A noise reduction structure and scroll compressor

Abstract

This application provides a noise reduction structure and a scroll compressor. A first chamber is disposed on the stationary scroll plate of the scroll compressor and connected to the exhaust passage of the stationary scroll plate. A second chamber is disposed above the first chamber and connected to it. The first and second chambers are constructed to satisfy one or more of the following: the equivalent diameter of the first chamber is greater than the equivalent diameter of the second chamber; the equivalent diameter of the first chamber is greater than the axial height of the first chamber; the equivalent diameter of the second chamber is greater than the axial height of the second chamber; and the volume of the first chamber is greater than the volume of the second chamber. On the one hand, this allows for a sudden increase in the flow area and a decrease in the velocity of the high-pressure refrigerant discharged from the pump body, thereby reducing exhaust noise and vibration. On the other hand, the high-pressure refrigerant can generate vibration and friction under the reflection of the first and second chambers, further reducing exhaust noise and vibration.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and particularly to a noise reduction structure and a scroll compressor. Background Technology

[0002] A scroll compressor is a positive displacement compressor. The compression component consists of a moving scroll and a stationary scroll. During operation, the high-pressure refrigerant obtained through the compression component is discharged from the pump body. The high-pressure refrigerant discharged from the pump body directly impacts the top cover of the scroll compressor, resulting in excessive noise and vibration at the top of the compressor. Summary of the Invention

[0003] This application provides a noise reduction structure and a scroll compressor, which can solve the problem that the high-pressure refrigerant in the existing discharge pump directly impacts the top cover of the scroll compressor, resulting in excessive noise and vibration at the top of the compressor.

[0004] In a first aspect, embodiments of this application provide a noise reduction structure, including:

[0005] The first cavity is located on the stationary scroll plate of the scroll compressor and is connected to the exhaust passage of the stationary scroll plate.

[0006] The second cavity is located above the first cavity and is connected to the first cavity;

[0007] The first cavity and the second cavity are constructed to satisfy one or more of the following:

[0008] The equivalent diameter of the first cavity is larger than the equivalent diameter of the second cavity;

[0009] The equivalent diameter of the first cavity is greater than the axial height of the first cavity;

[0010] The equivalent diameter of the second cavity is greater than the axial height of the second cavity; and

[0011] The volume of the first cavity is larger than the volume of the second cavity.

[0012] In some embodiments, the equivalent diameter of the first cavity and the equivalent diameter of the second cavity satisfy the following conditions: Where D1 is the equivalent diameter of the first cavity and D2 is the equivalent diameter of the second cavity.

[0013] In some embodiments, the equivalent diameter of the first cavity and the equivalent diameter of the exhaust channel satisfy the following conditions: Where D1 is the equivalent diameter of the first cavity and D is the equivalent diameter of the exhaust channel.

[0014] In some embodiments, the equivalent diameter of the first cavity and the axial height of the first cavity satisfy the following conditions: Wherein, H1 is the axial height of the first cavity and D1 is the equivalent diameter of the first cavity;

[0015] The equivalent diameter of the second cavity and the axial height of the second cavity satisfy the following conditions: Where H2 is the axial height of the second cavity and D2 is the equivalent diameter of the second cavity.

[0016] In some embodiments, the volume of the first cavity and the volume of the second cavity satisfy the following... Wherein, V1 is the equivalent volume of the first cavity and V2 is the equivalent volume of the second cavity.

[0017] In some embodiments, the volume of the first cavity, the volume of the second cavity, and the displacement of the scroll compressor satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity, V2 is the equivalent volume of the second cavity, and V is the displacement of the scroll compressor.

[0018] In some embodiments, at least one exhaust port is provided on the end face of the first cavity and / or the second cavity.

[0019] In some embodiments, the at least one vent is a plurality of vents, which are spaced apart circumferentially along the first cavity.

[0020] In some embodiments, the equivalent diameter of the exhaust port and the equivalent diameter of the exhaust channel satisfy the following conditions: Where D is the equivalent diameter of the exhaust channel and D3 is the equivalent diameter of the exhaust port.

[0021] In some embodiments, the noise reduction structure further includes a connecting pressure edge, which is connected to the bottom end of the first cavity and connected to the static vortex disk via a connector.

[0022] Secondly, embodiments of this application provide a scroll compressor, including a silencer structure as described in any one of the first aspects.

[0023] Compared with the prior art, the advantages of the embodiments of this application are that by placing the first cavity on the stationary scroll of the scroll compressor and connecting the first cavity with the exhaust channel of the stationary scroll; and placing the second cavity above the first cavity and connecting the second cavity with the first cavity, wherein the equivalent diameter of the first cavity is larger than the equivalent diameter of the second cavity, on the one hand, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be abruptly increased and the speed reduced, thereby reducing exhaust noise and vibration; on the other hand, the high-pressure refrigerant can generate vibration and friction under the reflection of the first cavity and the second cavity, reducing exhaust noise and vibration. Attached Figure Description

[0024] The invention will now be described in more detail with reference to embodiments and the accompanying drawings.

[0025] Figure 1 This is a cross-sectional view of a scroll compressor provided in an embodiment of the present invention;

[0026] Figure 2 This is a perspective view of a noise reduction structure provided in an embodiment of the present invention;

[0027] Figure 3 This is a bottom view of a noise-absorbing structure provided in an embodiment of the present invention;

[0028] Figure 4 This is an assembly diagram of a noise reduction structure provided in an embodiment of the present invention;

[0029] Figure 5 This is a perspective view of a noise reduction structure provided in another embodiment of the present invention;

[0030] Figure 6 This is an assembly diagram of a noise reduction structure provided in another embodiment of the present invention;

[0031] Figure 7 This is a perspective view of a noise reduction structure provided in another embodiment of the present invention;

[0032] Figure 8 This is a comparison diagram of the noise reduction effect provided by another embodiment of the present invention.

