Flanges, compressors and air conditioners

Abstract

This invention provides a flange, a compressor, and an air conditioner. The flange includes an exhaust pipe with a silencing hole on its inner wall. The silencing hole is a blind hole structure. When airflow passes through the opening of the silencing hole in the exhaust pipe, the silencing hole reduces airflow noise. By providing a blind hole-shaped silencing hole on the wall of the flange exhaust pipe, the air column inside the blind hole vibrates under the action of sound pressure, consuming energy to reduce exhaust noise.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, specifically relating to a flange, a compressor, and an air conditioner. Background Technology

[0002] Noise from household air conditioners is a significant factor affecting residents' comfort levels, and the noise generated by the compressor is the main source of noise in air conditioning systems. The noise composition of the compressor is complex, mainly including aerodynamic noise, mechanical noise, and electromagnetic noise. Aerodynamic noise primarily occurs in the exhaust area, where the airflow velocity is high, the flow channel structure is complex, and the interaction between the airflow and the solid wall is intense, resulting in significant airflow noise.

[0003] The prior art discloses that multiple square holes are arranged in the inner shaft groove of the upper flange exhaust port of the compressor and on the upper end face of the exhaust port. Turbulence is generated in the square holes to move the boundary layer structure to the outside of the exhaust port, increase the effective flow area of ​​the refrigerant gas, and allow the refrigerant gas to be smoothly discharged from the cylinder through the exhaust port.

[0004] However, the above solution has the following problems: the square hole structure itself is prone to causing secondary vortices and generating noise; the solution does not take into account the influence of the actual flow direction in the hole arrangement, which will further generate additional noise; the solution does not reasonably design the size of the square hole, and the design of the groove at the exhaust port will increase the clearance volume and reduce the performance of the compressor. Summary of the Invention

[0005] Therefore, the technical problem to be solved by the present invention is to provide a flange, compressor and air conditioner that can reduce the aerodynamic noise of exhaust.

[0006] To address the aforementioned problems, the present invention provides a flange comprising an exhaust pipe, wherein the inner wall of the exhaust pipe is provided with a silencing hole, the silencing hole being configured as a blind hole structure; when airflow passes through the opening of the silencing hole in the exhaust pipe, the silencing hole reduces airflow noise.

[0007] Preferably, multiple silencer holes are provided and arranged circumferentially along the exhaust pipe.

[0008] Preferably, the plurality of silencers are divided into at least two groups, each group of silencers is arranged circumferentially, and the plurality of groups of silencers are arranged axially along the exhaust pipe.

[0009] Preferably, the adjacent sets of sound-absorbing holes are staggered along the circumferential direction.

[0010] Preferably, the cross-sectional shape of the silencing hole is one or a combination of a circle, a triangle, and an ellipse.

[0011] Preferably, when the silencer hole is a circular hole, the number n, diameter D1, and hole depth h1 of the silencer holes are related to the discharge volume v of the exhaust pipe as follows: .

[0012] Preferably, the distance between the group of mufflers closest to the first end face of the exhaust pipe and the first end face is L1, and the distance between the group of mufflers closest to the second end face of the exhaust pipe and the second end face is L2. On the unfolded inner circumferential surface of the exhaust pipe, the axial distance between two adjacent groups of mufflers is L3, the minimum circumferential distance between two adjacent groups of mufflers is L4, the angle between the line connecting the centers of the staggered mufflers and the vertical axis passing through the center of one of the mufflers is α, the distance between adjacent mufflers in the same group is L5, the diameter of the exhaust pipe is D, and the axial height is H; wherein, 0.2mm≤L1=L2≤H / 2; H / D≤L3≤3H / 4; 0.30mm≤L4≤D / H; 0.25mm≤L5≤D / 2; H / D≤D1≤D / 2H; 0°≤α≤90°; 0.2mm≤h1≤2mm.

[0013] Preferably, 30°≤α≤60°.

[0014] Preferably, the relationship between displacement v and diameter D is as follows: .

[0015] According to another aspect of the invention, a compressor is provided, comprising the flange as described above.

[0016] Preferably, the compressor includes an upper flange, and the inner wall of the exhaust port of the upper flange is provided with a blind hole.

[0017] According to another aspect of the invention, an air conditioner is provided, comprising the flange as described above or the compressor as described above.

[0018] This invention provides a flange including an exhaust pipe with a silencing hole on its inner wall. The silencing hole is a blind hole structure. When airflow passes through the opening of the silencing hole in the exhaust pipe, the silencing hole reduces airflow noise. By providing a blind hole-shaped silencing hole on the exhaust pipe wall of the flange, the air column inside the blind hole vibrates under sound pressure, consuming energy to reduce exhaust noise. Attached Figure Description

[0019] Figure 1 This is an exploded view of the pump body component according to an embodiment of the present invention;

[0020] Figure 2 This is a structural diagram of the upper flange according to an embodiment of the present invention;

[0021] Figure 3This is a partial sectional view of the upper flange according to an embodiment of the present invention;

[0022] Figure 4 This is a cross-sectional view of the vent port of the upper flange in an embodiment of the present invention.

