Silencing structure and scroll compressor

Abstract

The invention provides a silencing structure and a scroll compressor. A first cavity is formed in a static scroll plate of the scroll compressor, and the first cavity communicates with an exhaust channel of the static scroll plate; the second cavity is arranged above the first cavity, the second cavity is communicated with the first cavity, and the first cavity and the second cavity are constructed to meet one or more of the following requirements: the equivalent diameter of the first cavity is larger than that 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; the size of the first cavity is larger than that of the second cavity, on one hand, the flow area of a high-pressure refrigerant discharged out of the pump body can be suddenly increased, the speed is reduced, and therefore exhaust noise and vibration are reduced; and on the other hand, the high-pressure refrigerant can generate vibration and friction under the reflection action of the first cavity and the second cavity, and exhaust noise and vibration are reduced.

Description

Technical Field

[0001] The invention relates to the field of compressor technology, in particular to a muffler structure and a scroll compressor. Background Art

[0002] A scroll compressor is a type of positive displacement compressor. The compression component consists of a movable scroll and a stationary scroll. When working, 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 upper cover of the scroll compressor, causing excessive noise and vibration at the top of the compressor. Summary of the invention

[0003] The embodiments of the present application provide a silencer structure and a scroll compressor, which can solve the problem that the high-pressure refrigerant discharged from the existing pump body directly impacts the upper cover of the scroll compressor, causing excessive noise and vibration at the top of the compressor.

[0004] In a first aspect, an embodiment of the present application provides a sound-absorbing structure, including:

[0005] A first cavity is provided on the fixed scroll of the scroll compressor and is connected to the exhaust passage of the fixed scroll;

[0006] A second cavity is disposed above the first cavity and communicated with the first cavity;

[0007] Wherein, the first cavity and the second cavity are configured to satisfy one or more of the following:

[0008] The equivalent diameter of the first cavity is greater 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 greater 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 Wherein, 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 passage satisfy Wherein, 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 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 Wherein, 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 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 Among them, 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 hole is disposed on the end surface of the first cavity and / or the second cavity.

[0019] In some embodiments, the at least one exhaust hole is a plurality of exhaust holes, and the plurality of exhaust holes are spaced apart along the circumference of the first cavity.

[0020] In some embodiments, the equivalent diameter of the exhaust hole and the equivalent diameter of the exhaust channel satisfy Wherein, D is the equivalent diameter of the exhaust channel, and D3 is the equivalent diameter of the exhaust hole.

[0021] In some embodiments, the muffler structure further includes a connecting pressure edge, which is connected to the bottom end of the first cavity and is connected to the fixed scroll plate via a connecting piece.

[0022] In a second aspect, an embodiment of the present application provides a scroll compressor, comprising a silencer structure as described in any one of the first aspects.

[0023] Compared with the prior art, the advantage of the embodiments of the present application lies in that, by arranging the first cavity on the static scroll disk of the scroll compressor and connecting the first cavity with the exhaust channel of the static scroll disk; arranging 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 suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, the high-pressure refrigerant can generate vibration and friction under the reflection action of the first cavity and the second cavity, thereby reducing the exhaust noise and vibration. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Hereinafter, the present invention will be described in more detail based on embodiments and with reference to the accompanying drawings.

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

[0026] Figure 2 is a three-dimensional diagram of a sound-absorbing structure provided by an embodiment of the present invention;

[0027] Figure 3 is a bottom view of a sound-absorbing structure provided by one embodiment of the present invention;

[0028] Figure 4 is a schematic diagram of the assembly of a sound-absorbing structure provided by an embodiment of the present invention;

[0029] Figure 5 is a three-dimensional diagram of a sound-absorbing structure provided by another embodiment of the present invention;

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

[0031] Figure 7 is a three-dimensional diagram of a sound-absorbing structure provided by another embodiment of the present invention;

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

[0033] Reference numerals:

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

[0035] 20. Static vortex disk;

[0036] 30. Exhaust channel. DETAILED DESCRIPTION

[0037] The present invention will be further described below in conjunction with the accompanying drawings.

[0038] The scroll compressor is composed of a closed shell, a static scroll, a movable scroll, a bracket, an eccentric crankshaft, an anti-rotation mechanism and a motor. The profiles of the movable scroll and the static scroll are both spiral. The movable scroll is installed 180° eccentrically relative to the static scroll, so a number of crescent-shaped spaces are formed between the movable scroll and the static scroll. When working, the movable scroll rotates around the center of the static scroll and makes a non-rotating rotational translation at a certain eccentric radius. The crescent-shaped space on its outer circle keeps moving toward the center. At this time, the refrigerant is gradually pushed toward the center space, and its volume keeps shrinking while the pressure keeps rising until it is connected with the center exhaust hole. The high-pressure refrigerant is discharged from the pump body. The high-pressure refrigerant discharged from the pump body directly impacts the upper cover, resulting in louder noise and vibration at the top of the scroll compressor.