[0033] Figure label:

[0034] 10. Silencing structure; 110. First cavity; 120. Second cavity; 130. Connecting pressure edge; 1001. Exhaust port;

[0035] 20. Static vortex disk;

[0036] 30. Exhaust passage. Detailed Implementation

[0037] The invention will now be further described with reference to the accompanying drawings.

[0038] A scroll compressor consists of a sealed casing, a stationary scroll, a moving scroll, a support frame, an eccentric crankshaft, an anti-rotation mechanism, and a motor. Both the moving and stationary scrolls have helical profiles. The moving scroll is installed with an eccentricity of 180° relative to the stationary scroll, thus creating multiple crescent-shaped spaces between them. During operation, the moving scroll rotates around the center of the stationary scroll with a certain eccentric radius, performing a non-rotating rotary translation. The outer crescent-shaped spaces continuously move towards the center, gradually pushing the refrigerant towards the central space. Its volume continuously decreases while its pressure continuously increases until it connects with the central exhaust port. The high-pressure refrigerant is discharged from the pump body, and the discharged high-pressure refrigerant directly impacts the top cover, resulting in significant noise and vibration at the top of the scroll compressor.

[0039] Example 1:

[0040] In response to the above technical problems, such as Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown in the figure, this application embodiment provides a noise reduction structure, including:

[0041] The first cavity 110 is located on the stationary scroll plate 20 of the scroll compressor and is connected to the exhaust passage 30 of the stationary scroll plate 20.

[0042] The second cavity 120 is located above the first cavity 110 and is connected to the first cavity 110.

[0043] The first cavity 110 and the second cavity 120 are configured to satisfy one or more of the following:

[0044] The equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120;

[0045] The equivalent diameter of the first cavity 110 is greater than the axial height of the first cavity 110;

[0046] The equivalent diameter of the second cavity 120 is greater than the axial height of the second cavity 120; and

[0047] The volume of the first cavity 110 is larger than the volume of the second cavity 120.

[0048] It should be noted that the above equivalent diameters are all dimensions after being equivalent to a circle. If its cross-section is a square, the equivalent diameter is the side length of the square; if its cross-section is a circle, the equivalent diameter is the diameter of the circle; if its cross-section is a combination of various shapes, the equivalent diameter is the square root of the cross-sectional area of ​​the expansion chamber.

[0049] It should be noted that the first cavity 110 is located above the stationary scroll plate 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the silencing structure 10 near the top cover of the scroll compressor can be smaller, thus avoiding contact with the top cover. The shape of the second cavity 120 can be adjusted according to the shape of the top cover or the shape of other components inside the scroll compressor, such as a circular shape. Figure 2 As shown), such as a near semicircle (as shown) Figure 5 , Figure 6 As shown), similarly, the shape of the first cavity 110 can also be adjusted according to the shape of the components inside the scroll compressor, such as... Figure 3 , Figure 7 As shown, the first cavity 110 is provided with a circular groove.

[0050] It should be noted that by placing the first chamber 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first chamber 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second chamber 120 above the first chamber 110 and connecting the second chamber 120 to the first chamber 110, wherein the equivalent diameter of the first chamber 110 is larger than the equivalent diameter of the second chamber 120, on the one hand, the high-pressure refrigerant enters the lower layer of the silencing structure 10 with a larger equivalent diameter from the exhaust passage 30 of the stationary scroll plate 20 with a smaller equivalent diameter. When the high-pressure refrigerant enters the first cavity 110 and then the second cavity 120 on the upper layer of the silencing structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can suddenly increase and the speed can be reduced, thereby reducing exhaust noise and vibration. On the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (i.e., the acoustic impedance changes), the sudden change in its flow cross section will reflect part of the sound waves back to the direction of the sound source. During this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces pressure pulsation energy, thereby reducing exhaust pulsation and improving exhaust noise.

[0051] It should be noted that, based on the noise reduction structure 10 provided in the embodiments of this application, a formula for the noise reduction amount of the noise reduction structure 10 of this application can be constructed, namely... Construct the expansion ratio formula, that is Construct the shrinkage ratio formula, that is Constructing the wavenumber formula, i.e. Where m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound velocity, and f is the sound wave frequency.

[0052] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the second cavity 120 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D2 is the equivalent diameter of the second cavity 120.

[0053] It should be noted that by making (Right now On the one hand, it allows sufficient space on the end face of the first cavity 110 to open the exhaust port 1001. On the other hand, it ensures that the first cavity 110 and the second cavity 120 have sufficient vibration space under the impact of high-pressure refrigerant, thereby reducing noise through the vibration of the first cavity 110 and the second cavity 120.

[0054] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D is the equivalent diameter of the exhaust channel 30.

[0055] It should be noted that if the equivalent diameter of the first cavity 110 is too large or too small, it will be difficult to achieve a good noise reduction effect. Furthermore, the space inside the scroll compressor is limited and cannot support a large first cavity 110 or a large second cavity 120. (Right now This means that the expansion ratio m of the silencing structure 10 can be limited, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, thereby allowing the high-pressure refrigerant to reduce its speed and have a large acoustic impedance when it is discharged into the silencing structure 10.

[0056] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy the following conditions: Wherein, H1 is the axial height of the first cavity 110 and D1 is the equivalent diameter of the first cavity 110;

[0057] The equivalent diameter and axial height of the second cavity 120 satisfy the following conditions: Wherein, H2 is the axial height of the second cavity 120 and D2 is the equivalent diameter of the second cavity 120.

[0058] It should be noted that if the axial height H1 of the first cavity 110 is too small, it will hinder the expansion of the high-pressure refrigerant; and due to the limited space inside the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. This allows the equivalent diameter D1 of the first cavity 110 to have a suitable ratio with its axial height H1, facilitating the expansion of the high-pressure refrigerant and the vibration and friction under the action of acoustic impedance, thereby reducing vibration and noise.