[0023] Figure 5 This is another structural schematic diagram of the silencer hole in the upper flange exhaust port according to an embodiment of the present invention;

[0024] Figure 6 This is a schematic diagram showing the depth of the sound-absorbing hole in an embodiment of the present invention;

[0025] Figure 7 This is a schematic diagram of the unfolded structure of the exhaust port according to an embodiment of the present invention;

[0026] Figure 8 Noise data diagram for an embodiment of the present invention where the upper flange exhaust port does not have a silencer hole;

[0027] Figure 9 Noise data diagram for a silencer hole provided inside the upper flange exhaust port according to an embodiment of the present invention;

[0028] Figure 10 This is a graph showing the variation of the performance parameters (COP) and noise reduction (△dB) of a single-cylinder compressor in an embodiment of the present invention with the number of silencer holes.

[0029] The reference numerals in the attached figures are as follows:

[0030] 1. Pump body screws; 2. Silencer; 3. Upper flange; 31. Exhaust port; 311. Silencer hole; 4. Spring; 5. Sliding vane; 6. Roller; 7. Cylinder; 8. Crankshaft; 9. Lower flange. Detailed Implementation

[0031] See also Figures 1 to 10 As shown, according to an embodiment of the present invention, a flange includes an exhaust pipe, and a silencing hole 311 is provided on the inner wall of the exhaust pipe. The silencing hole 311 is configured as a blind hole structure. When the airflow passes through the opening of the silencing hole 311 in the exhaust pipe, the silencing hole 311 reduces the airflow noise.

[0032] When the exhaust pipe can generate aerodynamic noise, a silencing hole 311 with a blind hole structure is set on the inner wall of the exhaust pipe. Utilizing the silencing principle of the blind hole, when the exhaust passes through the hole, the air column in the blind hole vibrates under the action of sound pressure. The frictional damping of the vibration causes some of the sound energy to be converted into heat energy and dissipated, thereby reducing the noise generated by the exhaust.

[0033] In addition, the sudden change in acoustic impedance between the muffler hole 311 and the exhaust pipe causes some of the sound energy to be reflected back, resulting in a phase difference between the propagating sound wave and the reflected wave, which interfere with each other and achieve the purpose of noise reduction.

[0034] To achieve better and faster elimination of aerodynamic noise, multiple silencer holes 311 are provided, evenly distributed along the circumference of the exhaust pipe. In particular, the multiple silencer holes 311 are divided into at least two groups, with each group of silencer holes 311 arranged circumferentially, and the multiple groups of silencer holes 311 arranged axially. Preferably, adjacent groups of silencer holes 311 are staggered along the circumferential direction.

[0035] The cross-sectional shape of the silencing hole 311 can be one or more combinations of circles, triangles, and ellipses, all of which can achieve a good silencing effect. Especially when the sound wave frequency is the same as the natural frequency of the silencing hole, the vibration speed reaches the maximum, the sound energy is consumed the most, and the silencing effect is the best.

[0036] The following analysis will focus on the silencing hole 311 as a circular hole:

[0037] While installing silencer holes on the wall of the exhaust pipe reduces noise, it also increases the clearance volume, leading to a performance decrease. The number n, diameter D1, and depth h1 of the silencer holes 311 are related to the exhaust pipe's displacement v as follows: At this time, the best noise reduction performance is achieved.

[0038] Furthermore, the distance between the set of mufflers closest to the first end face of the exhaust pipe and the first end face is L1, the distance between the set of mufflers closest to the second end face of the exhaust pipe and the second end face is L2, the axial distance between two adjacent sets of mufflers on the inner circumferential surface of the exhaust pipe is L3, the minimum circumferential distance between two adjacent sets of mufflers is L4, the angle between the line connecting the centers of the staggered mufflers and the vertical axis passing through the center of one of the mufflers is α, the distance between adjacent mufflers in the same set is L5, the diameter of the exhaust pipe is D, and the axial height is H; wherein, 0.2mm≤L1=L2≤H / 2; H / D≤L3≤3H / 4; 0.30mm≤L4≤D / H; 0.25mm≤L5≤D / 2; H / D≤D1≤D / 2H; 0°≤α≤90°; 0.2mm≤h1≤2mm.

[0039] For two circumferential arrangements with misalignment, the included angle α has a relatively optimal range of values: 30°≤α≤60°.

[0040] This invention addresses the issue of excessive noise from aerodynamic sources by designing blind-hole-shaped silencing holes 311 on the inner wall of the exhaust pipe. By rationally designing the parameters of the silencing holes, the problem of excessive noise from compressors, especially variable frequency compressors, under high-frequency conditions is solved while ensuring compressor performance.

[0041] According to an embodiment of the present invention, a compressor includes a flange as described above.