[0039] Embodiment 1:

[0040] In response to the above technical issues, such as Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown, the embodiment of the present application provides a sound-absorbing structure, including:

[0041] The first cavity 110 is disposed on the fixed scroll 20 of the scroll compressor and is connected to the exhaust passage 30 of the fixed scroll 20;

[0042] The second cavity 120 is disposed above the first cavity 110 and communicates with the first cavity 110;

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

[0044] The equivalent diameter of the first cavity 110 is greater 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 greater than the volume of the second cavity 120 .

[0048] It should be noted that the above-mentioned 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 disposed above the fixed scroll 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the muffler structure 10 close to the upper cover of the scroll compressor can be made smaller, thereby avoiding contact with the upper cover. The shape of the second cavity 120 can be adjusted according to the shape of the upper cover or the shapes of other parts in the scroll compressor, such as a circle (such as Figure 2 As shown), such as nearly semicircular (such as Figure 5 , Figure 6 Similarly, the shape of the first cavity 110 can also be adjusted according to the shapes of the parts in the scroll compressor, such as Figure 3 , Figure 7 As shown, a circular groove is provided on the first cavity 110 .

[0050] It should be noted that, by arranging the first cavity 110 on the fixed scroll disk 20 of the scroll compressor, and connecting the first cavity 110 with the exhaust passage 30 of the fixed scroll disk 20; arranging the second cavity 120 above the first cavity 110, and connecting the second cavity 120 with the first cavity 110, wherein the equivalent diameter of the first cavity 110 is greater than the equivalent diameter of the second cavity 120, on the one hand, the high-pressure refrigerant enters the lower layer of the muffler structure 10 with a larger equivalent diameter from the exhaust passage 30 of the fixed scroll disk 20 with a smaller equivalent diameter. When the high-pressure refrigerant passes through the first cavity 110 and then enters the second cavity 120 on the upper layer of the silencer structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (that is, 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. In this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces the pressure pulsation energy, thereby reducing the exhaust pulsation and improving the exhaust noise.

[0051] It should be noted that, in combination with the sound-absorbing structure 10 provided in the embodiment of the present application, a sound-absorbing amount formula of the sound-absorbing structure 10 of the present application can be constructed, namely: Construct the expansion ratio formula, that is, Construct the shrinkage ratio formula, that is, Construct the wave number formula, that is, Among them, m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound speed, 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 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 (Right now ), on the one hand, it can ensure that there is enough space on the end face of the first cavity 110 to open the exhaust hole 1001, and on the other hand, it can ensure that the first cavity 110 and the second cavity 120 can have enough vibration space under the impact of the 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 passage 30 satisfy 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 is difficult to obtain a good muffler effect, and the space in the scroll compressor is limited and cannot support the setting of a larger first cavity 110 and a second cavity 120. (Right now ), that is, it is possible to limit the expansion ratio m of the silencer structure 10, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, so that the high-pressure refrigerant can be sufficiently reduced in speed when discharged into the silencer structure 10 and has a larger acoustic impedance.

[0056] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy 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 of the second cavity 120 and the axial height of the second cavity 120 satisfy 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 be disadvantageous for the expansion of the high-pressure refrigerant. However, due to the limited space in the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. The equivalent diameter D1 and the axial height H1 of the first cavity 110 can have a suitable ratio, which is convenient for the expansion of the high-pressure refrigerant and the vibration and friction under the action of the acoustic impedance, thereby reducing vibration and noise.

[0059] It should be noted that the volume of the muffler structure 10 can be increased by providing the second cavity 120. However, if the height of the second cavity 120 is too large and the equivalent diameter is too small, it is not conducive to the entry and discharge of the high-pressure refrigerant. It is convenient for the high-pressure refrigerant to enter and be discharged from the second cavity 120 .

[0060] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy 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 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 The equivalent diameter of the second cavity 120 can be limited, so that the high-pressure refrigerant entering the first cavity 110 can enter the second cavity 120 with a smaller equivalent diameter again for silencing; The size parameters of the silencer structure 10 can be set in a targeted manner according to the displacement of the scroll compressor to achieve a better silencer effect.