[0059] It should be noted that while adding a second cavity 120 increases the volume of the silencing structure 10, if the height of the second cavity 120 is too large and its equivalent diameter is too small, it will hinder the entry and exit of the high-pressure refrigerant. It facilitates the entry and exit of high-pressure refrigerant into and out of the second chamber 120.

[0060] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110 and V2 is the equivalent volume of the second cavity 120;

[0061] In some embodiments, the volume of the first cavity 110, the volume of the second cavity 120, and the displacement of the scroll compressor satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110, V2 is the equivalent volume of the second cavity 120, and V is the displacement of the scroll compressor.

[0062] It should be noted that by making This limits the equivalent diameter of the second cavity 120, allowing the high-pressure refrigerant entering the first cavity 110 to re-enter the second cavity 120, which has a smaller equivalent diameter, for noise reduction; by making The size parameters of the silencing structure 10 can be set according to the displacement of the scroll compressor to achieve a better noise reduction effect.

[0063] In some embodiments, at least one exhaust port 1001 is provided on the end face of the first cavity 110 and / or the second cavity 120.

[0064] It should be noted that, as Figure 2 , Figure 4 , Figure 5 As shown, the end face of the first cavity 110 is the upper surface of the first cavity 110. The exhaust port 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120. A preset distance can be left between the exhaust port 1001 and the side wall of the first cavity 110, and a preset distance can be left between the exhaust port 1001 and the side wall of the second cavity 120, so that the exhaust port 1001 has sufficient vibration space (or position).

[0065] In some embodiments, the equivalent diameter of the exhaust port 1001 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Where D is the equivalent diameter of exhaust channel 30 and D3 is the equivalent diameter of exhaust hole 1001;

[0066] It should be noted that the high-pressure refrigerant entering the silencing structure 10 is eventually discharged from the silencing structure 10 through the exhaust port 1001. If the equivalent diameter of the exhaust port 1001 is too large, the high-pressure refrigerant entering the silencing structure 10 will be discharged from the silencing structure 10 without sufficient silencing. If the equivalent diameter of the exhaust port 1001 is too small, the high-pressure refrigerant that has undergone silencing and vibration reduction cannot be discharged from the silencing structure 10 in time. Therefore, setting the equivalent diameter of the exhaust port 1001 according to the equivalent diameter of the exhaust channel 30 of the scroll compressor (often representing the displacement) can ensure that the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 is discharged from the silencing structure 10 (first cavity 110 and second cavity 120) in time after sufficient silencing and vibration reduction.

[0067] It should be noted that, through simulation and actual testing, by making

[0068] (Right now This allows the noise reduction structure 10 of the present application embodiments to effectively reduce noise levels in the 1750-1850Hz and 2000-2300Hz frequency bands, as shown in Table 1 and... Figure 8 As shown, in actual tests, the noise reduction effect of the noise reduction structure 10 of this application embodiment and the conventional silencer is improved by 2dB to 3dB, which can improve product performance and user experience.

[0069] Table 1

[0070]

[0071] In summary, the advantages of this embodiment are that by placing the first cavity 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first cavity 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second cavity 120 above the first cavity 110 and connecting the second cavity 120 to the first cavity 110, wherein the equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120, on the one hand, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be abruptly increased and the speed reduced, thereby reducing exhaust noise and vibration; on the other hand, some sound energy can be canceled out under the reflection effect of the first cavity 110 and the second cavity 120, reducing exhaust noise and vibration.

[0072] Example 2:

[0073] like Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown in the figure, this application embodiment provides a noise reduction structure, including:

[0074] The first cavity 110 is located on the stationary scroll plate 20 of the scroll compressor and is connected to the exhaust passage 30 of the stationary scroll plate 20.

[0075] The second cavity 120 is located above the first cavity 110 and is connected to the first cavity 110.

[0076] The first cavity 110 and the second cavity 120 are configured to satisfy one or more of the following:

[0077] The equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120;

[0078] The equivalent diameter of the first cavity 110 is greater than the axial height of the first cavity 110;

[0079] The equivalent diameter of the second cavity 120 is greater than the axial height of the second cavity 120; and

[0080] The volume of the first cavity 110 is larger than the volume of the second cavity 120.

[0081] It should be noted that the above equivalent diameters are all dimensions after being equivalent to a circle. If its cross-section is a square, the equivalent diameter is the side length of the square; if its cross-section is a circle, the equivalent diameter is the diameter of the circle; if its cross-section is a combination of various shapes, the equivalent diameter is the square root of the cross-sectional area of ​​the expansion chamber.

[0082] It should be noted that the first cavity 110 is located above the stationary scroll plate 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the silencing structure 10 near the top cover of the scroll compressor can be smaller, thus avoiding contact with the top cover. The shape of the second cavity 120 can be adjusted according to the shape of the top cover or the shape of other components inside the scroll compressor, such as a circular shape. Figure 2 As shown), such as a near semicircle (as shown) Figure 5 , Figure 6 As shown), similarly, the shape of the first cavity 110 can also be adjusted according to the shape of the components inside the scroll compressor, such as... Figure 3 , Figure 7 As shown, the first cavity 110 is provided with a circular groove.

[0083] It should be noted that by placing the first chamber 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first chamber 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second chamber 120 above the first chamber 110 and connecting the second chamber 120 to the first chamber 110, wherein the equivalent diameter of the first chamber 110 is larger than the equivalent diameter of the second chamber 120, on the one hand, the high-pressure refrigerant enters the lower layer of the silencing structure 10 with a larger equivalent diameter from the exhaust passage 30 of the stationary scroll plate 20 with a smaller equivalent diameter. When the high-pressure refrigerant enters the first cavity 110 and then the second cavity 120 on the upper layer of the silencing structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can suddenly increase and the speed can be reduced, thereby reducing exhaust noise and vibration. On the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (i.e., the acoustic impedance changes), the sudden change in its flow cross section will reflect part of the sound waves back to the direction of the sound source. During this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces pressure pulsation energy, thereby reducing exhaust pulsation and improving exhaust noise.

