflection surface 330 can be a conical surface, or an arc surface or an elliptical surface that is concave in the direction away from the first partition 200. Since the side of the second partition 300 facing the first partition 200 is the second reflection surface 330, the sound waves entering the second silencing chamber 310 will be reflected when acting on the second reflection surface 330 and interfere with other sound waves, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0037] Continue to refer to Figure 2As shown, in the embodiment of the present invention, a third silencing chamber 140 is formed on a side of the second partition 300 away from the first partition 200 and a part of the inner wall of the inner cavity 110, and the third silencing chamber 140 is connected to the second vent 340 and the air outlet 130. Therefore, the refrigerant enters from the air inlet 120, passes through the first silencing chamber 210, the first vent 240, the second silencing bag 1000, the second vent 340 and the third silencing chamber 140 in sequence, and finally exits the silencing bag 1000 from the air outlet 130. When the refrigerant enters the third silencing chamber 140 from the second vent 340, it will also experience a sudden change in cross section, so that the sound waves generated by the refrigerant are reflected in the propagation direction of the sound source, that is, the reflected sound waves interfere with the sound waves along the original propagation direction, thereby reducing the sound wave energy to reduce the aerodynamic noise. Therefore, the energy of the refrigerant is further reduced after passing through the first silencing chamber 210 , the second silencing chamber 310 , and the third silencing chamber 140 , thereby effectively reducing the aerodynamic noise of the refrigerant.

[0038] Continue to refer to Figure 2 As shown, in the embodiment of the present invention, the first muffler chamber 210 includes a first diffusion chamber 250, and the first diffusion chamber 250 is formed on the side of the first baffle 200 away from the first muffler chamber 210. The first diffusion chamber 250 is connected to the first vent 240, and the cross-sectional area of ​​the first diffusion chamber 250 gradually increases along the direction from the first baffle 200 to the second baffle 300, that is, along the direction from left to right, the cross-sectional area of ​​the first diffusion chamber 250 gradually increases. Among them, the first diffusion chamber 250 is a structure formed by convexity on one side of the first baffle 200 and concave on the other side. When the refrigerant passes through the first air vent 240, it will first enter the first diffusion chamber 250. Since the cross-sectional area of ​​the first diffusion chamber 250 gradually increases, the refrigerant is relatively smooth when entering the second silencer chamber 310, and the flow direction of the refrigerant can be stably controlled, so that the sound waves generated by the refrigerant propagate in a predetermined direction, which is conducive to the sound waves being reflected on the second reflection surface 330, so that the sound waves in the second silencer bag 1000 interfere with each other, consume energy, and can further reduce the aerodynamic noise of the refrigerant.

[0039] Continue to refer to Figure 2As shown, in the embodiment of the present invention, the second muffler chamber 310 includes a second diffusion chamber 350, and the second diffusion chamber 350 is formed on the side of the second partition 300 away from the second muffler chamber 310. The second diffusion chamber 350 is connected to the second vent 340, and the cross-sectional area of ​​the second diffusion chamber 350 gradually increases along the direction from the second partition 300 to the second partition 300, that is, along the direction from left to right, the cross-sectional area of ​​the second diffusion chamber 350 gradually increases. Among them, the second diffusion chamber 350 is a structure formed by convexity on one side of the second partition 300 and concave on the other side. When the refrigerant passes through the second vent 340, it will first enter the second diffusion chamber 350. Since the cross-sectional area of ​​the second diffusion chamber 350 gradually increases, the refrigerant enters the third muffler chamber 140 more smoothly, and the flow direction of the refrigerant can be stably controlled, so that the sound waves generated by the refrigerant propagate in a predetermined direction, which is conducive to the interference of sound waves in the third muffler chamber 140, consuming energy, and further reducing the aerodynamic noise of the refrigerant.