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

[0064] It should be noted that if 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 hole 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120, a preset distance may be left between the exhaust hole 1001 and the side wall of the first cavity 110, and a preset distance may be left between the exhaust hole 1001 and the side wall of the second cavity 120, so that the exhaust hole 1001 has enough vibration space (or position).

[0065] In some embodiments, the equivalent diameter of the exhaust hole 1001 and the equivalent diameter of the exhaust channel 30 satisfy Wherein, D is the equivalent diameter of the exhaust passage 30, and D3 is the equivalent diameter of the exhaust hole 1001;

[0066] It should be noted that the high-pressure refrigerant entering the silencer structure 10 is eventually discharged from the silencer structure 10 through the exhaust hole 1001. If the equivalent diameter of the exhaust hole 1001 is too large, the high-pressure refrigerant discharged into the silencer structure 10 will be discharged from the silencer structure 10 without sufficient silencer. If the equivalent diameter of the exhaust hole 1001 is too small, the high-pressure refrigerant that has been silenced and damped cannot be discharged from the silencer structure 10 in time. Therefore, setting the equivalent diameter of the exhaust hole 1001 according to the equivalent diameter of the scroll compressor exhaust passage 30 (often representing the displacement) can enable the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 to be discharged from the silencer structure 10 (the first cavity 110, the second cavity 120) in time after sufficient silencer and damping.

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

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

[0069] Table 1

[0070]

[0071] In summary, the advantage of the embodiments of the present application is that, by arranging the first cavity 110 on the static scroll 20 of the scroll compressor and connecting the first cavity 110 with the exhaust passage 30 of the static scroll 20; arranging the second cavity 120 above the first cavity 110 and connecting the second cavity 120 with 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 suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, part of the sound energy can be offset and the exhaust noise and vibration can be reduced under the reflection effect of the first cavity 110 and the second cavity 120.

[0072] Embodiment 2:

[0073] like Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown, the embodiment of the present application provides a sound-absorbing structure, including:

[0074] The first cavity 110 is disposed on the fixed scroll 20 of the scroll compressor and is connected to the exhaust passage 30 of the fixed scroll 20;

[0075] The second cavity 120 is disposed above the first cavity 110 and communicates with the first cavity 110;

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

[0077] The equivalent diameter of the first cavity 110 is greater 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 greater than the volume of the second cavity 120 .

[0081] It should be noted that the above-mentioned 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 disposed above the fixed scroll 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the muffler structure 10 close to the upper cover of the scroll compressor can be made smaller, thereby avoiding contact with the upper cover. The shape of the second cavity 120 can be adjusted according to the shape of the upper cover or the shapes of other parts in the scroll compressor, such as a circle (such as Figure 2 As shown), such as nearly semicircular (such as Figure 5 , Figure 6 Similarly, the shape of the first cavity 110 can also be adjusted according to the shapes of the parts in the scroll compressor, such as Figure 3 , Figure 7 As shown, a circular groove is provided on the first cavity 110 .

[0083] It should be noted that, by arranging the first cavity 110 on the fixed scroll disk 20 of the scroll compressor, and connecting the first cavity 110 with the exhaust passage 30 of the fixed scroll disk 20; arranging the second cavity 120 above the first cavity 110, and connecting the second cavity 120 with the first cavity 110, wherein the equivalent diameter of the first cavity 110 is greater than the equivalent diameter of the second cavity 120, on the one hand, the high-pressure refrigerant enters the lower layer of the muffler structure 10 with a larger equivalent diameter from the exhaust passage 30 of the fixed scroll disk 20 with a smaller equivalent diameter. When the high-pressure refrigerant passes through the first cavity 110 and then enters the second cavity 120 on the upper layer of the silencer structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (that is, 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. In this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces the pressure pulsation energy, thereby reducing the exhaust pulsation and improving the exhaust noise.

[0084] It should be noted that, in combination with the sound-absorbing structure 10 provided in the embodiment of the present application, a sound-absorbing amount formula of the sound-absorbing structure 10 of the present application can be constructed, namely: Construct the expansion ratio formula, that is, Construct the shrinkage ratio formula, that is, Construct the wave number formula, that is, Among them, m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound speed, 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 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 (Right now ), on the one hand, it can ensure that there is enough space on the end face of the first cavity 110 to open the exhaust hole 1001, and on the other hand, it can ensure that the first cavity 110 and the second cavity 120 can have enough vibration space under the impact of the 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 passage 30 satisfy 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 is difficult to obtain a good muffler effect, and the space in the scroll compressor is limited and cannot support the setting of a larger first cavity 110 and a second cavity 120. (Right now ), that is, it is possible to limit the expansion ratio m of the silencer structure 10, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, so that the high-pressure refrigerant can be sufficiently reduced in speed when discharged into the silencer structure 10 and has a larger acoustic impedance.