[0084] It should be noted that, based on the noise reduction structure 10 provided in the embodiments of this application, a formula for the noise reduction amount of the noise reduction structure 10 of this application can be constructed, namely... Construct the expansion ratio formula, that is Construct the shrinkage ratio formula, that is Constructing the wavenumber formula, i.e. Where m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound velocity, and f is the sound wave frequency.

[0085] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the second cavity 120 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D2 is the equivalent diameter of the second cavity 120.

[0086] It should be noted that by making (Right now On the one hand, it allows sufficient space on the end face of the first cavity 110 to open the exhaust port 1001. On the other hand, it ensures that the first cavity 110 and the second cavity 120 have sufficient vibration space under the impact of high-pressure refrigerant, thereby reducing noise through the vibration of the first cavity 110 and the second cavity 120.

[0087] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D is the equivalent diameter of the exhaust channel 30.

[0088] It should be noted that if the equivalent diameter of the first cavity 110 is too large or too small, it will be difficult to achieve a good noise reduction effect. Furthermore, the space inside the scroll compressor is limited and cannot support a large first cavity 110 or a large second cavity 120. (Right now This means that the expansion ratio m of the silencing structure 10 can be limited, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, thereby allowing the high-pressure refrigerant to reduce its speed and have a large acoustic impedance when it is discharged into the silencing structure 10.

[0089] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy the following conditions: Wherein, H1 is the axial height of the first cavity 110 and D1 is the equivalent diameter of the first cavity 110;

[0090] The equivalent diameter and axial height of the second cavity 120 satisfy the following conditions: Wherein, H2 is the axial height of the second cavity 120 and D2 is the equivalent diameter of the second cavity 120.

[0091] It should be noted that if the axial height H1 of the first cavity 110 is too small, it will hinder the expansion of the high-pressure refrigerant; and due to the limited space inside the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. This allows the equivalent diameter D1 of the first cavity 110 to have a suitable ratio with its axial height H1, facilitating the expansion of the high-pressure refrigerant and the vibration and friction under the action of acoustic impedance, thereby reducing vibration and noise.

[0092] It should be noted that while adding a second cavity 120 increases the volume of the silencing structure 10, if the height of the second cavity 120 is too large and its equivalent diameter is too small, it will hinder the entry and exit of the high-pressure refrigerant. It facilitates the entry and exit of high-pressure refrigerant into and out of the second chamber 120.

[0093] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110 and V2 is the equivalent volume of the second cavity 120;

[0094] In some embodiments, the volume of the first cavity 110, the volume of the second cavity 120, and the displacement of the scroll compressor satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110, V2 is the equivalent volume of the second cavity 120, and V is the displacement of the scroll compressor.

[0095] It should be noted that by making This limits the equivalent diameter of the second cavity 120, allowing the high-pressure refrigerant entering the first cavity 110 to re-enter the second cavity 120, which has a smaller equivalent diameter, for noise reduction; by making The size parameters of the silencing structure 10 can be set according to the displacement of the scroll compressor to achieve a better noise reduction effect.

[0096] In some embodiments, at least one exhaust port 1001 is provided on the end face of the first cavity 110 and / or the second cavity 120.

[0097] In some embodiments, at least one vent 1001 is a plurality of vent 1001, which are spaced apart circumferentially along the first cavity 110.

[0098] It should be noted that, as Figure 2 , Figure 4 , Figure 5 As shown, the end face of the first cavity 110 is the upper surface of the first cavity 110. The exhaust port 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120. A preset distance can be left between the exhaust port 1001 and the side wall of the first cavity 110, and a preset distance can be left between the exhaust port 1001 and the side wall of the second cavity 120, so that the exhaust port 1001 has sufficient vibration space (or position).

[0099] It should be noted that, as Figure 7 As shown, the exhaust port 1001 is provided on the end face of the second cavity 120 (i.e., the upper surface of the second cavity 120). Multiple exhaust ports 1001 can be arranged at intervals along the circumference of the second cavity 120, such as being evenly distributed around the circumference. The exhaust ports 1001 can have a preset distance from the side wall of the second cavity 120 so that the exhaust ports 1001 have sufficient vibration space (or position). The shape of the exhaust port 1001 can be circular, square, rhomboid, etc. The shape of the exhaust port 1001 is not specifically limited in this embodiment.

[0100] In some embodiments, the equivalent diameter of the exhaust port 1001 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Where D is the equivalent diameter of exhaust channel 30 and D3 is the equivalent diameter of exhaust hole 1001;

[0101] It should be noted that the high-pressure refrigerant entering the silencing structure 10 is eventually discharged from the silencing structure 10 through the exhaust port 1001. If the equivalent diameter of the exhaust port 1001 is too large, the high-pressure refrigerant entering the silencing structure 10 will be discharged from the silencing structure 10 without sufficient silencing. If the equivalent diameter of the exhaust port 1001 is too small, the high-pressure refrigerant that has undergone silencing and vibration reduction cannot be discharged from the silencing structure 10 in time. Therefore, setting the equivalent diameter of the exhaust port 1001 according to the equivalent diameter of the exhaust channel 30 of the scroll compressor (often representing the displacement) can ensure that the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 is discharged from the silencing structure 10 (first cavity 110 and second cavity 120) in time after sufficient silencing and vibration reduction.

[0102] It should be noted that, through simulation and actual testing, by making

[0103] (Right now This allows the noise reduction structure 10 of the present application embodiments to effectively reduce noise levels in the 1750-1850Hz and 2000-2300Hz frequency bands, as shown in Table 1 and... Figure 8 As shown, in actual tests, the noise reduction effect of the noise reduction structure 10 of this application embodiment and the conventional silencer is improved by 2dB to 3dB, which can improve product performance and user experience.