[0040] Reference Figure 6 As shown, Figure 6 The curve with squares in the middle is the silencer package 1000 of the embodiment of the present invention, and the curve with diamond blocks is the silencer package 1000 in the related art. The horizontal axis represents the frequency of the sound wave, and the vertical axis represents the transmission loss of the sound wave. The silencer package 1000 of this embodiment is provided with a first partition 200 and a second partition 300, and the first partition 200 and the second partition 300 separate the first silencer chamber 210, the second silencer chamber 310 and the third silencer chamber 140 in the inner cavity 110. The first partition 200 is provided with a first reflecting surface 230, and the second partition 300 is provided with a second reflecting surface 330. The silencer package 1000 in the related art does not have the above structure. Usually, noise below 500Hz is called low-frequency noise, noise between 500Hz and 2000Hz is medium-frequency noise, and noise above 2000Hz is high-frequency noise. Generally speaking, the aerodynamic noise generated by the refrigerant is usually medium-frequency noise and high-frequency noise. From Figure 6 It can be seen that compared with the solutions in the related art, the solution of this embodiment has a better weakening effect on noise above 1110 Hz. Therefore, the solution of this embodiment has a better noise reduction effect on the medium-frequency noise and high-frequency noise of the compressor, thereby improving the user experience.

[0041] Reference Figure 2As shown, in the embodiment of the present invention, the central axis of the first vent 240 and the central axis of the second vent 340 coincide, that is, the first vent 240 and the second vent 340 are coaxially arranged. It can be understood that coaxiality is more conducive to the discharge of refrigerant, so that the refrigerant can flow in a straight line direction, and the exhaust resistance is reduced while ensuring the silencing effect. At the same time, the first vent 240 and the second vent 340 are coaxially arranged and are respectively located in the middle of the first baffle 200 and the second baffle 300, which can avoid damaging the structural integrity of the first reflection surface 230 and the second reflection surface 330, is conducive to the reflection of sound waves on the first reflection surface 230 and the second reflection surface 330, and is convenient for the production and manufacturing of the first baffle 200 and the second baffle 300.

[0042] Continue to refer to Figure 2 As shown, in the embodiment of the present invention, on the cross section coinciding with the central axis of the first vent 240, the contour line of the first reflective surface 230 on the cross section is an arc line, and the arc line is recessed in the direction away from the first muffler chamber 210. It should be noted that since the air inlet 120 is usually connected to the inner row pipe of the compressor, the inner row pipe will extend into the interior of the first muffler chamber 210, and the refrigerant directly enters the first muffler chamber 210 from the outlet end of the inner row pipe. It can be understood that by designing the contour line of the first reflective surface 230 as an arc line, it is beneficial for the sound wave to be reflected on the first reflective surface 230 to the inner wall of the inner cavity 110, and then reflected through the inner wall of the inner cavity 110 to the direction of the outlet end of the inner row pipe, which is beneficial for the reflected sound wave to overlap with the incident sound wave or overlap as much as possible, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0043] Continue to refer to Figure 2 As shown, in the embodiment of the present invention, the angle between the tangent line S3 of the intersection of the arc line of the first reflective surface 230 and the cavity wall of the inner cavity 110 and the central axis S1 of the first vent 240 is α, which satisfies: 60°≤α≤90°. For example, the value of α can be 60°, 65°, 70°, 75°, 80°, 90°, etc. It should be noted that Figure 2 The central axis of the first vent 240 is S1, and part of the side wall of the shell 100 is parallel to the central axis S1. For the convenience of marking, the angle α between the tangent S3 at one end of the arc line of the first reflective surface 230 and part of the side wall of the shell 100 is used for marking, which is equivalent to the angle between the tangent S3 and the central axis S1.

[0044] It can be understood that the size of α reflects the radius of the arc line of the first reflecting surface 230. When α is less than 60°, the radius of the arc line decreases, the depth of the depression increases, and the sound wave is difficult to interfere with the incident sound wave after being reflected on the first arc surface, resulting in a poor noise reduction effect. When α is greater than 90°, the radius of the arc line increases, that is, the depth of the depression decreases, which is also not conducive to the interference between the incident sound wave and the reflected sound wave, and the noise reduction effect is poor. To this end, by reasonably designing the value of α to be within the range of 60° to 90°, it is beneficial to the interference between the incident sound wave and the reflected sound wave, thereby improving the noise reduction effect.