[0089] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy 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 of the second cavity 120 and the axial height of the second cavity 120 satisfy 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 be disadvantageous for the expansion of the high-pressure refrigerant. However, due to the limited space in the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. The equivalent diameter D1 and the axial height H1 of the first cavity 110 can have a suitable ratio, which is convenient for the expansion of the high-pressure refrigerant and the vibration and friction under the action of the acoustic impedance, thereby reducing vibration and noise.

[0092] It should be noted that the volume of the muffler structure 10 can be increased by providing the second cavity 120. However, if the height of the second cavity 120 is too large and the equivalent diameter is too small, it is not conducive to the entry and discharge of the high-pressure refrigerant. It is convenient for the high-pressure refrigerant to enter and be discharged from the second cavity 120 .

[0093] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy 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 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 The equivalent diameter of the second cavity 120 can be limited, so that the high-pressure refrigerant entering the first cavity 110 can enter the second cavity 120 with a smaller equivalent diameter again for silencing; The size parameters of the silencer structure 10 can be set in a targeted manner according to the displacement of the scroll compressor to achieve a better silencer effect.

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

[0097] In some embodiments, the at least one exhaust hole 1001 is a plurality of exhaust holes 1001 , and the plurality of exhaust holes 1001 are spaced apart along the circumference of the first cavity 110 .

[0098] It should be noted that if 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 hole 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120, a preset distance may be left between the exhaust hole 1001 and the side wall of the first cavity 110, and a preset distance may be left between the exhaust hole 1001 and the side wall of the second cavity 120, so that the exhaust hole 1001 has enough vibration space (or position).

[0099] It should be noted that if Figure 7 As shown, the exhaust hole 1001 is provided on the end face of the second cavity 120 (i.e., the upper surface of the second cavity 120), and a plurality of exhaust holes 1001 may be arranged at intervals along the circumference of the second cavity 120, such as evenly distributed around the circumference, and the exhaust hole 1001 may have a preset spacing from the side wall of the second cavity 120 so that the exhaust hole 1001 has sufficient vibration space (or position), wherein the shape of the exhaust hole 1001 may be circular, square, diamond, etc., and the embodiment of the present application does not specifically limit the shape of the exhaust hole 1001.

[0100] In some embodiments, the equivalent diameter of the exhaust hole 1001 and the equivalent diameter of the exhaust channel 30 satisfy Wherein, D is the equivalent diameter of the exhaust passage 30, and D3 is the equivalent diameter of the exhaust hole 1001;

[0101] It should be noted that the high-pressure refrigerant entering the silencer structure 10 is eventually discharged from the silencer structure 10 through the exhaust hole 1001. If the equivalent diameter of the exhaust hole 1001 is too large, the high-pressure refrigerant discharged into the silencer structure 10 will be discharged from the silencer structure 10 without sufficient silencer. If the equivalent diameter of the exhaust hole 1001 is too small, the high-pressure refrigerant that has been silenced and damped cannot be discharged from the silencer structure 10 in time. Therefore, setting the equivalent diameter of the exhaust hole 1001 according to the equivalent diameter of the scroll compressor exhaust passage 30 (often representing the displacement) can enable the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 to be discharged from the silencer structure 10 (the first cavity 110, the second cavity 120) in time after sufficient silencer and damping.

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

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

[0104] Table 1

[0105]

[0106] In summary, the advantage of the embodiments of the present application is that, by arranging the first cavity 110 on the static scroll 20 of the scroll compressor and connecting the first cavity 110 with the exhaust passage 30 of the static scroll 20; arranging the second cavity 120 above the first cavity 110 and connecting the second cavity 120 with 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 suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, part of the sound energy can be offset and the exhaust noise and vibration can be reduced under the reflection effect of the first cavity 110 and the second cavity 120.

[0107] Embodiment three:

[0108] like Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown, the embodiment of the present application provides a sound-absorbing structure, including:

[0109] The first cavity 110 is disposed on the fixed scroll 20 of the scroll compressor and is connected to the exhaust passage 30 of the fixed scroll 20;

[0110] The second cavity 120 is disposed above the first cavity 110 and communicates with the first cavity 110;

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

[0112] The equivalent diameter of the first cavity 110 is greater 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 greater than the volume of the second cavity 120 .