[0104] Table 1

[0105]

[0106] In summary, the advantages of this embodiment are that by placing the first cavity 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first cavity 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second cavity 120 above the first cavity 110 and connecting the second cavity 120 to the first cavity 110, wherein the equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120, on the one hand, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be abruptly increased and the speed reduced, thereby reducing exhaust noise and vibration; on the other hand, some sound energy can be canceled out under the reflection effect of the first cavity 110 and the second cavity 120, reducing exhaust noise and vibration.

[0107] Example 3:

[0108] like Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown in the figure, this application embodiment provides a noise reduction structure, including:

[0109] The first cavity 110 is located on the stationary scroll plate 20 of the scroll compressor and is connected to the exhaust passage 30 of the stationary scroll plate 20.

[0110] The second cavity 120 is located above the first cavity 110 and is connected to the first cavity 110.

[0111] The first cavity 110 and the second cavity 120 are configured to satisfy one or more of the following:

[0112] The equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120;

[0113] The equivalent diameter of the first cavity 110 is greater than the axial height of the first cavity 110;

[0114] The equivalent diameter of the second cavity 120 is greater than the axial height of the second cavity 120; and

[0115] The volume of the first cavity 110 is larger than the volume of the second cavity 120.

[0116] It should be noted that the above equivalent diameters are all dimensions after being equivalent to a circle. If its cross-section is a square, the equivalent diameter is the side length of the square; if its cross-section is a circle, the equivalent diameter is the diameter of the circle; if its cross-section is a combination of various shapes, the equivalent diameter is the square root of the cross-sectional area of ​​the expansion chamber.

[0117] It should be noted that the first cavity 110 is located above the stationary scroll plate 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the silencing structure 10 near the top cover of the scroll compressor can be smaller, thus avoiding contact with the top cover. The shape of the second cavity 120 can be adjusted according to the shape of the top cover or the shape of other components inside the scroll compressor, such as a circular shape. Figure 2 As shown), such as a near semicircle (as shown) Figure 5 , Figure 6 As shown), similarly, the shape of the first cavity 110 can also be adjusted according to the shape of the components inside the scroll compressor, such as... Figure 3 , Figure 7 As shown, the first cavity 110 is provided with a circular groove.

[0118] It should be noted that by placing the first chamber 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first chamber 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second chamber 120 above the first chamber 110 and connecting the second chamber 120 to the first chamber 110, wherein the equivalent diameter of the first chamber 110 is larger than the equivalent diameter of the second chamber 120, on the one hand, the high-pressure refrigerant enters the lower layer of the silencing structure 10 with a larger equivalent diameter from the exhaust passage 30 of the stationary scroll plate 20 with a smaller equivalent diameter. When the high-pressure refrigerant enters the first cavity 110 and then the second cavity 120 on the upper layer of the silencing structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can suddenly increase and the speed can be reduced, thereby reducing exhaust noise and vibration. On the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (i.e., the acoustic impedance changes), the sudden change in its flow cross section will reflect part of the sound waves back to the direction of the sound source. During this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces pressure pulsation energy, thereby reducing exhaust pulsation and improving exhaust noise.

[0119] In some embodiments, the noise reduction structure 10 further includes a connecting pressure edge 130, which is connected to the bottom end of the first cavity 110 and connected to the static vortex disk 20 via a connector.

[0120] It should be noted that the shape of the connecting pressure edge 130 is the same as that of the first cavity 110, and its diameter is larger than that of the first cavity 110, so as to connect with the bottom end (i.e., the lower surface) of the first cavity 110 and with the stationary vortex disk 20. The connecting pressure edge 130 and the first cavity 110 can be integrally formed. The connecting pressure edge 130 and the stationary vortex disk 20 can be connected by a connector. The connector can be a screw or a bolt. The embodiments of this application do not specifically limit the type of connector.

[0121] It should be noted that, based on the noise reduction structure 10 provided in the embodiments of this application, a formula for the noise reduction amount of the noise reduction structure 10 of this application can be constructed, namely... Construct the expansion ratio formula, that is Construct the shrinkage ratio formula, that is Constructing the wavenumber formula, i.e. Where m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound velocity, and f is the sound wave frequency.

[0122] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the second cavity 120 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D2 is the equivalent diameter of the second cavity 120.

[0123] It should be noted that by making (Right now On the one hand, it allows sufficient space on the end face of the first cavity 110 to open the exhaust port 1001. On the other hand, it ensures that the first cavity 110 and the second cavity 120 have sufficient vibration space under the impact of high-pressure refrigerant, thereby reducing noise through the vibration of the first cavity 110 and the second cavity 120.

[0124] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D is the equivalent diameter of the exhaust channel 30.

[0125] It should be noted that if the equivalent diameter of the first cavity 110 is too large or too small, it will be difficult to achieve a good noise reduction effect. Furthermore, the space inside the scroll compressor is limited and cannot support a large first cavity 110 or a large second cavity 120. (Right now This means that the expansion ratio m of the silencing structure 10 can be limited, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, thereby allowing the high-pressure refrigerant to reduce its speed and have a large acoustic impedance when it is discharged into the silencing structure 10.

[0126] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy the following conditions: Wherein, H1 is the axial height of the first cavity 110 and D1 is the equivalent diameter of the first cavity 110;

[0127] The equivalent diameter and axial height of the second cavity 120 satisfy the following conditions: Wherein, H2 is the axial height of the second cavity 120 and D2 is the equivalent diameter of the second cavity 120.

[0128] It should be noted that if the axial height H1 of the first cavity 110 is too small, it will hinder the expansion of the high-pressure refrigerant; and due to the limited space inside the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. This allows the equivalent diameter D1 of the first cavity 110 to have a suitable ratio with its axial height H1, facilitating the expansion of the high-pressure refrigerant and the vibration and friction under the action of acoustic impedance, thereby reducing vibration and noise.