[0045] Continue to refer to Figure 2 As shown, in the embodiment of the present invention, on the cross section coinciding with the central axis of the second vent 340, the contour line of the second reflective surface 330 on the cross section is an arc line, and the second arc surface is recessed in the direction away from the second muffler chamber 310. It can be understood that by designing the contour line of the second reflective surface 330 as an arc line, it is beneficial for the sound wave to be reflected on the second reflective surface 330 to the inner wall of the inner cavity 110, and then reflected through the inner wall of the inner cavity 110 to the direction of the first vent 240, which is beneficial for the reflected sound wave to overlap with the incident sound wave or overlap as much as possible, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0046] Continue to refer to Figure 2 As shown, in the embodiment of the present invention, the angle between the tangent line S4 of the arc line of the second reflective surface 330 connected to one end of the inner wall of the inner cavity 110 and the central axis S2 of the second vent 340 is β, which satisfies: 60°≤β≤90°, for example, the value of β can be 60°, 65°, 70°, 75°, 80°, 90°, etc. It should be noted that Figure 2 The central axis of the second vent 340 is S2, and part of the side wall of the shell 100 is parallel to the central axis S2. For the convenience of marking, the angle β between the tangent S4 at one end of the arc line of the second reflecting surface 330 and part of the side wall of the shell 100 is used for marking, which is equivalent to the angle between the tangent S4 and the central axis S2.

[0047] It is understandable that the size of β reflects the radius of the arc line of the second reflection surface 330. When β is less than 60°, the radius of the arc line decreases, the depth of the depression increases, and the sound wave is difficult to interfere with the incident sound wave after being reflected on the second arc surface, resulting in a poor noise reduction effect. When β is greater than 90°, the radius of the arc line increases, that is, the depth of the depression decreases, which is also not conducive to the interference between the incident sound wave and the reflected sound wave, and the noise reduction effect is poor. To this end, by reasonably designing the value of β within the range of 60° to 90°, it is beneficial to the interference between the incident sound wave and the reflected sound wave, thereby improving the noise reduction effect.

[0048] Reference Figure 2 and Figure 5As shown, in the embodiment of the present invention, along the direction of the central axis of the first vent 240, that is, the left-right direction of the housing 100, the height of the first protrusion 220 protruding from the outer edge of the first partition 200 is H1, which satisfies: 2mm≤H1≤4mm, for example, the value of H1 can be 2mm, 2.5mm, 3mm, 3.5mm, 4mm, etc. It can be understood that when H1 is less than 2mm, that is, the protruding height of the first protrusion 220 is small, it is difficult to form the first reflecting surface 230 on the first partition 200. When H1 is greater than 4mm, that is, the protruding height of the first protrusion 220 is high, it occupies more space and is easy to interfere with the inner row of pipes. Therefore, by reasonably designing the protruding height H1 of the first protrusion 220 between 2mm and 4mm, the first reflecting surface 230 can be effectively formed on the first partition 200, while ensuring the rationality of the structural design.

[0049] Reference Figure 2 As shown, in the embodiment of the present invention, along the direction of the central axis of the second vent 340, that is, the left-right direction of the housing 100, the height of the second protrusion 320 protruding from the outer edge of the second baffle 300 is H2, which satisfies: 2mm≤H2≤4mm, for example, the value of H2 can be 2mm, 2.5mm, 3mm, 3.5mm, 4mm, etc. It can be understood that when H2 is less than 2mm, that is, the protruding height of the second protrusion 320 is small, it is difficult to form the second reflecting surface 330 on the second baffle 300. When H2 is greater than 4mm, that is, the protruding height of the second protrusion 320 is high, it occupies more space and is easy to interfere with the inner row of pipes. Therefore, by reasonably designing the protruding height H2 of the second protrusion 320 between 2mm and 4mm, the second reflecting surface 330 can be effectively formed on the second baffle 300, while ensuring the rationality of the structural design.