[0116] It should be noted that the above-mentioned 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 disposed above the fixed scroll 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the muffler structure 10 close to the upper cover of the scroll compressor can be made smaller, thereby avoiding contact with the upper cover. The shape of the second cavity 120 can be adjusted according to the shape of the upper cover or the shapes of other parts in the scroll compressor, such as a circle (such as Figure 2 As shown), such as nearly semicircular (such as Figure 5 , Figure 6 Similarly, the shape of the first cavity 110 can also be adjusted according to the shapes of the parts in the scroll compressor, such as Figure 3 , Figure 7 As shown, a circular groove is provided on the first cavity 110 .

[0118] It should be noted that, by arranging the first cavity 110 on the fixed scroll disk 20 of the scroll compressor, and connecting the first cavity 110 with the exhaust passage 30 of the fixed scroll disk 20; arranging the second cavity 120 above the first cavity 110, and connecting the second cavity 120 with the first cavity 110, wherein the equivalent diameter of the first cavity 110 is greater than the equivalent diameter of the second cavity 120, on the one hand, the high-pressure refrigerant enters the lower layer of the muffler structure 10 with a larger equivalent diameter from the exhaust passage 30 of the fixed scroll disk 20 with a smaller equivalent diameter. When the high-pressure refrigerant passes through the first cavity 110 and then enters the second cavity 120 on the upper layer of the silencer structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (that is, 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. In this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces the pressure pulsation energy, thereby reducing the exhaust pulsation and improving the exhaust noise.

[0119] In some embodiments, the muffler structure 10 further includes a connecting pressure edge 130 , which is connected to the bottom end of the first cavity 110 and is connected to the fixed scroll 20 via a connecting member.

[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 be connected to the bottom end (i.e., the lower surface) of the first cavity 110 and to the static scroll plate 20, wherein the connecting pressure edge 130 and the first cavity 110 can be formed as one piece, and the connecting pressure edge 130 and the static scroll plate 20 can be connected by a connecting piece, which can be a screw or a bolt. The embodiment of the present application does not specifically limit the type of the connecting piece.

[0121] It should be noted that, in combination with the sound-absorbing structure 10 provided in the embodiment of the present application, a sound-absorbing amount formula of the sound-absorbing structure 10 of the present application can be constructed, namely: Construct the expansion ratio formula, that is, Construct the shrinkage ratio formula, that is, Construct the wave number formula, that is, Among them, m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound speed, 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 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 (Right now ), on the one hand, it can ensure that there is enough space on the end face of the first cavity 110 to open the exhaust hole 1001, and on the other hand, it can ensure that the first cavity 110 and the second cavity 120 can have enough vibration space under the impact of the 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 passage 30 satisfy 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 is difficult to obtain a good muffler effect, and the space in the scroll compressor is limited and cannot support the setting of a larger first cavity 110 and a second cavity 120. (Right now ), that is, it is possible to limit the expansion ratio m of the silencer structure 10, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, so that the high-pressure refrigerant can be sufficiently reduced in speed when discharged into the silencer structure 10 and has a larger acoustic impedance.

[0126] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy 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 of the second cavity 120 and the axial height of the second cavity 120 satisfy 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 be disadvantageous for the expansion of the high-pressure refrigerant. However, due to the limited space in the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. The equivalent diameter D1 and the axial height H1 of the first cavity 110 can have a suitable ratio, which is convenient for the expansion of the high-pressure refrigerant and the vibration and friction under the action of the acoustic impedance, thereby reducing vibration and noise.

[0129] It should be noted that the volume of the muffler structure 10 can be increased by providing the second cavity 120. However, if the height of the second cavity 120 is too large and the equivalent diameter is too small, it is not conducive to the entry and discharge of the high-pressure refrigerant. It is convenient for the high-pressure refrigerant to enter and be discharged from the second cavity 120 .

[0130] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy 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 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 The equivalent diameter of the second cavity 120 can be limited, so that the high-pressure refrigerant entering the first cavity 110 can enter the second cavity 120 with a smaller equivalent diameter again for silencing; The size parameters of the silencer structure 10 can be set in a targeted manner according to the displacement of the scroll compressor to achieve a better silencer effect.

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

[0134] In some embodiments, the at least one exhaust hole 1001 is a plurality of exhaust holes 1001 , and the plurality of exhaust holes 1001 are spaced apart along the circumference of the first cavity 110 .