[0129] It should be noted that while adding a second cavity 120 increases the volume of the silencing structure 10, if the height of the second cavity 120 is too large and its equivalent diameter is too small, it will hinder the entry and exit of the high-pressure refrigerant. It facilitates the entry and exit of high-pressure refrigerant into and out of the second chamber 120.

[0130] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110 and V2 is the equivalent volume of the second cavity 120;

[0131] In some embodiments, the volume of the first cavity 110, the volume of the second cavity 120, and the displacement of the scroll compressor satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110, V2 is the equivalent volume of the second cavity 120, and V is the displacement of the scroll compressor.

[0132] It should be noted that by making This limits the equivalent diameter of the second cavity 120, allowing the high-pressure refrigerant entering the first cavity 110 to re-enter the second cavity 120, which has a smaller equivalent diameter, for noise reduction; by making The size parameters of the silencing structure 10 can be set according to the displacement of the scroll compressor to achieve a better noise reduction effect.

[0133] In some embodiments, at least one exhaust port 1001 is provided on the end face of the first cavity 110 and / or the second cavity 120.

[0134] In some embodiments, at least one vent 1001 is a plurality of vent 1001, which are spaced apart circumferentially along the first cavity 110.

[0135] It should be noted that, as Figure 2 , Figure 4 , Figure 5 As shown, the end face of the first cavity 110 is the upper surface of the first cavity 110. The exhaust port 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120. A preset distance can be left between the exhaust port 1001 and the side wall of the first cavity 110, and a preset distance can be left between the exhaust port 1001 and the side wall of the second cavity 120, so that the exhaust port 1001 has sufficient vibration space (or position).

[0136] It should be noted that, as Figure 7 As shown, the exhaust port 1001 is provided on the end face of the second cavity 120 (i.e., the upper surface of the second cavity 120). Multiple exhaust ports 1001 can be arranged at intervals along the circumference of the second cavity 120, such as being evenly distributed around the circumference. The exhaust ports 1001 can have a preset distance from the side wall of the second cavity 120 so that the exhaust ports 1001 have sufficient vibration space (or position). The shape of the exhaust port 1001 can be circular, square, rhomboid, etc. The shape of the exhaust port 1001 is not specifically limited in this embodiment.

[0137] In some embodiments, the equivalent diameter of the exhaust port 1001 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Where D is the equivalent diameter of exhaust channel 30 and D3 is the equivalent diameter of exhaust hole 1001;

[0138] It should be noted that the high-pressure refrigerant entering the silencing structure 10 is eventually discharged from the silencing structure 10 through the exhaust port 1001. If the equivalent diameter of the exhaust port 1001 is too large, the high-pressure refrigerant entering the silencing structure 10 will be discharged from the silencing structure 10 without sufficient silencing. If the equivalent diameter of the exhaust port 1001 is too small, the high-pressure refrigerant that has undergone silencing and vibration reduction cannot be discharged from the silencing structure 10 in time. Therefore, setting the equivalent diameter of the exhaust port 1001 according to the equivalent diameter of the exhaust channel 30 of the scroll compressor (often representing the displacement) can ensure that the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 is discharged from the silencing structure 10 (first cavity 110 and second cavity 120) in time after sufficient silencing and vibration reduction.

[0139] It should be noted that, through simulation and actual testing, by making

[0140] (Right now This allows the noise reduction structure 10 of the present application embodiments to effectively reduce noise levels in the 1750-1850Hz and 2000-2300Hz frequency bands, as shown in Table 1 and... Figure 8 As shown, in actual tests, the noise reduction effect of the noise reduction structure 10 of this application embodiment and the conventional silencer is improved by 2dB to 3dB, which can improve product performance and user experience.

[0141] Table 1

[0142]

[0143] In summary, the advantages of this embodiment are that by placing the first cavity 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first cavity 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second cavity 120 above the first cavity 110 and connecting the second cavity 120 to the first cavity 110, wherein the equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120, on the one hand, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be abruptly increased and the speed reduced, thereby reducing exhaust noise and vibration; on the other hand, some sound energy can be canceled out under the reflection effect of the first cavity 110 and the second cavity 120, reducing exhaust noise and vibration.

[0144] Example 4:

[0145] This application provides a scroll compressor, including the silencing structure 10 as described in Embodiment 3, such as... Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown, the noise reduction structure 10 includes:

[0146] The first cavity 110 is located on the stationary scroll plate 20 of the scroll compressor and is connected to the exhaust passage 30 of the stationary scroll plate 20.

[0147] The second cavity 120 is located above the first cavity 110 and is connected to the first cavity 110.

[0148] The first cavity 110 and the second cavity 120 are configured to satisfy one or more of the following:

[0149] The equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120;

[0150] The equivalent diameter of the first cavity 110 is greater than the axial height of the first cavity 110;

[0151] The equivalent diameter of the second cavity 120 is greater than the axial height of the second cavity 120; and

[0152] The volume of the first cavity 110 is larger than the volume of the second cavity 120.

[0153] It should be noted that the above equivalent diameters are all dimensions after being equivalent to a circle. If its cross-section is a square, the equivalent diameter is the side length of the square; if its cross-section is a circle, the equivalent diameter is the diameter of the circle; if its cross-section is a combination of various shapes, the equivalent diameter is the square root of the cross-sectional area of ​​the expansion chamber.

[0154] It should be noted that the first cavity 110 is located above the stationary scroll plate 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the silencing structure 10 near the top cover of the scroll compressor can be smaller, thus avoiding contact with the top cover. The shape of the second cavity 120 can be adjusted according to the shape of the top cover or the shape of other components inside the scroll compressor, such as a circular shape. Figure 2 As shown), such as a near semicircle (as shown) Figure 5 , Figure 6 As shown), similarly, the shape of the first cavity 110 can also be adjusted according to the shape of the components inside the scroll compressor, such as... Figure 3 , Figure 7 As shown, the first cavity 110 is provided with a circular groove.