[0050] Continue to refer to Figure 2 As shown, in an embodiment of the present invention, the diameter of the maximum inscribed circle of the first air vent 240 is D1, which satisfies: 1mm≤D1≤2mm. When D1 is less than 1mm, the aperture of the first air vent 240 is too small, the resistance of the refrigerant passing through the first air vent 240 increases, and the exhaust flow rate decreases. When D1 is greater than 2mm, the aperture of the first air vent 240 is too large, which will make the cross-sectional change after passing through the first air vent 240 unclear, and it is difficult to achieve a good noise reduction effect. Therefore, by reasonably designing the diameter D1 of the maximum inscribed circle of the first air vent 240 to be between 1mm and 2mm, the smoothness of the refrigerant exhaust can be guaranteed, and the noise reduction effect can be improved at the same time.

[0051] Continue to refer to Figure 2As shown, in an embodiment of the present invention, the diameter of the maximum inscribed circle of the second air vent 340 is D2, which satisfies: 1mm≤D2≤2mm. When D2 is less than 1mm, the aperture of the second air vent 340 is too small, the resistance of the refrigerant passing through the second air vent 340 increases, and the exhaust flow rate decreases. When D2 is greater than 2mm, the aperture of the second air vent 340 is too large, which will make the cross-sectional change after passing through the second air vent 340 unclear, and it is difficult to achieve a good noise reduction effect. Therefore, by reasonably designing the diameter D2 of the maximum inscribed circle of the second air vent 340 to be between 1mm and 2mm, the smoothness of the refrigerant exhaust can be guaranteed, and the noise reduction effect can be improved at the same time.

[0052] Continue to refer to Figure 2 As shown, in the embodiment of the present invention, the diameter of the maximum inscribed circle of the first vent 240 is D1, and the diameter of the maximum inscribed circle of the second vent 340 is D2, which satisfies: 0.9≤D1 / D2≤1.1, for example, the value of D1 / D2 can be 0.9, 0.95, 1, 1.05, 1.1, etc. It can be understood that in order to reduce production costs, the first baffle 200 and the second baffle 300 have similar structures and similar sizes, so only one type of baffle needs to be produced, and there is no need to produce two different baffles separately. To this end, by limiting the maximum inscribed circle diameter D1 of the first vent 240 and the maximum inscribed circle diameter D1 of the second vent 340 within the range of 0.9 to 1.1, it can ensure that the sizes of the first vent 240 and the second vent 340 are as similar as possible, reduce production costs, improve production efficiency, and simplify the assembly of the silencer package 1000.

[0053] Reference Figure 2As shown, in the embodiment of the present invention, the housing 100 includes a first shell 150, a second shell 160 and a third shell 170, the open end of the first shell 150 is sleeved on one end of the second shell 160, and the first shell 150 and the second shell 160 are fixedly connected by welding; the end of the second shell 160 away from the first shell 150 is sleeved on the open end of the third shell 170, and the second shell 160 and the third shell 170 are fixedly connected by welding. The welding method can improve the stability and reliability of the connection between the first shell 150, the second shell 160 and the third shell 170, and there is no need to design other connection structures, so that the overall structure of the silencer package 1000 is more compact. At the same time, the sealing of the first shell 150 and the second shell 160 at the connection point can be guaranteed, and the sealing of the second shell 160 and the third shell 170 at the connection point can be guaranteed, and the leakage of refrigerant can be effectively avoided. It should be noted that an air inlet 120 is provided at one end of the first shell 150 away from the second shell 160, and an air outlet 130 is provided at one end of the third shell 170 away from the second shell 160, and the air inlet 120, the first air vent 240, the second air vent 340 and the air outlet 130 are coaxially arranged, which can improve the smoothness of the refrigerant operation.