[0135] It should be noted that if 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 hole 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120, a preset distance may be left between the exhaust hole 1001 and the side wall of the first cavity 110, and a preset distance may be left between the exhaust hole 1001 and the side wall of the second cavity 120, so that the exhaust hole 1001 has enough vibration space (or position).

[0136] It should be noted that if Figure 7 As shown, the exhaust hole 1001 is provided on the end face of the second cavity 120 (i.e., the upper surface of the second cavity 120), and a plurality of exhaust holes 1001 may be arranged at intervals along the circumference of the second cavity 120, such as evenly distributed around the circumference, and the exhaust hole 1001 may have a preset spacing from the side wall of the second cavity 120 so that the exhaust hole 1001 has sufficient vibration space (or position), wherein the shape of the exhaust hole 1001 may be circular, square, diamond, etc., and the embodiment of the present application does not specifically limit the shape of the exhaust hole 1001.

[0137] In some embodiments, the equivalent diameter of the exhaust hole 1001 and the equivalent diameter of the exhaust channel 30 satisfy Wherein, D is the equivalent diameter of the exhaust passage 30, and D3 is the equivalent diameter of the exhaust hole 1001;

[0138] It should be noted that the high-pressure refrigerant entering the silencer structure 10 is eventually discharged from the silencer structure 10 through the exhaust hole 1001. If the equivalent diameter of the exhaust hole 1001 is too large, the high-pressure refrigerant discharged into the silencer structure 10 will be discharged from the silencer structure 10 without sufficient silencer. If the equivalent diameter of the exhaust hole 1001 is too small, the high-pressure refrigerant that has been silenced and damped cannot be discharged from the silencer structure 10 in time. Therefore, setting the equivalent diameter of the exhaust hole 1001 according to the equivalent diameter of the scroll compressor exhaust passage 30 (often representing the displacement) can enable the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 to be discharged from the silencer structure 10 (the first cavity 110, the second cavity 120) in time after sufficient silencer and damping.

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

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

[0141] Table 1

[0142]

[0143] In summary, the advantage of the embodiments of the present application is that, by arranging the first cavity 110 on the static scroll 20 of the scroll compressor and connecting the first cavity 110 with the exhaust passage 30 of the static scroll 20; arranging the second cavity 120 above the first cavity 110 and connecting the second cavity 120 with 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 suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, part of the sound energy can be offset and the exhaust noise and vibration can be reduced under the reflection effect of the first cavity 110 and the second cavity 120.

[0144] Embodiment 4:

[0145] The present application embodiment provides a scroll compressor, including the muffler structure 10 as described in the third embodiment. Figure 1 , Figure 2 , Figure 3 , Figure 4 As shown, the sound absorbing structure 10 includes:

[0146] The first cavity 110 is disposed on the fixed scroll 20 of the scroll compressor and is connected to the exhaust passage 30 of the fixed scroll 20;

[0147] The second cavity 120 is disposed above the first cavity 110 and communicates with the first cavity 110;

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

[0149] The equivalent diameter of the first cavity 110 is greater 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 greater than the volume of the second cavity 120 .

[0153] It should be noted that the above-mentioned 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 disposed above the fixed scroll 20. By making the diameter of the first cavity 110 larger than the diameter of the second cavity 120, the portion of the muffler structure 10 close to the upper cover of the scroll compressor can be made smaller, thereby avoiding contact with the upper cover. The shape of the second cavity 120 can be adjusted according to the shape of the upper cover or the shapes of other parts in the scroll compressor, such as a circle (such as Figure 2 As shown), such as nearly semicircular (such as Figure 5 , Figure 6 Similarly, the shape of the first cavity 110 can also be adjusted according to the shapes of the parts in the scroll compressor, such as Figure 3 , Figure 7 As shown, a circular groove is provided on the first cavity 110 .

[0155] It should be noted that, by arranging the first cavity 110 on the fixed scroll disk 20 of the scroll compressor, and connecting the first cavity 110 with the exhaust passage 30 of the fixed scroll disk 20; arranging the second cavity 120 above the first cavity 110, and connecting the second cavity 120 with the first cavity 110, wherein the equivalent diameter of the first cavity 110 is greater than the equivalent diameter of the second cavity 120, on the one hand, the high-pressure refrigerant enters the lower layer of the muffler structure 10 with a larger equivalent diameter from the exhaust passage 30 of the fixed scroll disk 20 with a smaller equivalent diameter. When the high-pressure refrigerant passes through the first cavity 110 and then enters the second cavity 120 on the upper layer of the silencer structure 10, the flow area of ​​the high-pressure refrigerant discharged from the pump body can be suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, due to the sudden increase in the flow area of ​​the high-pressure refrigerant (that is, 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. In this process, the high-pressure refrigerant undergoes intense vibration and friction, which converts sound energy into heat energy, reduces the pressure pulsation energy, thereby reducing the exhaust pulsation and improving the exhaust noise.