[0155] It should be noted that by placing the first chamber 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first chamber 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second chamber 120 above the first chamber 110 and connecting the second chamber 120 to the first chamber 110, wherein the equivalent diameter of the first chamber 110 is larger than the equivalent diameter of the second chamber 120, on the one hand, the high-pressure refrigerant enters the lower layer of the silencing structure 10 with a larger equivalent diameter from the exhaust passage 30 of the stationary scroll plate 20 with a smaller equivalent diameter. When the high-pressure refrigerant enters the first cavity 110 and then the second cavity 120 on the upper layer of the silencing structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can suddenly increase and the speed can be reduced, thereby reducing exhaust noise and vibration. On the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (i.e., the acoustic impedance changes), the sudden change in its flow cross section will reflect part of the sound waves back to the direction of the sound source. During this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces pressure pulsation energy, thereby reducing exhaust pulsation and improving exhaust noise.

[0156] In some embodiments, the noise reduction structure 10 further includes a connecting pressure edge 130, which is connected to the bottom end of the first cavity 110 and connected to the static vortex disk 20 via a connector.

[0157] It should be noted that the shape of the connecting pressure edge 130 is the same as that of the first cavity 110, and its diameter is larger than that of the first cavity 110, so as to connect with the bottom end (i.e., the lower surface) of the first cavity 110 and with the stationary vortex disk 20. The connecting pressure edge 130 and the first cavity 110 can be integrally formed. The connecting pressure edge 130 and the stationary vortex disk 20 can be connected by a connector. The connector can be a screw or a bolt. The embodiments of this application do not specifically limit the type of connector.

[0158] It should be noted that, based on the noise reduction structure 10 provided in the embodiments of this application, a formula for the noise reduction amount of the noise reduction structure 10 of this application can be constructed, namely... Construct the expansion ratio formula, that is Construct the shrinkage ratio formula, that is Constructing the wavenumber formula, i.e. Where m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound velocity, and f is the sound wave frequency.

[0159] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the second cavity 120 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D2 is the equivalent diameter of the second cavity 120.

[0160] It should be noted that by making (Right now On the one hand, it allows sufficient space on the end face of the first cavity 110 to open the exhaust port 1001. On the other hand, it ensures that the first cavity 110 and the second cavity 120 have sufficient vibration space under the impact of high-pressure refrigerant, thereby reducing noise through the vibration of the first cavity 110 and the second cavity 120.

[0161] In some embodiments, the equivalent diameter of the first cavity 110 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Wherein, D1 is the equivalent diameter of the first cavity 110 and D is the equivalent diameter of the exhaust channel 30.

[0162] It should be noted that if the equivalent diameter of the first cavity 110 is too large or too small, it will be difficult to achieve a good noise reduction effect. Furthermore, the space inside the scroll compressor is limited and cannot support a large first cavity 110 or a large second cavity 120. (Right now This means that the expansion ratio m of the silencing structure 10 can be limited, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, thereby allowing the high-pressure refrigerant to reduce its speed and have a large acoustic impedance when it is discharged into the silencing structure 10.

[0163] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy the following conditions: Wherein, H1 is the axial height of the first cavity 110 and D1 is the equivalent diameter of the first cavity 110;

[0164] The equivalent diameter and axial height of the second cavity 120 satisfy the following conditions: Wherein, H2 is the axial height of the second cavity 120 and D2 is the equivalent diameter of the second cavity 120.

[0165] It should be noted that if the axial height H1 of the first cavity 110 is too small, it will hinder the expansion of the high-pressure refrigerant; and due to the limited space inside the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. This allows the equivalent diameter D1 of the first cavity 110 to have a suitable ratio with its axial height H1, facilitating the expansion of the high-pressure refrigerant and the vibration and friction under the action of acoustic impedance, thereby reducing vibration and noise.

[0166] It should be noted that while adding a second cavity 120 increases the volume of the silencing structure 10, if the height of the second cavity 120 is too large and its equivalent diameter is too small, it will hinder the entry and exit of the high-pressure refrigerant. It facilitates the entry and exit of high-pressure refrigerant into and out of the second chamber 120.

[0167] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110 and V2 is the equivalent volume of the second cavity 120;

[0168] In some embodiments, the volume of the first cavity 110, the volume of the second cavity 120, and the displacement of the scroll compressor satisfy the following conditions: Wherein, V1 is the equivalent volume of the first cavity 110, V2 is the equivalent volume of the second cavity 120, and V is the displacement of the scroll compressor.

[0169] It should be noted that by making This limits the equivalent diameter of the second cavity 120, allowing the high-pressure refrigerant entering the first cavity 110 to re-enter the second cavity 120, which has a smaller equivalent diameter, for noise reduction; by making The size parameters of the silencing structure 10 can be set according to the displacement of the scroll compressor to achieve a better noise reduction effect.

[0170] In some embodiments, at least one exhaust port 1001 is provided on the end face of the first cavity 110 and / or the second cavity 120.

[0171] In some embodiments, at least one vent 1001 is a plurality of vent 1001, which are spaced apart circumferentially along the first cavity 110.

[0172] It should be noted that, as Figure 2 , Figure 4 , Figure 5 As shown, the end face of the first cavity 110 is the upper surface of the first cavity 110. The exhaust port 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120. A preset distance can be left between the exhaust port 1001 and the side wall of the first cavity 110, and a preset distance can be left between the exhaust port 1001 and the side wall of the second cavity 120, so that the exhaust port 1001 has sufficient vibration space (or position).

[0173] It should be noted that, as Figure 7 As shown, the exhaust port 1001 is provided on the end face of the second cavity 120 (i.e., the upper surface of the second cavity 120). Multiple exhaust ports 1001 can be arranged at intervals along the circumference of the second cavity 120, such as being evenly distributed around the circumference. The exhaust ports 1001 can have a preset distance from the side wall of the second cavity 120 so that the exhaust ports 1001 have sufficient vibration space (or position). The shape of the exhaust port 1001 can be circular, square, rhomboid, etc. The shape of the exhaust port 1001 is not specifically limited in this embodiment.