[0054] A compressor according to an embodiment of the present invention comprises a housing, a compression assembly, an inner row pipe, an exhaust pipe, and a muffler bag 1000 according to the above embodiment. The compressor may be a reciprocating compressor, a centrifugal compressor, a screw compressor, etc., and the compressor is applied to refrigeration equipment such as refrigerators and air conditioners. The compression assembly is arranged inside the housing, one end of the exhaust pipe is connected to the air outlet end of the compression assembly, the other end of the exhaust pipe is connected to the air inlet 120 of the muffler bag 1000, the air outlet 130 of the muffler bag 1000 is connected to the exhaust pipe, and the exhaust pipe passes through the housing.

[0055] The compressor of the embodiment of the present invention adopts the muffler package 1000 of the above embodiment, by setting an air inlet 120 and an air outlet 130 on the shell 100 of the muffler package 1000, the air inlet 120 and the air outlet 130 are connected through the inner cavity 110, and the first partition 200 is set in the inner cavity 110 and connected to the shell 100. The first partition 200 and the inner wall of the inner cavity 110 are enclosed to form a first muffler cavity 210, the first partition 200 is provided with a first protrusion 220, the first protrusion 220 is provided with a first vent 240, and the first vent 240 is connected with the first muffler cavity 210. Therefore, the refrigerant enters the first muffler cavity 210 through the air inlet 120, and then passes through the first vent 240, and finally discharged from the air outlet 130. Since the silencer package 1000 is usually connected to an inner row of pipes, which are arranged through the air inlet 120 and extend into the first silencer cavity 210, the cross section will suddenly change when the refrigerant enters the first silencer cavity 210 from the inner row of pipes, i.e., the acoustic impedance will suddenly change, so that the sound waves generated by the refrigerant are reflected in the propagation direction of the sound source, and the reflection will reduce the sound wave energy, thereby reducing the aerodynamic noise. Since the side of the first partition 200 facing the air inlet 120 is the first reflection surface 230, the sound waves will be reflected under the influence of the first reflection surface 230 and interfere with other sound waves, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0056] Since the compressor adopts all the technical solutions of the silencer package 1000 of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment, which will not be repeated here.

[0057] A refrigeration device according to an embodiment of the present invention includes the compressor according to the above embodiment. The refrigeration device may be a refrigerator, an air conditioner, etc. The refrigeration device according to the embodiment of the present invention adopts the compressor according to the above embodiment, and the compressor is provided with an air inlet 120 and an air outlet 130 in the outer shell 100 of the muffler package 1000, and the air inlet 120 and the air outlet 130 are connected through the inner cavity 110, and the first partition 200 is provided in the inner cavity 110 and connected to the outer shell 100. A first muffler cavity 210 is enclosed between the first partition 200 and a part of the inner wall of the inner cavity 110, and the first partition 200 is provided with a first protrusion 220, and the first protrusion 220 is provided with a first vent 240, and the first vent 240 is connected with the first muffler cavity 210. Therefore, the refrigerant enters the first muffler cavity 210 through the air inlet 120, and then passes through the first vent 240, and finally is discharged from the air outlet 130. Since the silencer package 1000 is usually connected to an inner row of pipes, which are arranged through the air inlet 120 and extend into the first silencer cavity 210, the cross section will suddenly change when the refrigerant enters the first silencer cavity 210 from the inner row of pipes, i.e., the acoustic impedance will suddenly change, so that the sound waves generated by the refrigerant are reflected in the propagation direction of the sound source, and the reflection will reduce the sound wave energy, thereby reducing the aerodynamic noise. Since the side of the first partition 200 facing the air inlet 120 is the first reflection surface 230, the sound waves will be reflected under the influence of the first reflection surface 230 and interfere with other sound waves, so that the sound wave energy cancels each other, thereby further reducing the aerodynamic noise of the refrigerant.

[0058] Since the refrigeration device adopts all the technical solutions of the compressor of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment, which will not be repeated here.