[0156] In some embodiments, the muffler structure 10 further includes a connecting pressure edge 130 , which is connected to the bottom end of the first cavity 110 and is connected to the fixed scroll 20 via a connecting member.

[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 be connected to the bottom end (i.e., the lower surface) of the first cavity 110 and to the static scroll plate 20, wherein the connecting pressure edge 130 and the first cavity 110 can be formed as one piece, and the connecting pressure edge 130 and the static scroll plate 20 can be connected by a connecting piece, which can be a screw or a bolt. The embodiment of the present application does not specifically limit the type of the connecting piece.

[0158] It should be noted that, in combination with the sound-absorbing structure 10 provided in the embodiment of the present application, a sound-absorbing amount formula of the sound-absorbing structure 10 of the present application can be constructed, namely: Construct the expansion ratio formula, that is, Construct the shrinkage ratio formula, that is, Construct the wave number formula, that is, Among them, m is the expansion ratio, m1 is the contraction ratio, k is the wave number, C is the exhaust sound speed, 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 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 (Right now ), on the one hand, it can ensure that there is enough space on the end face of the first cavity 110 to open the exhaust hole 1001, and on the other hand, it can ensure that the first cavity 110 and the second cavity 120 can have enough vibration space under the impact of the 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 passage 30 satisfy 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 is difficult to obtain a good muffler effect, and the space in the scroll compressor is limited and cannot support the setting of a larger first cavity 110 and a second cavity 120. (Right now ), that is, it is possible to limit the expansion ratio m of the silencer structure 10, so that the high-pressure refrigerant discharged from the pump body has sufficient expansion space, so that the high-pressure refrigerant can be sufficiently reduced in speed when discharged into the silencer structure 10 and has a larger acoustic impedance.

[0163] In some embodiments, the equivalent diameter of the first cavity 110 and the axial height of the first cavity 110 satisfy 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 of the second cavity 120 and the axial height of the second cavity 120 satisfy 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 be disadvantageous for the expansion of the high-pressure refrigerant. However, due to the limited space in the scroll compressor, the axial height H1 of the first cavity 110 cannot be set too large. The equivalent diameter D1 and the axial height H1 of the first cavity 110 can have a suitable ratio, which is convenient for the expansion of the high-pressure refrigerant and the vibration and friction under the action of the acoustic impedance, thereby reducing vibration and noise.

[0166] It should be noted that the volume of the muffler structure 10 can be increased by providing the second cavity 120. However, if the height of the second cavity 120 is too large and the equivalent diameter is too small, it is not conducive to the entry and discharge of the high-pressure refrigerant. It is convenient for the high-pressure refrigerant to enter and be discharged from the second cavity 120 .

[0167] In some embodiments, the volume of the first cavity 110 and the volume of the second cavity 120 satisfy 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 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 The equivalent diameter of the second cavity 120 can be limited, so that the high-pressure refrigerant entering the first cavity 110 can enter the second cavity 120 with a smaller equivalent diameter again for silencing; The size parameters of the silencer structure 10 can be set in a targeted manner according to the displacement of the scroll compressor to achieve a better silencer effect.

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

[0171] In some embodiments, the at least one exhaust hole 1001 is a plurality of exhaust holes 1001 , and the plurality of exhaust holes 1001 are spaced apart along the circumference of the first cavity 110 .

[0172] It should be noted that if 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 hole 1001 is located on the upper surface of the first cavity 110 and is not covered by the second cavity 120, a preset distance may be left between the exhaust hole 1001 and the side wall of the first cavity 110, and a preset distance may be left between the exhaust hole 1001 and the side wall of the second cavity 120, so that the exhaust hole 1001 has enough vibration space (or position).

[0173] It should be noted that if Figure 7 As shown, the exhaust hole 1001 is provided on the end face of the second cavity 120 (i.e., the upper surface of the second cavity 120), and a plurality of exhaust holes 1001 may be arranged at intervals along the circumference of the second cavity 120, such as evenly distributed around the circumference, and the exhaust hole 1001 may have a preset spacing from the side wall of the second cavity 120 so that the exhaust hole 1001 has sufficient vibration space (or position), wherein the shape of the exhaust hole 1001 may be circular, square, diamond, etc., and the embodiment of the present application does not specifically limit the shape of the exhaust hole 1001.