[0174] In some embodiments, the equivalent diameter of the exhaust port 1001 and the equivalent diameter of the exhaust channel 30 satisfy the following conditions: Where D is the equivalent diameter of exhaust channel 30 and D3 is the equivalent diameter of exhaust hole 1001;

[0175] It should be noted that the high-pressure refrigerant entering the silencing structure 10 is eventually discharged from the silencing structure 10 through the exhaust port 1001. If the equivalent diameter of the exhaust port 1001 is too large, the high-pressure refrigerant entering the silencing structure 10 will be discharged from the silencing structure 10 without sufficient silencing. If the equivalent diameter of the exhaust port 1001 is too small, the high-pressure refrigerant that has undergone silencing and vibration reduction cannot be discharged from the silencing structure 10 in time. Therefore, setting the equivalent diameter of the exhaust port 1001 according to the equivalent diameter of the exhaust channel 30 of the scroll compressor (often representing the displacement) can ensure that the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 is discharged from the silencing structure 10 (first cavity 110 and second cavity 120) in time after sufficient silencing and vibration reduction.

[0176] It should be noted that, through simulation and actual testing, by making (Right now This allows the noise reduction structure 10 of the present application embodiments to effectively reduce noise levels in the 1750-1850Hz and 2000-2300Hz frequency bands, as shown in Table 1 and... Figure 8 As shown, in actual tests, the noise reduction effect of the noise reduction structure 10 of this application embodiment and the conventional silencer is improved by 2dB to 3dB, which can improve product performance and user experience.

[0177] Table 1

[0178]

[0179] In summary, the advantages of this embodiment are that by placing the first cavity 110 on the stationary scroll plate 20 of the scroll compressor and connecting the first cavity 110 to the exhaust passage 30 of the stationary scroll plate 20; and placing the second cavity 120 above the first cavity 110 and connecting the second cavity 120 to the first cavity 110, wherein the equivalent diameter of the first cavity 110 is larger than the equivalent diameter of the second cavity 120, on the one hand, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be abruptly increased and the speed reduced, thereby reducing exhaust noise and vibration; on the other hand, some sound energy can be canceled out under the reflection effect of the first cavity 110 and the second cavity 120, reducing exhaust noise and vibration.

[0180] Although the invention has been described with reference to preferred embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, the technical features mentioned in the various embodiments can be combined in any manner as long as there is no structural conflict. The invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A noise-absorbing structure, characterized in that, include: The first cavity is located on the stationary scroll plate of the scroll compressor and is connected to the exhaust passage of the stationary scroll plate. The second cavity is located above the first cavity and is connected to the first cavity; The equivalent diameter of the first cavity is larger than the equivalent diameter of the second cavity; The equivalent diameter of the first cavity is greater than the axial height of the first cavity; The equivalent diameter of the second cavity is greater than the axial height of the second cavity; and The volume of the first cavity is larger than the volume of the second cavity; Multiple exhaust holes are provided on the end face of the first cavity, and the multiple exhaust holes are arranged at intervals along the circumference of the first cavity; The exhaust port is located on the upper surface of the first cavity and is not covered by the second cavity. A preset distance is left between the exhaust port and the side wall of the first cavity, and a preset distance is left between the exhaust port and the side wall of the second cavity, so that the exhaust port has sufficient vibration space. When the high-pressure refrigerant enters the first cavity with a larger equivalent diameter from the exhaust channel of the static vortex disk with a smaller equivalent diameter, and then enters the second cavity, the abrupt change in its flow cross section will reflect part of the sound waves back to the direction of the sound source. The high-pressure refrigerant vibrates and rubs, reducing exhaust pulsation and improving exhaust noise. The high-pressure refrigerant is finally discharged through the exhaust port.

2. The noise-absorbing structure according to claim 1, characterized in that, The equivalent diameters of the first cavity and the second cavity satisfy the following conditions: ,in, The equivalent diameter of the first cavity, This is the equivalent diameter of the second cavity.

3. The noise-absorbing structure according to claim 1, characterized in that, The equivalent diameter of the first cavity and the equivalent diameter of the exhaust channel satisfy the following conditions: ,in, The equivalent diameter of the first cavity, This is the equivalent diameter of the exhaust channel.

4. The noise-absorbing structure according to claim 1, characterized in that, The equivalent diameter of the first cavity and the axial height of the first cavity satisfy the following conditions: ,in, The axial height of the first cavity, The equivalent diameter of the first cavity; The equivalent diameter of the second cavity and the axial height of the second cavity satisfy the following conditions: ,in, The axial height of the second cavity, This is the equivalent diameter of the second cavity.

5. The noise-absorbing structure according to claim 1, characterized in that, The volume of the first cavity and the volume of the second cavity satisfy the following conditions: ,in, The equivalent volume of the first cavity, This is the equivalent volume of the second cavity.

6. The noise-absorbing structure according to claim 1, characterized in that, The volume of the first cavity, the volume of the second cavity, and the displacement of the scroll compressor satisfy the following conditions: ,in, The equivalent volume of the first cavity, The equivalent volume of the second cavity, This refers to the displacement of the scroll compressor.

7. The noise-absorbing structure according to claim 1, characterized in that, The equivalent diameter of the exhaust port and the equivalent diameter of the exhaust channel satisfy the following conditions: ,in, The equivalent diameter of the exhaust channel, This is the equivalent diameter of the vent hole.

8. The noise-absorbing structure according to any one of claims 1-7, characterized in that, The noise reduction structure also includes a connecting pressure edge, which is connected to the bottom end of the first cavity and connected to the static vortex disk through a connector.

9. A scroll compressor, characterized in that, Includes the noise-reducing structure as described in any one of claims 1-8.

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