[0042] Exploded view of the compressor pump body, as shown Figure 1 As shown, the system includes a muffler 2, an upper flange 3, a cylinder 7, a roller 6, a spring 4, a sliding vane 5, a lower flange 9, a crankshaft 8, and a pump body screw 1. The pump body screw 1 fixes the muffler 2, the upper flange 3, the cylinder 7, and the lower flange 9 together through a pre-set screw hole. The cylinder 7, the roller 6, and the sliding vane 5 together form a crescent-shaped compression chamber. The rotational motion of the crankshaft 8 drives the roller 6 to rotate along the wall of the cylinder 7 and causes the sliding vane 5 to reciprocate, thereby causing a change in volume and enabling the refrigerant to undergo the intake, compression, and exhaust processes.

[0043] After the refrigerant is compressed, the exhaust gas is discharged into the compressor housing through the upper flange 3 exhaust port 31. Due to the high exhaust pressure, high airflow velocity near the exhaust valve seat, complex flow channel structure, and intense interaction between the airflow and the solid wall, there is obvious airflow noise at the compressor exhaust port 31.

[0044] A blind hole is provided on the inner wall of the vent 31 of the upper flange 3. Noise data before and after the opening of the hole in the upper flange 3 is compared. Four small holes with a diameter of φ1mm and a depth of 0.8mm are evenly distributed on the middle plane of the side wall of the upper flange 3. Figure 8 and 9 The comparison before and after the hole is opened shows that the noise level after the hole is opened is lower than the level before the hole is opened, especially in the 800-2500Hz range, the noise improvement is even better.

[0045] A graph showing the variation of the performance parameters (COP) and noise reduction (ΔdB) of a single-cylinder compressor with the number of orifices, from... Figure 10 It can be seen that COP decreases with the increase of the number of pinholes, while ΔdB is the opposite. When the number of pinholes is 10-17, it achieves the effect of noise reduction without significantly affecting performance.

[0046] Table 1 shows the sound power ratio of the upper flange 3 exhaust port 31 for different cross-sectional shapes of the silencer hole 311; sound power L P As an indicator of compressor noise levels, a lower sound power value indicates lower compressor noise. O Using the reference sound power value, all of these schemes have four small holes evenly distributed on the three side walls of the upper flange, with a hole depth of 1mm. The results show that the circular small holes are the best at reducing the noise value.

[0047] Table 1 Noise values ​​for different schemes

[0048] plan <![CDATA[Sound power ratio L P / L O > Original design (no holes drilled) 10 Circular opening (φ1mm, hole depth 1mm) 9.4 Triangle (equilateral triangle, side length and hole depth 1mm) 9.75

[0049] According to an embodiment of the present invention, an air conditioner includes a flange as described above or a compressor as described above.

[0050] It will be readily understood by those skilled in the art that the above embodiments can be freely combined and superimposed without conflict.

[0051] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A flange, characterized in that, The system includes an exhaust pipe, the inner wall of which is provided with a silencing hole (311), which is a blind hole structure; when the airflow passes through the opening of the silencing hole (311) in the exhaust pipe, the silencing hole (311) reduces the airflow noise; The cross-sectional shape of the silencing hole (311) is circular; The number n, diameter D1, and depth h1 of the silencer holes (311) are related to the discharge volume v of the exhaust pipe as follows: ; The open end of the blind hole structure is located on the inner wall surface of the exhaust pipe; The plurality of silencers (311) are divided into at least two groups, each group of silencers (311) is arranged circumferentially, and the plurality of groups of silencers (311) are arranged axially along the exhaust pipe; adjacent groups of silencers (311) are staggered in the circumferential direction. The distance between the set of mufflers closest to the first end face of the exhaust pipe and the first end face is L1, and the distance between the set of mufflers closest to the second end face of the exhaust pipe and the second end face is L2. On the inner circumferential surface development view of the exhaust pipe, the axial distance between two adjacent sets of mufflers is L3, the minimum circumferential distance between two adjacent sets of mufflers (311) is L4, the angle between the center line connecting the staggered mufflers (311) and the vertical axis passing through the center of one of the mufflers is α, the distance between adjacent mufflers (311) in the same set is L5, the diameter of the exhaust pipe is D, and the axial height is H; wherein, 0.2mm≤L1=L2≤H / 2; H / D≤L3≤3H / 4; 0.30mm≤L4≤D / H; 0.25mm≤L5≤D / 2; H / D≤D1≤D / 2H; 0°<α<90°; 0.2mm≤h1≤2mm; The silencing hole (311) has a diameter of 1 mm and a depth of 1 mm.

2. The flange according to claim 1, characterized in that, 30°≤α≤60°。 3. A compressor, characterized in that, Includes the flange as described in any one of claims 1-2.

4. The compressor according to claim 3, characterized in that, The compressor includes an upper flange (3), and the inner wall of the exhaust port (31) of the upper flange (3) is provided with a blind hole.

5. An air conditioner, characterized in that, Includes the flange as described in any one of claims 1-2 or the compressor as described in any one of claims 3-4.

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