[0059] The embodiments of the present invention are described in detail above with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A silencer bag, characterized in that: include: A shell having an inner cavity and an air inlet and an air outlet communicating with the inner cavity; A first partition is provided in the inner cavity and connected to the outer shell, the first partition is configured to separate the inner cavity into a first silencer cavity located on the side of the air inlet, the first partition protrudes toward the first silencer cavity to form a first protrusion, the first protrusion is provided with a first vent connected to the first silencer cavity, and the first partition has a first reflecting surface extending from the first protrusion toward the outer shell on the side facing the first silencer cavity.

2. The sound-absorbing bag according to claim 1, characterized in that: The silencer bag also includes a second partition, which is located on the side of the first partition away from the first silencer cavity and is spaced apart from the first partition, a second silencer cavity is formed between the second partition and the first partition, the second partition is provided with a second vent, and the second silencer cavity connects the first vent and the second vent.

3. The sound-absorbing bag according to claim 2, characterized in that: The second partition protrudes toward the first partition to form a second protrusion, the second protrusion is provided with the second vent, and the second partition has a second reflecting surface extending from the second protrusion toward the shell on one side facing the first partition.

4. The sound-absorbing bag according to claim 3, characterized in that: A third silencing chamber is formed on a side of the second partition away from the first partition and a portion of the inner wall of the inner cavity. The third silencing chamber is connected to the second vent and the air outlet.

5. The sound-absorbing bag according to claim 4, characterized in that: The second silencing chamber comprises a first diffusion chamber, the first diffusion chamber is formed on a side of the first partition away from the first silencing chamber, the first diffusion chamber is communicated with the first vent, and the cross-sectional area of ​​the first diffusion chamber gradually increases along the direction from the first partition to the second partition; and / or, The third silencer chamber includes a second diffusion chamber, which is formed on a side of the second partition away from the first partition, and the second diffusion chamber is connected to the second vent. Along the direction in which the second partition is away from the first partition, the cross-sectional area of ​​the second diffusion chamber gradually increases.

6. The sound-absorbing bag according to claim 3, characterized in that: Along the direction of the central axis of the second vent, the height of the second protrusion protruding from the outer edge of the second partition is H2, which satisfies: 2mm≤H2≤4mm.

7. The sound-absorbing bag according to claim 2 or 3, characterized in that: The central axis of the first vent coincides with the central axis of the second vent.

8. The sound-absorbing bag according to claim 2 or 3, characterized in that: The diameter of the largest inscribed circle of the first vent is D1, and the diameter of the largest inscribed circle of the second vent is D2, which satisfies: 0.9≤D1 / D2≤1.

1.

9. The sound-absorbing bag according to claim 2, characterized in that: The diameter of the largest inscribed circle of the second vent is D2, which satisfies: 1mm≤D2≤2mm.

10. The sound-absorbing bag according to claim 1, characterized in that: The diameter of the largest inscribed circle of the first vent is D1, which satisfies: 1mm≤D1≤2mm.

11. The sound-absorbing bag according to claim 1, characterized in that: On a cross section coinciding with the central axis of the first vent, the contour line of the first reflective surface is an arc line, and the arc line is recessed in a direction away from the first muffler cavity.

12. The sound-absorbing bag according to claim 11, characterized in that: The angle between the tangent line of the intersection of the arc line and the cavity wall of the inner cavity and the central axis of the first vent is α, which satisfies: 60°≤α≤90°.

13. The sound-absorbing bag according to claim 1, characterized in that: Along the direction of the central axis of the first vent, the height of the first protrusion protruding from the outer edge of the first partition is H1, which satisfies: 2mm≤H1≤4mm.

14. A compressor, characterized in that: It comprises a shell, a compression assembly, an inner row pipe, an exhaust pipe and a silencer pack according to any one of claims 1 to 12, wherein the compression assembly is arranged inside the shell, one end of the exhaust pipe is connected to the air outlet end of the compression assembly, the other end of the exhaust pipe is connected to the air inlet of the silencer pack, the air outlet of the silencer pack is connected to the exhaust pipe, and the exhaust pipe passes through the shell.

15. Refrigeration equipment, characterized in that: Comprising the compressor as claimed in claim 14.

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