[0174] In some embodiments, the equivalent diameter of the exhaust hole 1001 and the equivalent diameter of the exhaust channel 30 satisfy Wherein, D is the equivalent diameter of the exhaust passage 30, and D3 is the equivalent diameter of the exhaust hole 1001;

[0175] It should be noted that the high-pressure refrigerant entering the silencer structure 10 is eventually discharged from the silencer structure 10 through the exhaust hole 1001. If the equivalent diameter of the exhaust hole 1001 is too large, the high-pressure refrigerant discharged into the silencer structure 10 will be discharged from the silencer structure 10 without sufficient silencer. If the equivalent diameter of the exhaust hole 1001 is too small, the high-pressure refrigerant that has been silenced and damped cannot be discharged from the silencer structure 10 in time. Therefore, setting the equivalent diameter of the exhaust hole 1001 according to the equivalent diameter of the scroll compressor exhaust passage 30 (often representing the displacement) can enable the high-pressure refrigerant entering the first cavity 110 and the second cavity 120 to be discharged from the silencer structure 10 (the first cavity 110, the second cavity 120) in time after sufficient silencer and damping.

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

[0177] Table 1

[0178]

[0179] In summary, the advantage of the embodiments of the present application is that, by arranging the first cavity 110 on the static scroll 20 of the scroll compressor and connecting the first cavity 110 with the exhaust passage 30 of the static scroll 20; arranging the second cavity 120 above the first cavity 110 and connecting the second cavity 120 with 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 suddenly increased and the speed can be reduced, thereby reducing the exhaust noise and vibration; on the other hand, part of the sound energy can be offset and the exhaust noise and vibration can be reduced under the reflection effect of the first cavity 110 and the second cavity 120.

[0180] Although the present invention has been described with reference to preferred embodiments, various modifications may be made thereto and parts thereof may be replaced by equivalents without departing from the scope of the present invention. In particular, the various technical features mentioned in the various embodiments may be combined in any manner as long as there are no structural conflicts. The present 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 sound-absorbing structure, characterized in that: include: A first cavity is provided on the fixed scroll of the scroll compressor and is connected to the exhaust passage of the fixed scroll; A second cavity is disposed above the first cavity and communicated with the first cavity; Wherein, the first cavity and the second cavity are configured to satisfy one or more of the following: The equivalent diameter of the first cavity is greater 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 greater than the volume of the second cavity.

2. The sound absorbing structure according to claim 1, characterized in that: The equivalent diameter of the first cavity and the equivalent diameter of the second cavity satisfy Wherein, D1 is the equivalent diameter of the first cavity, and D2 is the equivalent diameter of the second cavity.

3. The sound absorbing structure according to claim 1, characterized in that: The equivalent diameter of the first cavity and the equivalent diameter of the exhaust passage satisfy Wherein, D1 is the equivalent diameter of the first cavity, and D is the equivalent diameter of the exhaust passage.

4. The sound 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 Wherein, H1 is the axial height of the first cavity, and D1 is the equivalent diameter of the first cavity; The equivalent diameter of the second cavity and the axial height of the second cavity satisfy Wherein, H2 is the axial height of the second cavity, and D2 is the equivalent diameter of the second cavity.

5. The sound absorbing structure according to claim 1, characterized in that: The volume of the first cavity and the volume of the second cavity satisfy Wherein, V1 is the equivalent volume of the first cavity, and V2 is the equivalent volume of the second cavity.

6. The sound 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 Among them, 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.

7. The sound absorbing structure according to claim 1, characterized in that: At least one exhaust hole is disposed on the end surface of the first cavity and / or the second cavity.

8. The sound absorbing structure according to claim 7, characterized in that: The at least one exhaust hole is a plurality of exhaust holes, and the plurality of exhaust holes are arranged at intervals along the circumference of the first cavity.

9. The sound absorbing structure according to claim 7 or 8, characterized in that: The equivalent diameter of the exhaust hole and the equivalent diameter of the exhaust channel satisfy Wherein, D is the equivalent diameter of the exhaust channel, and D3 is the equivalent diameter of the exhaust hole.

10. The sound absorbing structure according to any one of claims 1 to 7, characterized in that: The muffler structure further includes a connecting pressure edge, which is connected to the bottom end of the first cavity and is connected to the fixed scroll plate through a connecting piece.

11. A scroll compressor, characterized in that: The method comprises the sound absorbing structure as claimed in any one of claims 1 to 10.

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